JPH0731090B2 - Torque limiter - Google Patents
Torque limiterInfo
- Publication number
- JPH0731090B2 JPH0731090B2 JP2133320A JP13332090A JPH0731090B2 JP H0731090 B2 JPH0731090 B2 JP H0731090B2 JP 2133320 A JP2133320 A JP 2133320A JP 13332090 A JP13332090 A JP 13332090A JP H0731090 B2 JPH0731090 B2 JP H0731090B2
- Authority
- JP
- Japan
- Prior art keywords
- gear
- load
- torque
- drive
- gears
- 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
Description
【発明の詳細な説明】 技術分野 本発明は、トルクリミッタ、より詳細には、歯車回転さ
れる負荷トルクを該負荷側歯車と駆動側歯車との間に回
転自在に軸承された中間歯車に作用する軸力からトルク
を測定するトルク計を利用したトルクリミッタに関す
る。Description: TECHNICAL FIELD The present invention relates to a torque limiter, and more particularly, to a load torque for rotating a gear, which acts on an intermediate gear rotatably supported between the load-side gear and a drive-side gear. The present invention relates to a torque limiter using a torque meter that measures torque from axial force.
従来技術 回転駆動される負荷のトルクを測定することは駆動軸の
駆動安全上も必要であり、また、エンジンの動力、船舶
の推進機の軸馬力の測定には欠かせないものである。ま
たバルブアクチュエータのように、閉弁に伴なう駆動停
止の検知手段としても利用され応用分野は枚挙できない
程である。トルクの測定には、駆動軸の捩り応力をスト
レンケージを用いて測定し、捩り応力に比例する値とし
てトルクを求めることが行われている。しかしストレン
ゲージの出力は小さく、しかも回転ひずみ出力を取り出
すためにスリップリングを使用しているので、その接触
ノイズは相対的に大きくSN比が劣化する等の問題があっ
た。また、ストレンケージを被側物体に貼着するとき、
絶縁抵抗が精度に大きく影響するので、特に屋外で使用
する場合絶縁処理に注意を要した。このようなトルクの
測定は精度の高いものであるが、通常は必ずしも高精度
である必要はなく、このために簡易なトルク計を利用し
たトルクリミッタ等が多く市販されている。2. Description of the Related Art Measuring the torque of a rotationally driven load is necessary for driving safety of a drive shaft, and is indispensable for measuring engine power and shaft horsepower of a propulsion device of a ship. Further, like the valve actuator, it is also used as a means for detecting the drive stop associated with the closing of the valve, and its application fields cannot be enumerated. To measure the torque, the torsional stress of the drive shaft is measured using a strain cage, and the torque is obtained as a value proportional to the torsional stress. However, the output of the strain gauge is small, and since the slip ring is used to take out the rotational strain output, the contact noise is relatively large and the SN ratio deteriorates. Also, when attaching the strain cage to the object on the side,
Since the insulation resistance has a great influence on the accuracy, attention was paid to the insulation treatment especially when used outdoors. Although such torque measurement is highly accurate, it does not necessarily have to be highly accurate, and for this reason, many torque limiters and the like using a simple torque meter are commercially available.
第６図に、一例としてトルクをばね力の変位に変換する
トルク計を利用したトルクリミッタ100の平面図を示
す。図において101は駆動軸101aに嵌着されるハブであ
り、駆動軸101aと共に回転する筒状体で底部に鍔101bを
有し、該鍔101bには直経上にピン穴101c,101cが穿孔さ
れており、一方のピン穴101cにはスプリング受け103の
ピン103aを嵌挿固定し、他方のピン穴101cにはドライブ
キー108がピン108aを軸として回動可能に緩挿されてい
る。102は負荷側の軸（図示せず）に固着されるハウジ
ングで、前記ハブ101とはトルクスプリング106,107およ
び円弧面で摺動可能なスプリングスライド104,105を介
して弾性的に接合されている。ａ図は無負荷回転または
静止状態のもので、溝102aに係止し、側面をトルクスプ
リング106,107により各々押圧されたスプリングスライ
ド104,105の端面でばね力により保持され接合してい
る。ｂ図はハブ101を矢印ｄ方向に回転駆動したとき、
負荷トルクがトルクスプリング106,107のばね力で設定
された値を越えた場合のもので、トルクスプリング106
に縮み、107は伸長し、ドライブキー108の端部は、溝10
2aから外れ、負荷側のハウジング102へのトルク伝達が
できずに空転する。FIG. 6 shows, as an example, a plan view of a torque limiter 100 using a torque meter that converts torque into displacement of spring force. In the figure, 101 is a hub fitted to the drive shaft 101a, which is a cylindrical body that rotates together with the drive shaft 101a and has a flange 101b at the bottom, and the flange 101b is provided with pin holes 101c and 101c directly above it. The pin 103a of the spring receiver 103 is fitted and fixed in one pin hole 101c, and the drive key 108 is loosely inserted in the other pin hole 101c so as to be rotatable about the pin 108a. Reference numeral 102 denotes a housing fixed to a load side shaft (not shown), which is elastically joined to the hub 101 via torque springs 106 and 107 and spring slides 104 and 105 which are slidable on circular arc surfaces. FIG. 5A shows a state of no load rotation or a stationary state, which is engaged with the groove 102a and is held and joined by the spring force by the end faces of the spring slides 104, 105 whose side faces are pressed by the torque springs 106, 107, respectively. Figure b shows when hub 101 is driven to rotate in the direction of arrow d.
When the load torque exceeds the value set by the spring force of the torque springs 106 and 107, the torque spring 106
Shrink, and 107 expands, and the end of drive key 108
It deviates from 2a, and the torque cannot be transmitted to the housing 102 on the load side, and it spins.
従来技術の問題点 以上に述べたトルクリミッタは、設定されたモーメント
以上の負荷となったとき負荷トルクを伝達するドライブ
キーの連結が解除され、設定値以上のトルクが伝達でき
ないようにする安全装置であるが、トルクを計測する手
段は、モーメントアーム一定条件において、トルクスプ
リングが接線力と平衡するトルクスプリングのたわみ量
を求めることであるが、このたわみ量はトライブキーの
連結を解除するのに必要な変位であるから、大きいトル
クを駆動軸に介装する場合は、適合するばね定数をもっ
た他のトルクスプリングと交換しなければならなかっ
た。また、軸径が大きくなると、トルクスプリングも大
きくなり、これに伴ってハウジング外径も大きくなり高
価となった。Problems of the prior art The torque limiter described above is a safety device that prevents the transmission of torque above the set value by disconnecting the drive key that transmits the load torque when the load exceeds the set moment. However, the means to measure the torque is to find the amount of deflection of the torque spring in which the torque spring balances the tangential force under a constant condition of the moment arm.This amount of deflection is used to release the connection of the tribe key. Because of the required displacement, if a large torque was to be placed on the drive shaft, it had to be replaced with another torque spring having a suitable spring constant. Further, as the shaft diameter becomes larger, the torque spring also becomes larger, and along with this, the housing outer diameter also becomes larger and it becomes expensive.
問題解決の手段 本発明は叙上の問題点を解決するためになされたもの
で、小形軽量でしかも簡単なトルク計により計測された
トルクに従って負荷側に伝達される駆動側の動力を遮断
するトルクリミッタを提供することを目的とするもので
ある。本発明の要旨とするものは、 1.負荷を回転駆動する負荷軸に固着された負荷側歯車
と、該負荷側歯車を駆動する駆動軸に固着された駆動側
歯車と、前記負荷側歯車に噛合する歯車および前記駆動
側歯車に噛合する歯車の２枚の歯車からなる中間歯車
と、これら２枚の歯車を回転可能に軸承し、何れか一方
の歯車を軸方向に移動可能に案内する中間軸と、該中間
軸上で前記２枚の歯車を軸方向に分離可能に支持し、常
時は、同軸に接合するクラッチと、前記中間歯車軸を前
記中間歯車の噛み合い接線方向に移動可能に固着した支
持手段と、前記負荷のトルクに比例して前記中間歯車の
噛み合い接線方向に作用する力と釣り合うばね力を前記
支持手段に与えるばね手段と、前記支持手段の変位を前
記移動可能な中間歯車の軸方向の変位に変換するリンク
機構とからなり、前記負荷のトルクが所定値を越えたと
き前記リンク機構を介して前記クラッチの接合を解き、
前記負荷側歯車に前記駆動歯車の駆動力を伝達しないよ
うにしたこと、 2.前記１において、前記支持手段の移動を検出する検知
手段を有し、前記支持手段の移動量が所定値に達したと
き前記駆動側歯車を駆動する駆動源を遮断すること、 を特徴とするトルクリミッタである。Means for Solving the Problem The present invention has been made to solve the above problems, and is a torque that cuts off the drive side power transmitted to the load side according to the torque measured by a small, lightweight and simple torque meter. The purpose is to provide a limiter. The gist of the present invention is: 1. a load-side gear fixed to a load shaft that rotationally drives a load, a drive-side gear fixed to a drive shaft that drives the load-side gear, and the load-side gear. An intermediate gear consisting of two gears of a gear that meshes with the gear on the driving side and a gear that meshes with the drive side gear, and an intermediate gear that rotatably supports these two gears and guides one of the gears to be movable in the axial direction. A shaft and a clutch that supports the two gears on the intermediate shaft so as to be separable in the axial direction, and is always coaxially joined, and the intermediate gear shaft is movably fixed in the tangential direction in which the intermediate gear meshes with the intermediate gear. Supporting means, spring means for imparting to the supporting means a spring force that balances with the force acting in the meshing tangential direction of the intermediate gear in proportion to the torque of the load, and the intermediate gear capable of moving the displacement of the supporting means. Convert to axial displacement of Consists of a link mechanism, solving bonding of the clutch via the link mechanism when the torque of the load exceeds a predetermined value,
2. The driving force of the drive gear is not transmitted to the load-side gear. 2. In the above 1, the detection means for detecting the movement of the support means is provided, and the movement amount of the support means reaches a predetermined value. When this is done, the drive source that drives the drive-side gear is shut off, and the torque limiter.
実 施 例 第１図は、本発明に使用されるトルク計についての原理
説明図である。１は固定されたモータ等駆動源の軸O1に
嵌着された半径γ３の第１歯車におけるピッチ曲線（以
下の歯車もすべて同様にピッチ曲線で図示する。）を示
すもので、駆動歯車となるものである。21は第１歯車１
と噛合する半径γ２の第２の歯車であり、図においてて
は半径γ１の歯車22と同軸O2で一体をなす段歯車で軸O2
に対して回転可能に軸承される。また軸O2は、該軸O2に
垂直な噛み合い接線方向に変位できるように支持されて
いる。３は軸O3を介してトルク負荷を回転駆動する半径
Ｒの第３の歯車で、第３の歯車３と軸O3とは固着され、
軸O3は回転可能に軸承される。即ち、該第３歯車は被駆
動の負荷側歯車である。各々の軸O1,O2,O3は同一線上に
配置されない場合でも微小範囲でトルク測定が可能であ
るが、後述のごとく一直線上Ｘ−Ｘ上に配列された場合
は測定感度は最も高くなる。いま負荷トルクを−Ｍとし
第３歯車O3を矢印Ｄ方向の回軸とした場合について説明
すると、駆動力として軸O3には反力としてのモーメント
Ｍが必要である。モーメントＭは、第３歯車３と噛合す
る第２の歯車22の噛合位置Ｂにおいて軸Ｘ−Ｘに垂直な
噛み合い接線方向の接線力をＦ′（点線で示す）とする
と Ｍ＝Ｆ′Ｒ （１） であり第２歯車22は反力Ｐ（実線で示す）を受ける。こ
れから（２）式が得られる。Practical Example FIG. 1 is a principle explanatory view of a torque meter used in the present invention. Reference numeral 1 denotes a pitch curve of the first gear of radius γ 3 fitted to the shaft O 1 of the drive source such as a fixed motor (all the following gears are also shown by the pitch curve). It will be. 21 is the first gear 1
Meshes with a second gear radius gamma 2, the axis O 2 by gear wheels forming the integral radius gamma 1 gear 22 coaxial O 2 is in FIG.
Is rotatably supported with respect to. The axis O 2 is supported so as to be displaceable in the tangential direction perpendicular engagement to the axis O 2. Reference numeral 3 denotes a third gear having a radius R for rotationally driving a torque load via the shaft O 3 , and the third gear 3 and the shaft O 3 are fixed to each other,
The axis O 3 is rotatably supported. That is, the third gear is a driven load-side gear. Even if the axes O 1 , O 2 and O 3 are not arranged on the same line, the torque can be measured in a very small range, but if they are arranged on a straight line XX as described later, the measurement sensitivity is the highest. Become. Now, a case where the load torque is −M and the third gear O 3 is a rotating shaft in the direction of arrow D will be described. A moment M as a reaction force is required for the shaft O 3 as a driving force. Moment M is M = F'R (where tangential force in the meshing tangential direction perpendicular to the axis XX at the meshing position B of the second gear 22 meshing with the third gear 3 is F '(shown by the dotted line). 1) and the second gear 22 receives the reaction force P (shown by the solid line). Equation (2) is obtained from this.
次に第２歯車21,22のモーメントについて考えると負荷
側の第２歯車22と駆動側の歯車21とが受けるモーメント
ｍは等しいから、第１歯車１と第２歯車21との噛合位置
Ａにおいて軸Ｘ−Ｘに垂直な噛み合い接線方向の接線力
ｆ（実線で示す）とすると（３）式が得られる。 Next, considering the moments of the second gears 21 and 22, since the moment m received by the load-side second gear 22 and the drive-side gear 21 is equal, at the meshing position A between the first gear 1 and the second gear 21. If the tangential force f (shown by the solid line) in the meshing tangential direction perpendicular to the axis XX is given by the equation (3).
ｍ＝γ1F＝γ2f （３） 軸O2には駆動側の接線力ｆと負荷側の反力Ｆとが作用す
るから（２），（３）式より となり、R,γ1,γ２は各々既知であるから（４）式よ
り、モーメントＭを第２歯車21,22の軸O2に作用する軸
力から検知することができる。各々の軸が一直線上にな
い一般の場合は、接線力F,fのベクトル和として作用す
るので直線上に配置された場合よりも小さくなる。尚、
図においては、第２歯車を21,22の段歯車として説明し
たが１枚の場合、複数の中間歯車が配設される場合にも
成立する。叙上の如く、軸O2にはモーメントＭに比例し
た軸力が作用するので、軸O2を変位可能に支持して力Ｆ
＋ｆ＝Ｐを検知すればモーメントＭが測定される。しか
も第１歯車１と第２歯車21が噛合い、更に第２歯車22と
第３歯車３が噛み合う２段歯車列であるから小形で大き
い減速比が得られる。m = γ 1 F = γ 2 f (3) Since the tangential force f on the drive side and the reaction force F on the load side act on the axis O 2 , from equations (2) and (3) Since R, γ 1 and γ 2 are already known, the moment M can be detected from the axial force acting on the shaft O 2 of the second gears 21 and 22 from the equation (4). In the general case where each axis is not on a straight line, it acts as a vector sum of the tangential forces F and f, and therefore becomes smaller than when they are arranged on a straight line. still,
In the figure, the second gear has been described as 21, 22 stepped gears, but the case of one sheet is also applicable when a plurality of intermediate gears are arranged. As the ordination, since axial force proportional to the moment M in the axis O 2 is applied, the force and displaceably supports a shaft O 2 F
When + f = P is detected, the moment M is measured. Moreover, since the first gear 1 and the second gear 21 mesh with each other, and the second gear 22 and the third gear 3 mesh with each other, the gear is a two-stage gear train, so that a small and large reduction ratio can be obtained.
第２図は、軸力Ｆ＋ｆを測定してモーメントＭを検知す
る例を示すもので各々の歯車は第１図と同一で同一の符
号を付す。（以下の例も同様）図において４は、軸O2に
垂直な噛み合い接線方向に軸力を伝達するバーで固定位
置10に固定されたガイド5,5で矢印Ｐ方向のみ変位させ
るもので、図示のように摺動するようにしてもよく、一
辺をバー４の軸に沿って固着した板ばね等で弾性的に支
持してもよい。バー４の他端41と固定点10との間には初
期値のたわみδのばね10を配設しＰ方向への変位量の変
化ΔδからモーメントＭを求めるものである。FIG. 2 shows an example in which the axial force F + f is measured to detect the moment M. Each gear is the same as in FIG. 1 and is given the same reference numeral. (The same applies to the following examples.) In FIG. 4, reference numeral 4 denotes a bar that transmits axial force in a meshing tangential direction perpendicular to the axis O 2 and displaces only in the arrow P direction by guides 5 and 5 fixed at a fixed position 10. It may be slid as shown, or may be elastically supported on one side by a leaf spring or the like fixed along the axis of the bar 4. Between the other end 41 of the bar 4 and the fixed point 10, a spring 10 having an initial deflection δ is provided, and the moment M is obtained from the change Δδ in the displacement amount in the P direction.
第３図は、モーメントＭを検知する他の例で、第２図の
計測ばね６に替えて計測板ばね８の固定位置10で片持支
持し、該計測板ばね８の矢印Ｐ又は反対方向Ｐ′の力を
支持位置近傍の両面に貼着されたひずみゲージ82および
83のひずみ量の変化から正逆両方向のモーメントＭを測
定するものである。尚、動点81は軸O2に固定されてい
る。FIG. 3 shows another example of detecting the moment M, which is cantilevered at a fixed position 10 of the measuring leaf spring 8 instead of the measuring spring 6 of FIG. The force of P ′ is applied to both sides of the strain gauge 82 near the supporting position and
The moment M in both forward and reverse directions is measured from the change in the strain amount of 83. The moving point 81 is fixed to the axis O 2 .
第４図は、軸力Ｐを圧力の変化からモーメントＭを検知
する他の実施例で７は油圧シリンダである。71はピスト
ンで、バー４とは端部41においてピストンロッド42に連
結されており、圧力の変化を圧力計73で読みとられ、現
場読取に利用される。FIG. 4 shows another embodiment in which the moment M is detected from the change of the axial force P from the pressure change, and 7 is a hydraulic cylinder. Reference numeral 71 denotes a piston, which is connected to the piston rod 42 at the end 41 with the bar 4, and the change in pressure is read by the pressure gauge 73 and used for on-site reading.
第５図は、本発明によるトルクリミッタで、（ａ）図は
側断面図、（ｂ）図は（ａ）図の矢視Ｘ−Ｘ断面図であ
る。図において11は基台で、摺動バー41を矢印Ｐ方向に
変位できるように、例えば溝44に嵌挿されたピン13,13
で案内される。ピン13,13は矢印Ｐ方向からみてコの字
形の位置決め部材12により摺動バー41が摺動できる程度
の僅かな隙を保つように基台11に螺着される。摺動バー
41は、一端をコの字形に開口して軸O2の両端を固着し、
開口部に中間歯車となる２枚の第２歯車21,22をベアリ
ング29,29により回転可能で何れか一方の第２歯車（図
においては第２歯車22）が軸O2方向に移動可能に軸承さ
れている。第２歯車21と、22とは、常時、例えば、軸方
向に微小変位して着脱する板状のクラッチ23により係止
されている。45は第２歯車21を回転自在に支えるスラス
トベアリングである。第２歯車22とクラッチ23との間に
は凹環部221が設けられ該凹環部221には、固定ピン90ま
わり矢印θ方向に回転するＬ金具９の腕91端部に配設さ
れたローラ93,93が当接している。Ｌ金具９の他端92に
はマイクロスイッチ94が当接し矢印θ方向の回転により
作動する。Ｌ金具９は軸力（Ｆ＋ｆ）により移動する第
２歯車21,22を支持する摺動バー41の移動を第２歯車22
の軸O2方向の移動に変換するリンク機構をなすもので常
時摺動バー41に固着したピン42で位置決めされ、ばね43
によりピン42と離間しないように押圧されている。摺動
バー41の他端側には板ばね61を収納する円筒室412が設
けられている。板ばね61は、前記円筒室412内面で摺動
する鍔部を配設した押え金具413により保持され圧力設
定ねじ14を回動してボール15を介して均一に板ばね61を
押圧し初期荷重を設定する。この時摺動バー41は肩部41
5が基台11に当接して板ばね61を受けている。前記、初
期荷重は、負荷の許容トルクに相当するもので、初期荷
重に達するまでの軸荷重P0範囲内では摺動バー41は移動
せず第２歯車21,22はクラッチ23により連結し、図示し
ない駆動側の第１歯車１からの動力を負荷駆動側の歯車
３に回転を伝達し続ける。負荷トルクが設定荷重を越え
ると摺動バー41は矢印Ｐ方向に移動を開始し、これに従
ってＬ字金具９は、ピン42に押圧され軸90まわりに矢印
θ方向に回転し、ローラ93により第２歯車22を軸方向に
押上げクラッチ23の接合を外し第３歯車３への動力伝達
を解く。更にまたマイクロスイッチの電気スイッチを閉
路し警報を発するとか、モータ（図示せず）の駆動を停
止する等の安全操作が行われる。FIG. 5 is a torque limiter according to the present invention, FIG. 5A is a side sectional view, and FIG. 5B is a sectional view taken along the line XX in FIG. In the figure, 11 is a base, for example, pins 13 and 13 fitted in the groove 44 so that the sliding bar 41 can be displaced in the arrow P direction.
Will be guided in. The pins 13 and 13 are screwed to the base 11 so as to maintain a slight clearance such that the sliding bar 41 can slide by the U-shaped positioning member 12 when viewed from the arrow P direction. Sliding bar
41 has one end opened in a U-shape and fixed at both ends of the axis O 2 .
Two second gears 21 and 22, which are intermediate gears, can be rotated in the opening by bearings 29 and 29, and either one of the second gears (second gear 22 in the figure) can move in the direction of the axis O 2. It is supported. The second gears 21 and 22 are always locked by, for example, a plate-like clutch 23 that is slightly displaced in the axial direction to be attached / detached. Reference numeral 45 is a thrust bearing that rotatably supports the second gear 21. A concave ring portion 221 is provided between the second gear 22 and the clutch 23, and the concave ring portion 221 is arranged at the end of the arm 91 of the L fitting 9 that rotates around the fixing pin 90 in the arrow θ direction. The rollers 93, 93 are in contact with each other. A micro switch 94 comes into contact with the other end 92 of the L fitting 9 and operates by rotating in the direction of the arrow θ. The L fitting 9 allows the sliding bar 41 that supports the second gears 21 and 22 that move by the axial force (F + f) to move the second gear 22.
It forms a link mechanism for converting the movement of the shaft in the direction of O 2 and is always positioned by a pin 42 fixed to a sliding bar 41 and a spring 43.
Is pressed by the pin 42 so that it is not separated from the pin 42. A cylindrical chamber 412 for accommodating the leaf spring 61 is provided on the other end side of the sliding bar 41. The leaf spring 61 is held by a holding metal fitting 413 provided with a flange portion that slides on the inner surface of the cylindrical chamber 412, and the pressure setting screw 14 is rotated to uniformly push the leaf spring 61 through the ball 15 to thereby obtain an initial load. To set. At this time, the sliding bar 41 is
5 contacts the base 11 to receive the leaf spring 61. The initial load corresponds to the allowable torque of the load, the sliding bar 41 does not move within the axial load P 0 range until reaching the initial load, and the second gears 21 and 22 are connected by the clutch 23, Power from the drive-side first gear 1 (not shown) is continuously transmitted to the load-drive-side gear 3 for rotation. When the load torque exceeds the set load, the sliding bar 41 starts moving in the direction of arrow P, and accordingly, the L-shaped metal fitting 9 is pressed by the pin 42 and rotates around the shaft 90 in the direction of arrow θ, and is moved by the roller 93 by the roller 93. The 2nd gear 22 is pushed up in the axial direction, the clutch 23 is disengaged, and the power transmission to the 3rd gear 3 is released. Furthermore, a safety operation such as closing the electric switch of the micro switch to issue an alarm or stopping driving of a motor (not shown) is performed.
効果 以上述べたように、本発明のトルクリミッタによれば、
各々軸位置の定まった駆動側歯車と負荷側歯車との間に
駆動側歯車と噛合する歯車と負荷側歯車と噛合する歯車
とからなる中間歯車を中間歯車軸に軸承したトルク計を
利用し、該中間歯車軸に垂直な方向に使用する軸力を測
定するという簡単で小形な構成により負荷のトルクに従
って負荷側への動力伝達を遮断するモーメントリミッタ
を提供できる。Effect As described above, according to the torque limiter of the present invention,
Utilizing a torque meter in which an intermediate gear consisting of a gear that meshes with the drive gear and a gear that meshes with the load gear is supported between the drive gear and the load gear each having a fixed axial position on the intermediate gear shaft, It is possible to provide a moment limiter that cuts off the power transmission to the load side according to the torque of the load with a simple and small structure in which the axial force used in the direction perpendicular to the intermediate gear shaft is measured.
第１図は、本発明に使用されるトルク計の原理説明図、
第2,3,4図は、図１の原理を用いてモーメントを検出す
る例を説明するための図、第５図は、本発明による多重
トルクリミッタの実施例を説明するための図、第６図
は、従来のトルク計を応用したトルクリミッタを説明す
るための図である。 １……第１歯車（駆動側）、21,22……第２歯車、３…
…第３歯車（負荷側）、４……バー、５……ガイド、６
……計測板ばね、７……油圧シリンダ、８……計測板ば
ね。FIG. 1 is an explanatory view of the principle of a torque meter used in the present invention,
2, 3 and 4 are views for explaining an example of detecting a moment using the principle of FIG. 1, and FIG. 5 is a view for explaining an embodiment of a multiple torque limiter according to the present invention. FIG. 6 is a diagram for explaining a torque limiter to which a conventional torque meter is applied. 1 ... 1st gear (driving side), 21, 22 ... 2nd gear, 3 ...
... 3rd gear (load side), 4 ... Bar, 5 ... Guide, 6
…… Measurement leaf spring, 7 …… hydraulic cylinder, 8 …… Measurement leaf spring.
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 昭58−189535（ＪＰ，Ａ) 特開 昭60−35233（ＪＰ，Ａ) 特開 昭52−9479（ＪＰ，Ａ) 特開 昭56−66719（ＪＰ，Ａ) 実開 昭59−118845（ＪＰ，Ｕ) 実開 昭58−59431（ＪＰ，Ｕ) 実開 昭56−157453（ＪＰ，Ｕ) 特公 昭60−29028（ＪＰ，Ｂ１) ─────────────────────────────────────────────────── ─── Continuation of the front page (56) Reference JP-A-58-189535 (JP, A) JP-A-60-35233 (JP, A) JP-A-52-9479 (JP, A) JP-A-56- 66719 (JP, A) Actual Open Sho 59-118845 (JP, U) Actual Open Sho 58-59431 (JP, U) Actual Open Sho 56-157453 (JP, U) Japanese Patent Sho 60-29028 (JP, B1)
Claims (2)
荷側歯車と、該負荷側歯車を駆動する駆動軸に固着され
た駆動側歯車と、前記負荷側歯車に噛合する歯車および
前記駆動側歯車に噛合する歯車の２枚の歯車からなる中
間歯車と、これら２枚の歯車を回転可能に軸承し、何れ
か一方の歯車を軸方向に移動可能に案内する中間軸と、
該中間軸上で前記２枚の歯車を軸方向に分離可能に支持
し、常時は、同軸に接合するクラッチと、前記中間歯車
軸を前記中間歯車の噛み合い接線方向に移動可能に固着
した支持手段と、前記負荷のトルクに比例して前記中間
歯車の噛み合い接線方向に作用する力と釣り合うばね力
を前記支持手段に与えるばね手段と、前記支持手段の変
位を前記移動可能な中間歯車の軸方向の変位に変換する
リンク機構とからなり、前記負荷のトルクが所定値を越
えたとき前記リンク機構を介して前記クラッチの接合を
解き、前記負荷側歯車に前記駆動歯車の駆動力を伝達し
ないようにしたことを特徴とするトルクリミッタ。1. A load-side gear fixed to a load shaft for rotationally driving a load, a drive-side gear fixed to a drive shaft for driving the load-side gear, a gear meshing with the load-side gear, and the drive. An intermediate gear consisting of two gears of gears that mesh with the side gears, and an intermediate shaft that rotatably supports these two gears and guides one of the gears to be movable in the axial direction,
A clutch that supports the two gears so as to be separable in the axial direction on the intermediate shaft, and that is always fixed coaxially to the clutch, and a supporting means that fixes the intermediate gear shaft so as to be movable in a tangential direction of meshing with the intermediate gear. A spring means for giving to the supporting means a spring force that balances the force acting in the meshing tangential direction of the intermediate gear in proportion to the torque of the load, and the displacement of the supporting means in the axial direction of the movable intermediate gear. Link mechanism for converting the displacement of the drive gear to prevent the driving force of the drive gear from being transmitted to the load side gear when the torque of the load exceeds a predetermined value. Torque limiter characterized by
有し、前記支持手段の移動量が所定値に達したとき前記
駆動側歯車を駆動する駆動源を遮断することを特徴とす
る請求項１に記載のトルクリミッタ。2. A detection means for detecting the movement of the support means, wherein a drive source for driving the drive-side gear is shut off when the movement amount of the support means reaches a predetermined value. The torque limiter according to Item 1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2133320A JPH0731090B2 (en) | 1990-05-22 | 1990-05-22 | Torque limiter |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2133320A JPH0731090B2 (en) | 1990-05-22 | 1990-05-22 | Torque limiter |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0427834A JPH0427834A (en) | 1992-01-30 |
| JPH0731090B2 true JPH0731090B2 (en) | 1995-04-10 |
Family
ID=15101945
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2133320A Expired - Lifetime JPH0731090B2 (en) | 1990-05-22 | 1990-05-22 | Torque limiter |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0731090B2 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4391576B1 (en) * | 2008-11-19 | 2009-12-24 | 株式会社オーバル | Torque limiter and valve actuator |
| KR101306639B1 (en) * | 2009-06-10 | 2013-09-10 | 닛또 세이꼬 가부시키가이샤 | Torque sensor |
| TWI573994B (en) * | 2015-10-06 | 2017-03-11 | Prodrives & Motions Co Ltd | A torque sensing device and a rotary drive tool incorporating a torque sensing device |
| KR102352326B1 (en) * | 2019-06-20 | 2022-01-18 | 주식회사프라임 | Rotary washing system |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS529479A (en) * | 1975-07-07 | 1977-01-25 | Haaku Inc | Torque measuring device for gear train |
| JPS5666719A (en) * | 1979-11-05 | 1981-06-05 | Yasuda Seisakusho:Kk | Detector for delivered power |
| JPS56157453U (en) * | 1980-04-25 | 1981-11-24 | ||
| JPS58189535A (en) * | 1982-04-30 | 1983-11-05 | Nissan Motor Co Ltd | Measuring method of torque |
| JPS6029028A (en) * | 1983-07-22 | 1985-02-14 | Seiko Epson Corp | High speed analog-digital converting circuit |
| JPS6035233A (en) * | 1983-08-06 | 1985-02-23 | Kataoka Kikai Seisakusho:Kk | Torque detecting method and winding torque detecting device |
| JPH032042Y2 (en) * | 1986-09-25 | 1991-01-21 |
-
1990
- 1990-05-22 JP JP2133320A patent/JPH0731090B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0427834A (en) | 1992-01-30 |
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