JPH01238713A - Method and device for guiding linear rolling - Google Patents
Method and device for guiding linear rollingInfo
- Publication number
- JPH01238713A JPH01238713A JP6038988A JP6038988A JPH01238713A JP H01238713 A JPH01238713 A JP H01238713A JP 6038988 A JP6038988 A JP 6038988A JP 6038988 A JP6038988 A JP 6038988A JP H01238713 A JPH01238713 A JP H01238713A
- Authority
- JP
- Japan
- Prior art keywords
- slider
- track
- guide device
- holder
- linear rolling
- 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
- 238000005096 rolling process Methods 0.000 title claims abstract description 49
- 238000000034 method Methods 0.000 title claims description 6
- 239000012530 fluid Substances 0.000 claims description 18
- 238000013016 damping Methods 0.000 abstract description 11
- 238000006073 displacement reaction Methods 0.000 abstract description 7
- 238000003754 machining Methods 0.000 abstract description 5
- 230000005284 excitation Effects 0.000 description 12
- 230000000694 effects Effects 0.000 description 11
- 230000008901 benefit Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 235000013399 edible fruits Nutrition 0.000 description 1
- 238000007730 finishing process Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
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
- F16C29/008—Systems with a plurality of bearings, e.g. four carriages supporting a slide on two parallel rails
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Machine Tool Units (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
- Bearings For Parts Moving Linearly (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、転動体と転動体の保持体（以下、両−者をま
とめてベアリングと呼ぶ。）と、転動体を。DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention relates to a rolling element, a holder for the rolling element (hereinafter referred to collectively as a bearing), and a rolling element.
介して保持体に係合する軌道とからなる直線ころがり案
内を用いる装置、たとえば工作機械、の直゛線ころがり
案内方法および装置に関する。 。The present invention relates to a linear rolling guide method and apparatus for a machine tool, for example, a machine tool, which uses a linear rolling guide consisting of a track that engages a holding body through a track. .
たとえば工作機械において、直線方向の案内を゛する装
置としてすべり案内の代りに軌道とベアリ・ングとから
なる直線ころがり案内装置を用いると次のような利点が
ある。すなわち、摩擦が小さいため駆動モータの容量を
小さくすることができ、１また、スティックスリップ現
象が発生しないため、精度の良い位置決めを容易に行な
うことができ、しかしながら、たとえば工作機械の１つ
である研削盤に直線ころがり案内装置を採用すると次の
ような問題がある。以下、図面により説明する。。For example, in machine tools, when a linear rolling guide device consisting of a track and a bearing is used instead of a sliding guide as a device for guiding in a linear direction, there are the following advantages. In other words, since the friction is small, the capacity of the drive motor can be made small.1 Also, since the stick-slip phenomenon does not occur, it is possible to easily perform highly accurate positioning. When a linear rolling guide device is used in a grinding machine, the following problems arise. This will be explained below with reference to the drawings. .
第１４図は研削盤の側面図を示すもので、１は。Figure 14 shows a side view of the grinding machine;
砥石。２は砥石１を回転自在に支持する主軸で、コラム
３に対しＹ軸方向に摺動自在である。４ａは直線ころが
り案内装置４を構成するベアリング・で、コラム３の下
部に固定されている。４ｂは直゛線ころがり案内装置４
を構成する軌道で、ベツド５に固定されている。Whetstone. Reference numeral 2 denotes a main shaft that rotatably supports the grindstone 1, and is slidable relative to the column 3 in the Y-axis direction. 4a is a bearing that constitutes the linear rolling guide device 4, and is fixed to the lower part of the column 3. 4b is a linear rolling guide device 4
It is fixed to the bed 5.
すなわち、コラム３けベツド５に対しＺ方向に摺動自在
である。６はワーク７を載置するテーブル。That is, it is slidable in the Z direction with respect to the three-column bed 5. 6 is a table on which the work 7 is placed.
で、Ｘ方向に摺動自在である。It is slidable in the X direction.
上記直線ころがり案内装置４を採用した研削盤の主軸２
とテーブル７との間に加振器を設置して゛加振力を加え
ると、研削盤の各部は第１４図にお（・いて２点鎖線で
示すように変位する。すなわち、・主軸２とコラム３（
以下、まとめて支持部８と呼る。さらに、前記加振器の
加振周波数を変化させるとき、横軸に加振周波数、縦軸
にコンプライア。Main shaft 2 of a grinding machine that employs the above-mentioned linear rolling guide device 4
When a vibrator is installed between the table 7 and the table 7 and an excitation force is applied, each part of the grinding machine is displaced as shown by the two-dot chain line in FIG. Column 3 (
Hereinafter, they will be collectively referred to as the support section 8. Furthermore, when changing the excitation frequency of the vibrator, the horizontal axis represents the excitation frequency and the vertical axis represents the compliance.
ンス（ただし、縦軸は対数表示である。）をとる。(However, the vertical axis is expressed in logarithm.)
と、支持部８の応答曲線は第３図に２点鎖線で示。The response curve of the support portion 8 is shown in FIG. 3 by a two-dot chain line.
す応答曲線（ａ）のようになる。すなわち、−様な曲線
ではなく、傾斜の急な山と谷を持ち、しか。The response curve is as shown in (a). In other words, it does not have a --like curve, but rather has steep peaks and valleys.
・ ４ ・
も山と谷の差が大きく、支持部８は加振力により゛大き
く変位することがわかる。・ 4 ・ The difference between the peak and the trough is also large, and it can be seen that the support part 8 is largely displaced by the excitation force.
上記研削盤でワーク７を加工すると、研削抵抗の変動に
より、ワーク７の表面９には第３図の応゛答曲線（ａ）
に対応した凹凸が発生する。そして、仕上加工により平
面度を向上させようとすると、こんどはすでに発生して
いる表面９の凹凸により゛研削抵抗が変動し、この結果
砥石１す彦わち支持部８が加振力を受けることになり、
≠４４巳仕上加工を〈シ返しても、表面９には数μｍの
凹凸が残り、平面度を向上させることができないという
・問題点があった。When the workpiece 7 is machined with the above-mentioned grinding machine, due to the fluctuation of the grinding resistance, the surface 9 of the workpiece 7 has a response curve (a) shown in Fig. 3.
Irregularities corresponding to this occur. Then, when an attempt is made to improve the flatness through finishing, the grinding resistance fluctuates due to the unevenness of the surface 9 that has already occurred, and as a result, the grinding wheel 1, that is, the support part 8, receives an excitation force. As a result,
≠44mm Even if the finishing process was repeated, unevenness of several micrometers remained on the surface 9, and the flatness could not be improved, which was a problem.
本発明の目的は、上記した問題点を解決し、直線ころが
り案内装置４の長所を損わず、しかも加振力による変位
が少ない直線ころがり案内方法お本発明者は、上記した
加振力による支持部８の変位の原因が、ベアリング４ａ
内の転動体と軌道４ｂとの間にできる油膜の厚さがない
か、あって。An object of the present invention is to solve the above-mentioned problems, to provide a linear rolling guide method that does not impair the advantages of the linear rolling guide device 4, and in which displacement due to the excitation force is small. The cause of the displacement of the support part 8 is the bearing 4a.
Is there a thick oil film formed between the inner rolling elements and the raceway 4b?
も僅かであることによるものであることをつきとめた。It was found that this was due to the fact that the amount of
そこで、上記の目的を達成するため、本発明の第１の実
施例図である第１図に示すように、。Therefore, in order to achieve the above object, as shown in FIG. 1, which is a diagram of a first embodiment of the present invention.
直線ころがり案内装置４と並列に、ベアリング４゜ａ側
に設けるスライダ１０と、軌道４ｂ側に設ける油槽１１
と、油１２からなる撮動減衰装置１３を設けた。なお、
スライダ１０と油［１１とは、糟
スライダ１０の表面１４と油膜１１の底面１５との間に
隙間１６ができるように配置される。 ・また、油１
２は油面１７が表面１４を越える高さりまで油槽１１に
入れる。A slider 10 is provided on the bearing 4°a side in parallel with the linear rolling guide device 4, and an oil tank 11 is provided on the track 4b side.
A photographic damping device 13 made of oil 12 was provided. In addition,
The slider 10 and the oil [11] are arranged so that a gap 16 is formed between the surface 14 of the slider 10 and the bottom surface 15 of the oil film 11.・Also, oil 1
2 is placed in the oil tank 11 until the oil level 17 exceeds the surface 14.
第４図に示すように、たとえば、スライダＩＧに矢印で
示す下向きの力を加えるものとする。隙間１６に何もな
ければ、スライダ１０は直ちに矢印方向に移動する。し
かしながら、隙間１６には油１２が入っているから、ス
ライダ１０は油１２を排除しながら沈むことになる。油
１２には粘性があるから、油１２はすぐには移動せず、
スライ。As shown in FIG. 4, for example, assume that a downward force indicated by an arrow is applied to slider IG. If there is nothing in the gap 16, the slider 10 immediately moves in the direction of the arrow. However, since oil 12 is contained in the gap 16, the slider 10 sinks while removing the oil 12. Since the oil 12 has viscosity, the oil 12 does not move quickly,
Sly.
ダ１０には粘性抵抗が上向きに働く。すなわち、−上記
したスライダ１０、油槽１１および油１２からなる振動
減衰装置１３はいわゆるダッシュボッ・トを構成する。Viscous resistance acts upward on the roller 10. That is, the vibration damping device 13 consisting of the slider 10, oil tank 11 and oil 12 described above constitutes a so-called dashbot.
そこで、第１図に示す直線ころがり案内装債を採用した
第２図に示す研削盤の等価振動系は、変形の少ないベツ
ド５を剛体とみなせるから、第５図のようにモデル化で
きる。同図に・おいて、ＭｓＵＹ軸方向の振動モードに
関する支持部８の等価質量。同様に、ＫＳは支持部８を
ばねと・みなしたときの等側割性。Ｋｂはころがり軸受
４のばね定数。Ｃｄは振動減衰装置１３の粘性抵抗であ
０る。Therefore, the equivalent vibration system of the grinding machine shown in FIG. 2 which employs the linear rolling guide device shown in FIG. 1 can be modeled as shown in FIG. 5, since the bed 5 with little deformation can be regarded as a rigid body. In the figure, the equivalent mass of the support part 8 regarding the vibration mode in the MsUY axis direction. Similarly, KS is equal lateral splitting property when the support part 8 is considered as a spring. Kb is the spring constant of the rolling bearing 4. Cd is the viscous resistance of the vibration damping device 13 and is 0.
砥石ＩＶＣ加わるＹ軸方向の加振力は支持部８に伝わる
。しかしながら、前記加振力に対し、ばねＫｂに作用す
る復元力は振動の変位量に応するもの。The excitation force in the Y-axis direction applied to the grindstone IVC is transmitted to the support portion 8. However, the restoring force acting on the spring Kb with respect to the excitation force corresponds to the amount of displacement of the vibration.
であり、粘性抵抗Ｃｄは振動の変位の速度に応ず石。, and the viscous resistance Cd depends on the speed of vibration displacement.
ものであって、力の位相が９０度ずれるため振動の減衰
効果が得られることになる。すなわち、第。Since the phase of the force is shifted by 90 degrees, a vibration damping effect can be obtained. Namely, No.
１４図に示す研削盤の主軸２とテーブル６の間に。Between the main shaft 2 and table 6 of the grinding machine shown in Fig. 14.
加えた加振力と同一の加振力を第２図に示す研削。Grinding with the same excitation force as shown in Figure 2.
盤の主軸２とテーブル６の間に加えると、支持部、７
。When added between the main shaft 2 of the board and the table 6, the support part 7
.
８の応答曲線は第３図に実線で示す応答曲線（ｂ’）の
ように凹凸の少ない曲線となり、表面９は凹凸の少ない
、平面度のすぐれるものとなる。 。The response curve of No. 8 is a curve with few irregularities like the response curve (b') shown by a solid line in FIG. 3, and the surface 9 has few irregularities and has excellent flatness. .
以下、本発明の直線ころがり案内装置を適用ピた研削盤
を例にとり、図面を用いて説明する。な。DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a description will be given with reference to the drawings, taking as an example a grinding machine to which the linear rolling guide device of the present invention is applied. Na.
お、第１４図と同じものは同一の符号を付してあ。Oh, the same parts as in Fig. 14 are given the same reference numerals.
る。Ru.
第１図は本発明の第１の実施例を示す直線ころ。FIG. 1 shows a straight roller showing a first embodiment of the present invention.
がり案内装置の正面断面図。第２図は第１図に示０す直
線ころがり案内装置を適用した研削盤の側面。FIG. Figure 2 is a side view of a grinding machine to which the linear rolling guide device shown in Figure 1 is applied.
図である。It is a diagram.
１０はコラム３に固定されたスライダ、１１けベツド５
に固定された油槽。１２は油。なお、ス“ライダ１０、
油槽１１および油１２をまとめて、１５振動減衰装置１
３と呼ぶ。また、スライダ１０の。10 is a slider fixed to column 3, 11 is bed 5
Oil tank fixed to. 12 is oil. In addition, slider 10,
The oil tank 11 and oil 12 are combined into 15 vibration damping device 1.
Call it 3. Also, the slider 10.
表面１４と油槽１１の底面１５との隙間１６は５゜〜５
００μｍであり、油面１７は表面１４を越え。The gap 16 between the surface 14 and the bottom 15 of the oil tank 11 is between 5° and 5°.
00 μm, and the oil level 17 exceeds the surface 14.
る高さにしである。また、１８はスライダ１０に。It should be at the same height. Also, 18 is the slider 10.
設けられた複数の細径の穴で、表面１４とスライー・Ｉ
Ｊ、８ 。A plurality of small diameter holes provided in the surface 14 and the slide I
J.8.
ダ１０の側面とを連通させている。なお、主軸２゜とテ
ーブル６との間に加振器を設置して、第１４゛図に示し
たものと同一の加振力を加えると、支持部８の応答曲線
は第３図に示す応答曲線（ｂ）のように、山および谷の
傾斜がゆるやかで、しか本山と谷との差が小さい曲線と
なる。It communicates with the side surface of the holder 10. If a vibrator is installed between the main shaft 2° and the table 6 and the same excitation force as shown in Fig. 14 is applied, the response curve of the support part 8 will be as shown in Fig. 3. As shown in response curve (b), the curve has gentle peaks and valleys, and a small difference between the peak and valley.
以下、動作について説明する。The operation will be explained below.
加工時、砥石１とワーク７との間には砥削抵抗によシ、
主としてＹ軸方向の力が加わる。一般に、砥石１および
ワーク７は完全に均一な幸ものでは＼ないから、前記し
た力の大きさは一様ではなり、゛大きさが変動し、加振
力となる。砥石１に加わる加振力は支持部８に伝わるが
、支持部８には振動減衰装置１３の構成部品でおるスラ
イダ１０が固定されているため、支持部８の変位は小さ
くなる・。During machining, there is a grinding resistance between the grinding wheel 1 and the workpiece 7.
Force is mainly applied in the Y-axis direction. Generally, the grindstone 1 and the workpiece 7 are not completely uniform, so the magnitude of the above-mentioned force is not uniform, but fluctuates and becomes an excitation force. The excitation force applied to the grindstone 1 is transmitted to the support part 8, but since the slider 10, which is a component of the vibration damping device 13, is fixed to the support part 8, the displacement of the support part 8 is reduced.
なお、本実施例においては穴１８Ｖｒ−より支持部８の
Ｚ方向の移動を円滑にすることができる。すなわち、隙
間１６が狭く、表面１４が底面１５ＶＣ。In addition, in this embodiment, the movement of the support part 8 in the Z direction can be made smooth by the hole 18Vr-. That is, the gap 16 is narrow and the surface 14 is the bottom surface 15VC.
対して傾いている状態で支持部８をＺ方向に移動させる
と、いわゆる油膜のくさび作用によって支・持部８に対
し上向きの力が発生し、移動が円滑に行なわれない。し
かしながら、本実施例においでは、穴１８により油１２
に発生する圧力を逃がすことができるから、油膜のくさ
び作用はほとんど発生せず、支持部８を２方向に円滑に
移動させる・ことができる。さらに、表面１４および底
面１５・の機械加工公差および組立精度を粗くすること
力やできるという経済的な効果もある。On the other hand, if the support part 8 is moved in the Z direction while it is tilted, an upward force will be generated on the support/hold part 8 due to the so-called wedge effect of the oil film, and the movement will not be carried out smoothly. However, in this embodiment, the oil 12 is
Since the pressure generated in the oil film can be released, the wedge effect of the oil film hardly occurs, and the support part 8 can be smoothly moved in two directions. Additionally, there is an economical benefit in that the machining tolerances and assembly precision of the top surface 14 and bottom surface 15 can be made coarser.
なお、穴１８は油膜のくさび作用をなくすためのもので
あるから、表面１４側でない側面側の開θ口部は油面１
７よりも下方にあってもよいことは・言うまでもない。Note that the hole 18 is for eliminating the wedge effect of the oil film, so the opening θ on the side surface side other than the surface 14 side is located at the oil level 1.
It goes without saying that it may be lower than 7.
第６図は第２の実施例を示す正面断面図で、第７図は同
図におけるＩ−Ｉ断面図である。FIG. 6 is a front sectional view showing the second embodiment, and FIG. 7 is a sectional view taken along line II in the same figure.
動作は第１の実施例と同一であるため省略する５が、こ
の場合スライダ１０の断面は１字形をして。Since the operation is the same as that of the first embodiment, the explanation of 5 is omitted, but in this case, the cross section of the slider 10 is 1-shaped.
おり、しかも油面１７を１字形部の上側の面２０゜を越
える高さにしであるから、粘性抵抗は表面１゜４だけで
なく面２０に対しても働き、減衰能を犬きくすることが
できるという効果がある。 ２゜以下、さらに第３
ないし第５の実施例について゛図面を用いて説明する。Moreover, since the oil level 17 is set at a height exceeding 20° of the upper surface of the 1-shaped portion, viscous resistance acts not only on the surface 1°4 but also on the surface 20, greatly increasing the damping ability. It has the effect of being able to. 2° or less, and further 3rd
The fifth embodiment will be described with reference to the drawings.
なお、動作については、“前記第１ないし第２の実施例
と同じであるため省略し、特有の効果についてのみ述べ
る。The operation will be omitted because it is the same as in the first and second embodiments, and only the unique effects will be described.
第８図は第３の実施例を示す正面断面図で、第９図は第
８図における■−■断面図である。 ゛この場合、ベ
アリング４ａがスライダの役目を果すように構成されて
いるから、特別にスライダ。FIG. 8 is a front sectional view showing the third embodiment, and FIG. 9 is a sectional view taken along the line -■ in FIG.゛In this case, since the bearing 4a is configured to play the role of a slider, it is specially designed as a slider.
を設けなくても良いという効果がある。This has the effect that it is not necessary to provide
第１０図は第４の実施例を示す正面断面図で、１・・第
１１図は第１０図におけるｍ−■断面図である・。FIG. 10 is a front sectional view showing the fourth embodiment, 1...FIG. 11 is a sectional view taken along the line m--■ in FIG. 10.
この場合、軌道４ｂに直接油１２を保持させるように構
成されているから、特別に油槽を設けなくてもよいとい
う効果がある。In this case, since the structure is such that the oil 12 is held directly in the track 4b, there is an advantage that there is no need to provide a special oil tank.
第１２図は第５の実施例を示す正面断面図で、１第１３
図は第１２図におけるＩＶ−ＩＶ断面図である。FIG. 12 is a front sectional view showing the fifth embodiment.
The figure is a sectional view taken along line IV-IV in FIG. 12.
この場合、ベアリング４ａがスライダの役目を。In this case, the bearing 4a plays the role of a slider.
果し、しかも軌道４ｂに直接油１２を保持させる。Moreover, the oil 12 is held directly in the orbit 4b.
ように構成されているから、スライダおよび油槽を特別
に設ける必要がなく、取扱いが容易である。。With this structure, there is no need to specially provide a slider and an oil tank, and handling is easy. .
・１１・ という効果がある。・１１・ There is an effect.
なお、第３および第５の実施例においてスライ゛ダ１０
を別に設けてもよいことは言うまでもない。Note that in the third and fifth embodiments, the slider 10
Needless to say, it may be provided separately.
さらに、前記した第１ないし第５の実施例においては、
ベアリング４ａ側を上側としてスライダ１５０を設け、
軌道４ｂ側を下側として油槽１１を設。Furthermore, in the first to fifth embodiments described above,
A slider 150 is provided with the bearing 4a side facing upward,
The oil tank 11 is installed with the track 4b side facing downward.
けたが、軌道４ｂ側を上側としてスライダ１０を。The girder is the slider 10 with the track 4b side facing upward.
設け、ベアリング４基側を下側として油槽１１を。Install the oil tank 11 with the bearing 4 side facing downward.
設けてもよいことは言うまでもない。また、流体。Needless to say, it may be provided. Also, fluid.
槽に充填する流体としては油に限らず、他の液体０ある
いはコロイド溶液などを用いてもよいことは゛言うまで
もない。また、隙間１６は５〜５００μ。It goes without saying that the fluid to be filled in the tank is not limited to oil, but other liquids, colloidal solutions, etc. may also be used. Moreover, the gap 16 is 5 to 500μ.
ｍに限らず、さらに広くすることもできる。 ゛〔発
明の効果〕
以上詳述したように、本発明の直線ころがｐ案５内方法
および装置においては、直線ころがり案内装置４と振動
減衰装置とを並列させるから、加振・力に対し変位の少
ない装置とすることができ、加・工精度を向上させるこ
とができる。さらに、表面・１４と底面１５とは接触し
ていないから、摩擦抵（・、１２゜
杭はほとんどなく、ころがり案内の長所を損うことがな
いという効果がある。It is not limited to m, but can be made wider. [Effects of the Invention] As detailed above, in the straight roller p-guide 5 guiding method and device of the present invention, the linear rolling guide device 4 and the vibration damping device are arranged in parallel, so that vibrations and forces are not affected. It is possible to create a device with less displacement, and it is possible to improve machining accuracy. Furthermore, since the surface 14 and the bottom surface 15 are not in contact, there is almost no frictional resistance (12° pile), which has the effect of not detracting from the advantages of rolling guide.
第１図は本発明の第１の実施例を示す直線ころ。
がり案内装置の正面断面図。第２図は第１図に示す直線
ころがり案内装置を適用した研削盤の説萌図。第３図な
いし第５図は本発明の原理および効。
果の説明図。第６図ないし第１３図は本発明の第。
２ないし第５の実施例を示す正面断面図および質面断面
図。第１４図は従来技術の説明図である。１０４・・・
直線ころがり案内装置、 ４ａ・・・ベアリン・グ、
４ｂ・・・軌道、 １０・・・スライダ、１１・
・・・油槽、 １２・・・油、 １３・・・振動減衰
装置、・１４・・・表面、 １５・・・底面、 １
６・・・隙間、 ・１７・・・油面、 １８・・・穴、
２０・・・面、１５代理人弁理士 小 川 勝
男
算５０ ＄４図
＄？０４
／６ １２
＄１０図
寡、７′高
＃４ｂ（ＩＩ）ｌＪ’
第１２図FIG. 1 shows a straight roller showing a first embodiment of the present invention. FIG. FIG. 2 is an illustration of a grinding machine to which the linear rolling guide device shown in FIG. 1 is applied. 3 to 5 illustrate the principle and effects of the present invention. An illustration of the fruit. FIGS. 6 to 13 are diagrams of the present invention. FIG. 3 is a front sectional view and a surface sectional view showing second to fifth embodiments. FIG. 14 is an explanatory diagram of the prior art. 104...
Straight rolling guide device, 4a...bearing,
4b...Trajectory, 10...Slider, 11.
... Oil tank, 12 ... Oil, 13 ... Vibration damping device, 14 ... Surface, 15 ... Bottom surface, 1
6... Gap, ・17... Oil level, 18... Hole,
Masaru Ogawa, Patent Attorney 20…15
Male calculation 50 $4 figure $? 04 /6 12 $10 figure low, 7' high #4b (II) lJ' Fig. 12
Claims (1)
直線方向に相対的に移動させる直線ころがり案内方法に
おいて、流体の粘性抵抗を作用させることを特徴とする
直線ころがり案内方法。 ２、転動体と、転動体を回転自在に保持する転動体の保
持体と、転動体を介して保持体に係合する軌道とからな
る直線ころがり案内装置において、保持体または軌道の
うちの一方と一体にスライダを設けると共に他方と一体
に流体槽を設け、スライダの表面と流体槽の底面とを隙
間を持たせて対向させ、流体を少なくともスライダの表
面を越えるように充填したことを特徴とする直線ころが
り案内装置。 ３、スライダが保持体の一部であり、流体槽が軌道に設
けられていることを特徴とする特許請求の範囲第２項記
載の直線ころがり案内装置。 ４、スライダが保持体の一部であり、流体槽が軌道を載
置するベースに設けられていることを特徴とする特許請
求の範囲第２項記載の直線ころがり案内装置。 ５、スライダが保持体を載置する部材の一部であり、流
体槽が軌道に設けられていることを特徴とする特許請求
の範囲第２項記載の直線ころがり案内装置。 ６、スライダが保持体を載置する部材の一部であり、流
体槽が軌道を載置するベースに設けられていることを特
徴とする特許請求の範囲第２項記載の直線ころがり案内
装置。 ７、スライダが軌道の一部であり、流体槽が保持体に設
けられていることを特徴とする特許請求の範囲第２項記
載の直線ころがり案内装置。 ８、スライダが軌道の一部であり、流体槽が保持体を載
置するベースに設けられていることを特徴とする特許請
求の範囲第２項記載の直線ころがり案内装置。 ９、スライダが軌道を載置する部材の一部であり、流体
槽が保持体に設けられていることを特徴とする特許請求
の範囲第２項記載の直線ころがり案内装置。 １０、スライダが軌道を載置する部材の一部であり、流
体槽が保持体を載置するベースに設けられていることを
特徴とする特許請求の範囲第２項記載の直線ころがり案
内装置。 １１、転動体と転動体を回転自在に保持する転動体の保
持体と、転動体を介して保持体に係合する軌道とからな
る直線ころがり案内装置において、表面に大気あるいは
低圧側の流体と連通する複数の細径穴を持たせたスライ
ダを保持体または軌道のうちの一方と一体に設けると共
に他方と一体に流体槽を設け、スライダの表面と流体槽
の底面とを隙間を持たせて対向させ、流体を少なくとも
スライダの表面を越えるように充填したことを特徴とす
る直線ころがり案内装置。[Claims] 1. A linear rolling guide method in which a rolling element is interposed between two members and the two members are moved relative to each other in a linear direction, characterized by applying viscous resistance of a fluid. Straight rolling guidance method. 2. In a linear rolling guide device consisting of a rolling element, a holder for the rolling element that rotatably holds the rolling element, and a track that engages with the holder via the rolling element, one of the holder and the track. A slider is provided integrally with the other, and a fluid tank is provided integrally with the other, the surface of the slider and the bottom of the fluid tank are opposed to each other with a gap, and the fluid is filled so as to exceed at least the surface of the slider. A linear rolling guide device. 3. The linear rolling guide device according to claim 2, wherein the slider is a part of the holder, and the fluid tank is provided on the track. 4. The linear rolling guide device according to claim 2, wherein the slider is a part of the holding body, and the fluid tank is provided on the base on which the track is placed. 5. The linear rolling guide device according to claim 2, wherein the slider is a part of the member on which the holding body is placed, and the fluid tank is provided on the track. 6. The linear rolling guide device according to claim 2, wherein the slider is a part of the member on which the holder is placed, and the fluid tank is provided on the base on which the track is placed. 7. The linear rolling guide device according to claim 2, wherein the slider is a part of the track, and the fluid tank is provided in the holder. 8. The linear rolling guide device according to claim 2, wherein the slider is a part of the track, and the fluid tank is provided on a base on which the holder is placed. 9. The linear rolling guide device according to claim 2, wherein the slider is a part of the member on which the track is placed, and the fluid tank is provided in the holder. 10. The linear rolling guide device according to claim 2, wherein the slider is a part of the member on which the track is placed, and the fluid tank is provided on the base on which the holder is placed. 11. In a linear rolling guide device consisting of a rolling element, a holder for the rolling element that rotatably holds the rolling element, and a track that engages the holder via the rolling element, the surface is exposed to air or low pressure fluid. A slider having a plurality of communicating small diameter holes is provided integrally with one of the holder or the track, and a fluid tank is provided integrally with the other, and a gap is provided between the surface of the slider and the bottom of the fluid tank. A linear rolling guide device characterized in that the sliders are opposed to each other and filled with fluid so as to extend at least beyond the surface of the slider.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63060389A JP2633610B2 (en) | 1988-03-16 | 1988-03-16 | Linear rolling guide device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63060389A JP2633610B2 (en) | 1988-03-16 | 1988-03-16 | Linear rolling guide device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH01238713A true JPH01238713A (en) | 1989-09-22 |
| JP2633610B2 JP2633610B2 (en) | 1997-07-23 |
Family
ID=13140743
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP63060389A Expired - Lifetime JP2633610B2 (en) | 1988-03-16 | 1988-03-16 | Linear rolling guide device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2633610B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2006051707A1 (en) * | 2004-11-15 | 2006-05-18 | Thk Co., Ltd. | Movement guiding device, table device, and damping method for movement guiding device |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5917320U (en) * | 1982-07-24 | 1984-02-02 | 日本精工株式会社 | track guide bearing |
-
1988
- 1988-03-16 JP JP63060389A patent/JP2633610B2/en not_active Expired - Lifetime
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5917320U (en) * | 1982-07-24 | 1984-02-02 | 日本精工株式会社 | track guide bearing |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2006051707A1 (en) * | 2004-11-15 | 2006-05-18 | Thk Co., Ltd. | Movement guiding device, table device, and damping method for movement guiding device |
| JP4864722B2 (en) * | 2004-11-15 | 2012-02-01 | Ｔｈｋ株式会社 | Motion guide device, table device, and damping method of motion guide device |
| US8231274B2 (en) | 2004-11-15 | 2012-07-31 | Thk Co., Ltd. | Motion guide device, table apparatus, and damping method for motion guide device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2633610B2 (en) | 1997-07-23 |
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