JP2003065355A - Torque hinge or torque limiter - Google Patents
Torque hinge or torque limiterInfo
- Publication number
- JP2003065355A JP2003065355A JP2001258857A JP2001258857A JP2003065355A JP 2003065355 A JP2003065355 A JP 2003065355A JP 2001258857 A JP2001258857 A JP 2001258857A JP 2001258857 A JP2001258857 A JP 2001258857A JP 2003065355 A JP2003065355 A JP 2003065355A
- Authority
- JP
- Japan
- Prior art keywords
- spring
- torque
- torque limiter
- annular plate
- hinge
- 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.)
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Abstract
Description
【０００１】[0001]
【発明の属する技術分野】 本発明は、トルクヒンジ又
はトルクリミッタに関し、特にノートブック型コンピュ
ータやさらに小形のいわゆるモバイル型の情報端末機器
などの液晶表示部を兼ねた蓋を本体に対して任意の傾斜
角の位置に停止させるのに好適なトルクヒンジなどに関
するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a torque hinge or a torque limiter, and more particularly to a lid that also serves as a liquid crystal display portion of a notebook computer or a smaller so-called mobile information terminal device for a main body. The present invention relates to a torque hinge or the like suitable for stopping at a position of an inclination angle.
【０００２】[0002]
【従来の技術】 この種のトルクヒンジとしては、本件
出願人の特許出願に係る特開２００１−１２５１４号公
報に開示されたものがある。特に、図３と図４に開示さ
れたばね部材を従来例として図１０（Ａ）−（Ｃ）によ
り説明すると、比較的剛性の大きな金属材料からなるば
ね部材１は、主として環状板体部１ａと、その放射内方
向にある傾斜をもって延びる４個のばね部１ｂとからな
る。隣り合うばね部１ｂとばね部１ｂとの間には狭い空
隙１ｃが存在し、各ばね部１ｂは等間隔で位置してい
る。シャフト２が図１０（Ｃ）の左側から嵌入されると
き、シャフト２の外周面に加圧接触する部分は各ばね部
１ｂの内側エッジ１ｂ’であり、シャフト２が挿入され
ない状態におけるこれら内側角部１ｂ’が形成する仮想
円の直径は、シャフト２の直径よりも小さい。したがっ
て、シャフト２が図１０（Ｃ）の左側から嵌入されると
き、各ばね部１ｂは軸方向に変位し、ラジアル方向にば
ね力を呈し、シャフト２の外周面と各ばね部１ｂの内側
エッジ１ｂ’との間には摩擦トルクが発生する。ばね部
１ｂは回転軸に対して対称に配置されているので、比較
的滑らかなトルク特性と組立作業性にも優れる。2. Description of the Related Art As this type of torque hinge, there is one disclosed in Japanese Patent Application Laid-Open No. 2001-12514 filed by the applicant of the present application. In particular, the spring member disclosed in FIGS. 3 and 4 will be described as a conventional example with reference to FIGS. 10A to 10C. The spring member 1 made of a metal material having a relatively large rigidity mainly includes an annular plate body portion 1a. , Four spring portions 1b extending with an inclination in the radial direction thereof. There is a narrow space 1c between the adjacent spring portions 1b, and the spring portions 1b are located at equal intervals. When the shaft 2 is fitted from the left side of FIG. 10 (C), the portion that comes into pressure contact with the outer peripheral surface of the shaft 2 is the inner edge 1b ′ of each spring portion 1b, and these inner corners when the shaft 2 is not inserted. The diameter of the imaginary circle formed by the portion 1b ′ is smaller than the diameter of the shaft 2. Therefore, when the shaft 2 is fitted from the left side of FIG. 10 (C), each spring portion 1b is displaced in the axial direction and exhibits a spring force in the radial direction, and the outer peripheral surface of the shaft 2 and the inner edge of each spring portion 1b. Friction torque is generated between 1b ′ and 1b ′. Since the spring portion 1b is arranged symmetrically with respect to the rotation axis, it has a relatively smooth torque characteristic and excellent assembling workability.
【０００３】[0003]
【発明が解決しようとする課題】 しかしながら、この
ようなトルクヒンジ又はトルクリミッタにあっては、ば
ね部材１の各ばね部１ｂの内側エッジ１ｂ’がシャフト
２の外周面に加圧接触して所定のトルクを発生させてい
るため、初期に内側エッジ１ｂ’の磨耗が激しく、トル
クが急激かつ大幅に低下するという問題があることが分
かった。したがって、トルクが急激かつ大幅に低下しな
いように、使用前に予めエージングを行う必要があっ
た。このエージングは単位時間当たり所定回転速度以上
の速度で予め決められた時間回転させて、互いの加圧接
触面をなじませるものである。また、ばね部材１は通
常、プレス加工により作られることが多く、各ばね部１
ｂの内側エッジ１ｂ’はそのプレス加工の破断面である
ため、面粗度のバラツキ、バリなどの影響によって、各
内側エッジ１ｂ’とシャフト２の外周面間で生じるトル
ク値に差が生じやすく、これがトルクの不安定要因にな
ると共に、寿命を短くする大きな要因となっていた。し
たがって、本発明はトルク特性が安定で、かつエージン
グが不要なトルクヒンジ又はトルクリミッタを提供する
ことを主たる課題としている。However, in such a torque hinge or torque limiter, the inner edge 1b ′ of each spring portion 1b of the spring member 1 is brought into pressure contact with the outer peripheral surface of the shaft 2 so as to have a predetermined shape. It was found that there is a problem in that the inner edge 1b ′ is heavily worn in the initial stage and the torque sharply and drastically decreases because the torque is generated. Therefore, it is necessary to perform aging before use so that the torque does not drop sharply and significantly. In this aging, the pressure contact surfaces are made to conform to each other by rotating at a speed equal to or higher than a predetermined rotation speed for a predetermined time per unit time. Further, the spring member 1 is usually manufactured by press working, and each spring portion 1
Since the inner edge 1b 'of b is a fracture surface of the press working, the torque value generated between each inner edge 1b' and the outer peripheral surface of the shaft 2 is likely to be different due to the influence of surface roughness variation, burr, and the like. However, this has become a major cause of torque instability and a shortening of service life. Therefore, the main object of the present invention is to provide a torque hinge or a torque limiter that has stable torque characteristics and does not require aging.
【０００４】[0004]
【課題を解決するための手段】 この課題を解決するた
めに、請求項１の発明では、環状板体部と該環状板体部
の放射内方向に延びる複数のばね部とからなるばね部材
と、そのばね部材が回転しないように支承する保持手段
とからなるトルクヒンジ又はトルクリミッタにおいて、
前記ばね部はそれぞれ先端部分に弧状の曲げ部を有し、
シャフトが圧入されるとき前記曲げ部の頂点が前記シャ
フトに加圧接触するトルクヒンジ又はトルクリミッタを
提案するものである。In order to solve this problem, in the invention of claim 1, a spring member comprising an annular plate body portion and a plurality of spring portions extending radially inward of the annular plate body portion, , A torque hinge or a torque limiter comprising a holding means for supporting the spring member so as not to rotate,
Each of the spring portions has an arcuate bent portion at the tip end portion,
The present invention proposes a torque hinge or a torque limiter in which the apex of the bent portion is in pressure contact with the shaft when the shaft is press-fitted.
【０００５】 この課題を解決するために、請求項２で
は、請求項１において、前記ばね部の弧状の曲げ部は、
該ばね部の板厚程度の半径をもつ円弧状であるトルクヒ
ンジ又はトルクリミッタを提案するものである。In order to solve this problem, in claim 2 according to claim 1, the arc-shaped bent part of the spring part is
The present invention proposes a torque hinge or a torque limiter having an arc shape having a radius of the plate thickness of the spring portion.
【０００６】 この課題を解決するために、請求項３で
は、請求項１又は請求項２において、前記ばね部がほぼ
一定間隔に３個以上備えられているトルクヒンジ又はト
ルクリミッタを提案するものである。To solve this problem, a third aspect of the present invention proposes a torque hinge or a torque limiter according to the first or second aspect, in which three or more spring portions are provided at substantially constant intervals. is there.
【０００７】 この課題を解決するために、請求項４で
は、請求項１ないし請求項３のいずれかにおいて、前記
ばね部材はその環状板体部の外周部に凸部及び凹部のい
ずれか一方又は双方を備え、これら突起又は凹みが前記
保持手段の内面に設けられた凹部又は凸部に嵌合するト
ルクヒンジ又はトルクリミッタを提案するものである。In order to solve this problem, according to a fourth aspect, in any one of the first to third aspects, the spring member has one of a convex portion and a concave portion on an outer peripheral portion of the annular plate body portion, or The present invention proposes a torque hinge or a torque limiter that includes both of them, and that these protrusions or depressions fit into the recesses or protrusions provided on the inner surface of the holding means.
【０００８】 この課題を解決するために、請求項５で
は、請求項１ないし請求項４のいずれかにおいて、前記
ばね部材を複数枚備えたトルクヒンジ又はトルクリミッ
タを提案するものである。In order to solve this problem, a fifth aspect proposes a torque hinge or a torque limiter according to any one of the first to fourth aspects, the torque hinge or the torque limiter including a plurality of the spring members.
【０００９】 この課題を解決するために、請求項６で
は、請求項５において、前記複数のばね部材のそれぞれ
のばね部の傾斜が同一方向にあり、隣り合う前記ばね部
材の環状板体部間には環状スペーサが介在するトルクヒ
ンジ又はトルクリミッタを提案するものである。In order to solve this problem, according to a sixth aspect, in the fifth aspect, the inclinations of the spring portions of the plurality of spring members are in the same direction, and between the annular plate body portions of the adjacent spring members. Proposes a torque hinge or torque limiter with an annular spacer interposed.
【００１０】 この課題を解決するために、請求項７で
は、請求項５において、一対の前記ばね部材のばね部の
傾斜が反対方向にあり、前記環状板体部は接触している
トルクヒンジ又はトルクリミッタを提案するものであ
る。To solve this problem, in a seventh aspect of the present invention, in the fifth aspect, the inclination of the spring portions of the pair of spring members are in opposite directions, and the annular plate body portions are in contact with each other. It proposes a torque limiter.
【００１１】 この課題を解決するために、請求項８で
は、請求項１ないし請求項７のいずれかにおいて、前記
ばね部材のばね部には、前記保持手段によってアキシア
ル方向の加圧力がかけられているトルクヒンジ又はトル
クリミッタを提案するものである。In order to solve this problem, in claim 8 according to any one of claims 1 to 7, a pressing force in an axial direction is applied to the spring portion of the spring member by the holding means. A torque hinge or torque limiter is proposed.
【００１２】 この課題を解決するために、請求項９で
は、請求項１ないし請求項８のいずれかにおいて、前記
ばね部材のばね部は、軽圧入で前記保持手段に係止され
ているトルクヒンジ又はトルクリミッタを提案するもの
である。In order to solve this problem, in a ninth aspect of the present invention, the torque hinge according to any one of the first to eighth aspects, wherein the spring portion of the spring member is lightly press-fitted to the holding means. Or, it proposes a torque limiter.
【００１３】[0013]
【発明の実施の形態】 本発明に係るトルクヒンジの基
本的構造は従来例と同様であるが、ばね部材のばね部が
シャフトの外周面に加圧接触する部分が異なり、加圧接
触する部分が弧状に曲げられていて、その弧状部分の頂
部、つまりばね部材のばね部の滑らかな板面がシャフト
の外周面に加圧接触することを特徴としている。BEST MODE FOR CARRYING OUT THE INVENTION The basic structure of the torque hinge according to the present invention is the same as that of the conventional example, but the portion of the spring portion of the spring member that makes pressure contact with the outer peripheral surface of the shaft is different, and the portion that makes pressure contact is different. Is bent in an arc shape, and the top of the arc-shaped portion, that is, the smooth plate surface of the spring portion of the spring member, comes into pressure contact with the outer peripheral surface of the shaft.
【００１４】 図１は、本発明に係るトルクヒンジの一
実施例を示す図である。図８に示した記号と同一の記号
は相当する部材を示すものとする。このトルクヒンジは
大別して後述するばね部材１、ばね部材１を収納する外
筒体３、及び外筒体３と共働してばね部材１を一定位置
に保持するシールド部材４とからなる。外筒体３は、シ
ャフト２の直径よりも大きな直径をもつ中央貫通孔３
ａ、その中央貫通孔３ａよりも大きな径を持ち、ばね部
材１のばね部１ｂを収容するための第１の収容部３ｂ、
第１の収容部３ｂよりも大きな径を持ち、ね部材１の環
状板体部１ａを収容すると共に、シールド部材４が圧入
される第２の収容部３ｃを備える。シールド部材４はシ
ャフト２の直径よりも大きな直径をもつ貫通孔４ａを備
える。シールド部材４は外筒体３と一緒にばね部材１の
保持手段を構成し、第１の収容部３ｃとばね部材１の環
状板体部１ａを両側から押さえて、軸方向に動かないよ
うにすると共に、後述するように軽圧入でラジアル方向
に回転するのを防止する。FIG. 1 is a diagram showing an embodiment of a torque hinge according to the present invention. The same symbols as those shown in FIG. 8 indicate corresponding members. The torque hinge is roughly divided into a spring member 1, which will be described later, an outer cylindrical body 3 that houses the spring member 1, and a shield member 4 that cooperates with the outer cylindrical body 3 to hold the spring member 1 at a fixed position. The outer cylindrical body 3 has a central through hole 3 having a diameter larger than that of the shaft 2.
a, a first accommodating portion 3b having a diameter larger than that of the central through hole 3a and accommodating the spring portion 1b of the spring member 1,
The second accommodating portion 3c has a larger diameter than the first accommodating portion 3b, accommodates the annular plate portion 1a of the spring member 1, and has the second accommodating portion 3c into which the shield member 4 is press-fitted. The shield member 4 includes a through hole 4 a having a diameter larger than that of the shaft 2. The shield member 4 constitutes a holding means of the spring member 1 together with the outer cylinder body 3, and presses the first accommodating portion 3c and the annular plate body portion 1a of the spring member 1 from both sides so as not to move in the axial direction. At the same time, as will be described later, it is prevented from rotating in the radial direction by light press-fitting.
【００１５】 このような構造のトルクヒンジに対して
図１の右側からシャフト２が圧入される。この方向から
圧入するのが、ばね部材１のばね性によって容易であ
る。また、従来構造のもののばね部材１のバネ部１ｂの
エッジがシャフト２に当接していたので後からシャフト
２を圧入し難かったが、この発明のものでは、バネ部１
ａの先端が弧状の曲がり部１ｃとなっていてその弧状の
曲がり部１ｃがシャフト２に当接しているので、ヒンジ
又はトルクリミッタの組立後に、ばね部材１に悪影響を
与えること無くシャフト２を容易に圧入できる。シャフ
ト２は通常の丸棒である円筒形の外周面を有するもので
あり、例えばノートブック型コンピュータの液晶表示部
の下側端面に接続されるものである。また、外筒体３
は、そのノートブック型コンピュータの本体及びキーボ
ード部の奥側端面に接続されるものであり、このトルク
ヒンジの作用により液晶表示部を任意の角度の傾斜位置
に滑らかに開閉、固定できる。なお、外筒体３の外周に
は図示しない他の機器などに取り付けるための取り付け
部３ｄが形成されている。The shaft 2 is press-fitted into the torque hinge having such a structure from the right side of FIG. Press-fitting from this direction is easy due to the spring property of the spring member 1. Further, since the edge of the spring portion 1b of the spring member 1 having the conventional structure is in contact with the shaft 2, it is difficult to press-fit the shaft 2 later.
Since the tip of a is an arc-shaped bent portion 1c, and the arc-shaped bent portion 1c is in contact with the shaft 2, the shaft 2 can be easily formed after the assembly of the hinge or the torque limiter without adversely affecting the spring member 1. Can be pressed into. The shaft 2 has a cylindrical outer peripheral surface which is an ordinary round bar, and is connected to, for example, a lower end surface of a liquid crystal display portion of a notebook computer. In addition, the outer cylindrical body 3
Is connected to the back end surface of the main body of the notebook computer and the keyboard portion, and the action of this torque hinge allows the liquid crystal display portion to be smoothly opened, closed and fixed at an inclined position at an arbitrary angle. A mounting portion 3d for mounting to another device (not shown) is formed on the outer periphery of the outer cylindrical body 3.
【００１６】 ばね部材１の基本的な構造についてさら
に詳細に構造を説明すると、比較的剛性の大きな金属材
料などからなり、図２（Ａ）−（Ｃ）に示すような構造
になっている。この実施例のばね部材１は、前述した従
来例と同様に、外形が円形の環状板体部１ａと、その環
状板体部１ａの放射内方向に等間隔で延びる四つのばね
部１ｂとからなる。ばね部材１は、プレス加工により一
定間隔で狭い四つの空隙１ｃを形成することにより、四
つのばね部１ｂが形成されると共に、各ばね部１ｂは所
定の傾斜で一方側に曲げられると同時に、それぞれの先
端部分が弧状になるように曲げられる。その部分が弧状
の曲げ部１Ｂであり、好ましくはその板厚と同程度の半
径をもつ円弧である。弧状の曲げ部１Ｂの頂部はばね部
１ｂを形成する板材料の滑らかな板面であり、その弧状
の板面がシャフト２に加圧接触するので、安定な滑りが
得られるだけでなく、エージングを行わなくても弧状の
曲げ部１Ｂの損耗が小さいので、安定なトルク特性を得
ることができ、また寿命を大幅に向上できる。さらに、
弧状の曲げ部１Ｂの頂部及びその近傍に潤滑被膜を形成
するか、グリースのような潤滑剤を封入することによ
り、更にトルク特性や寿命の向上を図ることができる。The basic structure of the spring member 1 will be described in more detail. The spring member 1 is made of a metal material having a relatively large rigidity, and has a structure shown in FIGS. 2 (A)-(C). The spring member 1 of this embodiment includes an annular plate body portion 1a having a circular outer shape and four spring portions 1b extending in the radial inward direction of the annular plate body portion 1a at equal intervals, as in the conventional example described above. Become. The spring member 1 is formed with four narrow gaps 1c at regular intervals by press working to form four spring portions 1b, and each spring portion 1b is bent to one side at a predetermined inclination and at the same time, Each tip is bent so as to form an arc. That portion is an arc-shaped bent portion 1B, and preferably an arc having a radius similar to the plate thickness. The top of the arc-shaped bent portion 1B is a smooth plate surface of the plate material that forms the spring portion 1b, and since the arc-shaped plate surface comes into pressure contact with the shaft 2, not only stable slippage is obtained, but also aging is performed. Even if it is not performed, the wear of the arc-shaped bent portion 1B is small, so that stable torque characteristics can be obtained and the life can be greatly improved. further,
By forming a lubricating coating on the top of the arc-shaped bent portion 1B and in the vicinity thereof, or by enclosing a lubricant such as grease, the torque characteristics and the life can be further improved.
【００１７】 図２ではシャフト２を圧入する前に、環
状板体部１ａに対して四つのばね部１ｂをある角度で曲
げているが、曲げておかなくても勿論良い。この場合に
は、四つのばね部１ｂは環状板体部１ａから放射内方向
に真っ直ぐに延び、それらの先端部だけが弧状になるよ
うに曲げられて弧状の曲げ部１Ｂが形成される。それら
弧状の曲げ部１Ｂの頂部が形成する仮想円の径に対して
大きな径を持つシャフト２を前述側から圧入すれば、ば
ね部１ｂは前記仮想円の径がシャフト２の径に等しくな
るまで曲げられ、ばね部１ｂは環状板体部１ａに対して
ある傾斜をもち、適当なばね力をシャフト２に与える。
環状板体部１ａとばね部１ｂとの角度が１８０度、つま
りそれらが同一平面にあるとき、あるいは直角に曲げら
れて９０度である場合には、ばね部材１とシャフト２と
の間に所望のトルクが発生しない。ばね部１ｂの曲がっ
た方向における環状板体部１ａとばね部１ｂとの間の角
度は、１１０度ないし１６０度の範囲にあることが安定
で比較的大きなトルクを発生することができ、好まし
い。In FIG. 2, the four spring portions 1b are bent at a certain angle with respect to the annular plate portion 1a before the shaft 2 is press-fitted, but it is not necessary to bend them. In this case, the four spring portions 1b extend straight in the radial inward direction from the annular plate portion 1a, and only the tips thereof are bent to form an arc-shaped bent portion 1B. When the shaft 2 having a larger diameter than the diameter of the virtual circle formed by the tops of the arc-shaped bent portions 1B is press-fitted from the above-mentioned side, the spring portion 1b becomes until the diameter of the virtual circle becomes equal to the diameter of the shaft 2. When bent, the spring portion 1b has a certain inclination with respect to the annular plate portion 1a, and applies a proper spring force to the shaft 2.
When the angle between the annular plate portion 1a and the spring portion 1b is 180 degrees, that is, when they are in the same plane or when they are bent at a right angle and are 90 degrees, a desired distance between the spring member 1 and the shaft 2 is desired. Torque does not occur. The angle between the annular plate portion 1a and the spring portion 1b in the bending direction of the spring portion 1b is preferably in the range of 110 to 160 degrees because stable and relatively large torque can be generated.
【００１８】 次に、図３により第２の実施例について
説明する。この実施例は、前述の構造の一対のばね部材
１を用い、環状板体部１ａを背中合わせにし、ばね部１
ｂが互いに反対方向に向くようにしている。この外筒体
３は前記実施例の外筒体のものよりも深い第２の収容部
３ｃを備え、シールド部材４は貫通孔４ａを備える他に
それと同心状にばね部材１のばね部１ｂを収納する収納
部４ｂを備える。外筒体３の第２の収容部３ｃには一方
のばね部材１の環状板体部１ａと、他方のばね部材１が
収納された形となり、さらにシールド部材４が圧入され
る。前述したように、本発明の構造ではばね部１ｂの先
端が弧状の曲げ部１Ｂとなっていて、その弧状の曲げ部
１Ｂがシャフト２に当接することになるので、その曲げ
部１Ｂとシャフト２間は潤滑剤の作用などにより滑り易
く、したがって、ばね部材１に悪影響を与えること無く
組立後に、シャフト２をいずれの側からも比較的容易に
圧入できる。この構造のものでは、第１の実施例のトル
クヒンジに比べてほぼ２倍の大きさのトルクを呈するこ
とができる。Next, a second embodiment will be described with reference to FIG. In this embodiment, the pair of spring members 1 having the above-mentioned structure are used, and the annular plate portions 1a are placed back to back.
b are oriented in opposite directions. The outer cylindrical body 3 has a second accommodating portion 3c deeper than that of the outer cylindrical body of the above-mentioned embodiment, and the shield member 4 has a through hole 4a and a spring portion 1b of the spring member 1 concentrically therewith. A storage section 4b for storing is provided. The second housing portion 3c of the outer cylindrical body 3 has a shape in which the annular plate body portion 1a of the one spring member 1 and the other spring member 1 are accommodated, and the shield member 4 is further press-fitted. As described above, in the structure of the present invention, the tip of the spring portion 1b is the arc-shaped bent portion 1B, and the arc-shaped bent portion 1B comes into contact with the shaft 2. Therefore, the bent portion 1B and the shaft 2 The gap is slippery due to the action of the lubricant, etc. Therefore, the shaft 2 can be relatively easily press-fitted from any side after assembly without adversely affecting the spring member 1. With this structure, it is possible to exhibit a torque which is almost twice as large as that of the torque hinge of the first embodiment.
【００１９】 次に、図４により第３の実施例について
説明する。この実施例は前述の構造の３個のばね部材１
を外筒体３の収納部に同一方向に並置し、隣り合うばね
部材１とばね部材１との間に環状スペーサ５を備えてい
る。環状スペーサ５の厚みは、シャフト２の圧入時に曲
がるばね部１ｂの傾斜量を見込んで決められている。環
状スペーサ５が薄す過ぎれば、シャフト２の圧入時にば
ね部材同士が干渉し合って所定のトルク値が得られなか
ったり、不良品となることがあり、また厚過ぎれば外筒
体３の軸方向に大きくなり、小型化という面で不都合が
生じる。したがって、環状スペーサ５の厚みはばね部１
ｂの軸方向の長さよりも若干大きくなるように設定され
る。また、環状スペーサ５はばね部材１の環状板体部１
ａの外径と同等以下の外径と、その中心点から狭い空隙
１ｃの最奥点までの環状板体部１ａの内径と同等以上の
内径とを有する。この実施例では、前述実施例よりも大
きなトルク値を得ることも可能である。Next, a third embodiment will be described with reference to FIG. In this embodiment, three spring members 1 having the above-mentioned structure are used.
Are arranged side by side in the same direction in the accommodating portion of the outer cylindrical body 3, and an annular spacer 5 is provided between the adjacent spring members 1. The thickness of the annular spacer 5 is determined in consideration of the amount of inclination of the spring portion 1b that bends when the shaft 2 is press-fitted. If the annular spacer 5 is too thin, the spring members may interfere with each other when the shaft 2 is press-fitted, and a predetermined torque value may not be obtained, or a defective product may be obtained. However, there is a problem in terms of size reduction. Therefore, the thickness of the annular spacer 5 depends on the spring portion 1.
It is set to be slightly larger than the axial length of b. Further, the annular spacer 5 is the annular plate body portion 1 of the spring member 1.
The outer diameter is equal to or smaller than the outer diameter of a, and the inner diameter is equal to or larger than the inner diameter of the annular plate body portion 1a from the center point to the deepest point of the narrow void 1c. In this embodiment, it is possible to obtain a larger torque value than the above-mentioned embodiments.
【００２０】 次に、図５及び図６により本発明にかか
るトルクヒンジの変形例について説明する。図５（Ａ）
はシャフト２の軸線方向に直径部分で切断した断面図を
示し、６はシャフト２を固定、例えばノートブック型コ
ンピュータの場合にはその本体にシャフト２を固定する
ための取り付け部材であり、シャフト２と取り付け部材
５との間では相対的に回転しないようになっている。図
５（Ｂ）、（Ｃ）、（Ｄ）は図５（Ａ）のＢ−Ｂ’にお
ける別々の変形例の断面を示す図である。図５（Ｂ）は
図６（Ａ）に示すばね部材１を用いており、その環状板
体部１ａの外形が４角形になっている。ばね部１ｂにつ
いては図１の実施例と同じであり、四つの狭い空隙１ｃ
で分割されたばね部１ｂの先端部は弧状の曲げ部１Ｂと
なっている。そして、図１の実施例で説明した外筒体３
の第２の収納部は、環状板体部１ａの４角形の外形とほ
ぼ同じ大きさの４角形の形状になっており、ばね部材１
の環状板体部１ａは外筒体３の第２の収納部に軽く圧入
されている。したがって、特別な回り止めを形成するこ
となく、ばね部材１の環状板体部１ａは外筒体３に対し
て動くことはない。Next, modified examples of the torque hinge according to the present invention will be described with reference to FIGS. 5 and 6. Figure 5 (A)
Shows a cross-sectional view of the shaft 2 taken along a diameter portion in the axial direction, and 6 is a mounting member for fixing the shaft 2, for example, in the case of a notebook computer, the shaft 2 is fixed to the main body. The mounting member 5 and the mounting member 5 do not rotate relative to each other. 5 (B), (C), and (D) are views showing cross sections of different modifications in BB ′ of FIG. 5 (A). FIG. 5 (B) uses the spring member 1 shown in FIG. 6 (A), and the outer shape of the annular plate body portion 1a is quadrangular. The spring portion 1b is the same as that of the embodiment of FIG. 1, and has four narrow voids 1c.
The tip portion of the spring portion 1b divided by is an arc-shaped bent portion 1B. Then, the outer cylindrical body 3 described in the embodiment of FIG.
The second storage portion of the spring member 1 has a quadrangular shape having substantially the same size as the quadrangular outer shape of the annular plate body 1a.
The annular plate body portion 1a is lightly pressed into the second housing portion of the outer cylinder body 3. Therefore, the annular plate portion 1a of the spring member 1 does not move with respect to the outer cylinder body 3 without forming a special detent.
【００２１】 図５（Ｃ）は、図６（Ｂ）に示すばね部
材１を用いており、ばね部材１の環状板体部１ａの円形
の外形に等間隔で３か所に凸状回り止め部ａ１、ａ２、
ａ３を形成したものであり、ばね部材１の製作時にプレ
ス加工で同時に形成される。外筒体３の第２の収納部に
は、凸状回り止め部ａ１、ａ２、ａ３が軽圧入されるの
に適した凹部が形成されており、環状板体部１ａの凸状
回り止め部ａ１、ａ２、ａ３が外筒体３の第２の収納部
の凹部に軽く圧入されることにより、ばね部材１の環状
板体部１ａが外筒体３に対して動くことはない。ばね部
１ｂについては前述した構造であるので説明を省く。FIG. 5 (C) uses the spring member 1 shown in FIG. 6 (B), and has a circular outer shape of the annular plate body portion 1 a of the spring member 1 which is provided with convex rotation stoppers at three equal intervals. Parts a1, a2,
a3 is formed, and is simultaneously formed by press working when the spring member 1 is manufactured. A concave portion suitable for lightly press-fitting the convex detent portions a1, a2, a3 is formed in the second storage portion of the outer cylindrical body 3, and the convex detent portion of the annular plate body portion 1a is formed. The annular plate body portion 1a of the spring member 1 does not move with respect to the outer cylinder body 3 by lightly press-fitting a1, a2, and a3 into the recesses of the second housing portion of the outer cylinder body 3. Since the spring portion 1b has the above-described structure, its explanation is omitted.
【００２２】 図５（Ｄ）は、図６（Ｃ）に示すばね部
材１を用いており、ばね部材１の環状板体部１ａの円形
の外形に等間隔で３か所に凹んだ凹状回り止め部ｂ１、
ｂ２、ｂ３を形成したものであり、外筒体３の第２の収
納部には、逆に凹状回り止め部ｂ１、ｂ２、ｂ３と適合
する凸部が形成されており、環状板体部１ａの凹状回り
止め部ｂ１、ｂ２、ｂ３に外筒体３の第２の収納部の前
記凸部が軽く圧入されることにより、ばね部材１の環状
板体部１ａは外筒体３に対して動くことはない。ばね部
１ｂについては前述した構造であるので詳細な説明を省
く。FIG. 5 (D) uses the spring member 1 shown in FIG. 6 (C), and has a circular outer shape of the annular plate body portion 1 a of the spring member 1 which is concavely recessed in three places at equal intervals. Stop b1,
b2 and b3 are formed, and the second accommodation portion of the outer cylindrical body 3 is formed with a convex portion which is opposite to the concave detent portions b1, b2 and b3, and the annular plate portion 1a. By lightly press-fitting the convex portion of the second storage portion of the outer cylindrical body 3 into the concave detent portions b1, b2, b3 of the outer cylindrical body 3, the annular plate portion 1a of the spring member 1 with respect to the outer cylindrical body 3. It does not move. Since the spring portion 1b has the above-described structure, detailed description thereof will be omitted.
【００２３】 次に、図７及び図８により本発明にかか
るトルクヒンジの別の変形例について説明する。図７
（Ａ）はシャフト２の軸線方向に直径部分で切断した断
面図を示し、図７（Ｂ）はそのｃ−ｃ’で切断した断面
図を示す。図８は本発明にかかるトルクヒンジに用いる
ばね部材１を示す。この例では、図４で示したばね部材
１間の環状スペーサ５を省略するために、環状板体部１
ａの円形の外形に等間隔で３か所に形成した凸状回り止
め部ａ１、ａ２、ａ３の最外側部にそれと直角に延びる
起立部a'１，a'２，a'３が形成される。これら起立部a'
１，a'２，a'３は、弧状の曲げ部１Ｂを含むばね部１ｂ
の軸方向の長さよりも若干長くなっており、図７（Ａ）
に示すように、二つのばね部材１を同方向に並べて配置
し、シャフト２が圧入されてばね部１ｂが所定の傾斜を
もったとき、他方のばね部材１にぶつからないようにな
っている。なお、この例では環状板体部１ａの内側、つ
まり放射内方向に等間隔で３個のばね部１ｂが延びてお
り、その各先端部には弧状の曲げ部１Ｂが形成されてい
る。この変形例では、図２のばね部材に比べて間隔１ｃ
が大きくなっており、ばね部１ｂの幅はかなり小さくな
っている。この変形例では、別途環状スペーサを配置す
ること無く、ばね性に悪影響を与えずに、複数個のばね
部材１を用いることができる。Next, another modification of the torque hinge according to the present invention will be described with reference to FIGS. 7 and 8. Figure 7
7A shows a sectional view taken along the axial direction of the shaft 2 at the diameter portion, and FIG. 7B shows a sectional view taken along the line cc '. FIG. 8 shows a spring member 1 used in the torque hinge according to the present invention. In this example, in order to omit the annular spacer 5 between the spring members 1 shown in FIG.
On the outermost part of the convex detents a1, a2, and a3 formed at three locations on the circular outer shape of a at equal intervals, standing parts a'1, a'2, and a'3 extending at right angles are formed. It These standing parts a '
1, a'2, a'3 are spring portions 1b including arc-shaped bent portions 1B
7 is slightly longer than the axial length of FIG.
2, the two spring members 1 are arranged side by side in the same direction so that when the shaft 2 is press-fitted and the spring portion 1b has a predetermined inclination, it does not hit the other spring member 1. In this example, three spring portions 1b extend at equal intervals inside the annular plate body portion 1a, that is, in the radial inward direction, and arc-shaped bent portions 1B are formed at their respective tip portions. In this modified example, the gap 1c is larger than that of the spring member of FIG.
Is large, and the width of the spring portion 1b is considerably small. In this modification, a plurality of spring members 1 can be used without disposing an annular spacer separately and without adversely affecting the spring property.
【００２４】 次に、図９に従来構造（特開2001-12514
号公報の図３、図４に示されたもの）と、本発明にかか
るトルクヒンジについて単位時間当たり所定の回転数で
回転させたエージング試験の結果を示す。曲線１は従来
構造のもののトルク特性を示し、エ−ジングを行った結
果、大幅かつ急激にトルク値が低下するのが明らかであ
る。この点、曲線２で示される本発明に係るトルクヒン
ジのトルク値は初期でも極めて僅か低下するだけであ
り、その後はほとんど変化せず、トルクは十分に安定し
ている。したがって、この結果から従来構造のトルクヒ
ンジの場合には、実際に使用する前に必ずエージングを
行う必要があるが、本発明のものではエージングを行う
必要の無いことが分かる。Next, FIG. 9 shows a conventional structure (Japanese Patent Laid-Open No. 2001-12514).
3 and 4 of the publication) and the results of an aging test in which the torque hinge according to the present invention is rotated at a predetermined rotation speed per unit time. Curve 1 shows the torque characteristic of the conventional structure, and it is clear that the torque value drastically and rapidly decreases as a result of aging. In this respect, the torque value of the torque hinge according to the present invention, which is shown by the curve 2, only slightly decreases at the initial stage, and thereafter hardly changes, and the torque is sufficiently stable. Therefore, from this result, it is understood that in the case of the torque hinge having the conventional structure, it is necessary to perform aging before actually using it, but in the present invention, it is not necessary to perform aging.
【００２５】 なお、以上述べた実施例ではトルクヒン
ジについて述べたが、使用方法が異なるだけで、全く同
一構造でトルクリミッタとして用いることが可能であ
り、トルク特性の安定したトルクリミッタが得られるこ
とは極めて容易に理解できる。また、以上の実施例では
いずれもばね部材１のばね部１ｂを４個又は３個で説明
したが、２個又は５個、あるいはそれ以上なら幾つでも
良い。隣接するばね部１ｂ間の空隙１ｃは、ばね部１ｂ
が干渉し合わない限り、狭い方が大きなトルク値が得ら
れるので、大きなトルクのトルクリミッタが必要な場合
には、狭い方が好ましい。さらにまた、環状板体部１ａ
の凸状回り止め部と凹状回り止め部の双方を備え、これ
に伴い外筒部の収納部の放射外方向の壁に、それらと軽
圧入の関係となるような凹凸双方を備えていても良い。Although the torque hinge has been described in the above-described embodiments, it can be used as a torque limiter with exactly the same structure except that the method of use is different, and a torque limiter with stable torque characteristics can be obtained. Is very easy to understand. Further, in the above embodiments, the spring portion 1b of the spring member 1 is described as 4 or 3 springs, but it may be 2 or 5 springs or any number of spring springs 1b. The gap 1c between the adjacent spring portions 1b is the spring portion 1b.
Since a larger torque value can be obtained as long as they do not interfere with each other, a narrower one is preferable when a torque limiter with a large torque is required. Furthermore, the annular plate body portion 1a
Both the convex anti-rotation part and the concave anti-rotation part are provided, and accordingly, the outer radial wall of the housing part of the outer tubular part may be provided with both the irregularities that are in a light press-fitting relationship with them. good.
【００２６】[0026]
【発明の効果】 以上述べたように、本発明によれば予
めエージングを行わなくても安定したトルクヒンジ又は
トルクリミッタを提供することができる。As described above, according to the present invention, it is possible to provide a stable torque hinge or torque limiter without performing aging in advance.
【図１】 本発明に係るトルクヒンジの第１の実施の態
様を示す図である。FIG. 1 is a diagram showing a first embodiment of a torque hinge according to the present invention.
【図２】 本発明に係るトルクヒンジに用いるばね部材
の例を示す図である。FIG. 2 is a diagram showing an example of a spring member used in the torque hinge according to the present invention.
【図３】 本発明に係るトルクヒンジの第２の実施の態
様を示す図である。FIG. 3 is a view showing a second embodiment of the torque hinge according to the present invention.
【図４】 本発明に係るトルクヒンジの第３の実施の態
様を示す図である。FIG. 4 is a diagram showing a third embodiment of a torque hinge according to the present invention.
【図５】 本発明に係るトルクヒンジの変形例を示す図
である。FIG. 5 is a diagram showing a modified example of the torque hinge according to the present invention.
【図６】 本発明に係るトルクヒンジに用いるばね部材
の例を示す図である。FIG. 6 is a view showing an example of a spring member used in the torque hinge according to the present invention.
【図７】 本発明に係るトルクヒンジの変形例を示す図
である。FIG. 7 is a diagram showing a modified example of the torque hinge according to the present invention.
【図８】 本発明に係るトルクヒンジに用いるばね部材
の例を示す図である。FIG. 8 is a diagram showing an example of a spring member used in the torque hinge according to the present invention.
【図９】 本発明と従来のトルクヒンジのトルク特性を
示す図である。FIG. 9 is a diagram showing torque characteristics of the present invention and a conventional torque hinge.
【図１０】 従来のトルクヒンジの一例を示す図であ
る。FIG. 10 is a diagram showing an example of a conventional torque hinge.
１・・・ばね部材
１ａ・・・環状板体部 １ｂ・・・ばね
部
１ｃ・・・空隙 １Ｂ・・・弧状
の曲げ部
ａ１−ａ３・・・凸状回り止め部 ｂ１−ｂ３・・
・凹状回り止め部
a'１−a'３・・・起立部
２・・・シャフト
３・・・外筒部
３ａ・・・中央貫通孔 ３ｂ・・・第１
の収容部
３ｃ・・・第２の収容部
４・・・シールド部材
４ａ・・・貫通孔 ４ｂ・・・収容
部
５・・・環状スペーサ
６・・・取り付け部材DESCRIPTION OF SYMBOLS 1 ... Spring member 1a ... Annular plate part 1b ... Spring part 1c ... Void 1B ... Arc-shaped bend part a1-a3 ... Convex detent part b1-b3 ...
-Concave detent part a'1-a'3 ... Standing part 2 ... Shaft 3 ... Outer cylinder part 3a ... Central through hole 3b ... 1st
Housing part 3c ... second housing part 4 ... shield member 4a ... through hole 4b ... housing part 5 ... annular spacer 6 ... mounting member
Claims (9)
に延びる複数のばね部とからなるばね部材と、該ばね部
材が回転しないように支承する保持手段とからなるトル
クヒンジ又はトルクリミッタにおいて、 前記ばね部はそれぞれ先端部分に弧状の曲げ部を有し、
シャフトが圧入されるとき前記曲げ部の頂点が前記シャ
フトに加圧接触することを特徴とするトルクヒンジ又は
トルクリミッタ。1. A torque hinge comprising a spring member composed of an annular plate member and a plurality of spring members extending radially inward of the annular plate member, and holding means for supporting the spring member so as not to rotate, or In the torque limiter, each of the spring portions has an arc-shaped bent portion at a tip end portion thereof,
A torque hinge or a torque limiter, wherein the apex of the bent portion comes into pressure contact with the shaft when the shaft is press-fitted.
径をもつ円弧状であることを特徴とするトルクヒンジ又
はトルクリミッタ。2. The torque hinge or torque limiter according to claim 1, wherein the arc-shaped bent portion of the spring portion has an arc shape having a radius approximately equal to the plate thickness of the spring portion.
を特徴とするトルクヒンジ又はトルクリミッタ。3. The torque hinge or torque limiter according to claim 1, wherein a plurality of the spring portions are provided at substantially constant intervals.
いて、 前記ばね部材はその環状板体部の外周部に凸部及び凹部
のいずれか一方又は双方を備え、これら突起又は凹みが
前記保持手段の内面に設けられた凹部又は凸部に嵌合す
ることを特徴とするトルクヒンジ又はトルクリミッタ。4. The spring member according to claim 1, wherein the spring member is provided with one or both of a convex portion and a concave portion on an outer peripheral portion of the annular plate body portion, and the protrusion or the concave portion holds the holding member. A torque hinge or a torque limiter fitted to a concave portion or a convex portion provided on the inner surface of the means.
いて、 前記ばね部材を複数枚備えたことを特徴とするトルクヒ
ンジ又はトルクリミッタ。5. The torque hinge or the torque limiter according to claim 1, further comprising a plurality of the spring members.
向にあり、隣り合う前記ばね部材の環状板体部間には環
状スペーサが介在することを特徴とするトルクヒンジ又
はトルクリミッタ。6. The spring member according to claim 5, wherein the respective spring portions of the plurality of spring members are inclined in the same direction, and an annular spacer is interposed between the annular plate body portions of the adjacent spring members. Torque hinge or torque limiter.
前記環状板体部は接触していることを特徴とするトルク
ヒンジ又はトルクリミッタ。7. The method according to claim 5, wherein the spring portions of the pair of spring members are inclined in opposite directions,
A torque hinge or a torque limiter, wherein the annular plate portions are in contact with each other.
いて、 前記ばね部材のばね部には、前記保持手段によってアキ
シアル方向の加圧力がかけられていることを特徴とする
トルクヒンジ又はトルクリミッタ。8. The torque hinge or the torque limiter according to claim 1, wherein a pressing force in an axial direction is applied to the spring portion of the spring member by the holding means. .
いて、 前記ばね部材のばね部は、軽圧入で前記保持手段に係止
されていることを特徴とするトルクヒンジ又はトルクリ
ミッタ。9. The torque hinge or the torque limiter according to claim 1, wherein the spring portion of the spring member is lightly press-fitted to the holding means.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001258857A JP3912724B2 (en) | 2001-08-29 | 2001-08-29 | Torque hinge or torque limiter |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001258857A JP3912724B2 (en) | 2001-08-29 | 2001-08-29 | Torque hinge or torque limiter |
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| JP2003065355A true JP2003065355A (en) | 2003-03-05 |
| JP3912724B2 JP3912724B2 (en) | 2007-05-09 |
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| Application Number | Title | Priority Date | Filing Date |
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| JP2001258857A Expired - Lifetime JP3912724B2 (en) | 2001-08-29 | 2001-08-29 | Torque hinge or torque limiter |
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| JP (1) | JP3912724B2 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2006006467A1 (en) * | 2004-07-12 | 2006-01-19 | Exedy Corporation | Method of manufacturing torque limiter apparatus |
| CN107269679A (en) * | 2017-07-26 | 2017-10-20 | 明阳科技（苏州）股份有限公司 | A kind of moment of torsion rotating shaft |
| JP2018071553A (en) * | 2016-10-24 | 2018-05-10 | スガツネ工業株式会社 | Torque hinge |
| JP7002691B1 (en) * | 2021-06-02 | 2022-01-20 | 株式会社オリジン | Torque hinge with clutch mechanism |
| WO2022138274A1 (en) * | 2020-12-25 | 2022-06-30 | ツインバード工業株式会社 | Plug lock mechanism |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6655654B2 (en) * | 2018-05-16 | 2020-02-26 | 株式会社オリジン | Torque limiter |
| JP7305737B1 (en) * | 2021-12-27 | 2023-07-10 | 株式会社オリジン | Manufacturing method of friction type torque limiter |
-
2001
- 2001-08-29 JP JP2001258857A patent/JP3912724B2/en not_active Expired - Lifetime
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2006006467A1 (en) * | 2004-07-12 | 2006-01-19 | Exedy Corporation | Method of manufacturing torque limiter apparatus |
| JP2006029358A (en) * | 2004-07-12 | 2006-02-02 | Exedy Corp | Manufacturing method for torque limiter |
| JP4666965B2 (en) * | 2004-07-12 | 2011-04-06 | 株式会社エクセディ | Method for manufacturing torque limiter device |
| US7954239B2 (en) | 2004-07-12 | 2011-06-07 | Exedy Corporation | Method of manufacturing a torque limiter device |
| JP2018071553A (en) * | 2016-10-24 | 2018-05-10 | スガツネ工業株式会社 | Torque hinge |
| CN107269679A (en) * | 2017-07-26 | 2017-10-20 | 明阳科技（苏州）股份有限公司 | A kind of moment of torsion rotating shaft |
| CN107269679B (en) * | 2017-07-26 | 2023-08-18 | 明阳科技（苏州）股份有限公司 | Torque rotating shaft |
| WO2022138274A1 (en) * | 2020-12-25 | 2022-06-30 | ツインバード工業株式会社 | Plug lock mechanism |
| JP7002691B1 (en) * | 2021-06-02 | 2022-01-20 | 株式会社オリジン | Torque hinge with clutch mechanism |
| WO2022254916A1 (en) | 2021-06-02 | 2022-12-08 | 株式会社オリジン | Torque hinge with clutch mechanism |
| KR20240010032A (en) | 2021-06-02 | 2024-01-23 | 가부시키가이샤 오리진 | Torque hinge with clutch mechanism |
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|---|---|
| JP3912724B2 (en) | 2007-05-09 |
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