JPS61197819A - Torque transmission joint - Google Patents
Torque transmission jointInfo
- Publication number
- JPS61197819A JPS61197819A JP60038451A JP3845185A JPS61197819A JP S61197819 A JPS61197819 A JP S61197819A JP 60038451 A JP60038451 A JP 60038451A JP 3845185 A JP3845185 A JP 3845185A JP S61197819 A JPS61197819 A JP S61197819A
- Authority
- JP
- Japan
- Prior art keywords
- tightening
- thread
- angle
- clamping
- cylinder
- 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.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
- F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
- F16D1/09—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces
- F16D1/093—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces using one or more elastic segmented conical rings forming at least one of the conical surfaces, the rings being expanded or contracted to effect clamping
- F16D1/095—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces using one or more elastic segmented conical rings forming at least one of the conical surfaces, the rings being expanded or contracted to effect clamping with clamping effected by ring contraction only
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/26—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected
- F16D3/38—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another
- F16D3/382—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another constructional details of other than the intermediate member
- F16D3/387—Fork construction; Mounting of fork on shaft; Adapting shaft for mounting of fork
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
- F16D3/72—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members with axially-spaced attachments to the coupling parts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
- F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
- F16D1/09—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces
- F16D1/093—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces using one or more elastic segmented conical rings forming at least one of the conical surfaces, the rings being expanded or contracted to effect clamping
- F16D1/095—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces using one or more elastic segmented conical rings forming at least one of the conical surfaces, the rings being expanded or contracted to effect clamping with clamping effected by ring contraction only
- F16D2001/0955—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces using one or more elastic segmented conical rings forming at least one of the conical surfaces, the rings being expanded or contracted to effect clamping with clamping effected by ring contraction only the clamping is effected by hub contraction, i.e. a compression of the hub instead of the ring
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
- Clamps And Clips (AREA)
Abstract
Description
【発明の詳細な説明】 （利用分野） 本発明は、トルク伝達継手に胸するものであり。[Detailed description of the invention] (Application field) The present invention relates to torque transmission joints.
百鮪ＭＩＦ丹鮨紬 ムス層Ｈ曲ｐ原動齢に取什叶る歯車
、グーり等の回転体をトルク伝達状態に連結又に取付け
るための継手として利用できる。It can be used as a joint for connecting or attaching rotating bodies such as gears and gears to the torque transmitting state, which can be attached to the mus layer H curve P driving age.
（従来技術及びその問題点）
との神継手として、すてに、特願昭５９−１４５５０５
号（昭和５９１ｆ−７月１２日出願）を提案したが、本
発明はこれの改良に関するものである。(Prior art and its problems) As a divine joint, patent application No. 59-145505
No. 591F (filed on July 12, 1982), and the present invention relates to improvements thereto.
上記従来のもの１に、Ｉｆ＜動軸（１０ａ）と従動軸（
１０ｂ）とをトルク伝達状態に連結する軸継手を例にと
って説明すると、この軸継手は、継手主体（１）の両端
に軸線方向のスリット（社）、α２を開削した締は筒０
υを形成し、この締付筒の外周をテーパネジ部０３とし
。In the conventional type 1 above, If<driving axis (10a) and driven axis (10a)
10b) in a torque transmitting state. This shaft joint has axial slits at both ends of the joint body (1), and a fastening cylinder 0 with an open cut α2.
υ is formed, and the outer periphery of this tightening cylinder is made into a tapered threaded portion 03.
このテーパネジ部に同様のテーパネジ（雌ネジ）ｔ−具
備する締付ナツト（２）を螺合させたものである。A tightening nut (2) having a similar taper thread (female thread) T is screwed into this tapered thread portion.
この従来のものでは、京動軸（１０ａ）及び従動輪（１
０ｂ）を各別Ｋｍ吋筒Ｏ１ｌに挿入し、締付ナツト（２
）を締付けると、テーパネジ部のテーパ嵌合効果により
、締付筒αυと各軸とが圧接され、この圧接部の岸擦力
により１京幼軸（１０ａ）−締付筒αＤ−継手主体（１
）→締付筒（１１１−従動軸（１０ｂ）の経路でトルク
が伝達される。In this conventional type, the pivoting shaft (10a) and the driven wheel (1
0b) into each separate Km cylinder O1l, and tighten the tightening nut (2
) is tightened, the tapered fitting effect of the tapered threaded part brings the clamping tube αυ into pressure contact with each shaft. 1
)→Torque is transmitted through the tightening cylinder (111-driven shaft (10b) path).
とのものでは、軸継手の装着、取外しが簡便であること
から、前記出願以前の従来の軸継手にくらべて便利に使
用できる。Since the shaft joint can be easily installed and removed, it can be used more conveniently than the conventional shaft joints made before the above-mentioned application.
ところが、上記出願発明を実施した軸継手においては、
伝達トルクをあまり大きくできないという問題があった
。However, in the shaft coupling in which the above applied invention is implemented,
There was a problem in that the transmitted torque could not be increased very much.
この問題は、結論的には、テーパネジ部のネジ山形状と
して一般的なネジ山（頂角が６６のもの）を採用してい
たことに基因する。This problem is ultimately due to the fact that a general thread (with an apex angle of 66 mm) was adopted as the thread shape of the tapered thread portion.
すなわち、締付ナフト（２）の締付けによって締付筒α
υが原動軸の外周面に圧接されるメカニズムは締付筒（
社）の肉厚にネジ山を付加した断面（第７図）を持つコ
イル状の楔が締付ナツト（２）と原動軸（１０ａ）又は
従動軸（１０ｂ）の外周面に圧入される場合と同一視で
きる。元来、ネジは軸線方向の締付力を確保するために
用いられるもので、ネジ山の形状も軸線方向の係合力を
高めるために鋭角的なものとなり、この鋭角的なネジ山
を相互にかみ合せているから、前記における柳と締付ナ
ツト（２）側との接触面が、撲圧入肋に平行な面から、
大幅に傾斜し念ものとなり、この接触面における圧接力
が効果的に枠側に伝達されず、との圧接力伝達部にロス
が生じる。従って、前記の横圧入力に相当する締付ナツ
ト（２）の締付力が、締付筒ｆ：床動輔又は従動軸に圧
接させる力（軸圧液力）Ｋ効率よく変換されないことと
なる。これが既述の問題点の主たる原因である。In other words, by tightening the tightening napft (2), the tightening cylinder α
The mechanism by which υ is pressed against the outer peripheral surface of the driving shaft is a tightening tube (
When a coil-shaped wedge with a cross section (Fig. 7) with a thread added to the wall thickness of the company) is press-fitted into the tightening nut (2) and the outer peripheral surface of the driving shaft (10a) or driven shaft (10b). can be equated with Originally, screws were used to secure tightening force in the axial direction, and the shape of the thread was also made to have an acute angle to increase the engagement force in the axial direction. Because they are interlocked, the contact surface between the willow and the tightening nut (2) side is from the plane parallel to the press-fit rib,
This causes a large inclination, and the pressure contact force on this contact surface is not effectively transmitted to the frame side, resulting in a loss in the pressure contact force transmission section. Therefore, the tightening force of the tightening nut (2), which corresponds to the above-mentioned lateral pressure input, is not efficiently converted to the force (axial pressure hydraulic force) K that presses the tightening tube f: the floor moving member or the driven shaft. Become. This is the main cause of the problems mentioned above.
（技術的ａｌｌ）
本発明け、このような１回転軸に外嵌する締付筒ａＤの
外周に？−パネジ都ａ３を形成してこのテーパネジ部０
３ＫＪＩ付ナツト＋２） １にネジ嵌合させる形式のも
のにおいて、締付ナツト（２）の締付トルクが効率よく
継手部の伝達トルクに変換されるようＫするため、締付
ナツト（２）のネジ嵌合ｆｆ１Ｋおける半径方向の圧接
力が効果的に締付ｍ ａｎ ｍＩＩに作用するようにす
ることをその課厘とする。(Technical All) The present invention is applied to the outer periphery of the tightening cylinder aD that fits around such a one-rotation shaft. - form the pan thread capital a3 and this taper thread part 0
3 KJI nut + 2) In the case of a type that is screwed into 1, in order to efficiently convert the tightening torque of the tightening nut (2) into the transmission torque of the joint, the tightening nut (2) is Its task is to ensure that the radial pressing force in the screw fitting ff1K effectively acts on the tightening m an mII.
（技術的手段）
上記技術的ＦＩＬＭを解決するための本発明の技術的手
段は、締付ナツト（２）の内周及び締付筒αＤの外周に
設けられるテーパネジ部のネジ山を、少なくとも、圧力
側フランクＩのネジ軸線（Ａ）に対する角１１ｉｔ小さ
く設定したネジ山形状としたことである。(Technical Means) The technical means of the present invention for solving the above-mentioned technical FILM is such that the threads of the tapered threaded portion provided on the inner periphery of the tightening nut (2) and the outer periphery of the tightening cylinder αD are at least The screw thread shape is set such that the angle of the pressure side flank I with respect to the screw axis (A) is smaller by 11 it.
（作用）
本発明の上記技術的手段は次のように作用丁ん締付ナツ
ト（２）を所定のトルクで締付けると、締ｆＬｔ＃Ｊａ
υとけテーパネジ部α３で嵌合しているから。(Operation) The above technical means of the present invention operates as follows: When the tightening nut (2) is tightened with a predetermined torque, the tightening fLt#Ja
This is because they fit together at the υ taper thread part α3.
締付ナツトのネジ山のフランクが相手方の締付筒部のネ
ジ山の７ランクに圧接される。一般的には、ネジ山の山
部と谷部の嵌合にわずかの余裕（いわゆるパックラシェ
）があることから、ネジ山の追い剣フランク相互、すな
わち、圧力側フランク相互が他方のフランク相互にくら
べて強く圧接される。The flank of the thread of the tightening nut is pressed against the seventh rank of the thread of the mating tightening cylinder. In general, there is a slight margin (so-called packlash) in the fit between the crests and troughs of the screw threads, so the pressure side flanks are compared to the other flanks. It is strongly pressed.
この圧力側フランクのネジ軸線に対する角度が小さく設
定されていることから、締付ナツト（２）全締付けたと
きの前記フランク相互の圧接力の力の対して直角な方向
から、わずかに傾斜しただけとなり１通常の一般的なネ
ジ山のものＫくらべて。Since the angle of this pressure side flank with respect to the screw axis is set small, the tightening nut (2) is only slightly inclined from the direction perpendicular to the pressure force between the flanks when fully tightened. Next 1Compared to the normal screw thread type K.
圧力側フランク相互の圧接力２゛軸王接力に効果的に変
換されることとなる。The pressure contact force between the pressure side flanks is effectively converted into a 2° axial wrench force.
（効果）
締付ナツト（２）ｔ−締けけることＫよって生じるネジ
山の圧力側７ランジα−の圧接力が効果的に軸圧液力に
変換されるから、一般的なネジ山を採用するものＫくら
べて、締付ナツトの締付トルクが同じであっても伝達ト
ルクが大きくなる。(Effect) The pressure contact force of the 7 langes α- on the pressure side of the screw thread generated by tightening the tightening nut (2) T-K is effectively converted into axial pressure hydraulic force. Compared to the adopted model K, the transmitted torque is larger even if the tightening torque of the tightening nut is the same.
（実施態様）
本発明の実施態様は圧力１１［ＩＪ ７ランジα４の反
対側この実施態様によれば、締付ナツト（２）と締付筒
＋Ｉｌ＋のネジ山の進み剣のフランク相互の圧接力（圧
力側フランクと反対側の７ランク相互の圧接力）も軸線
に直角な方向に近似するから、圧力側の７ランクの庄培
″′ｈふルＬｒ軸鳳沈ｆ鮎繍μ＋ｆ亦礒され、一層伝達
トルクが大きくなる。(Embodiment) In an embodiment of the present invention, a pressure of 11 [IJ 7 On the opposite side of the flange α4, according to this embodiment, the pressure contact force between the flanks of the thread advancing sword of the tightening nut (2) and the tightening cylinder +Il+ (The pressing force between the pressure side flank and the 7 ranks on the opposite side) is also approximated in the direction perpendicular to the axis, so the 7 ranks on the pressure side are , the transmitted torque becomes even larger.
（実施例）
以下１本発明の実施例を第１図〜第５図に基づいて説明
する。(Example) An example of the present invention will be described below with reference to FIGS. 1 to 5.
第１図、第２図に示す第１実施例＃ｉ、ユニバーサルジ
曽ントの一種であるベロー継手に実施したもので、継手
主体（１）としてのベローの両端に外周面にテーパネジ
部ａ３を形成した締付筒αＤを連設し、この締付筒部に
４つの軸線方向のスリット■。The first embodiment #i shown in Figs. 1 and 2 is a bellows joint, which is a type of universal joint, and has tapered threaded portions a3 on the outer peripheral surface at both ends of the bellows as the joint main body (1). The formed tightening cylinder αD is arranged in series, and four axial slits ■ are formed in this tightening cylinder part.
ａ２ヲ開削するとともに同様のテーパネジ部（！３１に
有する締付ナツト（２）をそれぞれの締付筒部に外嵌螺
合させたものである。A2 was drilled and a similar tapered threaded portion (!31) was fitted with a tightening nut (2) externally fitted into each tightening cylindrical portion.
また、この締付篩部及び締付ナツトに形成したテーパネ
ジ部α：１ 、 ［３１は第２図の如く圧力側フランク
Ｃｌ４１がネジ軸線（Ａ）に対してｌＯ度〜美度傾斜し
た逆ノコ歯ネジとしである。In addition, the tapered threaded part α:1, [31] formed on the tightening sieve part and the tightening nut is a reverse saw whose pressure side flank Cl41 is inclined from 10 degrees to the screw axis (A) as shown in FIG. It is a tooth screw.
この実施例のものでは、締付ナツト（２）を締付蝮αＢ
に螺合させて締付けると、ネジ山相互が上記傾斜角度（
１０度〜２０度）に相当するかみ合いで締め込憧れ、最
終締付状急において締付ナツト＋２） ０ＩＩＪから締
付筒［１］、１の外周に作用する圧接力の大部分は圧力
側フランク相互の圧接に＊ｒＬｒ伝達される。In this embodiment, tighten the tightening nut (2) with the tightening ring αB.
When screwed into the
10 degrees to 20 degrees), and in the final tightening state, the tightening nut + 2) from 0IIJ to the tightening cylinder [1], most of the pressure force acting on the outer circumference of 1 is on the pressure side flank. *rLr is transmitted to the mutual pressure contact.
従って、既述した梗効果による圧接力（Ｐ）の方向はと
なる。Therefore, the direction of the pressing force (P) due to the above-mentioned stroke effect is as follows.
次に、第３図に示す第２実施例のものけ１回転体の一種
としての歯車（３）Ｋ第１実施例の締付筒部と同様の締
付筒α１１を連設し、この締付筒に締付ナラ） （２）
’ｋ ［合させるよう処したもので、この場合に＃−
ｉ、、テーパネジ部０のネジ山を、第４図のようにネジ
山角度を鈍角に設定しである。Next, a tightening cylinder α11 similar to the tightening cylinder part of the first embodiment is installed in series with the gear (3) K as a kind of rotary body of the second embodiment shown in FIG. (2)
'k [In this case, #-
i. The thread angle of the tapered threaded portion 0 is set to an obtuse angle as shown in FIG.
この第２病例のものでは、実施態様の項において既述し
たように、一層伝達力が向上する。In this second case, the transmission force is further improved as described in the embodiment section.
この第２実施例のネジ山角度は締付ナツト（２）と締付
筒（Ｉｌｌとがかみ合うかぎり大きい程伝達トルクが大
きくなる。The transmission torque increases as the thread angle of the second embodiment increases as long as the tightening nut (2) and the tightening tube (Ill) are engaged with each other.
例えば、９４図の６値を同じにしてネジ山角度を６０度
、１２０度、１５０度に設定し、このネジ山がネジ軸線
に対して垂直方向に形成されｆｃ４０について比較した
ところ１次の結果が得られた。For example, when the six values in Figure 94 are set to the same value and the thread angles are set to 60 degrees, 120 degrees, and 150 degrees, the threads are formed perpendicular to the screw axis, and when compared for fc40, the first order result is obtained. was gotten.
但し、締付ナツトの締付トルクは４０ｋｇｔｎ−とする
。However, the tightening torque of the tightening nut shall be 40 kgtn-.
このことから、上記した。ネジ山角度を大きく］、たこ
とＫよる効果が、実証できるとともに、ネジ山角度が一
定以上になると、締付ナツト（２）の締付トルク以上の
伝達トルクが生まれることが明らかである。For this reason, as mentioned above. The effect of increasing the thread angle] can be demonstrated, and it is clear that when the thread angle exceeds a certain value, a transmitted torque greater than the tightening torque of the tightening nut (2) is generated.
従って１例えば、１５０度のネジ山角度とした場合には
、締付ナツト（２）を仮り締めするときに主体１１１１
Ｊを作詩する必要があるが、最終締付時Ｋｌ−を保持し
なくてもすべりが生じないこととなり、締付ナツト（２
）が締付やすくなる。Therefore, for example, if the thread angle is 150 degrees, when temporarily tightening the tightening nut (2), the main body 1111
It is necessary to compose J, but slipping does not occur even if Kl- is not held during final tightening, and the tightening nut (2
) becomes easier to tighten.
また、ピッチ一定の条件下では、ネジ山角度が大きくな
るにつれて、締付筒１１１の断面におけるネジ山高さが
その分低くなり、ネジ山の谷底から締付筒αＢの内周面
までの肉厚（実質肉厚）を厚く設定できる。言い換えれ
ば、同一寸法の締付筒αＤにテーパネジ部ａｌｔ−加工
する場合を考えれば、前記理由から、締付筒αＢの実質
肉厚を厚くできることとなり、この部分の強度が増し、
この点で有益である。すなわち、締付ナツト（２）の外
径を小さくしても所定の伝達トリクが得られることとな
る。In addition, under the condition that the pitch is constant, as the thread angle increases, the thread height in the cross section of the tightening tube 111 becomes correspondingly lower, and the wall thickness from the root of the thread to the inner circumferential surface of the tightening tube αB decreases accordingly. (actual wall thickness) can be set thicker. In other words, if we consider the case where the taper thread part alt-processing is performed on the tightening tube αD of the same size, for the above-mentioned reason, the actual wall thickness of the tightening tube αB can be increased, and the strength of this part increases.
It is useful in this respect. That is, even if the outer diameter of the tightening nut (2) is made smaller, a predetermined transmission torque can be obtained.
上記第２実施例では、ネジ山がネジ軸線に対して直立す
るようＫしたが、これを第５図の如く。In the second embodiment, the screw thread was arranged to stand upright with respect to the screw axis, as shown in FIG.
テーパ面に対して直立する構成としてもよい。この場合
も上記実施例と同様の効果が得られた。It may also be configured to stand upright with respect to the tapered surface. In this case as well, the same effects as in the above example were obtained.
また１本発明のトルク伝達継手は、上記のように、軸継
手や回転体固定具等の軸との連結又は取付部に使用でき
るものである。Furthermore, as described above, the torque transmission joint of the present invention can be used for connection or attachment to a shaft of a shaft joint, a rotating body fixture, or the like.
第１図は本発明の第１％施例の分解断面図、第２図はテ
ーパネジ部α３の拡大図、第３図は第２実施例の使用状
態の断面図、第４図はこの場合のテーパネジｓＱ３の拡
大図、第５図はテーパネジ部■の他の変形例の拡大図、
第６図は従来例の説明図、第７図は模作用説明用の断面
図であり１図中（１）・・・・・・継手主体 αＤ・
・・・・・締付筒＠・・・・・・スリット α３・・
・・・・テーパネジ部αＱ・・・・・・圧力側フランク
代理人 弁理士 坂 上 好 博
才ろ１ｎｌｏｂ
才１１ゴ
゛１Fig. 1 is an exploded sectional view of the 1% embodiment of the present invention, Fig. 2 is an enlarged view of the tapered threaded portion α3, Fig. 3 is a sectional view of the second embodiment in use, and Fig. 4 is the An enlarged view of the taper screw sQ3, FIG. 5 is an enlarged view of another modification of the taper screw part ■,
Fig. 6 is an explanatory diagram of the conventional example, and Fig. 7 is a sectional view for explaining the simulation.
...Tightening tube @...Slit α3...
...Taper thread part αQ...Pressure side flank agent Patent attorney Yoshi Sakagami Hiroshiro1nlob Sai11Go1
Claims (1)
パネジ部（１３）を形成してこのテーパネジ部（１３）
に締付ナット（２）をネジ嵌合させる形式のものにおい
て、締付ナット（２）の内周及び締付筒（１１）の外周
に設けられるテーパネジ部のネジ山を、少なくとも、圧
力側フランク（１４）のネジ軸線（Ａ）に対する角度を
小さく設定したネジ山形状としたトルク伝達継手 ［２］、圧力側フランク（１４）の反対側のフランクと
ネジ軸線との角度をも小さく設定し、フランク角度を鈍
角に設定した特許請求の範囲第１項記載のトルク伝達継
手。[Claims] [1] A tapered threaded portion (13) is formed on the outer periphery of a tightening tube (11) that fits around the rotating shaft, and the tapered threaded portion (13)
In the case of a type in which the tightening nut (2) is screwed into the tightening nut (2), the threads of the tapered threads provided on the inner periphery of the tightening nut (2) and the outer periphery of the tightening cylinder (11) are at least connected to the pressure side flank. (14) A torque transmission joint [2] having a screw thread shape with a small angle with respect to the screw axis (A), the angle between the flank on the opposite side of the pressure side flank (14) and the screw axis is also set small, The torque transmission joint according to claim 1, wherein the flank angle is set to an obtuse angle.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60038451A JPH0721288B2 (en) | 1985-02-26 | 1985-02-26 | Torque transmission coupling |
| EP85304389A EP0171156B1 (en) | 1984-07-12 | 1985-06-19 | Shaft coupling |
| DE8585304389T DE3562036D1 (en) | 1984-07-12 | 1985-06-19 | Shaft coupling |
| US06/748,562 US4645473A (en) | 1984-07-12 | 1985-06-25 | Torque transmitting coupling with obtuse screw edge angles |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60038451A JPH0721288B2 (en) | 1985-02-26 | 1985-02-26 | Torque transmission coupling |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61197819A true JPS61197819A (en) | 1986-09-02 |
| JPH0721288B2 JPH0721288B2 (en) | 1995-03-08 |
Family
ID=12525646
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60038451A Expired - Lifetime JPH0721288B2 (en) | 1984-07-12 | 1985-02-26 | Torque transmission coupling |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0721288B2 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6376916A (en) * | 1986-09-18 | 1988-04-07 | Masanori Mochizuki | Friction coupling |
| FR2826078A1 (en) * | 2001-06-19 | 2002-12-20 | Inst Francais Du Petrole | Mechanical transmission connecting single cylinder engine to braking system comprises shaft with plate at each end connected to cheek webs by elastic element adapted to transmit torque |
| JP2009046004A (en) * | 2007-08-20 | 2009-03-05 | Nsk Ltd | Coupling device for steering shaft |
| JP2011042212A (en) * | 2009-08-20 | 2011-03-03 | Jtekt Corp | Electric power steering device |
| JP2012159192A (en) * | 2011-01-28 | 2012-08-23 | General Electric Co <Ge> | Fastener |
| CN105889442A (en) * | 2015-02-16 | 2016-08-24 | 锕玛科技股份有限公司 | Power connection structure of ball screw |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60208618A (en) * | 1984-03-01 | 1985-10-21 | エス ケイ エフ ノーバ エービー | Mechine element fixing apparatus |
| JPH0710835U (en) * | 1993-07-26 | 1995-02-14 | ミツミ電機株式会社 | Magnetic disk device |
-
1985
- 1985-02-26 JP JP60038451A patent/JPH0721288B2/en not_active Expired - Lifetime
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60208618A (en) * | 1984-03-01 | 1985-10-21 | エス ケイ エフ ノーバ エービー | Mechine element fixing apparatus |
| JPH0710835U (en) * | 1993-07-26 | 1995-02-14 | ミツミ電機株式会社 | Magnetic disk device |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6376916A (en) * | 1986-09-18 | 1988-04-07 | Masanori Mochizuki | Friction coupling |
| FR2826078A1 (en) * | 2001-06-19 | 2002-12-20 | Inst Francais Du Petrole | Mechanical transmission connecting single cylinder engine to braking system comprises shaft with plate at each end connected to cheek webs by elastic element adapted to transmit torque |
| JP2009046004A (en) * | 2007-08-20 | 2009-03-05 | Nsk Ltd | Coupling device for steering shaft |
| JP2011042212A (en) * | 2009-08-20 | 2011-03-03 | Jtekt Corp | Electric power steering device |
| JP2012159192A (en) * | 2011-01-28 | 2012-08-23 | General Electric Co <Ge> | Fastener |
| CN105889442A (en) * | 2015-02-16 | 2016-08-24 | 锕玛科技股份有限公司 | Power connection structure of ball screw |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0721288B2 (en) | 1995-03-08 |
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|---|---|---|---|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
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