JPH056306Y2 - - Google Patents
Info
- Publication number
- JPH056306Y2 JPH056306Y2 JP11170886U JP11170886U JPH056306Y2 JP H056306 Y2 JPH056306 Y2 JP H056306Y2 JP 11170886 U JP11170886 U JP 11170886U JP 11170886 U JP11170886 U JP 11170886U JP H056306 Y2 JPH056306 Y2 JP H056306Y2
- Authority
- JP
- Japan
- Prior art keywords
- guide rail
- brake
- pressing surface
- pressing
- friction
- 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.)
- Expired - Lifetime
Links
- 230000003028 elevating effect Effects 0.000 claims description 8
- QNRATNLHPGXHMA-XZHTYLCXSA-N (r)-(6-ethoxyquinolin-4-yl)-[(2s,4s,5r)-5-ethyl-1-azabicyclo[2.2.2]octan-2-yl]methanol;hydrochloride Chemical compound Cl.C([C@H]([C@H](C1)CC)C2)CN1[C@@H]2[C@H](O)C1=CC=NC2=CC=C(OCC)C=C21 QNRATNLHPGXHMA-XZHTYLCXSA-N 0.000 description 4
- 229910000831 Steel Inorganic materials 0.000 description 2
- 239000000919 ceramic Substances 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 229910000967 As alloy Inorganic materials 0.000 description 1
- ATJFFYVFTNAWJD-UHFFFAOYSA-N Tin Chemical compound [Sn] ATJFFYVFTNAWJD-UHFFFAOYSA-N 0.000 description 1
- 229910001315 Tool steel Inorganic materials 0.000 description 1
- 239000003779 heat-resistant material Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
Landscapes
- Maintenance And Inspection Apparatuses For Elevators (AREA)
Description
【考案の詳細な説明】
〔産業上の利用分野〕
この考案はエレベータの非常止め装置に関する
ものである。[Detailed description of the invention] [Field of industrial application] This invention relates to an emergency stop device for an elevator.
この種の装置は、たとえば特開昭59−43782号
公報、実開昭55−136759号公報、実開昭55−
136760号公報、実開昭55−136795号公報に開示さ
れており、これを第136795号公報に開示されてお
り、これを第６図に示す典型例を用いて説明す
る。
This type of device is disclosed in, for example, Japanese Unexamined Patent Publication No. 59-43782, Japanese Utility Model Application No. 55-136759, and Japanese Utility Model Application No. 55-136759.
This is disclosed in Japanese Utility Model Publication No. 136760 and Japanese Utility Model Application Publication No. 136795, and will be explained using a typical example shown in FIG.
図中、１はエレベータの図示しない昇降路に立
設されたガイドレール、２はガイドレール１に案
内されて昇降するかごからなる昇降体、３は昇降
体２に設けられた非常止め装置、４は非常止め装
置３の制動子であつて通常はガイドレール１から
離れて保持され、詳細な説明は省略するが、昇降
体２の下降速度が所定値を超えたときに昇降体２
に対して上昇し非常止め装置３の押圧体５の斜面
およびローラ６を介してガイドレール１面に押圧
される。 In the figure, 1 is a guide rail installed in an elevator hoistway (not shown), 2 is an elevating body consisting of a car that goes up and down guided by the guide rail 1, 3 is an emergency stop device provided on the elevating body 2, and 4 is a brake of the emergency stop device 3, which is normally held apart from the guide rail 1, and although detailed explanation will be omitted, when the descending speed of the elevating object 2 exceeds a predetermined value, the elevating object 2
It rises against the surface of the emergency stop device 3 and is pressed against the guide rail 1 surface via the slope of the pressing body 5 of the emergency stop device 3 and the roller 6.
すなわち、制動子４は、非常時に動作してガイ
ドレール１に押圧され、制動子４とガイドレール
１との摩擦によつて昇降体２が制動される。この
ときの制動能力は、制動子４とガイドレール１面
の摩擦係数と、制動子４の押圧力の積で決定され
る。したがつて、小型で高能力の非常止め装置３
を得るためには、摩擦係数を高め、押圧力を小さ
くすればよいことになる。そのためには制動子４
の押圧面に多数の突起を設ければよいが、こうし
た場合には、ガイドレール１に対する制動子４の
押圧時、ガイドレール１に細かい切粉が発生し、
この切粉が突起に付着するため、摩擦係数が大き
く変動し、制動が不安定になる。このような摩擦
係数の変動は、制動子４の押圧面における平面度
が悪い場合にも生ずることになる。 That is, the brake 4 operates in an emergency and is pressed against the guide rail 1, and the lifting body 2 is braked by the friction between the brake 4 and the guide rail 1. The braking ability at this time is determined by the product of the friction coefficient between the brake 4 and the guide rail 1 surface and the pressing force of the brake 4. Therefore, a small and highly capable emergency stop device 3
In order to obtain this, it is sufficient to increase the coefficient of friction and reduce the pressing force. For that purpose, brake 4
A large number of protrusions may be provided on the pressing surface of the guide rail 1, but in such a case, fine chips are generated on the guide rail 1 when the brake element 4 is pressed against the guide rail 1.
Since these chips adhere to the protrusions, the coefficient of friction fluctuates greatly, making braking unstable. Such a variation in the coefficient of friction also occurs when the flatness of the pressing surface of the brake element 4 is poor.
そこでこれに対処するため、制動子４の押圧面
に突歯を設けることが既に提案されている（実開
昭55−136759号公報）。 To deal with this problem, it has already been proposed to provide protruding teeth on the pressing surface of the brake element 4 (Japanese Utility Model Publication No. 136759/1983).
制動子４の押圧面に突歯を設けることの利点
は、上記から明らかなように、ガイドレール１に
切粉が発生し難く、また制動子４の平面度もそれ
ほどの精度を要求されないことである。しかしな
がら、摩擦係数を上げるために制動子全面に突歯
を設けて押圧すると、レール長手方向の受圧面積
が大きいため、各々の突歯面圧が不均一となり、
さらに押圧面のガイドレール平面度や制動子の平
面度の影響を受け、突歯の面圧の不均一さが大き
くなる。これにより特に制動子が偏荷重を受けた
場合には、制動時、摩擦係数が大きく変動すると
いう問題点があつた。
As is clear from the above, the advantage of providing the protruding teeth on the pressing surface of the brake element 4 is that chips are less likely to be generated on the guide rail 1, and the flatness of the brake element 4 does not require much precision. . However, when protruding teeth are provided on the entire surface of the brake in order to increase the coefficient of friction, the surface pressure of each protruding tooth becomes uneven because the pressure receiving area in the longitudinal direction of the rail is large.
Furthermore, it is affected by the guide rail flatness of the pressing surface and the flatness of the brake, and the unevenness of the surface pressure of the protruding teeth increases. This has caused a problem in that the coefficient of friction varies greatly during braking, especially when the brake is subjected to an uneven load.
この考案は、上記問題点を解決するためになさ
れたもので、制動子の押圧面に均一な荷重が作用
するエレベータの非常止め装置を得ることを目的
とする。 This invention was made in order to solve the above-mentioned problems, and its purpose is to obtain an emergency stop device for an elevator in which a uniform load is applied to the pressing surface of the brake.
この考案は、制動子の押圧面に多数の突歯を形
成するとともに、該押圧面の昇降方向における中
央部にこの押圧面の幅全域にわたり凹部を設け
た、というものである。
In this invention, a large number of protruding teeth are formed on the pressing surface of the brake, and a recess is provided in the center of the pressing surface in the vertical direction, over the entire width of the pressing surface.
非常時、制動子は昇降体に対して上昇し、ガイ
ドレールに押圧され、この際、突歯がガイドレー
ルに係合するため、大きな摩擦係数が得られる。
また、制動子には押圧面の幅全域にわたり凹部が
形成されて、押圧面が上下２ケ所に分けられるた
め、ガイドレールに対する制動子の押圧力は、押
圧面において均一となり、このため摩擦係数はほ
とんど変動しない。
In an emergency, the brake element rises relative to the elevating body and is pressed against the guide rail, and at this time, the protruding teeth engage with the guide rail, resulting in a large coefficient of friction.
In addition, since a recess is formed in the brake element over the entire width of the pressing surface, and the pressing surface is divided into two areas, upper and lower, the pressing force of the brake element against the guide rail is uniform on the pressing surface, and therefore the coefficient of friction is There is almost no change.
以下、この考案の一実施例を図面を参照しなが
ら説明する。なお、第１図ないし第５図において
第６図と同一符号は、同一部分または相当部分を
示すものとする。第１図は非常止め装置３を示す
もので、１は上述の如く図示しない昇降路に立設
されたガイドレールであつて、制動子４はガイド
レール１から離れた状態に保持されている。５は
押圧体であつて、この押圧体５は昇降体２の底部
に設けられた枠体７に保持され、ばね８によつて
常時ガイドレール１方向に弾発付勢されている。
この押圧体５のガイドレール１に近い側の面は、
ガイドレール１と交差する方向に傾斜し、上部に
向かうにつれてガイドレール１との間隔が狭くな
つている。制動子４の背面、つまりガイドレール
１から遠い側の面も傾斜し、押圧体５の傾斜面と
ほぼ平行に形成され、押圧体５と制動子４との両
傾斜面間には、複数のローラ６が配設されてい
る。
An embodiment of this invention will be described below with reference to the drawings. Note that in FIGS. 1 to 5, the same reference numerals as in FIG. 6 indicate the same or equivalent parts. FIG. 1 shows an emergency stop device 3, in which reference numeral 1 is a guide rail erected in a hoistway (not shown) as described above, and a brake 4 is held apart from the guide rail 1. Reference numeral 5 denotes a pressing body, and this pressing body 5 is held by a frame 7 provided at the bottom of the elevating body 2, and is always resiliently biased in the direction of the guide rail 1 by a spring 8.
The surface of this pressing body 5 closer to the guide rail 1 is
It is inclined in the direction intersecting the guide rail 1, and the distance from the guide rail 1 becomes narrower toward the top. The rear surface of the brake element 4, that is, the surface far from the guide rail 1, is also inclined, and is formed almost parallel to the inclined surface of the pressing body 5, and between both the inclined surfaces of the pressing body 5 and the brake element 4, there are a plurality of slopes. A roller 6 is provided.
制動子４の押圧面５ａ、つまりガイドレール１
に近い側の面には、同図に明示するようにこの押
圧面の幅全域にわたり凹部９が形成されている。
この凹部９の位置は、非常時、制動子４が昇降体
２に対して上昇し、ガイドレール１に押圧された
際、押圧力が押圧面５ａにおいて均一になるよう
な個所、つまり押圧面５ａの昇降方向における中
央部に設定される。 The pressing surface 5a of the brake 4, that is, the guide rail 1
As clearly shown in the figure, a recess 9 is formed over the entire width of the pressing surface.
The position of this recess 9 is such that in an emergency, when the brake 4 rises relative to the elevating body 2 and is pressed against the guide rail 1, the pressing force is uniform on the pressing surface 5a, that is, the pressing surface 5a. It is set at the center in the vertical direction.
第２図および第３図に示すように、押圧面５ａ
の凹部９を除いた部分には多数の突歯１０が形成
されている。突歯１０は、第３図では平坦な菱形
面１０ａを有し、かつ該菱形面１０ａは昇降方向
に対し交差する方向に配列されている。相隣の菱
形面１０ａ間には、横断面形状が三角形状でかつ
菱形面１０ａの配列方向に対して平行状に延びる
溝１０ｂが形成されている。溝１０ｂの幅Ｗと間
隔Ｐとの大小関係はＷ＜Ｐ／２であることが好まし
く、このように設定して試験を行つたところ、第
４図に示すようにＡ，B2曲線が得られた。同図
から明らかなように、制動子４の面圧ｆが３〜７
Kg／mm2の範囲では摩擦係数μは0.3〜0.4の範囲を
示している。従来の摩擦係数は0.16であるからこ
の値の約２倍に達している。 As shown in FIGS. 2 and 3, the pressing surface 5a
A large number of protruding teeth 10 are formed in the portion excluding the recess 9. The protruding teeth 10 have flat rhombic surfaces 10a in FIG. 3, and the rhombic surfaces 10a are arranged in a direction intersecting the vertical direction. A groove 10b having a triangular cross-sectional shape and extending parallel to the arrangement direction of the rhombic surfaces 10a is formed between adjacent rhombic surfaces 10a. It is preferable that the magnitude relationship between the width W of the groove 10b and the interval P is W<P/2, and when a test was conducted with this setting, curves A and B2 were obtained as shown in Fig. 4. Ta. As is clear from the figure, the surface pressure f of the brake element 4 is 3 to 7.
In the range of Kg/mm 2 , the friction coefficient μ is in the range of 0.3 to 0.4. The conventional coefficient of friction is 0.16, which is approximately twice this value.
ところで、摩擦係数を高くするためには、面圧
ｆを高くすればよく、したがつて面圧ｆを高くす
るために同一押圧面５ａ内で溝１０ｂの幅Ｗを大
きくすることが考えられるが、Ｗ＞Ｐ／２とすると、
曲線Ｃに示すように、面圧ｆに対して摩擦係数が
不安定になる。 By the way, in order to increase the coefficient of friction, it is sufficient to increase the surface pressure f, and therefore, in order to increase the surface pressure f, it is conceivable to increase the width W of the groove 10b within the same pressing surface 5a. , W>P/2, as shown by curve C, the friction coefficient becomes unstable with respect to the surface pressure f.
また、第３図に示すように突歯１０の頂角θは
θ＝90°〜120°であることが好ましく、さらに第
２図に示すように菱形面１０ａの昇降方向に対す
る開き角度αはα＝45°〜90°であることが好まし
い。 Further, as shown in FIG. 3, the apex angle θ of the protruding tooth 10 is preferably θ=90° to 120°, and as shown in FIG. Preferably, the angle is between 45° and 90°.
さらに、第１図および第３図に示すように、制
動子４の昇降方向における端部１１は面取りされ
ることが望ましく、かつこの面取り部分の昇降方
向における長さは、菱形面１０ａの昇降方向にお
ける対角線の長さＬの1/2が適当である。このよ
うに制動子４の端部に面取りを施すと、ガイドレ
ール１に対する制動子４の摺動時に安定した制動
力が得られないことになる。この安定性は面取り
の長さが1/2より大であつても小であつても悪く
なる。 Furthermore, as shown in FIGS. 1 and 3, it is desirable that the end portion 11 of the brake element 4 in the vertical direction is chamfered, and the length of this chamfered portion in the vertical direction is determined by the length of the diamond-shaped surface 10a in the vertical direction. 1/2 of the diagonal length L is appropriate. If the end of the brake element 4 is chamfered in this way, a stable braking force cannot be obtained when the brake element 4 slides on the guide rail 1. This stability worsens whether the length of the chamfer is larger or smaller than 1/2.
第５図は上記条件を満たす制動子４を用いた場
合の制動特性と従来例の制動特性とを比較したも
ので、グラフＤはこの考案に係る装置の制動特性
を示し、グラフＥは従来例の制動特性を示し、ま
た横軸は制動子４のガイドレール１に対する摺動
距離ｌを示す。同図から明らかなように、この考
案に係る装置の制動時におけるガイドレール１に
対する制動子４の摩擦係数は従来の装置の約２倍
に達している。 FIG. 5 compares the braking characteristics when using the brake element 4 that satisfies the above conditions with the braking characteristics of a conventional example. Graph D shows the braking characteristics of the device according to this invention, and graph E shows the conventional example. The horizontal axis shows the sliding distance l of the brake element 4 with respect to the guide rail 1. As is clear from the figure, the coefficient of friction of the brake element 4 against the guide rail 1 during braking in the device according to this invention is about twice that of the conventional device.
なお、制動子４の材質としては、高温に耐える
合金鋼、工具鋼、拘束度鋼、セラミツク等の耐熱
材が用いられる。表面硬度はHKC55以上に硬化し
て用いてもよく、あるいは表面にTiC，TiN等の
炭化物やセラミツクをコーテイングしてもよい。 As the material for the brake element 4, heat-resistant materials such as alloy steel, tool steel, restraint steel, and ceramic that can withstand high temperatures are used. The surface hardness may be hardened to H KC 55 or higher, or the surface may be coated with carbide such as TiC or TiN or ceramic.
この考案は、以上から明らかなように、制動子
に多数の突歯を設けて、制動子とガイドレールと
の間の摩擦係数を大にしたので、ガイドレールに
対する押圧力を小さくすることができ、したがつ
て装置の小型化が図れる。
As is clear from the above, in this invention, the brake element is provided with a large number of protruding teeth to increase the coefficient of friction between the brake element and the guide rail, so that the pressing force against the guide rail can be reduced. Therefore, the device can be made smaller.
また、制動子の押圧面の昇降方向における中央
部に、この押圧面の幅全域にわたり凹部を形成し
たので、制動時、制動子のガイドレールに対する
押圧力が均一になり、したがつて摩擦係数の変動
がほとんど生じない。 In addition, since a recess is formed in the center of the pressing surface of the brake in the vertical direction, over the entire width of the pressing surface, the pressing force of the brake against the guide rail becomes uniform during braking, and this reduces the coefficient of friction. Almost no fluctuations occur.
第１図はこの考案の係るエレベータの非常止め
装置の略示断面図、第２図は第１図の−線か
ら見た矢視図、第３図は第２図の−線に沿う
断面図、第４図は溝間隔Ｐと溝幅Ｗとの関係をＷ
＜Ｐ／２とした場合における摩擦係数と制動子の面
圧との関係を示すグラフ、第５図はこの考案に係
る装置と従来例との制動特性を比較した場合のグ
ラフ、第６図は従来のエレベータの非常止め装置
の略示断面図である。
１……ガイドレール、２……昇降体、４……制
動子、５ａ……押圧面、９……凹部、１０……突
歯。なお、図中同一符号は同一または相当部分を
示す。
Fig. 1 is a schematic sectional view of an elevator safety device according to this invention, Fig. 2 is a sectional view taken from the - line in Fig. 1, and Fig. 3 is a sectional view taken along the - line in Fig. 2. , Figure 4 shows the relationship between the groove interval P and the groove width W.
A graph showing the relationship between the friction coefficient and the surface pressure of the brake when <P/2, Figure 5 is a graph comparing the braking characteristics of the device according to this invention and a conventional example, and Figure 6 is a graph showing the relationship between the friction coefficient and the surface pressure of the brake. FIG. 2 is a schematic cross-sectional view of a conventional elevator emergency stop device. DESCRIPTION OF SYMBOLS 1... Guide rail, 2... Lifting body, 4... Brake element, 5a... Pressing surface, 9... Recessed part, 10... Projection tooth. Note that the same reference numerals in the figures indicate the same or corresponding parts.
Claims (1)
られ、非常時に前記ガイドレールに押圧される制
動子を備えたエレベータの非常止め装置におい
て、前記制動子の押圧面に多数の突歯を形成する
とともに該押圧面の昇降方向における中央部に、
この押圧面の幅全域にわたり凹部を設けたことを
特徴とするエレベーターの非常止め装置。 In an elevator emergency stop device including a brake which is provided on an elevating body guided by a guide rail and which is pressed against the guide rail in an emergency, a large number of protruding teeth are formed on the pressing surface of the brake. At the center of the pressing surface in the vertical direction,
An elevator emergency stop device characterized in that a recess is provided over the entire width of the pressing surface.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11170886U JPH056306Y2 (en) | 1986-07-21 | 1986-07-21 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11170886U JPH056306Y2 (en) | 1986-07-21 | 1986-07-21 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6318456U JPS6318456U (en) | 1988-02-06 |
| JPH056306Y2 true JPH056306Y2 (en) | 1993-02-18 |
Family
ID=30991882
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP11170886U Expired - Lifetime JPH056306Y2 (en) | 1986-07-21 | 1986-07-21 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH056306Y2 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH076780Y2 (en) * | 1990-10-04 | 1995-02-22 | 小松ゼノア株式会社 | Backpack work machine |
| JP4797786B2 (en) * | 2006-05-15 | 2011-10-19 | 株式会社日立製作所 | Elevator emergency stop device and elevator |
| JP6660853B2 (en) * | 2016-08-30 | 2020-03-11 | 株式会社日立製作所 | Emergency stop device and elevator using the same |
-
1986
- 1986-07-21 JP JP11170886U patent/JPH056306Y2/ja not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6318456U (en) | 1988-02-06 |
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