JPS6334326A - Flexible joint for coupling shaft - Google Patents
Flexible joint for coupling shaftInfo
- Publication number
- JPS6334326A JPS6334326A JP62180214A JP18021487A JPS6334326A JP S6334326 A JPS6334326 A JP S6334326A JP 62180214 A JP62180214 A JP 62180214A JP 18021487 A JP18021487 A JP 18021487A JP S6334326 A JPS6334326 A JP S6334326A
- Authority
- JP
- Japan
- Prior art keywords
- membrane
- flexible joint
- ring
- bolts
- membrane ring
- 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.)
- Pending
Links
- 230000008878 coupling Effects 0.000 title claims description 16
- 238000010168 coupling process Methods 0.000 title claims description 16
- 238000005859 coupling reaction Methods 0.000 title claims description 16
- 239000012528 membrane Substances 0.000 claims description 53
- 238000005452 bending Methods 0.000 claims description 11
- 239000002184 metal Substances 0.000 claims description 8
- 230000002093 peripheral effect Effects 0.000 claims 1
- 239000000463 material Substances 0.000 description 4
- 238000006243 chemical reaction Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000007796 conventional method Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000010408 film Substances 0.000 description 1
- 210000003127 knee Anatomy 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000035515 penetration Effects 0.000 description 1
- 230000002028 premature Effects 0.000 description 1
- 239000004575 stone Substances 0.000 description 1
- 239000010409 thin film Substances 0.000 description 1
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
- 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
- F16D3/78—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 shaped as an elastic disc or flat ring, arranged perpendicular to the axis of the coupling parts, different sets of spots of the disc or ring being attached to each coupling part, e.g. Hardy couplings
- F16D3/79—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 shaped as an elastic disc or flat ring, arranged perpendicular to the axis of the coupling parts, different sets of spots of the disc or ring being attached to each coupling part, e.g. Hardy couplings the disc or ring being metallic
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fuel Cell (AREA)
- Separation Using Semi-Permeable Membranes (AREA)
- Diaphragms And Bellows (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Abstract] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
〔産業上の利用分卦〕
本発明は、少なくとも１つの金属膜環により互いに結合
されている金属従動円板と金属従動円板とを有し、膜間
が、一方では周囲にわたって対をなして均一に分布した
第１群の結合ねじにより駆動円板に取付けられ、他方で
は周囲にわたって対をなして均一に分布して周方向に第
１群の結合ねじと交互に設けられる第２群の結合ねじに
より従動円板に取付けられている、軸の結合用撓み継手
に関する。DETAILED DESCRIPTION OF THE INVENTION [Industrial Application] The present invention has a metal driven disk and a metal driven disk that are connected to each other by at least one metal film ring. on the other hand, by means of a first group of coupling screws uniformly distributed in pairs over the circumference, and on the other hand, arranged uniformly in pairs over the circumference and alternating with the first group of coupling screws in the circumferential direction. The present invention relates to a flexible joint for connecting a shaft, which is attached to a driven disk by means of a second group of connecting screws provided.
この種の撓み継手は潤滑や保守なしに構成されており、
高出力用、産業用及び船舶用駆動装置に益々使用されて
いる。場所的な理由から、撓み継手の直径をできるだけ
小さくすることをしばしば余儀なくされている。他方伝
達可能なトルクは、膜間を駆動円板及び従動円板に結合
するのに役立つ結合ねじ即ちボルトのそれに応じた数を
必要とする。これらの要求により必然的に、このような
撓み継手の弾性的性質即ち軸線方向及び周方向の可撓性
が著しく制限され、早すぎる疲労による故障の危険が増
大する。This type of flexible joint is constructed without lubrication or maintenance,
It is increasingly used in high power, industrial and marine drives. Space considerations often force the diameter of the flexible joint to be made as small as possible. On the other hand, the transmissible torque requires a corresponding number of connecting screws or bolts serving to connect the membranes to the driving and driven discs. These requirements necessarily severely limit the elastic properties, ie, axial and circumferential flexibility, of such flexible joints, increasing the risk of failure due to premature fatigue.
この種の撓み継手において、ピッチ円上に等間隔で設け
られている４本、６本、８本、１０本又はそれ以上のボ
ルトにより、膜間を交互に駆動円板と従動円板とに結合
することは公知である。駆動円板にある各ボルトから、
膜間によりボルトからボルトへ形成される結合部材を介
して、適当な調合のトルクが従動円板にあって隣接する
ボルトへ伝達される。例えば４本のボルトを持つ撓み継
手は２本の駆動ボルト及び２本の従動ボルトを持ち、６
本のボルトを持つ撓み継手は３本の駆動ボルト及び３本
の従動ボルトを持っている。撓み継手の軸線方向剛性は
ボルトの数につれて非常に速やかに増大し、取付は点に
おける膜間の局部応力はこのような撓み継手の有効出力
を著しく制限する。In this type of flexible joint, 4, 6, 8, 10 or more bolts equally spaced on a pitch circle alternately connect the drive and driven discs between the membranes. Coupling is known. From each bolt on the drive disc,
Via the coupling members formed from bolt to bolt by means of the membranes, the torque of the appropriate proportion is transmitted to the adjacent bolt in the driven disc. For example, a 4-bolt flexible joint has 2 driving bolts and 2 driven bolts, and 6 bolts.
A double bolted flexible joint has three driving bolts and three driven bolts. The axial stiffness of a flexible joint increases very quickly with the number of bolts, and the local stress between the membranes at the point of attachment significantly limits the effective output of such a flexible joint.
ボルトにより膜間を円板に取付ける普通のやり方は、撓
み継手の周方向撓みの際膜間が曲げられる時許容できな
い程大きい応力を回避するため、環状に丸められた稜を
持つ円形座金を使用することである。The usual method of attaching the membrane to the disc by means of bolts is to use circular washers with annularly rounded edges to avoid unacceptably large stresses when the membrane is bent during circumferential deflection of the flexible joint. It is to be.
本発明の諜顆は、公知の撓み継手に比較して、軸線方向
及び周方向可ｉ性のような弾性的性質を維持しながら、
同じ寸法で著しく大きいトルクを伝達可能なこの種の撓
み継手を構成することである。更に膜間の締付は個所に
おける許容できない程大きい応力が回避されるように撓
み継手を構成する。The condyle of the present invention maintains elastic properties such as axial and circumferential flexibility compared to known flexible joints, while maintaining elastic properties such as axial and circumferential flexibility.
The object is to construct a flexible joint of this type which is capable of transmitting significantly greater torques with the same dimensions. Furthermore, the clamping between the membranes constitutes a flexible joint in such a way that unacceptably high stresses at points are avoided.
最初に述べた種類の撓み継手から出発して、この課題を
解決するため本発明によれば、駆動円板と従動円板が、
１つの群の隣接する結合ねじの間で半ピッチ又はそれ以
下だけ互いにずれた周囲位置に設けられている少なくと
も２つの並ダ１接続された膜間により結合され、両方の
膜間の結合ねじが１つ又は隣接する同心ピッチ円上にあ
り、膜間が、それらの周囲において順次に統く２つの結
合ねじの間に、周縁がそれぞれ他方の膜間の結合ねじの
半径方向鳴に延びるような深さのウェスト状くびれをそ
れぞれ持っている。To solve this problem, according to the invention, starting from a flexible joint of the type mentioned at the outset, the driving disc and the driven disc are
connected by at least two parallel connected membranes arranged circumferentially offset from each other by half a pitch or less between adjacent connecting screws of a group, the connecting screws between both membranes between two coupling screws on one or adjacent concentric pitch circles and whose membranes run one after the other around their periphery, such that the periphery extends in the radial direction of the coupling screw between each other membrane; Each has a deep waist-like constriction.
一体の膜間の代りに、周方向に複数に分割して構成され
た膜間も使用できる。Instead of a single membrane, membranes divided into a plurality of parts in the circumferential direction can also be used.
本発明により得られる主な利点は、２つの並列接続され
る膜間の使用により、車−の膜間を持つ撓み継手に比較
して、実際上２倍の大きさのトルクが伝達可能で、弾性
的性質における制限を甘受する必要のないことである。The main advantages provided by the invention are that by using two parallel connected membranes, practically twice as much torque can be transmitted as compared to a flexible joint with a vehicle membrane; There is no need to accept limitations in elastic properties.
これは大体において、２ｎ本のボルトを持つ２つのｌＩ
り環を重ねるため膜間をウェスト状にして、ｎ本のボル
トを持つ１つの膜間の弾性で２ｎ本のボルトを持つトル
ク出力をこのような撓み継手により生ずることによって
達せられる。This is roughly equivalent to two lIs with 2n bolts.
This is achieved by creating a torque output with 2n bolts with elasticity between one membrane with n bolts by such a flexible joint, with the membranes forming a waist shape for overlapping rings.
締付は個所における許容できない程大きい応力を回避す
るため、これらの個所において両側に金属から成る支持
板を設けると有利である。In order to avoid unacceptably high stresses at the tightening points, it is advantageous to provide support plates made of metal on both sides at these points.
これらの支持板はなるべく曲げ弾性を持つように石Ｉ牟
成できる。These supporting plates can be made of stone so as to have as much bending elasticity as possible.
支持板は締付は取付は個所において膜環を支持し、座金
の丸められた稜に生ずることのあるような小さすぎる曲
率半径を防止する。The support plate supports the membrane ring at the tightening point and prevents too small a radius of curvature, such as can occur with rounded edges of the washer.
本発明の実施例が図面に示されており、以下これについ
て説明する。An embodiment of the invention is shown in the drawing and will be described below.
従来例を示す第１図において、膜環ｌは４本のボルトを
持つ特別の形状をしており、２本のボルト２及び３は駆
動ボルト、２本のボルト４及び５は従動ボルトである。In FIG. 1 showing a conventional example, the membrane ring l has a special shape with four bolts, two bolts 2 and 3 are driving bolts, and two bolts 4 and 5 are driven bolts. .
締付は座金６は、ボルト２からボルト５への結合部材に
おいて曲げスパンＬｌを可能にする。The tightening washer 6 allows a bending span Ll in the connection member from the bolt 2 to the bolt 5.
同様に従来例を示す第２図は６本のボルトを持つ成環を
示し、３本のボルト７、８．９は駆動ボルト、３本のボ
ルト１０．１１．１２は従動ボルトであり、曲げスパン
Ｌ２を持っている。Similarly, Fig. 2, which shows a conventional example, shows a ring assembly with six bolts, three bolts 7, 8.9 are driving bolts, three bolts 10, 11, 12 are driven bolts, and bending It has span L2.
従来例を示す第３図は８本のボルトを持つ膜環を示し、
４本のボルト１３．１４．１５．１６は駆動ボルト、４
本のボルト１７．１８．１９．２０は従動ボルトであり
、曲げスパンＬ３を持っている。Figure 3, which shows a conventional example, shows a membrane ring with eight bolts.
4 bolts 13.14.15.16 are drive bolts, 4
The main bolts 17, 18, 19, 20 are driven bolts and have a bending span L3.
第４図は本発明によりそれぞれ４本のボルトを持つ膜環
から成る８本のボルトを有する二重系を示している。４
本の駆動ボルト２１．２２．２３゜２４と同様に４本の
従動ボルト２５．２６．２７．２８は、図においてそれ
ぞれ対をなして横に並んで設けられている。注意すべき
ことは、油げスパンＬｌが第１図におけると同様で、Ｌ
ｌ≧２．５×Ｌ３となっていることである。後述する計
算かられかるように、結合部材において駆動ボルトと従
動ボルトとの相対軸線方向移動は、以下のように引張り
応力と軸線方向反力とを生ずる。FIG. 4 shows a double system according to the invention with eight bolts consisting of a membrane ring with four bolts each. 4
Four driven bolts 25, 26, 27, 28, as well as the main driving bolts 21, 22, 23, 24, are arranged side by side in pairs in the figure. It should be noted that the oil span Ll is the same as in Fig. 1, and L
This means that l≧2.5×L3. As can be seen from the calculations described below, relative axial movement between the driving bolt and the driven bolt in the coupling member produces a tensile stress and an axial reaction force as follows.
第３図のような８本のボルトを持つ継手では、軸線方向
の反作用は第４図のような８本のボルトを持つ継手にお
けるより約１５倍大きい。同じように引張り応力は第４
図におけるより約６倍大きくなる。In a joint with eight bolts, such as in FIG. 3, the axial reaction is approximately 15 times greater than in a joint with eight bolts, such as in FIG. Similarly, tensile stress is the fourth
It is about 6 times larger than in the figure.
第５図は締付は座金３０．３１．３２を持つ２つの隣接
する膜薄結合部材２９を”示している。図はスパンＬを
持ち３３におけるような湾曲状１褒にある膜環を示す。FIG. 5 shows two adjacent membrane coupling members 29 with fastening washers 30, 31, 32. The figure shows a membrane ring in a curved position as in 33 with a span L. .
Ｆ ＝ Ｅａ （２）３ ５ニー！−（１）２Ｌ
２Ｌ
ここでＦ＝２つの隣接する結合部材から生ずる軸線方向
推力
Ｓ＝＝合部材に生ずる引張り応力
ｙ＝１つの結合部材のスパン
ａ ＝＝ １つの結合部材の断面積
Ｅ＝膜膜材材料弾性係数
前記の式かられかるように、継手の軸線方向剛性は結合
部材のスパンの３乗に反比例し、生ずる応力はスパンの
２乗に反比例している。これから、第３図の構成に対す
る第４図の構成の利点がわかる。同様な考察が、もつと
多数即ち１０本、１２本等のボルトを持つ継手について
も当てはまる。F = Ea (2) 3 5 knees! -(1) 2L
2L Here, F = Axial thrust S generated from two adjacent connecting members = Tensile stress generated on the joining member y = Span a of one connecting member = Cross-sectional area of one connecting member E = Elasticity of membrane material material Coefficients As can be seen from the above equations, the axial stiffness of the joint is inversely proportional to the cube of the span of the connecting members, and the resulting stress is inversely proportional to the square of the span. From this it can be seen that the advantages of the configuration of FIG. 4 over the configuration of FIG. 3 can be seen. Similar considerations apply to joints having a large number of bolts, such as 10, 12, etc.
第６図は、第４図に示した原理を含む８本のボルトを持
つ継手の特有の構造を例として示している。２つの同様
な駆動円板及び従動円板としての剛性環３４及び３５が
二重膜憚を保持している。ボルト３６．３７．３８．３
９により２つの膜環積層の駆動隅が従動継手環部分３４
に取付けられ、ボルト４０．４１．４２．４３により２
つの膜環積層の従動隅が従動継手環部分３５に取付けら
れている。駆８１１１環を駆動軸のボスに取付けるため
多数のねじ貫通口４４を使用し、従動環を継手の間隔片
に取付は更に第６図と同様な第２の撓み継手を介して従
動軸に取付けるため対応する貫通口４５を従動環３５に
使用するのがよい。FIG. 6 shows by way of example a specific construction of a joint with eight bolts, which includes the principle shown in FIG. Two similar rigid rings 34 and 35 as driving and driven discs hold the double membrane. Bolt 36.37.38.3
9, the drive corner of the two membrane ring stacks is connected to the driven joint ring portion 34.
2 by bolts 40.41.42.43.
The driven corners of the two membrane ring stacks are attached to the driven joint ring portion 35. A number of threaded holes 44 are used to attach the drive ring to the boss of the drive shaft, and the driven ring is attached to the spacing piece of the joint, and is further attached to the driven shaft via a second flexible joint similar to that shown in Fig. 6. Therefore, it is preferable to use a corresponding through hole 45 in the driven ring 35.
第８図と第９図及び第、９ａ図には、自由に撓む膜環を
ボルトにより剛性ボスへ取付ける通常の方法の欠点が示
され、第７図及び第７ａ図は本発明により与えられる解
決策を示している。8 and 9 and 9a illustrate the disadvantages of the conventional method of attaching a freely deflecting membrane ring to a rigid boss by means of bolts; FIGS. 7 and 7a are provided by the present invention. Shows a solution.
第８図はフランジ４７にねじ止めされたＨａ積層４６を
示し、この膜環積層は第５図に示すように湾曲され、鋭
い稜を持つ２つの座金４８及び４９によりＡの所に締付
けられている。結合部材の引張り力Ｔは、（ａ）継手か
ら伝達されるトルクと（ｂ）第５図に示す湾曲から生ぐ
る。点Ａにおける応力は次の３つの重なる応力の和であ
る。FIG. 8 shows a Ha stack 46 screwed to a flange 47, the membrane ring stack being tightened at A by two curved and sharp edged washers 48 and 49 as shown in FIG. There is. The tensile force T in the coupling member results from (a) the torque transmitted from the joint and (b) the curvature shown in FIG. The stress at point A is the sum of the following three overlapping stresses:
（ａ）力Ｔによる引張り応力
（ｂ）力Ｔのため点Ａに生ずる曲げ応力（ｃ）座金４９
とこれに当る膜環との接触の仕方により点Ａに集まる応
力
第９図は、（ｂ）及び（Ｃ）に述べた曲げ応力を減少す
る普通のやり方を示す。締付は座金５０及び５１は点Ｂ
に曲率半径Ｑ丸められた稜を持ち、直径ＤＩから直径Ｄ
２へ延びる環状表面Ｃが生ずる。この方法は次の欠点を
持っている。(a) Tensile stress due to force T (b) Bending stress produced at point A due to force T (c) Washer 49
Figure 9 shows the usual way to reduce the bending stresses mentioned in (b) and (c). Tighten washers 50 and 51 at point B
has a rounded edge with a radius of curvature Q, and a radius of curvature Q from the diameter DI to the diameter D
An annular surface C is created which extends to 2. This method has the following drawbacks.
（ａ）曲率半径ｐを大きくして膜環の曲げ応力を少なく
するいかなる試みも、同時に直径Ｄ１を小さくシ、従っ
て膜環の適当な締付けをそこなう。(a) Any attempt to reduce the bending stress in the membrane ring by increasing the radius of curvature p simultaneously reduces the diameter D1, thus impairing proper tightening of the membrane ring.
（ｂ）湾曲状態で膜環は、軸線ｘ−ｘに沿って引張り力
Ｔに対し直角に曲がる傾向がある。(b) In the curved state, the membrane ring tends to bend at right angles to the tensile force T along the axis x-x.
座金５０と膜環との点りにおける接触は、面Ｙ−Ｙ上で
ｘ−Ｘに対し直角に延び、曲げられる膜環の部分ａ及び
ｂは全く支持されないままであり、点りに別の複合応力
が生じ、いずれも引張り力Ｔに関係する。The contact between the washer 50 and the membrane ring at the point extends on the plane Y-Y at right angles to Complex stresses result, both related to the tensile force T.
第７図及び第７ａ図は本発明により片側を締付けられる
支持板を示し、この支持板は前述した欠点を受けない。7 and 7a show a one-sided clamped support plate according to the invention, which support plate does not suffer from the drawbacks mentioned above.
膜環積Ａ’ｊ５２は２つの円形座金５３と５４との間に
２つの支持板５５と５６を介して締付けられ、これらの
支持板は膜環の隅の輪郭にほぼ一致している。長方形断
面を持つ板が曲がると、応力と曲率半径との関係は次の
通りになる。The membrane ring area A'j 52 is clamped between two circular washers 53 and 54 via two support plates 55 and 56, which approximately correspond to the corner contours of the membrane ring. When a plate with a rectangular cross section is bent, the relationship between stress and radius of curvature is as follows.
ｔ ｐ ここでＳ＝曲げ応力 ｔ＝板の厚さ ｐ＝曲げによる曲率半径 Ｅ＝材料の弾性係数 次の特徴はこれらの板の構成にとって重要である。t p Here S = bending stress t=thickness of plate p = radius of curvature due to bending E = elastic modulus of material The following features are important to the construction of these plates.
（ａ）板の寸法即ち厚さｔと突出長ｌは、曲率半径ρを
できるだけ大きくシ、板を膜環の湾曲に追従させること
によって、膜環の湾曲及びその応力を小さくするように
選ぶことができる。(a) The dimensions of the plate, that is, the thickness t and the protrusion length l, are selected so that the radius of curvature ρ is as large as possible and the plate follows the curvature of the membrane ring, thereby minimizing the curvature of the membrane ring and its stress. Can be done.
（ｂ）板と隣接する板は軸線ｘ−Ｘに沿って曲げられ、
それにより第９図の点りに応力が集まるのを回避される
。(b) the plate and the adjacent plate are bent along the axis x-X;
This avoids stress from gathering at the dots in FIG.
（ｃ）板の長さｌは曲率半径ｐを最適化するように定め
ることができ、これは特に第４図に示す結合部材のかな
りの長さし１で可能である。(c) The length l of the plate can be determined in such a way as to optimize the radius of curvature p, which is possible in particular with the considerable length 1 of the coupling member shown in FIG.
（ｄ）板５５及び５６は膜環による曲げのみを受け、膜
環の結合部材の全応力に作用する引張り力Ｔの形番を受
けない。(d) Plates 55 and 56 are only subjected to bending by the membrane ring and are not subjected to the tensile force T acting on the total stress of the connecting member of the membrane ring.
（ｅ）板は継手により伝達されるトルクに寄与せず、そ
の形番も受けない。板ば通常膜薄用に使用されるのとは
興なる材料から製造でき、従って通常は族環用に規定さ
れる程度を越える聞は応力を受は止めるため硬化及び熱
処理可能である。(e) The plate does not contribute to the torque transmitted by the joint and does not receive its model number. The plates can be made from materials different from those normally used for thin films and can therefore be hardened and heat treated to resist stresses beyond those normally specified for group rings.
（ｆ）上述した板はなるべく弾性部材として作用し、従
って荷重を受けない状態で通常は平らである。その代り
に板５５で示すように変形して製造することもできる。(f) The above-mentioned plates preferably act as elastic members and are therefore normally flat in the unloaded state. Alternatively, it can be manufactured in a modified form as shown by plate 55.
第１図ないし第３図は結合ねじ貫通口と締付は取付は座
金と結合の適当なスパンを示す公知の描込の３つの膜環
の正面図、第４図はそれぞれ４つのボルト貫通口を持つ
２つの本発明により重ねられた膜環の正面図、第５図は
湾曲した膜環の側面図、第６図は本発明による８本のボ
ルトを持つ撓み継手の正面図、第７図及び第７ａ図は本
発明による膜環の締付は個所の断面図、第８図と第９図
及び第９ａ図は従来の膜環の締付は個所の断面図である
。
２１〜２４．３６〜３９・・・駆動用結合ねじ（ボルト
）、２５〜２８１４０〜４３・・・従動用結合ねじ（ボ
ルト）、３４・・・駆動円板（環）、３５・・・従動円
板（環）。
ニＴ万１１ 二Ｔ万ｒ２
１ 、、、、、ｖｔｃａ
１５ １９．、、ボ、、ト２ 、、、、、ボル
ト １６ ・・・・・１ル
８３ 、、、、、ボルト
１７ 、、、、、ボＪレト／、 、、、、、ボル
ト １８ 、、、、、ボ
ルトＳ 、、、、、□、、Ｆ、１９ 、、、、、ボ
ルト６ 、、、、、 ｎ付は座金
２０ 、、、、、ボルト７ 、、、、、ボル
ト ２１ 、、、、、ボ
少しト８ 、、、、、ボルト
２２ 、、、、、ボＪレト９ 、、、、、ボ
ルト ２３ 、、、、、
ボルトｉｏ 、、、、、□、、、２４ 、、、、、
ボルト１１ 、、、、、ボルト
２５ 、、、、、ボルトト１２ 、、、、
、 、、、 ）、２６ 、、、、、ボルト１３ 、
、、、、ボルト ２７
、、、、、ボルト１４ 、、、、、ボルト
２８ 、、、、、ボ、レト二０１
ｓ ｊ口１◆
３８ 、、、、、ボルト Ｙ
、、、、、スパン；３ 、、．０．ｓ分
５阿？δ ｂ 、、、、、あ。
Ａ 、、、、、 点
１ 、、、、。Figures 1 to 3 are front views of three membrane rings of known drawings showing the coupling screw through holes, mounting washers, and appropriate spans for the coupling, and Figure 4 each shows four bolt penetration holes. FIG. 5 is a side view of a curved membrane ring; FIG. 6 is a front view of a flexible joint with eight bolts according to the invention; FIG. 7 7a is a cross-sectional view of the tightening portion of the membrane ring according to the present invention, and FIGS. 8, 9, and 9a are cross-sectional views of the tightening portion of the conventional membrane ring. 21-24. 36-39... Drive coupling screw (bolt), 25-28140-43... Drive coupling screw (bolt), 34... Drive disk (ring), 35... Driven Disc (ring). 2T million 11 2T million r2 1 ,,,,vtca
15 19. ,,Bo,,To2 ,,,,,Bolt 16...1le83 ,,,,,Bolt
17 , , , , Bolt J / , , , , , Bolt 18 , , , , Bolt S , , , , □ , , F, 19 , , , , Bolt 6 , , , with n is washer
20 , Bolt 7 , Bolt 21 , Bolt 8 , Bolt
22 ,,,,,Boruto 9,,,,,Boruto 23,,,,,,
Bolt io , , , □ , , 24 , , , ,
Bolt 11 ,,,,, bolt
25 , , , Bolt 12 , , ,
, , , ), 26 , , , bolt 13 ,
,,,, bolt 27
, , , , bolt 14 , , , , bolt
28 ,,,,,Bo, Reto201
s j mouth 1◆ 38 , , , , bolt Y
,,,,,span;3,,. 0. s minutes 5 hours? δ b ,,,,,ah. A,,,,, point
1.
Claims (1)
いる金属駆動円板と金属従動円板とを有し、膜環が、一
方では周囲にわたつて対をなして均一に分布した第１群
の結合ねじにより駆動円板に取付けられ、他方では周囲
にわたつて対をなして均一に分布して周方向に第１群の
結合ねじと交互に設けられる第２群の結合ねじにより従
動円板に取付けられているものにおいて、駆動円板と従
動円板が、１つの群の隣接する結合ねじの間で半ピッチ
又はそれ以下だけ互いにずれた周囲位置に設けられてい
る少なくとも２つの並列接続された膜環により結合され
、両方の膜環の結合ねじが１つ又は隣接する同心ピッチ
円上にあり、膜環が、それらの周囲において順次に続く
２つの結合ねじの間に、周縁がそれぞれ他方の膜環の結
合ねじの半径方向内側に延びるような深さのウェスト状
くびれをそれぞれ持つていることを特徴とする、軸の結
合用撓み継手。 ２ 各膜環が周方向に複数に分割して構成されているこ
とを特徴とする、特許請求の範囲第１項に記載の撓み継
手。 ３ 各膜環が付属する結合ねじの数に等しい数の同じ部
材から構成されていることを特徴とする、特許請求の範
囲第２項に記載の撓み継手。 ４ 膜環の締付け取付け個所即ち結合ねじの所において
膜環の両側に、金属から成る支持板が設けられているこ
とを特徴とする、特許請求の範囲第１項ないし第３項の
１つにに記載の撓み継手。 ５ 支持板が曲げ弾性を持つように構成されていること
を特徴とする、特許請求の範囲第４項に記載の撓み継手
。[Scope of Claims] 1 A metal driving disk and a metal driven disk connected to each other by at least one metal membrane ring, the membrane rings being uniformly distributed in pairs over the circumference on the one hand; on the other hand, a second group of connecting screws arranged uniformly in pairs over the circumference and alternating with the first group of connecting screws in the circumferential direction; at least two circumferential positions, in which the driving disk and the driven disk are arranged at circumferential positions offset from each other by half a pitch or less between adjacent coupling screws of a group. connected by two parallel-connected membrane rings, the connecting screws of both membrane rings lie on one or adjacent concentric pitch circles, and the membrane rings are connected between two connecting screws that follow one after another around their periphery; Flexible joint for connecting shafts, characterized in that the peripheral edge each has a waist-like constriction of such depth that it extends radially inwardly of the connecting thread of the other membrane ring. 2. The flexible joint according to claim 1, wherein each membrane ring is divided into a plurality of parts in the circumferential direction. 3. Flexible joint according to claim 2, characterized in that each membrane ring is constructed from a number of identical parts equal to the number of associated connecting screws. 4. In accordance with one of the claims 1 to 3, characterized in that support plates made of metal are provided on both sides of the membrane ring at the tightening point of the membrane ring, i.e. at the connecting screw. Flexible joints described in . 5. The flexible joint according to claim 4, wherein the support plate is configured to have bending elasticity.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB868618282A GB8618282D0 (en) | 1986-07-26 | 1986-07-26 | Flexible couplings |
| GB8618282 | 1986-07-26 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS6334326A true JPS6334326A (en) | 1988-02-15 |
Family
ID=10601742
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP62180214A Pending JPS6334326A (en) | 1986-07-26 | 1987-07-21 | Flexible joint for coupling shaft |
Country Status (8)
| Country | Link |
|---|---|
| JP (1) | JPS6334326A (en) |
| CN (1) | CN87105237A (en) |
| BR (1) | BR8703849A (en) |
| DE (1) | DE3722511A1 (en) |
| FI (1) | FI873194A (en) |
| FR (1) | FR2602016A1 (en) |
| GB (2) | GB8618282D0 (en) |
| IT (1) | IT1211656B (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6246034A (en) * | 1986-07-31 | 1987-02-27 | Nissin Kogyo Kk | Disc brake |
| JPH02116040U (en) * | 1989-03-07 | 1990-09-17 | ||
| JP4987158B1 (en) * | 2011-07-13 | 2012-07-25 | 保男 平山 | Flexible plate and leaf spring type flexible coupling using the flexible plate |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4016235C1 (en) * | 1990-05-16 | 1991-09-19 | Mannesmann Ag, 4000 Duesseldorf, De | Flexible coupling for rotating shaft - incorporates hollow square coupling member bolted to shaft flanges |
| DE10017512A1 (en) | 2000-04-10 | 2001-10-18 | Atec Weiss Gmbh & Co Kg | Ring plate for flexible shaft couplings, plate pack formed from such ring plates and flexible shaft coupling with such ring plates |
| RU2533007C1 (en) * | 2013-04-12 | 2014-11-20 | Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Алтайский государственный технический университет им. И.И. Ползунова" (АлтГТУ) | Resilient coupling (versions) |
| GB2514386B (en) | 2013-05-22 | 2019-07-31 | Euroflex Trans Limited | Flexible shaft coupling |
| RU2533859C1 (en) * | 2013-06-27 | 2014-11-20 | Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Алтайский государственный технический университет им. И.И. Ползунова" (АлтГТУ) | Coupling (versions) |
| RU2533012C1 (en) * | 2013-06-27 | 2014-11-20 | Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Алтайский государственный технический университет им. И.И. Ползунова" (АлтГТУ) | Coupling (versions) |
| US9458891B2 (en) * | 2014-06-16 | 2016-10-04 | Goodrich Corporation | Contoured disc coupling |
| CN105108915A (en) * | 2015-09-24 | 2015-12-02 | 金方明 | Main shaft transmission mechanism connecting piece of large stone cutter |
| CN111577780B (en) * | 2020-05-22 | 2021-06-08 | 中国船舶科学研究中心 | Elastic diaphragm coupling |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1283723A (en) * | 1969-10-14 | 1972-08-02 | Kaman Aerospace Corp | Flexible coupling |
| AT303466B (en) * | 1970-04-27 | 1972-11-27 | Leonhard Geislinger Dr Ing | Flexible coupling |
| FR2114660A5 (en) * | 1970-11-14 | 1972-06-30 | Atec Weiss Kg | |
| US4055966A (en) * | 1975-10-10 | 1977-11-01 | Rexnord, Inc. | Torque transmission coupling |
| US4321805A (en) * | 1979-06-01 | 1982-03-30 | Kaman Aerospace Corporation | Rotary drive flexible coupling |
| EP0082797A3 (en) * | 1981-12-22 | 1983-08-17 | Rexnord Inc. | Double-flexing coupling in a parallel arrangement |
| DE8414654U1 (en) * | 1984-05-14 | 1984-08-02 | Voith-Turbo Gmbh & Co Kg, 7180 Crailsheim | TENSIONER, BOW-ELASTIC SHAFT COUPLING |
-
1986
- 1986-07-26 GB GB868618282A patent/GB8618282D0/en active Pending
-
1987
- 1987-07-08 DE DE19873722511 patent/DE3722511A1/en not_active Withdrawn
- 1987-07-16 IT IT8748184A patent/IT1211656B/en active
- 1987-07-20 FI FI873194A patent/FI873194A/en not_active Application Discontinuation
- 1987-07-20 GB GB08717106A patent/GB2192969A/en not_active Withdrawn
- 1987-07-21 JP JP62180214A patent/JPS6334326A/en active Pending
- 1987-07-24 BR BR8703849A patent/BR8703849A/en unknown
- 1987-07-24 FR FR8710570A patent/FR2602016A1/en not_active Withdrawn
- 1987-07-25 CN CN198787105237A patent/CN87105237A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6246034A (en) * | 1986-07-31 | 1987-02-27 | Nissin Kogyo Kk | Disc brake |
| JPH0112974B2 (en) * | 1986-07-31 | 1989-03-02 | Nisshin Kogyo Kk | |
| JPH02116040U (en) * | 1989-03-07 | 1990-09-17 | ||
| JP4987158B1 (en) * | 2011-07-13 | 2012-07-25 | 保男 平山 | Flexible plate and leaf spring type flexible coupling using the flexible plate |
Also Published As
| Publication number | Publication date |
|---|---|
| FI873194A (en) | 1988-01-27 |
| DE3722511A1 (en) | 1988-01-28 |
| GB8618282D0 (en) | 1986-09-03 |
| IT8748184A0 (en) | 1987-07-16 |
| GB2192969A (en) | 1988-01-27 |
| GB8717106D0 (en) | 1987-08-26 |
| FR2602016A1 (en) | 1988-01-29 |
| FI873194A0 (en) | 1987-07-20 |
| IT1211656B (en) | 1989-11-03 |
| CN87105237A (en) | 1988-02-10 |
| BR8703849A (en) | 1988-03-29 |
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