JPH08261257A - Brake device for linear motion - Google Patents
Brake device for linear motionInfo
- Publication number
- JPH08261257A JPH08261257A JP10452495A JP10452495A JPH08261257A JP H08261257 A JPH08261257 A JP H08261257A JP 10452495 A JP10452495 A JP 10452495A JP 10452495 A JP10452495 A JP 10452495A JP H08261257 A JPH08261257 A JP H08261257A
- Authority
- JP
- Japan
- Prior art keywords
- brake
- guide rod
- rotation moment
- reaction force
- brake member
- 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.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/26—Locking mechanisms
- F15B15/262—Locking mechanisms using friction, e.g. brake pads
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Braking Arrangements (AREA)
Abstract
Description
【０００１】［産業上の利用分野］従来、ロッドレスエ
ァーシリンダあるいは電動シリンダを使用している極め
て広範囲な分野で特に落下防止、非常停止、及び中間停
止を目的とする場合に利用する。[Industrial field of application] Conventionally, the present invention is used in a very wide range of fields where rodless air cylinders or electric cylinders have been used, particularly for the purpose of fall prevention, emergency stop, and intermediate stop.
【０００２】［従来の技術］ （１）ロッドレスシリンダのチューブ側面のレールへ上
下よりブレーキ力を作用させるツインロック機構。（ブ
レーキ付スーパーロッドレスシリンダ） （２）スプリング力により傾いたリングがシリンダ推力
でさらにその傾度を増加させてピストンロッドを確実に
ロックするエァーシリンダ（ロックアップシリンダ）。[Prior Art] (1) A twin lock mechanism that applies a braking force from above and below to the rail on the tube side surface of a rodless cylinder. (Super rodless cylinder with brake) (2) An air cylinder (lock-up cylinder) that locks the piston rod securely by the ring tilted by spring force further increasing its tilt by cylinder thrust.
【０００３】［発明が解決しようとする課題］従来技術
に於いては、ブレーキ部材を回転モーメントに平行にガ
イドロッドに押し付けているために、可動体の推力の反
力に対してだけ摩擦力となっており、回転モーメントの
反力が摩擦力として生じる構造となっていない。故に、
安定性、耐久性、小型化、低価格化等の面で難点があ
る。本願発明はこれらの難点を解決することを課題とし
ている。[Problems to be Solved by the Invention] In the prior art, since the brake member is pressed against the guide rod parallel to the rotational moment, frictional force is generated only against the reaction force of the thrust of the movable body. The reaction force of the rotation moment is not generated as a frictional force. Therefore,
There are difficulties in terms of stability, durability, downsizing, and cost reduction. An object of the present invention is to solve these problems.
【０００４】［課題を解決しようとするための手段］ブ
レーキ部材２、３のガイドロッド５に接する部分を図１
のごとく切り欠き、回転モーメントに平行な分力をでき
るだけ少なくし、逆に、回転モーメントに直角な分力を
増大させる。[Means for Solving the Problem] The portions of the brake members 2 and 3 in contact with the guide rod 5 are shown in FIG.
The component force parallel to the rotation moment is reduced as much as possible, and the component force perpendicular to the rotation moment is increased.
【０００５】［作用］図面にしたがつて説明する。図２
において、図２はブレーキがかかった状態であり、ハウ
ジング１の左端に設けられたエァーポートから排気され
てピストン５はフリーの状態である。ブレーキ部材２は
スプリング６によりＡ点を支点として左方向に回転モー
メントを与えられている。又、ブレーキ部材３もスプリ
ング６によりＢ点を支点として左方向に回転モーメント
を与えられている。ブレーキ部材２，３はガイドロッド
４に微少なすきまで嵌合されており回転することにより
ガイドロッド４に摩擦ブレーキがかかる。可動体（図示
せず）に取り付けられたハウジング１が右方向に動くと
ブレーキ部材２にＡ点を支点とした回転モーメントがス
プリング６のみならず可動体推力による分も加わる。
又、可動体即ちハウジング１が左方向に動くとブレーキ
部材３にＢ点を支点として可動体推力による分も加わ
る。次に、ブレーキを解放する場合について述べる。図
２に於いてハウジング１に設けられたエァーポートから
給気されるとピストン５が右方向に押される、従ってピ
ストン５はブレーキ部材２にＣ点を支点として右方向の
回転モーメントをあたえる、これにつれてブレーキ部材
２はＤ点に於いてブレーキ部材３にＢ点を支点とした右
方向の回転モーメントを与える。この結果最終的に図３
に示すブレーキ解放状態となる。次に、本願発明の要旨
はガイドロッド４とブレーキ部材２、３の嵌合部にあり
以下図１において述べる。ブレーキ部材２とガイドロッ
ド４の嵌合部はガイドロッド４の外周とすきまばめのは
めあい状態にあるものの一部を切り欠いた形状になって
いる。又、ブレーキ部材３についても同様である。故
に、ブレーキ部材２、３に回転モーメントがかかった場
合の反力から切り欠き部分の反力を取り除いたことにな
る。[Operation] The operation will be described with reference to the drawings. Figure 2
2 shows a state in which the brake is applied, and the piston 5 is in a free state because the air is exhausted from the air port provided at the left end of the housing 1. The brake member 2 is given a rotational moment to the left by the spring 6 with the point A as a fulcrum. The brake member 3 is also given a rotational moment to the left by the spring 6 with the point B as a fulcrum. The brake members 2 and 3 are fitted to the guide rod 4 up to a minute clearance, and the friction brake is applied to the guide rod 4 by rotating. When the housing 1 attached to a movable body (not shown) moves to the right, a rotational moment about the point A as a fulcrum is applied to the brake member 2 by not only the spring 6 but also the thrust of the movable body.
Further, when the movable body, that is, the housing 1 moves to the left, a portion due to the movable body thrust is added to the brake member 3 with the point B as a fulcrum. Next, the case of releasing the brake will be described. In FIG. 2, when air is supplied from the air port provided in the housing 1, the piston 5 is pushed to the right. Therefore, the piston 5 applies a rotational moment in the right direction to the brake member 2 with the point C as a fulcrum. At the point D, the brake member 2 gives a rightward rotational moment to the brake member 3 about the point B as a fulcrum. As a result, finally
The brake is released as shown in. Next, the gist of the present invention resides in the fitting portion between the guide rod 4 and the brake members 2 and 3, which will be described below with reference to FIG. The fitting portion between the brake member 2 and the guide rod 4 has a shape in which a part of the fitting portion in a clearance fit with the outer periphery of the guide rod 4 is cut out. The same applies to the brake member 3. Therefore, the reaction force of the notch portion is removed from the reaction force when the rotational moment is applied to the brake members 2 and 3.
【０００６】［実施例］ピストン５外径６３ｍｍ、ガイ
ドロッド外径２０ｍｍ、ブレーキ部材の切り欠き幅１８
ｍｍ。以上の構造で実施した結果、本願発明の技術思想
を裏付ける明確な結果がでている。[Embodiment] Piston 5 outer diameter 63 mm, guide rod outer diameter 20 mm, notch width 18 of brake member
mm. As a result of implementing the above structure, there are clear results that support the technical idea of the present invention.
【０００７】［発明の効果］ブレーキ部材２、３に回転
モーメントＭを与えた場合のガイドロッド４からの反力
を回転モーメントと平行な分力Ｒと回転モーメントに直
角な分力ｒとに分解して考えた場合次式が成立する。 Ｍ＝Ｒｌ＋ｋｒｌ （１） （ｌはブレーキ部材２の反力間の回転半径であり、ｋは
摩擦係数である。） 次に、可動体の推力をＦとした場合に次式が成立する。 Ｆ＝ｋＲ＋ｋｒ （２） 以下、極論的に判断すると次のようになる。平行な分力
だけ即ちｒ＝０とすれば （１）、（２）式から Ｆ＝Ｍｋ／ｌ （３） となり、直角な分力だけ即ちＲ＝０とすれば、同様に Ｆ＝Ｍ／ｌ （４） となる。ここで、Ｆによる回転モーメントを除外したＦ
の値はスプリングだけの回転モーメントであり安定性
（初期スリップを無くし確実にロックする）を比較する
値となる。（３）、（４）式を比較すると直角分力の場
合が平行分力の場合の１／ｋとなり、例えばｋ＝０．２
とすると５倍の安定性があることになる。又、（３）、
（４）式に於いてＦを一定としてＭを比較すると使用す
るスプリング力を１／５にできるということであり、
又、ブレーキ解放力も１／５で良く、このことが小型化
及び低価格化を可能にする要因である。又、この点で、
本願発明のブレーキ装置はエァー操作のみならず電磁ソ
レノイド操作も可能である。次に、耐久性について述べ
る。（３）、（４）式のｌの値で耐久性の比較が出来る
（即ち、ブレーキ面圧を下げ得る要因となる。ｋ＝０．
２とすると回転モーメントに直角な反力の場合は平行な
反力の５倍の耐久性を可能にする。以上に述べた発明の
効果は全くの極論であり、本願発明が従来技術と比較し
て量的な相違のみならず質的な相違を発揮する点を明確
にしたに過ぎない。次に、実際の数値として、実施例等
についての計算値を示す。実施例で使用したブレーキ部
材（ガイドロッド径２０ｍｍ、切り欠き幅１８ｍｍにつ
いて計算すると、Ｒとｒの比は ０．４４対０．９とな
り、前記極論で示した５倍の数値は実施例では２．１６
倍ということになる。ちなみに、ブレーキ部材の切り欠
き幅を１９ｍｍとして計算すると上記値は２．５倍とな
る。[Advantages of the Invention] The reaction force from the guide rod 4 when the rotation moment M is applied to the brake members 2 and 3 is decomposed into a component force R parallel to the rotation moment and a component force r perpendicular to the rotation moment. Then, the following equation is established. M = Rl + krl (1) (l is the radius of gyration between the reaction forces of the brake member 2 and k is the coefficient of friction.) Next, when the thrust of the movable body is F, the following equation holds. F = kR + kr (2) The following is a theoretical determination as follows. If only parallel component force is set, that is, r = 0, then (1) and from the equation (2), F = Mk / l (3), and if only right-angled component force is set, that is, R = 0, then F = M / l (4). Here, F excluding the rotational moment due to F
The value of is the rotational moment of only the spring and is a value for comparing stability (locking securely without initial slip). Comparing equations (3) and (4), the case of the perpendicular force component is 1 / k of the case of the parallel force component, for example, k = 0.2.
If so, it means that there is a 5 times stability. Also, (3),
In equation (4), if F is kept constant and M is compared, the spring force used can be reduced to 1/5.
Also, the brake releasing force is only 1/5, which is a factor that enables downsizing and cost reduction. Also in this respect,
The brake device of the present invention can be operated not only by the air operation but also by the electromagnetic solenoid operation. Next, durability will be described. The durability can be compared with the value of l in the equations (3) and (4) (that is, it is a factor that can reduce the brake surface pressure. K = 0.
When set to 2, the reaction force perpendicular to the rotation moment enables durability 5 times that of the parallel reaction force. The effects of the invention described above are completely extreme, and merely clarify that the invention of the present application exhibits not only a quantitative difference but also a qualitative difference as compared with the prior art. Next, as actual numerical values, calculated values for Examples and the like are shown. When the brake member used in the example (guide rod diameter 20 mm, notch width 18 mm was calculated, the ratio of R and r was 0.44 to 0.9, and the five times numerical value shown in the above-mentioned theory was 2 in the example. .16
It will be doubled. By the way, if the notch width of the brake member is calculated as 19 mm, the above value becomes 2.5 times.
【図面の簡単な説明】[Brief description of drawings]
【図１】ブレーキ部を表す図で、図３のＡ−Ｂ断面図。FIG. 1 is a view showing a brake unit and is a cross-sectional view taken along the line AB of FIG.
【図２】ブレーキがかかった状態を表す軸方向断面図。FIG. 2 is an axial sectional view showing a braked state.
【図３】ブレーキ解放状態を表す軸方向断面図。FIG. 3 is an axial sectional view showing a brake released state.
（１）はハウジング。 （２）は右方向用ブレーキ部材。 （３）は左方向用ブレーキ部材。 （４）はガイドロッド。 （５）はブレーキ解放用ピストン。 （６）はスプリング。 （７）、（８）、（９）はＯ−リング。 Ａ、Ｂ、Ｃはそれぞれ支点を表し、Ｄは作用点を表す。 (1) is a housing. (2) is a brake member for the right direction. (3) is a brake member for the left direction. (4) is a guide rod. (5) is a piston for releasing the brake. (6) is a spring. (7), (8), and (9) are O-rings. A, B, and C represent fulcrums, and D represents an action point.
Claims (1)
ドロッドを設け、該ガイドロッドの外周にブレーキ部材
を取り付け、該ブレーキ部材に該ガイドロッド中心軸を
含む平面にそって回転モーメントを与えることにより生
じる、該ガイドロッドと該ブレーキ部材の間の摩擦力
を、上記可動体のブレーキ力とするブレーキ装置に於
て、該ブレーキ部材を該ガイドロッド外周に部分的に接
させることにより、前記回転モーメントに平行な反力の
大半を取り除き前記回転モーメントに直角な反力を増大
させたことを特徴とする直線運動用ブレーキ装置。1. A guide rod is provided along the movement of a movable body that moves linearly, a brake member is attached to the outer periphery of the guide rod, and a rotation moment is applied to the brake member along a plane including the center axis of the guide rod. In a brake device in which the frictional force between the guide rod and the brake member caused by giving the brake force to the movable body, the brake member is brought into partial contact with the outer periphery of the guide rod, A linear motion brake device, characterized in that most of the reaction force parallel to the rotation moment is removed and the reaction force perpendicular to the rotation moment is increased.
Priority Applications (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10452495A JPH08261257A (en) | 1995-03-23 | 1995-03-23 | Brake device for linear motion |
| US08/702,698 US5823300A (en) | 1995-01-31 | 1996-01-24 | Brake device of linear moving body |
| PCT/JP1996/000121 WO1996023979A1 (en) | 1995-01-31 | 1996-01-24 | Brake system for linearly movable bodies |
| KR1019960705044A KR100259746B1 (en) | 1995-01-31 | 1996-01-24 | Brake system for linearly movable bodies |
| EP96901102A EP0753670B1 (en) | 1995-01-31 | 1996-01-24 | Brake system for linearly movable bodies |
| DE69610798T DE69610798T2 (en) | 1995-01-31 | 1996-01-24 | BRAKE SYSTEM FOR A MOVABLE BODY |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10452495A JPH08261257A (en) | 1995-03-23 | 1995-03-23 | Brake device for linear motion |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH08261257A true JPH08261257A (en) | 1996-10-08 |
Family
ID=14382888
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10452495A Pending JPH08261257A (en) | 1995-01-31 | 1995-03-23 | Brake device for linear motion |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH08261257A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002314298A (en) * | 2001-04-18 | 2002-10-25 | Matsushita Electric Ind Co Ltd | Device for packaging electronic component |
-
1995
- 1995-03-23 JP JP10452495A patent/JPH08261257A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002314298A (en) * | 2001-04-18 | 2002-10-25 | Matsushita Electric Ind Co Ltd | Device for packaging electronic component |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20040420 |
|
| A02 | Decision of refusal |
Effective date: 20041124 Free format text: JAPANESE INTERMEDIATE CODE: A02 |