JP2008170010A - Power transmission device provided with torque limiter - Google Patents

Power transmission device provided with torque limiter Download PDF

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Publication number
JP2008170010A
JP2008170010A JP2008053701A JP2008053701A JP2008170010A JP 2008170010 A JP2008170010 A JP 2008170010A JP 2008053701 A JP2008053701 A JP 2008053701A JP 2008053701 A JP2008053701 A JP 2008053701A JP 2008170010 A JP2008170010 A JP 2008170010A
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rotating shaft
torque limiter
power transmission
transmission device
shaft
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Tsukumo Mizoguchi
九十九 溝口
Takamasa Miyazaki
貴征 宮崎
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SHINDENSHA KK
Tsukasa Electric Co Ltd
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SHINDENSHA KK
Tsukasa Electric Co Ltd
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Priority to JP2008053701A priority Critical patent/JP2008170010A/en
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Abstract

<P>PROBLEM TO BE SOLVED: To increase designing flexibility of a power transmission device having a gear wheel row and provided with a torque limiter, and to attain cost reduction of the power transmission device provided with the torque limiter. <P>SOLUTION: The torque limiter is constituted by inserting and fitting a cylinder body part applied with slitting of a second rotation shaft 31 press-fitted with an annular spring 41 having a part cut in an axial direction and outwardly biased to a first rotation shaft 21 having a hollow part, and the torque limiter is fixed to the gear positioned at an end of power transmission of the power transmission device having the gear wheel row. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

本発明は、歯車の輪列を有する動力伝達装置に係わり、特にトルクを所定の値以下に制限するトルク・リミッタを備えた動力伝達装置に関するものである。   The present invention relates to a power transmission device having a gear train, and more particularly to a power transmission device including a torque limiter that limits a torque to a predetermined value or less.

複数個の歯車を組み合わせた減速装置は、自動販売機、ATM、カーテン開閉機構等において、モータの回転力を駆動すべき対象機器(以下、負荷機器という。)に所定の回転数とトルクで伝達するために広く用いられている。このような減速装置においては、モータの回転が付与される入力回転軸に対して、出力回転軸には、大きなトルクが発生するため、何らかの理由により負荷に過大なトルクが印加され、負荷装置、減速装置内の歯車の破損、あるいは入力側のモータの焼き付き等不測の事故が発生する。   A reduction gear combined with a plurality of gears is transmitted to a target device (hereinafter referred to as a load device) to drive the rotational force of a motor at a predetermined rotational speed and torque in a vending machine, ATM, curtain opening / closing mechanism, etc. It is widely used to In such a reduction gear, since a large torque is generated in the output rotation shaft with respect to the input rotation shaft to which the rotation of the motor is applied, an excessive torque is applied to the load for some reason. Unexpected accidents such as damage to the gears in the reduction gear or seizure of the motor on the input side may occur.

このような不測の事故の発生を防止するためには、減速装置の出力回転軸に付与するトルク耐力を所定の値以下に制限する必要がある。このような機能を備えた従来の減速装置としては、減速装置を構成する複数段の歯車の軸の一つに、皿バネを用いたトルク・リミッタを備えたものが知られている。皿バネを用いた典型的なトルク・リミッタは、2枚の摩擦板で回転軸に遊嵌された平歯車を挟む構造を有する。一方の摩擦板は回転軸と一体化されるが、他方の摩擦板は回転軸に対し非回転であるが回転軸に平行に移動できる。上記、他方の摩擦板は皿バネによって平歯車に圧接し、平歯車は一方の摩擦板とも圧接する。ここで、皿バネのバネ圧は、回転軸に圧入する、平歯車側と反対の側を押さえるための押さえ環等の回転軸方向の位置によって定まる。   In order to prevent the occurrence of such an unexpected accident, it is necessary to limit the torque resistance applied to the output rotation shaft of the reduction gear to a predetermined value or less. As a conventional speed reducer having such a function, one having a torque limiter using a disc spring on one of the shafts of a plurality of gears constituting the speed reducer is known. A typical torque limiter using a disc spring has a structure in which a spur gear loosely fitted on a rotating shaft is sandwiched between two friction plates. One friction plate is integrated with the rotating shaft, but the other friction plate is non-rotating with respect to the rotating shaft but can move parallel to the rotating shaft. The other friction plate is pressed against the spur gear by a disc spring, and the spur gear is also pressed against one of the friction plates. Here, the spring pressure of the disc spring is determined by the position in the direction of the rotating shaft such as a presser ring for pressing the side opposite to the spur gear side that is press-fitted into the rotating shaft.

このような構成により、平歯車の負荷が過大になると、一方の摩擦板と平歯車との間および他方の摩擦板と平歯車との間でスリップが生じ、回転軸に遊嵌された平歯車に伝達されるトルクが制限される。   With such a configuration, when the load of the spur gear becomes excessive, slip occurs between one friction plate and the spur gear and between the other friction plate and the spur gear, and the spur gear is loosely fitted to the rotating shaft. The torque transmitted to is limited.

しかし、上述したような従来の皿バネを用いたトルク・リミッタにおいては、摩擦板および皿バネの直径はこれらを装着する回転軸の直径より大きくなることから、動力伝達装置に装填する場合、装填場所に制約があった。また、平歯車は摩擦板等の直径より大きいものでなければならならない。すなわち、皿バネを用いたトルク・リミッタを備えた動力伝達装置では、設計自由度が小さかった。   However, in the torque limiter using the conventional disc spring as described above, the diameter of the friction plate and the disc spring is larger than the diameter of the rotating shaft on which the friction plate and the disc spring are mounted. There were restrictions on the location. The spur gear must be larger than the diameter of the friction plate or the like. In other words, the power transmission device provided with a torque limiter using a disc spring has a low degree of design freedom.

さらに、皿バネを用いたトルク・リミッタを備えた動力伝達装置においては部品点数が多く、そのために組み立が煩雑であり、工数も多くコストが高かった。   Furthermore, the power transmission device provided with a torque limiter using a disc spring has a large number of parts, which makes it difficult to assemble, increases the number of steps, and increases the cost.

本発明は、上記の従来の問題点に鑑みてなされたもので、設計自由度が大きく、低コスト化が可能であるトルク・リミッタを備えた減速装置あるいは増速装置としての動力伝達装置を提供することを目的とするものである。   The present invention has been made in view of the above-described conventional problems, and provides a power transmission device as a speed reducer or speed increasing device provided with a torque limiter that has a high degree of design freedom and can be reduced in cost. It is intended to do.

本出願にかかる発明の動力伝達装置は、同芯状の中空部が設けられた第1の回転軸と、この第1の回転軸の前記中空部の内径とほぼ同一の外径を有し、端部からすり割り加工が施された円筒体部分を有する第2の回転軸と、この第2の回転軸の前記円筒体部分内に収納され、前記円筒体部分の内径を拡大するように付勢する弾性部材とを有し、この弾性部材が収納された前記第2の回転軸の円筒体部分を前記第1の回転軸の中空部に圧入した構造を有するトルク・リミッタと、入力回転軸および出力回転軸を備え、前記入力回転軸に付与された回転力を前記出力回転軸に歯車を介して伝達する複数段の回転軸からなる歯車機構と、これらの歯車機構の少なくも1段を構成する前記回転軸として前記トルク・リミッタが装着された動力伝達装置であって、前記第2の回転軸の前記円筒体部分の前記すり割り加工が施された端部には、この回転軸の外径よりも大きな外形を有する径大部が設けられ、前記第2の回転軸の円筒体部分を前記第1の回転軸の中空部に圧入したとき、前記円筒体部端部の径大部が前記第1の回転軸の端部から突出して繋止されるように構成されていることを特徴とするものである。   The power transmission device of the invention according to the present application has a first rotating shaft provided with a concentric hollow portion, and an outer diameter substantially the same as the inner diameter of the hollow portion of the first rotating shaft, A second rotating shaft having a cylindrical portion that has been slotted from the end, and the second rotating shaft is housed in the cylindrical portion of the second rotating shaft, and is attached so as to increase the inner diameter of the cylindrical portion. A torque limiter having a structure in which a cylindrical portion of the second rotating shaft in which the elastic member is housed is press-fitted into a hollow portion of the first rotating shaft, and an input rotating shaft And a gear mechanism comprising a plurality of rotary shafts for transmitting the rotational force applied to the input rotary shaft to the output rotary shaft via a gear, and at least one of these gear mechanisms. A power transmission device in which the torque limiter is mounted as the rotating shaft And the large diameter part which has an outer shape larger than the outer diameter of this rotating shaft is provided in the edge part by which the said slot process of the said cylindrical body part of the said 2nd rotating shaft was given, The said 2nd When the cylindrical portion of the rotating shaft is press-fitted into the hollow portion of the first rotating shaft, the large diameter portion of the end portion of the cylindrical body protrudes from the end portion of the first rotating shaft and is locked. It is comprised by these.

本発明によれば、動力伝達装置に複数本ある回転軸のいずれにも本発明のトルク・リミッタを装填することができるため、制限すべきトルク値を容易に設定することが可能となる。   According to the present invention, since the torque limiter of the present invention can be loaded on any of a plurality of rotating shafts in the power transmission device, the torque value to be limited can be easily set.

また、本発明におけるトルク・リミッタは、動力伝達装置における回転軸内に収納することができ極めて小型にできるため、かかるトルク・リミッタを装着した動力伝達装置全体の設計自由度が大きく、小型化に大きく貢献することができる。さらに、トルク・リミッタを備えた減速装置の低コスト化に貢献することができる。   In addition, since the torque limiter according to the present invention can be housed in the rotating shaft of the power transmission device and can be made extremely small, the design flexibility of the entire power transmission device equipped with such a torque limiter is large, and the size can be reduced. It can contribute greatly. Furthermore, it can contribute to the cost reduction of the speed reducer provided with the torque limiter.

以下、本発明の実施形態について図面を用いて説明する。   Hereinafter, embodiments of the present invention will be described with reference to the drawings.

図1は本発明を3段の歯車機構からなる減速装置に適用した実施形態を示す。モータからの動力は入力回転軸11に固着され、歯の数がmであるモータピニオン12を介して第1段歯車機構の回転軸13aに固着され歯の数がnである平歯車14aに伝えられる。ここで、減速装置の場合、nはmより大きな値である。回転軸13aの回転速度は入力回転軸11の回転速度のm/nに減速される。また、エネルギの損失が無いと仮定すると、回転軸13aのトルクは入力回転軸11のトルクのn/m倍になる。   FIG. 1 shows an embodiment in which the present invention is applied to a speed reducer comprising a three-stage gear mechanism. The power from the motor is fixed to the input rotating shaft 11 and transmitted to the spur gear 14a fixed to the rotating shaft 13a of the first stage gear mechanism and the number of teeth n through the motor pinion 12 having the number of teeth m. It is done. Here, in the case of a reduction gear, n is a value larger than m. The rotational speed of the rotary shaft 13a is reduced to m / n of the rotational speed of the input rotary shaft 11. Assuming that there is no energy loss, the torque of the rotating shaft 13a is n / m times the torque of the input rotating shaft 11.

回転軸13aにはピニオン15aも固着されており、ピニオン15aは平歯車14aと同一の速度で回転する。回転軸13aの動力はピニオン15aを介して第2段歯車機構の回転軸13bに固着された平歯車14bに伝えられる。回転軸13bに固着された平歯車14bの歯の数は、回転軸13aに固着されたピニオン15aの歯の数よりも大きな値に設定されるため、回転軸13bの回転速度は回転軸13aの回転速度よりも減少するとともに、回転軸13bのトルクは回転軸13aのトルクよりも増大する。   A pinion 15a is also fixed to the rotary shaft 13a, and the pinion 15a rotates at the same speed as the spur gear 14a. The power of the rotating shaft 13a is transmitted to the spur gear 14b fixed to the rotating shaft 13b of the second gear mechanism through the pinion 15a. Since the number of teeth of the spur gear 14b fixed to the rotating shaft 13b is set to a value larger than the number of teeth of the pinion 15a fixed to the rotating shaft 13a, the rotational speed of the rotating shaft 13b is While decreasing from the rotational speed, the torque of the rotating shaft 13b increases more than the torque of the rotating shaft 13a.

同様に、回転軸13bにはピニオン15bも固着されており、ピニオン15bは平歯車14bと同一の速度で回転する。回転軸13bの動力はピニオン15bを介して第3段歯車機構としての出力回転軸16に固着された平歯車14cに伝えられる。出力回転軸16に固着された平歯車14cの歯の数は、回転軸13bに固着されたピニオン15bの歯の数よりも大きな値に設定されるため、出力回転軸16の回転速度は回転軸13bの回転速度よりも減少するとともに、出力回転軸16のトルクは回転軸13bのトルクよりも増大する。   Similarly, a pinion 15b is also fixed to the rotary shaft 13b, and the pinion 15b rotates at the same speed as the spur gear 14b. The power of the rotating shaft 13b is transmitted to a spur gear 14c fixed to an output rotating shaft 16 as a third stage gear mechanism through a pinion 15b. Since the number of teeth of the spur gear 14c fixed to the output rotating shaft 16 is set to a value larger than the number of teeth of the pinion 15b fixed to the rotating shaft 13b, the rotational speed of the output rotating shaft 16 is set to the rotating shaft. The torque of the output rotating shaft 16 increases more than the torque of the rotating shaft 13b while decreasing from the rotational speed of 13b.

その結果、上記の3段階の歯車機構を経て、出力回転軸16の回転速度は入力回転軸11の回転速度よりも大きく減少するとともに、出力回転軸16のトルクは入力回転軸11のトルクよりも大きく増大する。すなわち、減速装置においては、出力回転軸の回転数は入力回転軸の回転数よりも減速されるとともに、出力回転軸には入力回転軸に付与されるトルクよりも大きなトルクを得ることができる。   As a result, through the above three-stage gear mechanism, the rotation speed of the output rotation shaft 16 is greatly reduced from the rotation speed of the input rotation shaft 11, and the torque of the output rotation shaft 16 is larger than the torque of the input rotation shaft 11. Increase greatly. That is, in the speed reducer, the rotation speed of the output rotation shaft is decelerated more than the rotation speed of the input rotation shaft, and a torque larger than the torque applied to the input rotation shaft can be obtained on the output rotation shaft.

ここで、出力回転軸16には後に詳細に説明するトルク・リミッタが装着されている。このトルク・リミッタは、互いに同芯である第1の回転軸21と第2の回転軸31から構成されている。   Here, a torque limiter, which will be described in detail later, is attached to the output rotating shaft 16. The torque limiter includes a first rotating shaft 21 and a second rotating shaft 31 that are concentric with each other.

図2はトルク・リミッタの第1の回転軸21を示す。第1の回転軸21には歯車を圧入したとき両者の結合を強固なものとするためのローレット部22を設けている。第1の回転軸21の一端には同軸状に第1の中空部23が設けてある。また第1の中空部23の開放端と反対側の端部には、第1の中空部23よりも内径が大きな第2の中空部24が同軸的に設けられている。   FIG. 2 shows a first rotating shaft 21 of the torque limiter. The first rotating shaft 21 is provided with a knurled portion 22 for strengthening the coupling between the two when a gear is press-fitted. A first hollow portion 23 is provided coaxially at one end of the first rotating shaft 21. In addition, a second hollow portion 24 having an inner diameter larger than that of the first hollow portion 23 is coaxially provided at an end portion of the first hollow portion 23 opposite to the open end.

図3(A)は一端が負荷機器(図示せず。)に連結される第2の回転軸31の一部を断面で示す側面図である。第2の回転軸31は、図2に示した第1の回転軸21とほぼ同じ外径を備え、その一端32はその外周面の一部が平坦に削られており、この部分を負荷機器の回転導入部に設けられ、第2の回転軸31の一端32とほぼ同一形状の挿入孔(図示せず。)に挿入することにより、減速機の回転出力が負荷機器に伝達される。第2の回転軸31の他端には、円筒体部33が設けられている。この円筒体部33は、外径が第1の回転軸21の第1の中空部23の内径とほぼ同一であり、その先端部には外径が円筒体部33より大きな径大部34が形成されている。この径大部34の外径は、第1の回転軸21の第2の中空部24の内径とほぼ同一となっている。また円筒体部33には、その径大部34を含めた軸方向のほぼ全長に亘り、すり割35が設けられている。さらに本体部33の外周の一部には油溜めとなる溝36が設けられている。この溝36に注油することにより耐久性の向上が得られる。   FIG. 3A is a side view showing, in section, a part of the second rotating shaft 31 whose one end is connected to a load device (not shown). The second rotating shaft 31 has substantially the same outer diameter as that of the first rotating shaft 21 shown in FIG. 2, and one end 32 thereof has a part of its outer peripheral surface cut to be flat, and this portion is used as a load device. The rotation output of the speed reducer is transmitted to the load device by being inserted into an insertion hole (not shown) having substantially the same shape as the one end 32 of the second rotation shaft 31. A cylindrical body portion 33 is provided at the other end of the second rotation shaft 31. The cylindrical body portion 33 has an outer diameter that is substantially the same as the inner diameter of the first hollow portion 23 of the first rotating shaft 21, and a large-diameter portion 34 having an outer diameter larger than that of the cylindrical body portion 33 is formed at the tip portion thereof. Is formed. The outer diameter of the large diameter portion 34 is substantially the same as the inner diameter of the second hollow portion 24 of the first rotating shaft 21. Further, the cylindrical body portion 33 is provided with a slit 35 over almost the entire length in the axial direction including the large diameter portion 34. Further, a groove 36 serving as an oil reservoir is provided on a part of the outer periphery of the main body 33. Durability can be improved by lubricating the groove 36.

図3(B)は第2の回転軸31を円筒体部33側の端面から見た平面図である。第2の回転軸31の円筒体部33の内部には、軸方向に一部を切断して外方に付勢した環状のバネ41が装填されている。環状のバネ41の材質は鋼、ステンレスなどであり、いわゆるスプリングピンも環状バネとして使うことができる。また、環状のバネ41は上記の形状や材質に限ることなくゴムのような弾性体でもよく、さらに弾性体であれば環状である必要はなく空洞部が無いソリッドなものであってもよい。尚、これらを弾性部材と総称することとする。環状のバネ41を第2の回転軸31の円筒体部33の内部に軽圧入することによって、すり割35が設けられている円筒体部33は外方に付勢される。これによって、トルク・リミッタにおける制限トルク値の安定化が図られる。   FIG. 3B is a plan view of the second rotating shaft 31 as viewed from the end face on the cylindrical body 33 side. An annular spring 41 that is partially cut in the axial direction and biased outward is loaded inside the cylindrical body portion 33 of the second rotating shaft 31. The material of the annular spring 41 is steel, stainless steel or the like, and so-called spring pins can also be used as the annular spring. Further, the annular spring 41 is not limited to the shape and material described above, and may be an elastic body such as rubber. Further, as long as it is an elastic body, the annular spring 41 does not need to be annular and may be solid without a hollow portion. These are collectively referred to as elastic members. By lightly press-fitting the annular spring 41 into the cylindrical body portion 33 of the second rotating shaft 31, the cylindrical body portion 33 provided with the slit 35 is urged outward. This stabilizes the limit torque value in the torque limiter.

図4は第1の回転軸21と第2の回転軸31とが相互に連結される状態を示す図である。同図において、第2の回転軸31の下端部の一部は、断面図で示されている。環状のバネ41が装填された第2の回転軸31は第1の回転軸21の第1の中空部23内に挿入され、第2の回転軸31の円筒体部33の径大部34が、第1の回転軸21の第2の中空部24に嵌合することにより、第1の回転軸21と第2の回転軸31が抜けないようになっている。第1の回転軸21と第2の回転軸31とが連結された状態において、相互にスリップ回転したときの焼き付きを防止するために油を用いるが、第2の回転軸31の溝36は、油溜まりの機能を果たす。溝36の幅および条数は、制限トルク値、耐久条件に応じて適宜定めることができる。   FIG. 4 is a diagram illustrating a state where the first rotating shaft 21 and the second rotating shaft 31 are connected to each other. In the drawing, a part of the lower end portion of the second rotating shaft 31 is shown in a sectional view. The second rotating shaft 31 loaded with the annular spring 41 is inserted into the first hollow portion 23 of the first rotating shaft 21, and the large-diameter portion 34 of the cylindrical body portion 33 of the second rotating shaft 31 is inserted. The first rotary shaft 21 and the second rotary shaft 31 are prevented from being detached by fitting into the second hollow portion 24 of the first rotary shaft 21. In the state where the first rotary shaft 21 and the second rotary shaft 31 are connected, oil is used to prevent seizure when the slip rotation is performed, but the groove 36 of the second rotary shaft 31 is Acts as a sump. The width and the number of strips of the groove 36 can be appropriately determined according to the limit torque value and the durability condition.

図5は、第1の回転軸21と第2の回転軸31とが相互に連結された状態を示す、トルク・リミッタの完成図である。第2の回転軸31の円筒体部33には環状バネ41によって中心軸から外方に力が働き、第2の回転軸31の円筒体部分の外壁33と、第1の回転軸21の第1の中空部23の内壁との間には、摩擦が生じ、所定の値のトルクに到るまでは、第2の回転軸31の一端32を介してトルクが負荷機器に伝達される。しかし、トルクが摩擦力を上まわると、第2の回転軸31の円筒体部33の本体部外壁と、第1の回転軸21の第1の中空部23の内壁はスリップし始め、負荷に伝達されるトルクが制限され、トルク・リミッタの機能が働く。   FIG. 5 is a completed view of the torque limiter showing a state in which the first rotating shaft 21 and the second rotating shaft 31 are connected to each other. A force is exerted outwardly from the central axis on the cylindrical portion 33 of the second rotating shaft 31 by the annular spring 41, and the outer wall 33 of the cylindrical portion of the second rotating shaft 31 and the first rotation shaft 21. Friction occurs between the inner wall of the first hollow portion 23, and torque is transmitted to the load device via the one end 32 of the second rotating shaft 31 until the torque reaches a predetermined value. However, when the torque exceeds the frictional force, the outer wall of the main body portion of the cylindrical body portion 33 of the second rotating shaft 31 and the inner wall of the first hollow portion 23 of the first rotating shaft 21 begin to slip and become loaded. The transmitted torque is limited, and the function of the torque limiter works.

トルクの制限値は、第2の回転軸31の円筒体部33の本体部外壁と、第1の回転軸21の第1の中空部23の内壁との接触面積と環状バネ41(弾性部材)による外方への付勢力とを制御することにより、バラツキの小さな安定したものとすることができる。接触面積は、第2の回転軸31の円筒体部33の長さ、外径寸法、円筒体部33に設けられるすり割35の本数、幅等と、溝36の条数、幅とにより制御することができる。   The torque limit value is determined by the contact area between the outer wall of the main body portion of the cylindrical portion 33 of the second rotating shaft 31 and the inner wall of the first hollow portion 23 of the first rotating shaft 21 and the annular spring 41 (elastic member). By controlling the outward urging force due to, it can be made stable with little variation. The contact area is controlled by the length and outer diameter of the cylindrical portion 33 of the second rotating shaft 31, the number and width of the slits 35 provided in the cylindrical portion 33, and the number and width of the grooves 36. can do.

上述した減速装置においては、トルク・リミッタはほぼ同じ外径を有する第1の回転軸21と第2の回転軸31とを相互に連結することにより構成されているため、全体としてコンパクトであり、かつ、減速装置における他の回転軸と同様な外観を呈するため、装置全体の外観に優れている。   In the speed reducer described above, the torque limiter is configured by mutually connecting the first rotating shaft 21 and the second rotating shaft 31 having substantially the same outer diameter, and thus is compact as a whole. And since the external appearance similar to the other rotating shaft in a deceleration device is exhibited, the external appearance of the whole apparatus is excellent.

図6は上記回転軸と異なる態様とした第1の回転軸21と第2の回転軸31を嵌合させ、一部を断面とした図である。図6においては、図2ないし図5における符号の指示箇所と同一の機能を有する箇所の符号は、図2ないし図5における符号と同一にしてある。第1の回転軸21には貫通した第1の中空部23が設けられている。第1の回転軸21の一端には負荷に固着される平面部32が設けられ、負荷機器に回転出力が伝達される。第2の回転軸31には歯車を圧入したとき両者の結合を強固なものとするためのローレット部22を設けている。第2の回転軸31には、さらに、第1の中空部23と所定の嵌合精度を持つ円筒体部33、油溜まりの溝36、円筒体部33の長さとほぼ同じ長さの第3の中空部45、円筒体部33の軸方向のほぼ全長に亘るすり割35、この円筒体部33の軸方向端部には、この円筒体部33より僅かに外径を大きくした径大部34が形成されている。この径大部34は第1の回転軸21の端部から突出して繋止し、第1の回転軸21が第2の回転軸31より離脱することを防止している。第3の中空部45には環状のバネ41が収納されている。図6に示される回転軸の構成においては、図4に示した第2の中空部24の加工が不要となり、加工の際、省力化が可能である。また、トルク・リミッタとしての動作に異常な状態が生じたときは、図6の上部に示した矢印の方向に径大部34を押圧することにより第2の回転軸31から第1の回転軸21を離脱させることができるため、点検、修理が可能となる特徴を備えている。   FIG. 6 is a diagram in which a first rotary shaft 21 and a second rotary shaft 31 which are different from the above-described rotary shafts are fitted and a part thereof is a cross section. In FIG. 6, the reference numerals of the parts having the same functions as the reference numerals in FIGS. 2 to 5 are the same as those in FIGS. The first rotating shaft 21 is provided with a first hollow portion 23 penetrating therethrough. One end of the first rotating shaft 21 is provided with a flat portion 32 that is fixed to a load, and a rotation output is transmitted to the load device. The second rotating shaft 31 is provided with a knurled portion 22 for strengthening the coupling between the two when a gear is press-fitted. The second rotating shaft 31 further includes a cylindrical body portion 33 having a predetermined fitting accuracy with the first hollow portion 23, an oil sump groove 36, and a third length substantially the same as the length of the cylindrical body portion 33. The hollow portion 45, the slit 35 extending over substantially the entire length in the axial direction of the cylindrical body portion 33, and a large diameter portion having a slightly larger outer diameter than the cylindrical body portion 33 at the axial end portion of the cylindrical body portion 33. 34 is formed. The large-diameter portion 34 protrudes from the end of the first rotating shaft 21 and is locked to prevent the first rotating shaft 21 from being detached from the second rotating shaft 31. An annular spring 41 is accommodated in the third hollow portion 45. In the configuration of the rotating shaft shown in FIG. 6, the processing of the second hollow portion 24 shown in FIG. 4 is not necessary, and labor can be saved during the processing. Further, when an abnormal state occurs in the operation as the torque limiter, the large rotation portion 34 is pressed in the direction of the arrow shown in the upper part of FIG. Since 21 can be detached, it has a feature that enables inspection and repair.

以上、便宜上、減速装置を例に説明を行ったが、本発明は増速装置や、入力回転軸と出力回転軸との位置を異ならせるための等速装置にも適用できることは明らかである。さらに、本発明はベベルギヤ、ハイポイドギヤなどを用い、入力回転軸と出力回転軸とが平行ではなく角度を持つ動力伝達装置にも適用できる。増速装置に適用する際には、トルク・リミッタを出力回転軸としてではなく入力回転軸として用い、モータの動力はトルク・リミッタに入力し、図1における入力回転軸11の位置に増速機の出力回転軸を設けると、実用的には好ましい結果が得られる。   For the sake of convenience, the speed reducer has been described above as an example, but it is apparent that the present invention can also be applied to a speed increasing device and a constant speed device for making the positions of the input rotation shaft and the output rotation shaft different. Further, the present invention can be applied to a power transmission device that uses a bevel gear, a hypoid gear, and the like, and the input rotation shaft and the output rotation shaft are not parallel but have an angle. When applied to the speed increasing device, the torque limiter is used not as an output rotating shaft but as an input rotating shaft, and the power of the motor is input to the torque limiter, and the speed increasing device is placed at the position of the input rotating shaft 11 in FIG. If the output rotation shaft is provided, a preferable result can be obtained practically.

なお、入力回転軸は通常、ピニオンを設けたモータの回転軸を指すが、この回転を受け継ぐ歯車のみの、入力回転軸を具備していない動力伝達装置であっても、本発明の技術的思想と異なるものではない。   The input rotation shaft usually indicates the rotation shaft of a motor provided with a pinion. However, even if the power transmission device is a gear that inherits this rotation and does not include the input rotation shaft, the technical idea of the present invention is not limited. Is not different.

また、本発明におけるトルク・リミッタを、減速装置などの動力伝達装置へ適用する際に、入力と出力の中間段の回転軸として用いても、トルク・リミッタの機能が発揮されることは明らかである。   In addition, when the torque limiter according to the present invention is applied to a power transmission device such as a reduction gear, it is clear that the function of the torque limiter is exhibited even if it is used as a rotary shaft at an intermediate stage between input and output. is there.

さらに、本発明におけるトルク・リミッタは、歯車の輪列を持つ動力伝達装置への適用に留まるものではなく、例えばベルトを用いた動力伝達装置へも適用できることも明らかである。   Furthermore, it is apparent that the torque limiter according to the present invention is not limited to application to a power transmission device having a gear train, but can be applied to a power transmission device using a belt, for example.

さらに、上述した減速装置においては、トルク・リミッタはほぼ同じ外径を有する第1の回転軸21と第2の回転軸31とを相互に連結することにより構成したが、第1の回転軸21と第2の回転軸31とを互いに異なる外径としてもよいことは言うまでもない。   Furthermore, in the speed reducer described above, the torque limiter is configured by interconnecting the first rotary shaft 21 and the second rotary shaft 31 having substantially the same outer diameter. Needless to say, the second rotating shaft 31 and the second rotating shaft 31 may have different outer diameters.

本発明の動力伝達装置の実施形態を示す断面図である。It is sectional drawing which shows embodiment of the power transmission device of this invention. 本発明におけるトルク・リミッタの実施形態における第1の回転軸の側面図である。It is a side view of the 1st rotating shaft in embodiment of the torque limiter in this invention. 本発明におけるトルク・リミッタの実施形態における第2の回転軸を示す図で、同図(A)は一部を断面で示す側面図、同図(B)は同図(A)に示す第2の回転軸をその下方から見た平面図である。It is a figure which shows the 2nd rotating shaft in embodiment of the torque limiter in this invention, The figure (A) is a side view which shows a part in cross section, The figure (B) is the 2nd shown in the figure (A). It is the top view which looked at the axis of rotation from the lower part. 本発明におけるトルク・リミッタの実施形態における組み立状態の説明図である。It is explanatory drawing of the assembly state in embodiment of the torque limiter in this invention. 本発明におけるトルク・リミッタの一実施形態を示す側面図である。It is a side view which shows one Embodiment of the torque limiter in this invention. 本発明におけるトルク・リミッタの他の実施形態を示す側面図である。It is a side view which shows other embodiment of the torque limiter in this invention.

符号の説明Explanation of symbols

11 入力回転軸
12 モータピニオン
13 回転軸
14 平歯車
15 ピニオン
16 出力回転軸
21 第1の回転軸
22 ローレット部
23 第1の回転軸の第1の中空部
24 第1の回転軸の第2の中空部
31 第2の回転軸
32 負荷に固着される部分
33 円筒体の本体部
34 円筒体の径大部
35 すり割
36 溝
41 環状のバネ
45 第3の中空部
DESCRIPTION OF SYMBOLS 11 Input rotating shaft 12 Motor pinion 13 Rotating shaft 14 Spur gear 15 Pinion 16 Output rotating shaft 21 1st rotating shaft 22 Knurled part 23 1st hollow part of 1st rotating shaft 24 2nd of 1st rotating shaft Hollow portion 31 Second rotating shaft 32 Part fixed to load 33 Main body portion of cylindrical body 34 Large diameter portion of cylindrical body 35 Slot 36 groove 41 Annular spring 45 Third hollow portion

Claims (1)

同芯状の中空部が設けられた第1の回転軸と、
この第1の回転軸の前記中空部の内径とほぼ同一の外径を有し、端部からすり割り加工が施された円筒体部分を有する第2の回転軸と、
この第2の回転軸の前記円筒体部分内に収納され、前記円筒体部分の内径を拡大するように付勢する弾性部材とを有し、
この弾性部材が収納された前記第2の回転軸の円筒体部分を前記第1の回転軸の中空部に圧入した構造を有するトルク・リミッタと、
入力回転軸および出力回転軸を備え、前記入力回転軸に付与された回転力を前記出力回転軸に歯車を介して伝達する複数段の回転軸からなる歯車機構と、
これらの歯車機構の少なくも1段を構成する前記回転軸として前記トルク・リミッタが装着された動力伝達装置であって、
前記第2の回転軸の前記円筒体部分の前記すり割り加工が施された端部には、この回転軸の外径よりも大きな外形を有する径大部が設けられ、前記第2の回転軸の円筒体部分を前記第1の回転軸の中空部に圧入したとき、前記円筒体部端部の径大部が前記第1の回転軸の端部から突出して繋止されるように構成されていることを特徴とする動力伝達装置。
A first rotating shaft provided with a concentric hollow part;
A second rotating shaft having an outer diameter substantially the same as the inner diameter of the hollow portion of the first rotating shaft and having a cylindrical body portion that is slit from the end;
An elastic member housed in the cylindrical body portion of the second rotating shaft and biased so as to expand the inner diameter of the cylindrical body portion;
A torque limiter having a structure in which the cylindrical portion of the second rotating shaft in which the elastic member is accommodated is press-fitted into the hollow portion of the first rotating shaft;
A gear mechanism comprising a plurality of rotary shafts, each of which includes an input rotary shaft and an output rotary shaft, and transmits a rotational force applied to the input rotary shaft to the output rotary shaft via a gear;
A power transmission device in which the torque limiter is mounted as the rotating shaft constituting at least one stage of these gear mechanisms,
An end portion of the cylindrical portion of the second rotating shaft that has been subjected to the slot processing is provided with a large-diameter portion having an outer shape larger than the outer diameter of the rotating shaft, and the second rotating shaft When the cylindrical body portion is press-fitted into the hollow portion of the first rotating shaft, the large-diameter portion of the cylindrical body end portion protrudes from the end portion of the first rotating shaft and is locked. A power transmission device characterized by that.
JP2008053701A 2008-03-04 2008-03-04 Power transmission device provided with torque limiter Pending JP2008170010A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011148470A (en) * 2010-01-25 2011-08-04 Toyota Motor Corp Wheel independent driving unit

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH1113851A (en) * 1997-06-30 1999-01-22 Rhythm Watch Co Ltd Output gear mechanism which can slip
JPH1131908A (en) * 1997-07-08 1999-02-02 Harada Ind Co Ltd Clutch for rod antenna elevation device

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH1113851A (en) * 1997-06-30 1999-01-22 Rhythm Watch Co Ltd Output gear mechanism which can slip
JPH1131908A (en) * 1997-07-08 1999-02-02 Harada Ind Co Ltd Clutch for rod antenna elevation device

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011148470A (en) * 2010-01-25 2011-08-04 Toyota Motor Corp Wheel independent driving unit

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