JPH0712912B2 - Overload prevention device for hoisting machine - Google Patents
Overload prevention device for hoisting machineInfo
- Publication number
- JPH0712912B2 JPH0712912B2 JP28952486A JP28952486A JPH0712912B2 JP H0712912 B2 JPH0712912 B2 JP H0712912B2 JP 28952486 A JP28952486 A JP 28952486A JP 28952486 A JP28952486 A JP 28952486A JP H0712912 B2 JPH0712912 B2 JP H0712912B2
- Authority
- JP
- Japan
- Prior art keywords
- transmission
- gear
- engagement
- load
- transmission gear
- 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 - Fee Related
Links
- 230000002265 prevention Effects 0.000 title claims description 18
- 230000005540 biological transmission Effects 0.000 claims description 123
- 238000004804 winding Methods 0.000 description 6
- 230000000903 blocking effect Effects 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
Landscapes
- Insulation, Fastening Of Motor, Generator Windings (AREA)
- Manufacture Of Motors, Generators (AREA)
- Transmission Devices (AREA)
Description
【発明の詳細な説明】 （産業上の利用分野） 本発明は捲上機の過負荷防止装置、詳しくは、定格負荷
以上の荷重が作用した状態での捲上げを防止する捲上機
の過負荷防止装置に関する。Description: TECHNICAL FIELD The present invention relates to an overload prevention device for a hoisting machine, and more specifically, a hoisting machine overload preventing apparatus for preventing hoisting under a condition where a load higher than a rated load is applied. Load prevention device.
（従来の技術） 従来、この種過負荷防止装置は、例えば実開昭51−7636
0号公報に示される如く、捲上機における伝動軸に、該
伝動軸に遊嵌される伝動ギヤと前記伝動軸に軸方向にの
み摺動可能に支持され、前記伝動ギヤと摩擦接触する伝
動体とこの伝動体を前記伝動ギヤに押圧する弾性部材と
を備えて成り、前記伝動ギヤが伝動体に対しスリップす
るスリップ開始荷重を、前記伝動ギヤと伝動体との摩擦
抵抗値により設定して、前記スリップ開始荷重以上の荷
重が作用したときに、前記伝動ギヤと伝動体とをスリッ
プさせ、定格負荷以上の負荷の捲上げが行なえないよう
に構成している。(Prior Art) Conventionally, this kind of overload prevention device is disclosed, for example, in Japanese Utility Model Laid-Open No. 51-7636.
As disclosed in Japanese Patent No. 0, the transmission shaft of a hoisting machine is supported by a transmission gear that is loosely fitted to the transmission shaft and a transmission gear that is slidable only in the axial direction of the transmission shaft, and that makes frictional contact with the transmission gear. A body and an elastic member that presses the transmission body against the transmission gear, and a slip start load at which the transmission gear slips with respect to the transmission body is set by a friction resistance value between the transmission gear and the transmission body. When a load equal to or greater than the slip start load is applied, the transmission gear and the transmission body are slipped so that a load equal to or higher than the rated load cannot be hoisted.
（発明が解決しようとする問題点） ところが、前記した従来の過負荷防止装置のように、前
記伝動ギヤが伝動体に対しスリップするスリップ開始荷
重を、前記伝動ギヤと伝動体との摩擦抵抗値のみにより
設定する構成のものにあっては、前記スリップ開始荷重
をやゝ越えた程度の負荷が作用する状態のもとで荷物を
捲上げる際、つまり地切りを行なう際、前記スリップ開
始荷重と負荷との差が僅かであるため、前記伝動ギヤと
伝動体との滑りがごく僅かしか現われないのである。こ
のため、荷物の地切り時に過負荷を検出できず、過負荷
状態であるにも拘わらず、気づかずに捲上げを行なって
いるのが現状である。この結果、荷物を捲上げて宙吊り
状態を維持するような場合に、前記伝動ギヤと伝動体と
が徐々に滑り出し、その滑りがある程度行なわれて、摩
擦面が熱をもつと前記摩擦抵抗値が急激に低下し、前記
伝動ギヤと伝動体とが一気にスリップして荷物が落下す
る問題を有していた。(Problems to be Solved by the Invention) However, like the above-described conventional overload prevention device, the slip start load at which the transmission gear slips with respect to the transmission body is determined by the frictional resistance value between the transmission gear and the transmission body. In the configuration set only by the slip start load when the load is rolled up under the condition that the load slightly exceeding the slip start load is applied, that is, when the ground cutting is performed. Since the difference from the load is small, the slip between the transmission gear and the transmission body appears very little. For this reason, the overload cannot be detected at the time of ground cutting of the load, and the winding is performed without noticing even in the overloaded state. As a result, when the load is hoisted up and the suspended state is maintained, the transmission gear and the transmission body are gradually slid, and the sliding is performed to some extent. There is a problem that the load suddenly drops, the transmission gear and the transmission body slip at a stretch, and the load falls.
本発明の目的は、スリップ開始荷重以上の負荷が作用す
る状態での捲上時、前記スリップ開始荷重と負荷との差
が僅かであっても、伝動ギヤと伝動体とを直ちに、かつ
一挙にスリップさせ、捲上げが行なえないようにして前
記した従来の問題を解決しようとするものである。An object of the present invention is, when hoisting in a state in which a load equal to or more than a slip start load is applied, immediately and at once the transmission gear and the transmission body even if the difference between the slip start load and the load is small. The present invention is intended to solve the above-mentioned conventional problems by slipping and preventing winding.
（問題点を解決するための手段） 本発明は、駆動軸（60）の回転動力をロードシーブ
（５）に伝達する捲上機における伝動軸（86）に、該伝
動軸（86）に遊嵌される伝動ギヤ（87）と前記伝動軸
（86）に軸方向のみ摺動可能に支持され、前記伝動ギヤ
（87）と摩擦接触する伝動体（22）とこの伝動体（22）
を前記伝動ギヤ（87）に押圧する弾性部材（24）とを備
えた過負荷防止装置において、前記伝動ギヤ（87）と伝
動体（22）との対向面の一方に係合凹部（22c）を設
け、他方に、前記係合凹部（22c）に係合する係合体（2
7）と該係合体（27）を前記係合凹部（22c）の方向に付
勢するばね（28）とを設け、前記伝動ギヤ（87）が伝動
体（22）に対してスリップするスリップ開始荷重を、前
記伝動ギヤ（87）と伝動体（22）との摩擦抵抗値と、前
記係合体（27）の係合凹部（22c）との係合抵抗値との
トータルで設定する如くしたものである。(Means for Solving Problems) The present invention relates to a transmission shaft (86) in a hoisting machine that transmits the rotational power of the drive shaft (60) to the load sheave (5), and the transmission shaft (86) has a free play. A transmission body (22), which is slidably supported only in the axial direction by the transmission gear (87) to be fitted and the transmission shaft (86), and makes frictional contact with the transmission gear (87), and the transmission body (22).
And an elastic member (24) for pressing the transmission gear (87) against the transmission gear (87). In the overload prevention device, one of the facing surfaces of the transmission gear (87) and the transmission body (22) is engaged with a recess (22c). Is provided on the other side, and on the other side, an engaging body (2
7) and a spring (28) for urging the engaging body (27) toward the engaging recess (22c) are provided, and the transmission gear (87) starts slipping with respect to the transmitting body (22). A load is set by a total of a frictional resistance value between the transmission gear (87) and the transmission body (22) and an engagement resistance value between the engagement recess (22c) of the engagement body (27). Is.
（作用） 上記構成により、前記スリップ開始荷重よりも大きな負
荷が作用する状態で捲上げを行なうと、前記係合体（2
7）がばね（28）に抗し、前記伝動ギヤ（87）又は伝動
体（22）の係合凹部（22c）から外れて該伝動ギヤ（8
7）又は伝動体（22）の対向面に乗り上げる如く移動
し、この移動により前記係合体（27）と伝動ギヤ（87）
又は伝動体（22）との係合抵抗がなくなり、つまり前記
係合体（27）の前記対向面への当接抵抗と、該係合体
（27）の前記対向面への乗り上げに伴って減少する前記
伝動ギヤ（87）と伝動体（29）とによる摩擦抵抗とが作
用することになり、このため、これら当接抵抗と摩擦抵
抗とのトータルによるスリップ阻止荷重が前記スリップ
開始荷重に較べて低下し、この結果、前記スリップ開始
荷重と負荷との差が僅かであっても直ちに、かつ一挙に
大きなスリップが発生して捲上げが行なえなくなるので
ある。(Operation) With the above configuration, when the winding is performed in a state where a load larger than the slip start load acts, the engaging body (2
7) resists the spring (28) and disengages from the engaging recess (22c) of the transmission gear (87) or the transmission body (22).
7) Or it moves so as to ride on the facing surface of the transmission body (22), and by this movement, the engagement body (27) and the transmission gear (87)
Alternatively, the engagement resistance with the transmission body (22) disappears, that is, the contact resistance of the engagement body (27) to the facing surface and the resistance decrease as the engagement body (27) rides on the facing surface. Friction resistance due to the transmission gear (87) and the transmission body (29) acts, so that the slip prevention load due to the total of the contact resistance and the friction resistance is lower than the slip start load. However, as a result, even if the difference between the slip start load and the load is small, a large amount of slip occurs immediately and the winding cannot be performed.
（実施例） 第４図に示すものは、本発明過負荷防止装置を装着した
電動式捲上機であって、該捲上機は所定間隔を置いて相
対向する一対の第1,第２サイドプレート（１）（２）の
中心部に軸受（３）（４）を介してロードシーブ（５）
を回転自由に支持すると共に、前記各サイドプレート
（１）（２）のうち、第１サイドプレート（１）の外側
にモータ（６）を設け、該モータ（６）の駆動軸（60）
の一端を前記第１サイドプレート（１）に設ける軸受
（７）により支持する一方、第２サイドプレート（２）
の外側に、減速歯車機構（８）とギヤケース（80）及び
ブレーキ装置（９）を設け、かつ、前記ギヤケース（8
0）と第２サイドプレート（２）との間に軸受（11）（1
2）を介して前記減速歯車機構（８）の第１軸（81）を
回転自由に支持し、この第１軸（81）と前記駆動軸（6
0）との一端部を対向させて、これら対向部間に動力伝
達機構（13）を設け、前記駆動軸（60）の回転を、前記
動力伝達機構（13）から前記減速歯車機構（８）を介し
て前記ロードシーブ（５）に伝達すべく成している。(Embodiment) FIG. 4 shows an electric hoist equipped with the overload prevention device of the present invention, wherein the hoist comprises a pair of first and second opposing hoisting machines at predetermined intervals. Load sheave (5) through bearings (3) and (4) at the center of side plates (1) and (2)
Of the side plates (1) and (2), a motor (6) is provided outside the first side plate (1), and a drive shaft (60) of the motor (6) is supported.
One end of the second side plate (2) is supported by a bearing (7) provided on the first side plate (1).
A reduction gear mechanism (8), a gear case (80), and a brake device (9) are provided on the outer side of the gear case (8).
0) and the second side plate (2) between the bearings (11) (1
The first shaft (81) of the reduction gear mechanism (8) is rotatably supported via 2), and the first shaft (81) and the drive shaft (6) are supported.
0) and one end thereof are opposed to each other, and a power transmission mechanism (13) is provided between these opposing portions to rotate the drive shaft (60) from the power transmission mechanism (13) to the reduction gear mechanism (8). It is designed to be transmitted to the load sheave (5) via the.
前記減速歯車機構（８）はギヤケース（80）を備え、こ
のケース（８）と前記第２サイドプレート（２）との間
には、前記した如く第１ギヤ（82）をもつ第１軸（81）
の他、第2,第３ギヤ（84）（85）をもった第２軸（83）
と、第4,第５ギヤ（87）（88）をもった第３軸（86）と
が回転自由に支持され、前記第５ギヤ（88）を前記ロー
ドシーブ軸（51）に固定の第６ギヤ（89）に噛合わせて
構成されている。The reduction gear mechanism (8) includes a gear case (80), and the first shaft (1) having the first gear (82) as described above is provided between the case (8) and the second side plate (2). 81)
Second shaft (83) with second and third gears (84) (85)
And a third shaft (86) having fourth and fifth gears (87) (88) are rotatably supported, and the fifth gear (88) is fixed to the load sheave shaft (51). It is configured to mesh with 6 gears (89).
しかして、前記減速歯車機構（８）の前記第３軸（86）
には次の如き過負荷防止装置が配設されている。Thus, the third shaft (86) of the reduction gear mechanism (8)
The following overload prevention device is provided in the.
即ち、第１図に示す如く、前記減速歯車機構（８）の前
記第３軸（86）の第５ギヤ（88）固定側とは反対側に、
スプライン部（86a）とねじ部（86b）とを形成して、前
記スプライン部（86a）に前記第４ギヤ（87）を遊嵌支
持する支持部（21a）（22a）と前記第４ギヤ（87）と摩
擦接触する鍔部（21b）（22b）とをもつ受止体（21）と
伝動体（22）とを軸方向に摺動可能で回転不能にスプラ
イン嵌合し、かつ、前記両鍔部（21b）（22b）で挾持す
る如く前記第４ギヤ（87）を前記両支持部（21a）（22
a）に遊嵌支持する一方、前記ねじ部（86b）に調整ナッ
ト（23）を螺合すると共に、該ナット（23）と前記伝動
体（22）との間に主として皿ばねから成る弾性部材（2
4）を介装し、前記調整ナット（23）の締付け具合で、
つまり、皿ばね（24）による前記伝動体（22）への押圧
力で前記伝動体（22）と第４ギヤ（87）との摩擦抵抗値
を設定すべく成している。この場合、前記受止体（21）
は第５ギヤ（88）の一側面に当接して、該受止体（21）
の第５ギヤ（88）側への移動が阻止されている。That is, as shown in FIG. 1, on the side opposite to the fifth gear (88) fixed side of the third shaft (86) of the reduction gear mechanism (8),
A support portion (21a) (22a) for forming a spline portion (86a) and a screw portion (86b) to loosely fit and support the fourth gear (87) on the spline portion (86a), and the fourth gear ( 87) and the transmission body (22), which has a flange portion (21b) (22b) that makes frictional contact, and a transmission body (22) are axially slidable and non-rotatably spline-fitted, and The fourth gear (87) is attached to both the support parts (21a) (22) so as to be held by the collar parts (21b) (22b).
While being loosely fitted and supported in a), an adjusting nut (23) is screwed into the screw portion (86b), and an elastic member mainly composed of a disc spring is provided between the nut (23) and the transmission body (22). (2
4) and tighten the adjusting nut (23).
That is, the disc spring (24) presses the transmission body (22) to set the frictional resistance value between the transmission body (22) and the fourth gear (87). In this case, the receiving body (21)
Is in contact with one side surface of the fifth gear (88), and the receiving body (21)
Is prevented from moving toward the fifth gear (88).
又、前記第４ギヤ（87）の両側面には、環状の凹入部
（87a）（87a）が形成され、これら凹入部（87a）（87
a）に摩擦板（25）（26）をそれぞれ装着し、これら各
摩擦板（25）（26）を介して前記第４ギヤ（87）の一側
と伝動体（22）とが、また、第４ギヤ（87）の他側と受
止体（21）とがそれぞれ摩擦接触すべく成している。In addition, annular recesses (87a) (87a) are formed on both side surfaces of the fourth gear (87), and these recesses (87a) (87a)
The friction plates (25) and (26) are attached to a), respectively, and one side of the fourth gear (87) and the transmission body (22) through the friction plates (25) and (26). The other side of the fourth gear (87) and the receiving body (21) are in frictional contact with each other.
そして、前記伝動体（22）には、例えば複数の円錐形状
を呈する係合凹部（22c）を形成すると共に、該伝動体
（22）と対向する摩擦板（25）と第４ギヤ（87）とに複
数の貫通孔（25a）及び（87b）を形成して、これら各貫
通孔（25a）（87b）内に前記係合凹部（22c）に係合す
る主としてボールなどの係合体（27）と該係合体（27）
を前記係合凹部（22c）の方向に付勢するばね（28）と
を設けて、前記係合体（27）の係合凹部（22c）への係
合により前記伝動体（22）と第４ギヤ（87）とに係合抵
抗を与えるようにしている。The transmission body (22) is formed with, for example, a plurality of conical recesses (22c) having a conical shape, and the friction plate (25) and the fourth gear (87) facing the transmission body (22) are formed. A plurality of through holes (25a) and (87b) are formed in the and, and an engaging body (27) such as a ball mainly engaged with the engaging recess (22c) in each of the through holes (25a) (87b). And the engaging body (27)
A spring (28) for urging the engaging member (27) toward the engaging recess (22c), and by engaging the engaging member (27) with the engaging recess (22c), Engagement resistance is given to the gear (87).
しかして、前記皿ばね（24）の伝動体（22）への押圧力
による前記第４ギヤ（87）と伝動体（22）との摩擦抵抗
値と、前記ばね（28）をした係合体（27）の係合凹部
（22c）への係合による係合抵抗値とのトータルで、前
記第４ギヤ（87）が伝動体（22）に対しスリップするス
リップ開始荷重を設定すべく成している。Thus, the frictional resistance value between the fourth gear (87) and the transmission body (22) due to the pressing force of the disc spring (24) on the transmission body (22), and the engagement body (which includes the spring (28) ( The total value of (27) and the engagement resistance value due to the engagement with the engagement recess (22c) is used to set the slip start load at which the fourth gear (87) slips on the transmission body (22). There is.
又、第１図及び第２図において、（29）は前記調整ナッ
ト（23）の弛みを阻止するのこ歯状係合部（29a）をも
つ阻止板であって、該阻止板（29）の基部を前記伝動体
（22）の外周部側面にボルト（30）（30）により着脱可
能とし、前記調整ナット（23）の締付後、この阻止板
（29）を前記伝動体（22）に取付けて、前記調整ナット
（23）の角部にのこ歯状係合部（29a）に係止させ、前
記調整ナット（23）の弛みを阻止するようにしている。
また前記阻止板（29）の中間部には立上り段部が形成さ
れ、該阻止板（29）と前記皿ばね（24）との干渉をなく
すようにし、また、前記係合部（29a）は、前記調整ナ
ット（23）の角部の少なくとも一つが必らず係止できる
よう前記調整ナット（23）の直径をもとに描いた円弧線
上に沿って、ほゞ90°の範囲に亘って形成されている。Further, in FIGS. 1 and 2, reference numeral (29) is a blocking plate having a sawtooth engagement portion (29a) for blocking the loosening of the adjusting nut (23). The base portion of the transmission body (22) can be attached to and detached from the side surface of the outer periphery of the transmission body (22) with bolts (30) (30). The adjusting nut (23) is attached to the corner of the adjusting nut (23) and is engaged with the sawtooth engaging portion (29a) to prevent the adjusting nut (23) from loosening.
Further, a rising step is formed in the intermediate portion of the blocking plate (29) so as to eliminate interference between the blocking plate (29) and the disc spring (24), and the engaging portion (29a) is , Along the arc line drawn based on the diameter of the adjusting nut (23) so that at least one of the corners of the adjusting nut (23) can be locked without fail, over a range of about 90 °. Has been formed.
本発明は以上の如く構成するもので、定格負荷の荷物を
捲上げるときには、前記第４ギヤ（87）を挾持する摩擦
板（25）（26）と伝動体（22）との摩擦抵抗値と前記係
合体（27）の係合凹部（22c）への係合による係合抵抗
値とのトータルにより設定するスリップ開始荷重が負荷
よりも大きいために、前記荷物の捲上げが行なえる。The present invention is configured as described above, and when rolling up a load having a rated load, a frictional resistance value between the friction plates (25) (26) holding the fourth gear (87) and the transmission body (22) is set. Since the slip start load set by the total of the engagement resistance value due to the engagement of the engagement body (27) with the engagement recess (22c) is larger than the load, the luggage can be hoisted.
また、定格負荷以上の荷物を捲上げるときには、前記ス
リップ開始荷重よりも負荷が大きいため、前記係合体
（27）がばね（28）に抗して第４ギヤ（87）側に移動し
ながら第３図に示す如く、伝動体（22）の係合凹部（22
c）から伝動体（22）の対向面に乗り上げることにな
る。このように係合体（27）が伝動体（22）の対向面に
乗り上げると、該係合体（27）と伝動体（22）とは点接
触することになってこれら係合体（27）と伝動体（22）
の係合凹部（22c）との係合抵抗がなくなることにな
る。この結果、前記第４ギヤ（87）と伝動体（22）との
間には、前記係合体（27）の前記伝動体（22）における
対向面への当接抵抗と、皿ばね（22）による前記第４ギ
ヤ（87）と伝動体（22）との摩擦対抗とが作用すること
になって、前記係合体（27）の前記対向面への乗り上げ
時における前記第４ギヤ（87）と伝動体（22）との伝達
トルクが前記スリップ開始荷重の設定時における伝達ト
ルク、換言すれば負荷トルクに較べて低下することにな
り、これにより、前記係合体（27）が伝動体（22）の前
記対向面に乗り上げた時には、直ちに、かつ一挙に大き
なスリップが発生し、捲上げが行なえなくなるのであ
る。尚、前記係合体（27）が対向面に乗り上げたとき、
前記ばね（28）の反発力が大きくなるため、前記皿ばね
（24）ねの押圧力が小さくなり、このため、前記第４ギ
ヤ（87）と伝動体（22）との摩擦抵抗は減少するのであ
る。Further, when a load having a load equal to or higher than the rated load is wound up, the load is larger than the slip start load, so that the engagement body (27) moves toward the fourth gear (87) side against the spring (28). As shown in FIG. 3, the engaging recesses (22
From c), you will ride on the facing surface of the transmission (22). When the engagement body (27) rides on the opposing surface of the transmission body (22) in this way, the engagement body (27) and the transmission body (22) come into point contact with each other and the transmission body and the transmission body (27) are transmitted. Body (22)
The engagement resistance with the engagement concave portion (22c) is eliminated. As a result, between the fourth gear (87) and the transmission body (22), the contact resistance of the engagement body (27) to the facing surface of the transmission body (22) and the disc spring (22). The frictional opposition between the fourth gear (87) and the transmission body (22) due to the action acts on the fourth gear (87) when the engagement body (27) rides on the facing surface. The transmission torque with the transmission body (22) is lower than the transmission torque when the slip start load is set, in other words, the load torque, whereby the engagement body (27) is transferred to the transmission body (22). When the vehicle rides on the facing surface, a large slip occurs immediately and at once, and the winding cannot be performed. When the engagement body (27) rides on the facing surface,
Since the repulsive force of the spring (28) increases, the pressing force of the disc spring (24) decreases, which reduces the frictional resistance between the fourth gear (87) and the transmission body (22). Of.
又、前記係合体（27）の前記対向面への乗り上げ時にお
ける伝達トルク減少値の設定は、前記皿ばね（24）によ
る前記伝動ギヤ（87）と伝動体（22）との摩擦抵抗値
と、ばね（28）による前記係合体（27）の係合凹部（22
c）との係合対抗値との割合を選択することにより行な
えるのであって、前記係合抵抗値の前記摩擦対抗値に対
する割合を大きくするほど前記伝達トルクを減少するこ
とができる。この場合、前記係合体（27）の前記対向面
への乗り上げに伴なう前記ばね（28）の反発力が前記皿
ばね（24）の押圧力よりも大きくなるように設定して前
記係合体（27）の前記対向面への乗り上げ時における前
記第４ギヤ（87）と伝動体（22）との摩擦抵抗値が零と
なるようにしてもよい。The reduction value of the transmission torque when the engagement body (27) rides on the facing surface is set by the friction resistance value between the transmission gear (87) and the transmission body (22) by the disc spring (24). , The engaging recess (22) of the engaging body (27) by the spring (28).
This can be done by selecting the ratio of the engagement resistance value to c), and the transmission torque can be reduced as the ratio of the engagement resistance value to the friction resistance value increases. In this case, the repulsive force of the spring (28) accompanying the riding of the engagement body (27) onto the facing surface is set to be larger than the pressing force of the disc spring (24). The frictional resistance value between the fourth gear (87) and the transmission body (22) when the (27) rides on the facing surface may be zero.
以上の実施例では、過負荷調整ナット（23）をギヤケー
ス（80）に内蔵する構成としたけれども、この他、ギヤ
ケース（80）の外部に前記調整ナット（23）を配置し
て、ギヤケース（80）を取外すことなく摩擦抵抗の調整
が簡素容易に行なえるようにしてもよい。In the above embodiments, the overload adjusting nut (23) is built in the gear case (80). However, in addition to this, the adjusting nut (23) is arranged outside the gear case (80) to make the gear case (80). The frictional resistance may be simply and easily adjusted without removing.
この場合、例えば第５図に示す如く前記第３軸（86）の
スプライン部（86a）外側に、先端にねじ部（86b）をも
つ小径部（86c）を形成して、該小径部（86c）に皿ばね
（24）の押え体（31）を挿嵌支持すると共に、該押え体
（31）の外周を軸受（32）を介してギヤケース（80）に
支持させる一方、前記押え体（31）の外方端部を前記軸
受（32）、つまりギヤケース（80）よりも外方に延出
し、かつ、前記小径部（86c）の先端ねじ部（86b）に過
負荷調整ナット（23）を螺合することにより、前記ギヤ
ケース（80）外部からの前記調整ナット（23）の締付け
調整により前記押え体（31）、皿ばね（24）を介して伝
動体（29）を第４図ギヤ（87）側へ押付け、前記伝動体
（22）と第４ギヤ（87）との摩擦抵抗値を設定できるの
である。In this case, for example, as shown in FIG. 5, a small diameter portion (86c) having a screw portion (86b) at the tip is formed outside the spline portion (86a) of the third shaft (86), and the small diameter portion (86c ), The pressing body (31) of the disc spring (24) is inserted and supported, and the outer periphery of the pressing body (31) is supported by the gear case (80) via the bearing (32) while the pressing body (31 ) Extends outward from the bearing (32), that is, the gear case (80), and an overload adjustment nut (23) is attached to the tip screw portion (86b) of the small diameter portion (86c). By screwing, the transmission nut (23) is fixed to the gear nut (23) from the outside of the gear case (80) via the pressing body (31) and the disc spring (24) by the tightening adjustment of the adjusting nut (23). It is possible to set the frictional resistance value between the transmission body (22) and the fourth gear (87) by pressing it toward the 87) side.
尚、以上の実施例では、第４ギヤ（87）側に係合体（2
7）及びばね（28）を内装し、伝動体（22）に係合凹部
（22c）を形成したけれども、第４ギヤ（87）側に係合
凹部（22c）を形成し、伝動体（22）に係合体（27）及
びばね（28）を内装するようにしてもよいし、又、前記
受止体（21）は実質的に伝動体を構成するものであるか
ら、該受止体（伝動体）（21）と第４ギヤ（87）との間
に前記係合体（27）と係合凹部（22c）とから成る係合
抵抗手段を設けてもよい。さらに、前記過負荷防止装置
の取付位置についても何ら第３軸（86）の第４ギヤ（8
7）に限定されるものでなく、他の伝動軸の伝動ギヤに
取付けてもよいことは勿論である。In the above embodiment, the engaging body (2
Although the engagement recess (22c) is formed in the transmission body (22) by incorporating the 7) and the spring (28), the engagement recess (22c) is formed on the fourth gear (87) side and the transmission body (22) is formed. ), The engagement body (27) and the spring (28) may be incorporated, and since the receiving body (21) substantially constitutes a transmission body, the receiving body (21) Engagement resistance means composed of the engagement body (27) and the engagement recess (22c) may be provided between the transmission body (21) and the fourth gear (87). Further, regarding the mounting position of the overload prevention device, the fourth gear (8
It is needless to say that the invention is not limited to 7) and may be attached to a transmission gear of another transmission shaft.
（発明の効果） 以上の如く本発明は、伝動ギヤ（87）に伝動体（22）を
弾性部材により押圧して前記伝動ギヤ（87）と伝動体
（22）とに摩擦抵抗を与えるようにした過負荷防止装置
において、前記伝動ギヤ（87）と伝動体（22）との対向
面の一方に係合凹部（22c）を設け、他方に、前記係合
凹部（22c）に係合する係合体（27）と該係合体（27）
を前記係合凹部（22c）の方向に付勢するばね（28）と
を設け、前記伝動ギヤ（87）が伝動体（22）に対しスリ
ップするスリップ開始荷重を、前記伝動ギヤ（87）と伝
動体（22）との摩擦抵抗値と、前記係合体（27）の係合
凹部（22c）との係合抵抗値とのトータルで設定する如
くしたものであるから、荷物の捲上時、つまり荷物の地
切り動作時に、前記摩擦抵抗値と係合抵抗値とのトータ
ルで設定したスリップ荷重に対し僅かでも大きな負荷が
かゝると、前記係合体（27）がばね（28）に抗し伝動ギ
ヤ（87）又は伝動体（22）の係合凹部（22c）から外れ
て、前記伝動ギヤ（87）又は伝動体（22）の対向面に乗
り上げる如く移動し、この移動により前記係合体（27）
の係合凹部（22c）との係合抵抗がなくなり、つまり、
前記係合体（27）の前記対向面への当接抵抗と、該係合
体（27）の前記対向面への乗り上げに伴って減少する前
記伝動ギヤ（87）と伝動体（22）とによる摩擦抵抗とが
作用することになり、このため、これら当接抵抗と摩擦
抵抗とのトータルによるスリップ阻止荷重が前記スリッ
プ開始荷重に較べて低下することになり、この結果、前
記スリップ開始荷重と負荷との差が僅かであっても直ち
に、かつ一挙に大きなスリップが発生して捲上げが行な
えなくなり、これにより、従来のように過負荷の状態で
あるにも拘わらず、捲上げが行なわれ、宙吊り状態から
荷物が落下するといったことを確実になくし得るのであ
る。(Effects of the Invention) As described above, the present invention is designed to apply frictional resistance to the transmission gear (87) and the transmission body (22) by pressing the transmission body (22) to the transmission gear (87) with an elastic member. In the overload prevention device described above, an engagement recess (22c) is provided on one of the facing surfaces of the transmission gear (87) and the transmission body (22), and the other engages with the engagement recess (22c). Combined body (27) and the engagement body (27)
And a spring (28) for urging the gear in the direction of the engaging recess (22c), and a slip start load at which the transmission gear (87) slips with respect to the transmission body (22) is set to the transmission gear (87). Since the frictional resistance value with the transmission body (22) and the engagement resistance value with the engagement recess (22c) of the engagement body (27) are set in total, when the load is hoisted, That is, when the load is cut off, if the slip load set by the total of the friction resistance value and the engagement resistance value is slightly large, the engagement body (27) resists the spring (28). The transmission gear (87) or the transmission body (22) disengages from the engagement recess (22c) and moves so as to ride on the opposing surface of the transmission gear (87) or the transmission body (22). (27)
There is no engagement resistance with the engaging recess (22c), that is,
Contact resistance of the engagement body (27) to the facing surface, and friction between the transmission gear (87) and the transmission body (22) that decrease as the engagement body (27) rides on the facing surface. As a result, the resistance acts, and thus the slip prevention load due to the total of the contact resistance and the frictional resistance becomes lower than the slip start load. As a result, the slip start load and the load Even if the difference between the two is small, a large amount of slip occurs immediately and the winding cannot be performed. It is possible to surely prevent the luggage from falling from the state.
第１図は本発明に係る過負荷防止装置の実施例を示す要
部の縦断面図、第２図は調整ナットの弛み阻止板の正面
図、第３図は係合体の伝動体の対向面への乗り上げ状態
を示す説明図、第４図は本発明過負荷防止装置を適用し
た電動チェンブロックの縦断面図、第５図は過負荷防止
装置の他の実施例を示す要部の断面図である。 （５）……ロードシーブ （22）……伝動体 （22c）……係合凹部 （24）……皿ばね（弾性部材） （27）……係合体 （60）……駆動軸 （86）……伝動軸 （87）……伝動ギヤFIG. 1 is a vertical cross-sectional view of a main part showing an embodiment of an overload prevention device according to the present invention, FIG. 2 is a front view of a loosening prevention plate of an adjusting nut, and FIG. 3 is a surface of an engagement body facing a transmission body. FIG. 4 is a vertical sectional view of an electric chain block to which the overload prevention device of the present invention is applied, and FIG. 5 is a cross-sectional view of essential parts showing another embodiment of the overload prevention device. Is. (5) ...... Load sheave (22) ...... Transmission body (22c) ...... Engagement recess (24) ...... Disc spring (elastic member) (27) ...... Engagement body (60) ...... Drive shaft (86) ...... Transmission shaft (87) ...... Transmission gear
Claims (1)
（５）に伝達する捲上機における伝動軸（86）に、該伝
動軸（86）に遊嵌される伝動ギヤ（87）と前記伝動軸
（86）に軸方向のみ摺動可能に支持され、前記伝動ギヤ
（87）と摩擦接触する伝動体（22）とこの伝動体（22）
を前記伝動ギヤ（87）に押圧する弾性部材（24）とを備
えた過負荷防止装置において、前記伝動ギヤ（87）と伝
動体（22）との対向面の一方に係合凹部（22c）を設
け、他方に、前記係合凹部（22c）に係合する係合体（2
7）と該係合体（27）を前記係合凹部（22c）の方向に付
勢するばね（28）とを設け、前記伝動ギヤ（87）が伝動
体（22）に対しスリップするスリップ開始荷重を、前記
伝動ギヤ（87）と伝動体（22）との摩擦抵抗値と、前記
係合体（27）の係合凹部（22c）との係合抵抗値とのト
ータルで設定する如くしたことを特徴とする捲上機の過
負荷防止装置。1. A transmission gear (87) loosely fitted to a transmission shaft (86) of a hoisting machine for transmitting rotational power of a drive shaft (60) to a load sheave (5). A transmission body (22) supported by the transmission shaft (86) so as to be slidable only in the axial direction and in frictional contact with the transmission gear (87), and the transmission body (22).
And an elastic member (24) for pressing the transmission gear (87) against the transmission gear (87). In the overload prevention device, one of the facing surfaces of the transmission gear (87) and the transmission body (22) is engaged with a recess (22c). Is provided on the other side, and on the other side, an engaging body (2
7) and a spring (28) for urging the engagement body (27) in the direction of the engagement recess (22c), and a slip start load at which the transmission gear (87) slips with respect to the transmission body (22). Is set as a total of the friction resistance value between the transmission gear (87) and the transmission body (22) and the engagement resistance value between the engagement recess (22c) of the engagement body (27). Characteristic hoist overload prevention device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP28952486A JPH0712912B2 (en) | 1986-12-04 | 1986-12-04 | Overload prevention device for hoisting machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP28952486A JPH0712912B2 (en) | 1986-12-04 | 1986-12-04 | Overload prevention device for hoisting machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS63143199A JPS63143199A (en) | 1988-06-15 |
| JPH0712912B2 true JPH0712912B2 (en) | 1995-02-15 |
Family
ID=17744368
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP28952486A Expired - Fee Related JPH0712912B2 (en) | 1986-12-04 | 1986-12-04 | Overload prevention device for hoisting machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0712912B2 (en) |
-
1986
- 1986-12-04 JP JP28952486A patent/JPH0712912B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPS63143199A (en) | 1988-06-15 |
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| LAPS | Cancellation because of no payment of annual fees |