JP2012102785A - Shaft coupling - Google Patents

Shaft coupling Download PDF

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JP2012102785A
JP2012102785A JP2010250606A JP2010250606A JP2012102785A JP 2012102785 A JP2012102785 A JP 2012102785A JP 2010250606 A JP2010250606 A JP 2010250606A JP 2010250606 A JP2010250606 A JP 2010250606A JP 2012102785 A JP2012102785 A JP 2012102785A
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Prior art keywords
spacer
shaft coupling
hub
members
hubs
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JP5280423B2 (en
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Toru Otojima
透 音島
Hiroshi Shinke
博 新家
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Tsubakimoto Chain Co
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Tsubaki Emerson Co
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    • 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
    • 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Clamps And Clips (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a shaft coupling having a large allowable amount of parallel eccentricity, and assuring good easiness in handling with a compact configuration.SOLUTION: The shaft coupling 10 is composed of pressing members 11 and 21, discs 12 and 22, hubs 14 and 24 having bosses 14b and 24b, annular wedge members 16 and 26, and a spacer 30. The pressing members 11 and 21, hubs 14 and 24, and wedge members 16 and 26 are furnished with respective shaft holes 18 and 28 to admit insertion of a shaft. The spacer 30 is arranged between the hubs 14 and 24. Because the distance between the discs 12 and 22 is long and the pressing members 11 and 21 are arranged in such a manner as directed from the spacer 30 toward the discs 12 and 22, the shaft coupling 10 is configured compactly and has a large allowable amount of parallel eccentricity. As only the bosses 14b and 24b and the pressing members 11 and 21 having small wall thickness exist at the inner circumferences of the discs 12 and 22, it is possible to enlarge the shaft holes 18 and 28.

Description

本発明は、軸と軸をつなぐための軸継手に関する。   The present invention relates to a shaft coupling for connecting a shaft and a shaft.

軸継手は、軸を延長したり、一方の軸から他方の軸へ動力を伝達するために使用され、従来から種々のものが提案されている。
その例として、特許文献１〜３に示すものがある。 BACKGROUND ART A shaft coupling is used for extending a shaft or transmitting power from one shaft to the other, and various types have been proposed in the past.
Examples thereof include those shown in Patent Documents 1 to 3.

実開昭６３−３０６２７号公報Japanese Utility Model Publication No. 63-30627 実公平６−６２５１号公報No. 6-6251 特開２００４−１９７８４０号公報JP 2004-197840 A

特許文献１には、フランジハブのボス部のテーパ状外周面に、突き当てを有するテーパスリーブが嵌合された、軸継手が開示されている。特許文献１の考案によれば、テーパスリーブの突き当てにより、フランジハブの鍔部のねじ孔にボルトがねじ込まれた際に生じる鍔部の変形を阻止できる、とされている。
特許文献２の考案は、雄テーパリングの後端面がボス部の端面から突出しないようにし、ボス部の端面にボルト頭部を収納する切欠部が形成された軸継手である。特許文献２によると、このような構成とすることで、ボルトを締めた際にフランジハブが軸方向に移動するのを防止できる、とされている。
特許文献３は、締付け部材の回転操作に伴って、締結具が軸方向に変位する、回転体と軸の締結構造を開示する。特許文献３の発明は、締付け部材の回転操作だけで簡単に締結及び解除ができ、また、取付け精度の向上、回転体の加工コストを低減できる、という効果を奏する、とされている。 Patent Document 1 discloses a shaft coupling in which a tapered sleeve having a butting is fitted to a tapered outer peripheral surface of a boss portion of a flange hub. According to the device of Patent Literature 1, it is possible to prevent deformation of the flange portion that occurs when a bolt is screwed into the screw hole of the flange portion of the flange hub by abutting the taper sleeve.
The invention of Patent Document 2 is a shaft coupling in which a rear end surface of a male taper ring does not protrude from an end surface of a boss portion, and a notch portion for accommodating a bolt head is formed on the end surface of the boss portion. According to Patent Document 2, such a configuration can prevent the flange hub from moving in the axial direction when the bolt is tightened.
Patent Document 3 discloses a fastening structure of a rotating body and a shaft in which a fastener is displaced in the axial direction in accordance with a rotation operation of a fastening member. The invention of Patent Document 3 is said to be advantageous in that it can be easily fastened and released simply by rotating the fastening member, and can improve the mounting accuracy and reduce the processing cost of the rotating body.

使い勝手が良く、狭いスペースでも使用可能な軸継手を提供するためには、以下の点を具えた軸継手であることが要請される。
１．軸継手の全長が短く、軸孔の大きさが大きい。
２．許容される平行偏心量が大きい。
３．ハブを軸に固定する際の軸方向の位置決めが容易。
４．軸継手の伝達トルクが大きい。
５．楔部材の修理、取替えが容易。
特許文献１の考案は、ハブの軸方向の長さが長いため、許容される平行偏心量が小さい、という問題がある。
特許文献２の考案は、ハブのボス部にテーパ状の孔を設けているため、軸孔が小さくなる欠点がある。
そして、特許文献３の発明は、締付け部材を回転させる際、スプロケットが軸方向に移動するため、スプロケットの位置決めが困難である。
また、特許文献１〜３の発明、考案ともに、スリップが発生した場合、ハブやスプロケットそのものを交換しなければならないため、コストや時間がかかる上、熱処理により、歪みが発生した場合は、歪みを矯正する必要が生じる。 In order to provide a shaft coupling that is easy to use and can be used even in a narrow space, a shaft coupling having the following points is required.
1. The overall length of the shaft coupling is short and the size of the shaft hole is large.
2. Large allowable amount of parallel eccentricity.
3. Easy axial positioning when fixing hub to shaft.
4). The transmission torque of the shaft coupling is large.
5. Easy repair and replacement of wedge members.
The device of Patent Document 1 has a problem that the allowable amount of parallel eccentricity is small because the axial length of the hub is long.
The device of Patent Document 2 has a drawback that the shaft hole becomes small because a tapered hole is provided in the boss portion of the hub.
In the invention of Patent Document 3, when the fastening member is rotated, the sprocket moves in the axial direction, so that it is difficult to position the sprocket.
In addition, in the inventions and devices of Patent Documents 1 to 3, when a slip occurs, the hub or sprocket itself must be replaced. Therefore, cost and time are required. Need to correct.

次に、図４に示す軸継手がある。図４の軸継手１００は、主として、左右一対の加圧部材１０２ａ，１０２ｂ、左右一対のハブ１０４ａ、１０４ｂ、環状の内外楔部材１０６、中間のスペーサ１０８、及び左右一対のディスク１１０ａ，１１０ｂからなる。
２組の環状の内外楔部材１０６は、いずれも、インナーリング１０６ａ、アウターリング１０６ｂからなり、ハブ１０４ａ，１０４ｂの内周に配設されている。楔部材１０６に、軸方向に平行なスリットは形成されていない。アウターリング１０６ｂは、加圧部材１０２ａとボス１０５のねじ孔に加圧ボルト１１２ａをねじ込むことにより、軸方向に加圧され、環状の内外楔部材１０６を楔係合させる。
スペーサ１０８は、ディスク（板ばね）１１０ａ，１１０ｂと相俟って平行偏心を弾性的に許容するように設けられ、ディスク１１０ａは、ハブ１０４ａとスペーサ１０８の間に配設され、ディスク固定用ボルト１１６、座金１１４ａ、１１４ｂ、ナット１１７により、ハブ１０４ａのボス１０５から突出するフランジ部１０５ａに固定される。符号１１４ｄは、ディスク固定用ボルト１１６が挿通される孔部である。
他方のハブ１０４ｂにおいては、スペーサ連結用ボルト１２６が孔部１２４ｄに挿通され、座金１２４ａ、１２４ｂに挟まれたディスク１１０ｂがスペーサ連結用ボルト１２６のスペーサ１０８へのねじ込みにより、スペーサ１０８に固定され、スペーサ連結用ボルト１２６の頭部側は、孔部１２４ｄに遊びをもって受け入れられている。
この軸継手１００は、アウターリング１０６ｂを加圧することにより、ハブ１０４ａに対して移動できないインナーリング１０６ａが軸に締付け固定されることから、ハブ１０４ａの位置決めが容易、というメリットがある。
しかし、加圧部材１０２ａ，１０２ｂ、加圧ボルト１１２ａ，１１２ｂがいずれも外方向から取付けられるため、軸継手１００の全長が長くなることが避けられない。また、一対のディスク１１０ａ、１１０ｂ間の距離ｄ’が比較的短いため、許容される平行偏心量が小さい、という問題もある。 Next, there is a shaft coupling shown in FIG. 4 mainly includes a pair of left and right pressure members 102a and 102b, a pair of left and right hubs 104a and 104b, an annular inner and outer wedge member 106, an intermediate spacer 108, and a pair of left and right disks 110a and 110b. .
Each of the two sets of annular inner and outer wedge members 106 includes an inner ring 106a and an outer ring 106b, and is disposed on the inner periphery of the hubs 104a and 104b. The wedge member 106 is not formed with a slit parallel to the axial direction. The outer ring 106b is pressurized in the axial direction by screwing the pressure bolt 112a into the screw holes of the pressure member 102a and the boss 105, and the annular inner and outer wedge members 106 are wedge-engaged.
The spacer 108 is provided so as to elastically allow parallel eccentricity in combination with the discs (plate springs) 110a and 110b, and the disc 110a is disposed between the hub 104a and the spacer 108 and includes a disc fixing bolt. 116, washers 114a and 114b, and nut 117 are fixed to the flange portion 105a protruding from the boss 105 of the hub 104a. Reference numeral 114d is a hole through which the disk fixing bolt 116 is inserted.
In the other hub 104b, the spacer connecting bolt 126 is inserted into the hole 124d, and the disk 110b sandwiched between the washers 124a and 124b is fixed to the spacer 108 by screwing the spacer connecting bolt 126 into the spacer 108. The head side of the spacer connecting bolt 126 is received in the hole 124d with play.
This shaft coupling 100 has an advantage that positioning of the hub 104a is easy because the inner ring 106a that cannot move relative to the hub 104a is fastened to the shaft by pressurizing the outer ring 106b.
However, since the pressurizing members 102a and 102b and the pressurizing bolts 112a and 112b are all attached from the outside, it is inevitable that the total length of the shaft coupling 100 becomes long. Further, since the distance d ′ between the pair of disks 110a and 110b is relatively short, there is a problem that the allowable parallel eccentricity is small.

そこで、本発明は、前述した従来技術の問題点に鑑み、上記１〜５の特徴を具えた軸継手の提供をその目的とする。   In view of the above-described problems of the prior art, an object of the present invention is to provide a shaft coupling having the features 1 to 5 described above.

本発明は、軸との間に環状の内外楔部材を介在させた一対のハブ、前記内外楔部材の一方を押圧して楔係合させる一対の加圧部材、中間に配置されるスペーサ、及び該スぺーサと前記ハブの間に配設されるディスクとからなり、前記ディスクがディスク固定用ボルトとスペーサ連結用ボルトによってそれぞれ前記ハブとスぺーサに固定される軸継手であって、
前記一対のハブは、フランジ部、ボス、及び前記楔部材を収納する段付部を有し、
前記一対の加圧部材は前記一対のハブのボスに外方向に向けてねじ込まれるようになっており、
前記スペーサは中央部に前記加圧部材の端部を受け入れる孔を有することを特徴とする軸継手により前記課題を解決した。 The present invention includes a pair of hubs having annular inner and outer wedge members interposed between shafts, a pair of pressure members that press one of the inner and outer wedge members to engage the wedge, a spacer disposed in the middle, and A shaft coupling comprising a disk disposed between the spacer and the hub, wherein the disk is fixed to the hub and the spacer by a disk fixing bolt and a spacer connecting bolt, respectively.
The pair of hubs includes a flange portion, a boss, and a stepped portion for storing the wedge member,
The pair of pressure members are adapted to be screwed outwardly into the bosses of the pair of hubs,
The said subject was solved by the shaft coupling characterized by the said spacer having the hole which receives the edge part of the said pressurizing member in the center part.

本発明によると、一対の加圧部材が一対のハブに対して内側から外側に向けてねじ込まれるように配設されているため、軸継手の全長が短く、一対のディスク間の距離を長くできる。これにより、従来技術と比べて、コンパクトで許容される平行偏心量が大きい軸継手を提供できる。
第２に、ディスクの内周側に配置されるのは、肉厚が薄いハブのボスと加圧部材の２点だけであるため、軸孔の大きさを大きくすることができる。
第３に、楔部材がハブとは別に設けられているため、スリップが発生して楔部材が損傷しても、楔部材だけを交換するだけでよい利点がある。また、熱処理も楔部材のみに行なえばよく、ハブに特別な加工を行う必要がない。 According to the present invention, since the pair of pressure members are arranged to be screwed into the pair of hubs from the inside to the outside, the overall length of the shaft coupling is short, and the distance between the pair of disks can be increased. . Thereby, compared with a prior art, a shaft coupling with a large amount of parallel eccentricity permitted compactly can be provided.
Secondly, since only the hub boss and the pressure member having a small thickness are arranged on the inner peripheral side of the disk, the size of the shaft hole can be increased.
Thirdly, since the wedge member is provided separately from the hub, even if slip occurs and the wedge member is damaged, there is an advantage that only the wedge member needs to be replaced. Further, the heat treatment may be performed only on the wedge member, and it is not necessary to perform special processing on the hub.

（ａ）は、（ｂ）のＡ−Ａ線での断面図、（ｂ）は、本発明の軸継手を軸方向から見た図。(A) is sectional drawing in the AA of (b), (b) is the figure which looked at the shaft coupling of this invention from the axial direction. （ａ）、（ｂ）、（ｃ）、（ｄ）、（ｅ）は、本発明の軸継手の加圧部材の異なる形状を示した図。(A), (b), (c), (d), (e) is the figure which showed the different shape of the pressurization member of the shaft coupling of this invention. 楔部材を複数設けた場合の、各楔部材の面圧の大きさを示した図。The figure which showed the magnitude | size of the surface pressure of each wedge member at the time of providing multiple wedge members. 従来の軸継手の軸方向断面図。The axial direction sectional view of the conventional shaft coupling.

以下、添付図面１〜３を参照して、本発明の実施形態を説明する。但し、本発明はこの実施形態に限定されるものではない。   Embodiments of the present invention will be described below with reference to the accompanying drawings 1 to 3. However, the present invention is not limited to this embodiment.

図１（ａ）において、軸継手１０は、一対のハブ１４，２４、環状の内外楔部材１６，２６（以下、単に「楔部材」と略称することがある。）、一対の加圧部材１１，２１、中央に一つのスペーサ３０、ディスク（板ばね）１２，２２からなり、ディスク１２，２２がディスク固定用ボルト１３とスペーサ連結用ボルト２３によってそれぞれハブ１４，２４とスペーサ３０に固定されるようになっている。
一対の加圧部材１１，２１、ハブ１４，２４、楔部材１６，２６には、それぞれ、軸を挿入するための軸孔１８，２８が各々設けられている。
ハブ１４，２４は、フランジ部１４ａ，２４ａ、ボス１４ｂ，２４ｂ、段付部１４ｃ，２４ｃを有している。
ボス１４ｂ，２４ｂの内周には、加圧部材１１，２１が螺合されるための雌ねじが形成されている。
スペーサ３０は、一対のハブ１４，２４の中間に設けられ、中央に、加圧部材１１，２１の端部であるフランジ１１ａ，２１ａが受け入れられる孔３１を有する。 1A, a shaft coupling 10 includes a pair of hubs 14 and 24, annular inner and outer wedge members 16 and 26 (hereinafter simply referred to as “wedge members”), and a pair of pressure members 11. 21, one spacer 30 in the center, and discs (plate springs) 12, 22. The discs 12, 22 are fixed to the hubs 14, 24 and the spacer 30 by disc fixing bolts 13 and spacer connecting bolts 23, respectively. It is like that.
The pair of pressure members 11 and 21, the hubs 14 and 24, and the wedge members 16 and 26 are provided with shaft holes 18 and 28 for inserting shafts, respectively.
The hubs 14 and 24 have flange portions 14a and 24a, bosses 14b and 24b, and stepped portions 14c and 24c.
On the inner circumferences of the bosses 14b and 24b, female screws for screwing the pressure members 11 and 21 are formed.
The spacer 30 is provided in the middle of the pair of hubs 14 and 24, and has a hole 31 in the center for receiving the flanges 11a and 21a which are the end portions of the pressure members 11 and 21.

楔部材１６，２６は、それぞれ、インナーリング１６ａ，２６ａ、アウターリング１６ｂ，２６ｂからなり、ハブ１４，２４の内周に配設され、図示しない軸との間に介在するように、段付部１４ｃ，２４ｃに収納される。段付部１４ｃ，２４ｃに収納されることにより、楔部材１６，２６の位置は容易に決まる。また、楔部材１６，２６は、他の部材から独立しているため、スリップ等の発生により、楔部材１６，２６が損傷しても、楔部材１６，２６だけを交換すればよい。また、熱処理も楔部材１６，２６のみに行なえばよく、ハブ１４，２４に特別な加工は不要である。
なお、インナーリング１６ａ，２６ａ、アウターリング１６ｂ，２６ｂ各々に軸方向に平行なスリットを形成すると、変形しやすくなって好適である。 Each of the wedge members 16 and 26 includes inner rings 16a and 26a and outer rings 16b and 26b. The wedge members 16 and 26 are disposed on the inner periphery of the hubs 14 and 24, and are stepped portions so as to be interposed between shafts (not shown). 14c and 24c. By being accommodated in the stepped portions 14c and 24c, the positions of the wedge members 16 and 26 are easily determined. Further, since the wedge members 16 and 26 are independent of other members, even if the wedge members 16 and 26 are damaged due to the occurrence of slip or the like, only the wedge members 16 and 26 may be replaced. The heat treatment may be performed only on the wedge members 16 and 26, and no special processing is required for the hubs 14 and 24.
It should be noted that it is preferable to form slits parallel to the axial direction in each of the inner rings 16a and 26a and the outer rings 16b and 26b, because it is easy to deform.

加圧部材１１，２１について説明する。
図２（ａ）〜（ｃ）に示すとおり、加圧部材１１，２１の内側の端部であるフランジ１１ａ，２１ａの外形は、四角形、六角形、又は小判形とすることができる。このように、平行なレンチ係合面を有していると、通常のトルクレンチを使用して締付けることができる。
一方、図２（ｄ）、（ｅ）に示すように、加圧部材１１，２１のフランジ１１ａ，２１ａの外形を円形とした場合は、その外周に、フックレンチを引っかけて回転させるための切欠１１ｄ，２１ｄ又は孔部１１ｄ，２１ｄを設ける。なお、図２（ｄ）、（ｅ）では、切欠１１ｄ，２１ｄ又は孔部１１ｄ，２１ｄを等間隔で４つ設けているが、必要に応じて、凹部や孔部の数を変えてもよい。
加圧部材１１，２１のボス１１ｂ，２１ｂの外周には、ハブ１４、２４のボス１４ｂ，２４ｂと螺合させるための雄ねじ部１１ｆ，２１ｆが形成されている。 軸孔１８，２８に挿入された軸（図示せず。）は、ハブ１４、２４のボス１４ｂ，２４ｂに加圧部材１１，２１のボス１１ｂ，２１ｂを外方向に向けてねじ込むことにより、加圧部材１１，２１の段付部１１ｃ，２１ｃがインナーリング１６ａ，２６ａを押圧して、楔係合により、２つの軸は、ハブ１４，２４に各々締結される。楔部材１６，２６に軸方向に平行なスリットが形成されていると、スリットがない楔部材に比べ変形しやすいので、加圧部材１１，２１を締めた結果発生する伝達トルクを大きくすることができる。 The pressure members 11 and 21 will be described.
As shown in FIGS. 2A to 2C, the outer shapes of the flanges 11a and 21a, which are the inner ends of the pressure members 11 and 21, can be rectangular, hexagonal, or oval. Thus, when it has a parallel wrench engagement surface, it can tighten using a normal torque wrench.
On the other hand, as shown in FIGS. 2D and 2E, when the outer shapes of the flanges 11a and 21a of the pressurizing members 11 and 21 are circular, a notch for hooking and rotating a hook wrench around the outer periphery thereof. 11d, 21d or holes 11d, 21d are provided. 2D and 2E, four notches 11d and 21d or holes 11d and 21d are provided at equal intervals, but the number of recesses and holes may be changed as necessary. .
Male screw portions 11f and 21f for screwing with the bosses 14b and 24b of the hubs 14 and 24 are formed on the outer circumferences of the bosses 11b and 21b of the pressure members 11 and 21, respectively. The shafts (not shown) inserted into the shaft holes 18 and 28 are added by screwing the bosses 11b and 21b of the pressure members 11 and 21 outward into the bosses 14b and 24b of the hubs 14 and 24, respectively. The stepped portions 11c, 21c of the pressure members 11, 21 press the inner rings 16a, 26a, and the two shafts are fastened to the hubs 14, 24 by wedge engagement. If the wedge members 16 and 26 are formed with slits parallel to the axial direction, the wedge members 16 and 26 are more easily deformed than a wedge member having no slits. Therefore, the transmission torque generated as a result of tightening the pressure members 11 and 21 can be increased. it can.

フランジ部１４ａには、軸方向に、ディスク連結用ボルト１３を挿通させる孔部１４ｄが形成されている。
フランジ部２４ａとスペーサ３０には、スペーサ連結用ボルト２３を挿通させる軸方向の孔部２４ｄ、スペーサ連結用ボルト２３が螺合されるねじ孔３２が、それぞれ形成されている。
なお、ディスク１２，２２は、複数枚のディスク（板ばね）を重ねて多層式に構成するのがよい。 The flange portion 14a is formed with a hole portion 14d through which the disk connecting bolt 13 is inserted in the axial direction.
The flange portion 24a and the spacer 30 are respectively formed with an axial hole portion 24d through which the spacer connecting bolt 23 is inserted and a screw hole 32 into which the spacer connecting bolt 23 is screwed.
The disks 12 and 22 are preferably configured in a multilayer manner by overlapping a plurality of disks (plate springs).

この軸継手１０では、加圧部材１１，２１がスペーサ３０側からハブ１４，２４に向かって設けられているため、図４の軸継手１００に比べて、全長を短くすることができ、ディスク１２，２２間の距離ｄが長くなる（ｄ＞ｄ’）。従って、軸継手１０は、軸継手１００よりもコンパクトで、しかも、許容される平行偏心量が大きい。
また、ディスク１２，２２の内周には、肉厚が薄い加圧部材１１，２１とボス１４ｂ，２４ｂしかないため、軸孔１８，２８の大きさを従来の軸継手１００の軸孔１１８よりも大きくすることができる。 In this shaft coupling 10, since the pressure members 11 and 21 are provided from the spacer 30 side toward the hubs 14 and 24, the total length can be shortened compared to the shaft coupling 100 of FIG. , 22 becomes longer (d> d ′). Therefore, the shaft coupling 10 is more compact than the shaft coupling 100, and the allowable amount of parallel eccentricity is large.
Further, since the inner circumferences of the disks 12 and 22 are only the pressure members 11 and 21 and the bosses 14b and 24b having a small thickness, the size of the shaft holes 18 and 28 is larger than that of the shaft hole 118 of the conventional shaft coupling 100. Can also be increased.

図１（ｂ）に示すように、ディスク固定用ボルト１３とスペーサ連結用ボルト２３はハブ１４，２４に交互に配置される。なお、図１（ｂ）では、ディスク固定用ボルト１３とスペーサ連結用ボルト２３を９０度間隔で配置しているが、ディスク固定用ボルト１３、スペーサ連結用ボルト２３が交互に配置されていれば、これに限定されない。   As shown in FIG. 1B, the disk fixing bolts 13 and the spacer connecting bolts 23 are alternately arranged on the hubs 14 and 24. In FIG. 1B, the disk fixing bolts 13 and the spacer connecting bolts 23 are arranged at intervals of 90 degrees. However, if the disk fixing bolts 13 and the spacer connecting bolts 23 are alternately arranged. However, the present invention is not limited to this.

次に、軸継手１０の組立方法を説明する。
ハブ１４に楔部材１６と加圧部材１１とを配設し、軸孔１８に軸（図示せず。）を挿通する。軸を挿通した後、加圧部材１１を、レンチで、仮締めする。片方のハブ２４側も同様である。レンチは、平行なレンチ係合面を有する図２（ａ）、（ｂ）、（ｃ）の場合は、通常のトルクレンチを、図２（ｄ）、（ｅ）の場合は、フックレンチを使用する。その際、ハブ１４に設けた切欠１４ｅ，１４ｅをフックレンチで押さえて、回り止めとする。
次に、ハブ１４，２４に挿通した軸を突き合わせ、フランジ部１４ａ，２４ａ間の距離を調整することにより、ハブの位置決めを行う。その後、所定の位置にハブ１４，２４が固定されるように、加圧部材１１，２１をさらにねじ込み、軸孔１８，２８に挿通された各軸とハブ１４，２４を確実に締結する。
最後に、ディスク固定用ボルト１３、ナット１７、ディスク１２，２２、スペーサ３０、スペーサ連結用ボルト２３、座金１９ａ，１９ｂ，２９ａ，２９ｂの配設及び固定を行う。
具体的には、ディスク固定用ボルト１３をディスク固定用孔部１４ｄに挿通し、ナット１７と螺合させることにより、ディスク１２を、フランジ部１４ａに固定する。ディスク１２は、座金１９ａ，１９ｂで挟まれる。ハブ２４側も同様である。
次に、スペーサ連結用ボルト２３を孔部２４ｄに挿入し、スペーサのねじ孔３２と螺合させることにより、ディスク２２は、スペーサ連結用ボルト２３、座金２９ａ，２９ｂによって、スペーサ３０に固定される。スペーサ連結用ボルト２３の頭部側は、ハブ２４の孔部２４ｄに対して遊びが持たされている。
同様に、ハブ１４のスペーサ連結用ボルト（図示せず。）を螺合させることにより、ハブ１４とスペーサ３０が連結され、ハブ２４に挿通された軸とハブ１４に挿通された軸が連結される。
加圧部材１１，２１の端部であるフランジ１１ａ，２１ａは、スペーサ３０の孔３１内に受け入れられる。
このようにして、加圧部材１１，２１によって各ハブに締結された２つの軸が、平行偏心が許容できるように、ディスク１２，２２、スペーサ３０と連結されたことになる。 Next, a method for assembling the shaft coupling 10 will be described.
The wedge member 16 and the pressure member 11 are disposed on the hub 14, and a shaft (not shown) is inserted through the shaft hole 18. After inserting the shaft, the pressure member 11 is temporarily tightened with a wrench. The same applies to one hub 24 side. 2 (a), (b) and (c) having a parallel wrench engaging surface, a normal torque wrench is used, and in FIGS. 2 (d) and (e), a hook wrench is used. use. At that time, the notches 14e and 14e provided in the hub 14 are pressed with a hook wrench to prevent rotation.
Next, the shafts inserted into the hubs 14 and 24 are butted together, and the hub is positioned by adjusting the distance between the flange portions 14a and 24a. Thereafter, the pressure members 11 and 21 are further screwed so that the hubs 14 and 24 are fixed at predetermined positions, and the shafts inserted into the shaft holes 18 and 28 and the hubs 14 and 24 are securely fastened.
Finally, the disk fixing bolt 13, the nut 17, the disks 12, 22, the spacer 30, the spacer connecting bolt 23, and the washers 19a, 19b, 29a, 29b are disposed and fixed.
Specifically, the disk 12 is fixed to the flange part 14a by inserting the disk fixing bolt 13 through the disk fixing hole 14d and screwing it with the nut 17. The disk 12 is sandwiched between washers 19a and 19b. The same applies to the hub 24 side.
Next, the spacer connecting bolt 23 is inserted into the hole 24d and screwed into the spacer screw hole 32, whereby the disk 22 is fixed to the spacer 30 by the spacer connecting bolt 23 and washers 29a and 29b. . The head side of the spacer connecting bolt 23 has play with respect to the hole 24 d of the hub 24.
Similarly, by screwing a spacer connecting bolt (not shown) of the hub 14, the hub 14 and the spacer 30 are connected, and the shaft inserted through the hub 24 and the shaft inserted through the hub 14 are connected. The
The flanges 11 a and 21 a which are the end portions of the pressure members 11 and 21 are received in the holes 31 of the spacer 30.
In this way, the two shafts fastened to each hub by the pressure members 11 and 21 are connected to the disks 12 and 22 and the spacer 30 so as to allow parallel eccentricity.

本発明の軸継手１０と従来技術の軸継手１００の伝達トルクについて、説明する。   The transmission torque of the shaft coupling 10 of the present invention and the shaft coupling 100 of the prior art will be described.

図３は、複数組の楔部材を設けた場合の、各楔部材面圧の大きさを矢印Ｐの長さで示したものである。矢印の長さが短いほど、伝達トルクが小さいことを表している。
楔部材を複数組設けたとしても、摩擦抵抗の影響を受けるため、楔部材の数だけ伝達トルクが大きくなる訳ではなく、楔部材のテーパ部の角度θに対応した比率で、伝達トルクは低下する。これは、加圧部材により楔部材が矢印Ｆ方向に加圧された場合、加圧部材から離れた楔部材ほど、摩擦抵抗により、面圧が小さくなることによる。
従って、楔部材の数を増やすこととは別の方法で、伝達トルクの向上を図る必要がある。
表１に、本発明の軸継手１０と、従来の軸継手１００の伝達トルクを比較した結果を示す。条件は、孔径が同じ２５ｍｍで、同一の軸方向締付力とし、本発明では、楔部材は一組だけで軸方向スリットがあり、一方、従来例では、楔部材は２組で軸方向スリットはないものとしている。なお、軸継手１０では、楔部材のテーパ部の角度θを従来例に対して約６０％、楔部材の内径と全幅の比率を１．８（従来例では４）にしている。 FIG. 3 shows the magnitude of each wedge member surface pressure by the length of the arrow P when a plurality of sets of wedge members are provided. The shorter the length of the arrow, the smaller the transmission torque.
Even if a plurality of sets of wedge members are provided, the transmission torque is not increased by the number of wedge members because of the influence of frictional resistance, but the transmission torque decreases at a ratio corresponding to the angle θ of the tapered portion of the wedge member. To do. This is because when the wedge member is pressed in the direction of the arrow F by the pressing member, the surface pressure is reduced by the frictional resistance as the wedge member is separated from the pressing member.
Therefore, it is necessary to improve the transmission torque by a method different from increasing the number of wedge members.
Table 1 shows the result of comparing the transmission torque of the shaft coupling 10 of the present invention and the conventional shaft coupling 100. The conditions are the same hole diameter of 25 mm and the same axial clamping force. In the present invention, only one pair of wedge members has an axial slit, whereas in the conventional example, two wedge members have an axial slit. Not supposed to be. In the shaft coupling 10, the angle θ of the tapered portion of the wedge member is about 60% of the conventional example, and the ratio between the inner diameter and the full width of the wedge member is 1.8 (4 in the conventional example).

Figure 2012102785
Figure 2012102785

表１のとおり、本発明の軸継手１０は、軸継手１００よりも、伝達トルクが１．３倍以上あることが分る。
なお、楔部材のテーパ部の角度θを１１度以下、楔部材の内径と全幅の比を２以下にすれば、伝達トルクは軸継手１００よりも大きくできることが判明している。 As shown in Table 1, it can be seen that the shaft coupling 10 of the present invention has a transmission torque 1.3 times or more that of the shaft coupling 100.
It has been found that if the angle θ of the tapered portion of the wedge member is 11 degrees or less and the ratio between the inner diameter and the full width of the wedge member is 2 or less, the transmission torque can be made larger than that of the shaft coupling 100.

１０ 軸継手
１１，２１ 加圧部材
１１ａ，２１ａ フランジ
１２，２２ ディスク
１３ ディスク固定用ボルト
１４，２４ ハブ
１４ａ，２４ａ フランジ部
１４ｂ，２４ｂ ボス
１４ｃ，２４ｃ 段付部
１４ｄ，２４ｄ ディスク固定用孔部
１６，２６ 楔部材
２３ スペーサ連結用ボルト
３０ スペーサ
３１ 孔 10 Shaft coupling 11, 21 Pressure member 11a, 21a Flange 12, 22 Disc 13 Disc fixing bolt 14, 24 Hub 14a, 24a Flange 14b, 24b Boss 14c, 24c Stepped portion 14d, 24d Disc fixing hole 16 , 26 Wedge member 23 Spacer connecting bolt 30 Spacer 31 Hole

Claims (3)

軸との間に環状の内外楔部材を介在させた一対のハブ、前記内外楔部材の一方を押圧して楔係合させる一対の加圧部材、中間に配置されるスペーサ、及び該スペーサと前記ハブの間に配設されるディスクとからなり、前記ディスクがディスク固定用ボルトとスペーサ連結用ボルトによってそれぞれ前記ハブとスペーサに固定される軸継手であって、
前記一対のハブは、前記ディスク固定用ボルトとスペーサ連結用ボルトを挿通する孔部を有するフランジ部、ボス、及び前記楔部材を収納する段付部を有し、 前記一対の加圧部材は前記一対のハブのボスに外方向に向けてねじ込まれるようになっており、
前記スペーサは中央部に前記加圧部材の端部を受け入れる孔を有することを特徴とする、
軸継手。 A pair of hubs each having an annular inner and outer wedge member interposed between the shaft, a pair of pressure members that press one of the inner and outer wedge members to engage the wedge, a spacer disposed in the middle, and the spacer and the A disk joint disposed between the hub, wherein the disk is fixed to the hub and the spacer by a disk fixing bolt and a spacer connecting bolt, respectively.
The pair of hubs include a flange portion having a hole portion through which the disk fixing bolt and the spacer connecting bolt are inserted, a boss, and a stepped portion for storing the wedge member, It is designed to be screwed outwardly into a pair of hub bosses,
The spacer has a hole for receiving an end portion of the pressure member in a central portion,
Shaft coupling. 前記ハブの前記端部が平行なレンチ係合面を有するフランジである、請求項１の軸継手。   The shaft coupling of claim 1, wherein the end of the hub is a flange having parallel wrench engagement surfaces. 前記ハブの前記端部が円形のフランジで、外周に切欠又は孔部が形成されている、請求項１の軸継手。   The shaft coupling according to claim 1, wherein the end of the hub is a circular flange, and a notch or a hole is formed on the outer periphery.
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117588501A (en) * 2024-01-18 2024-02-23 常州沪戚铁路配件有限公司 Elastic coupling with flexible strength structure for railway vehicle

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0338426U (en) * 1989-08-28 1991-04-15
JPH0763227A (en) * 1993-08-26 1995-03-07 Daido Sprague Kk Flexible joint
JPH07279988A (en) * 1994-04-13 1995-10-27 Tsubakimoto Emason:Kk Coupling incorporating floating shaft
JP2001140923A (en) * 1999-11-19 2001-05-22 Sumitomo Metal Ind Ltd Flexible joints for railway vehicles
JP2005042832A (en) * 2003-07-23 2005-02-17 Tsubaki Emerson Co Fastener of shaft and rotating body
JP2008095778A (en) * 2006-10-10 2008-04-24 Sumitomo Metal Ind Ltd Flexible plate shaft coupling for railway vehicles
JP2010138922A (en) * 2008-12-09 2010-06-24 Koji Ishido Friction fastener, friction fastening structure, and friction fastener set for rotating body

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0338426U (en) * 1989-08-28 1991-04-15
JPH0763227A (en) * 1993-08-26 1995-03-07 Daido Sprague Kk Flexible joint
JPH07279988A (en) * 1994-04-13 1995-10-27 Tsubakimoto Emason:Kk Coupling incorporating floating shaft
JP2001140923A (en) * 1999-11-19 2001-05-22 Sumitomo Metal Ind Ltd Flexible joints for railway vehicles
JP2005042832A (en) * 2003-07-23 2005-02-17 Tsubaki Emerson Co Fastener of shaft and rotating body
JP2008095778A (en) * 2006-10-10 2008-04-24 Sumitomo Metal Ind Ltd Flexible plate shaft coupling for railway vehicles
JP2010138922A (en) * 2008-12-09 2010-06-24 Koji Ishido Friction fastener, friction fastening structure, and friction fastener set for rotating body

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117588501A (en) * 2024-01-18 2024-02-23 常州沪戚铁路配件有限公司 Elastic coupling with flexible strength structure for railway vehicle

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