JP2009257382A - Shaft connection device and torque limiter - Google Patents

Shaft connection device and torque limiter Download PDF

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JP2009257382A
JP2009257382A JP2008104868A JP2008104868A JP2009257382A JP 2009257382 A JP2009257382 A JP 2009257382A JP 2008104868 A JP2008104868 A JP 2008104868A JP 2008104868 A JP2008104868 A JP 2008104868A JP 2009257382 A JP2009257382 A JP 2009257382A
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cylindrical
axial direction
peripheral surface
hydraulic passage
shaft
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JP5012631B2 (en
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Takekata Morimoto
健固 森本
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JTEKT Corp
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a shaft connection device having welding parts on both sides of a hydraulic path hardly destroyed, and having a long life and a high reliability, and a torque limiter. <P>SOLUTION: A first member 2 and a second member 3 are disposed to overlap each other in the axial direction in a welding part 30 between the axial end face opposite to the ring part 12 of the first member 2 and the axial end face of the ring part 22 of the second member 3. The first member 2 and the second member 3 are also disposed to overlap each other in the axial direction in a welding part 31 between the axial end face opposite to the ring part 22 of the second member 3 and the axial end face of the ring part 12 of the first member 2. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、軸連結装置およびトルクリミッタに関する。   The present invention relates to a shaft coupling device and a torque limiter.

従来、トルクリミッタとしては、特開昭６２−１５９８１５号公報（特許文献１）に記載されているものがある。   Conventional torque limiters include those described in Japanese Patent Application Laid-Open No. 62-159815 (Patent Document 1).

このトルクリミッタは、軸部材と、この軸部材に外嵌した筒部材とを備え、筒部材は、環状の油圧通路を有する。   The torque limiter includes a shaft member and a cylindrical member that is externally fitted to the shaft member, and the cylindrical member has an annular hydraulic passage.

上記油圧通路は、軸部材の軸方向に延在している。上記筒部材は、筒状の第１部材と、筒状の第２部材とを有し、上記第１部材の内周面は、油圧通路を介して第２部材の外周面に径方向に対向している。   The hydraulic passage extends in the axial direction of the shaft member. The cylindrical member includes a cylindrical first member and a cylindrical second member, and an inner peripheral surface of the first member is opposed to an outer peripheral surface of the second member via a hydraulic passage in a radial direction. is doing.

上記第１部材と、上記第２部材とは、油圧通路の一端に軸方向に隣接する第１箇所および油圧通路の他端に軸方向に隣接する第２箇所で溶接されて接合されている。上記第１箇所および第２箇所において、上記第１部材と上記第２部材とは、径方向のみに重なっていて軸方向に重なっていない構成になっている。   The first member and the second member are welded and joined at a first location adjacent to one end of the hydraulic passage in the axial direction and a second location adjacent to the other end of the hydraulic passage in the axial direction. In the first location and the second location, the first member and the second member are configured to overlap only in the radial direction and not in the axial direction.

上記トルクリミッタは、上記環状の油圧通路に油を封入して、油圧通路を径方向に拡張することにより、上記筒部材の第２部材の内周面を縮径して、この内周面を軸部材の外周面に押しつけて、筒部材と軸部材とを摩擦結合して、軸部材と軸部材との間でトルクを伝達するようになっている。   The torque limiter reduces the diameter of the inner peripheral surface of the second member of the cylindrical member by enclosing oil in the annular hydraulic passage and expanding the hydraulic passage in the radial direction. The cylinder member and the shaft member are frictionally coupled by pressing against the outer peripheral surface of the shaft member, and torque is transmitted between the shaft member and the shaft member.

上記トルクリミッタは、筒部材と、軸部材との間に、所定以上のトルクが作用して、筒部材に対する軸部材の相対回転が生じた場合、上記油圧通路に連通している油抜き通路の油圧通路側とは反対側の密封された端部が、上記相対回転に起因して破断して、外部に対して開口するようになっている。このようにして、上記油圧通路内の油を外部に排出して、筒部材と軸部材との摩擦結合を解除して、筒部材と軸部材との間のトルクの伝達を遮断するようになっている。
特開昭６２−１５９８１５号公報（第１図） The torque limiter is configured such that when a torque greater than a predetermined value acts between the tubular member and the shaft member and relative rotation of the shaft member with respect to the tubular member occurs, the oil drain passage communicated with the hydraulic passage. The sealed end opposite to the hydraulic passage side is broken due to the relative rotation and opens to the outside. In this way, the oil in the hydraulic passage is discharged to the outside, the frictional coupling between the tubular member and the shaft member is released, and the transmission of torque between the tubular member and the shaft member is interrupted. ing.
JP 62-159815 (Fig. 1)

上記従来のトルクリミッタにおいては、トルクの伝達時に、油圧通路を径方向に拡張して、筒部材を、軸部材に押圧する構成であるから、トルクの伝達時に、上記油圧通路の両側の溶接部が、常時、股裂き方向である径方向に引っ張り応力を受けることになる。したがって、上記溶接部の周辺で疲労が起こって、上記溶接部が破壊するということを避けがたい。   In the conventional torque limiter, when the torque is transmitted, the hydraulic passage is expanded in the radial direction and the cylindrical member is pressed against the shaft member. However, a tensile stress is always received in the radial direction which is the crotch tear direction. Therefore, it is unavoidable that fatigue occurs around the weld and the weld is destroyed.

そこで、本発明の課題は、液圧通路の両側にある溶接部が破壊しにくくて、寿命が長くて、信頼性が高い軸連結装置を、提供することにある。   SUMMARY OF THE INVENTION An object of the present invention is to provide a shaft coupling device that is less likely to break the welded portions on both sides of the hydraulic passage, has a long life, and has high reliability.

また、本発明の課題は、油圧通路の両側にある溶接部が破壊しにくくて、寿命が長くて、信頼性が高いトルクリミッタを、提供することにある。   It is another object of the present invention to provide a torque limiter that has a long life and high reliability, with the welds on both sides of the hydraulic passage being difficult to break.

上記課題を解決するため、この発明の軸連結装置は、
軸部材と、
この軸部材に外嵌した筒部材と
を備え、
上記筒部材および上記軸部材のうちの一方の部材は、その一方の部材と、上記筒部材および上記軸部材のうちの他方の部材との間でトルクの伝達を行うときに、上記一方の部材の周面を上記他方の部材の周面に押し付けるための液圧通路を有し、
上記液圧通路は、上記一方の部材の略軸方向に延在し、
上記一方の部材は、
環状の第１部材と、
上記第１部材に上記液圧通路を介して対向する環状の第２部材と
を有し、
上記第１部材と、上記第２部材とは、上記液圧通路の一端側において、環状の第１溶接部によって溶接接合される一方、上記液圧通路の他端側において、環状の第２溶接部によって溶接接合され、
上記第１溶接部において、上記第１部材と上記第２部材とは、上記一方の部材の軸方向に重なっていることを特徴としている。 In order to solve the above problems, the shaft coupling device of the present invention is:
A shaft member;
A cylindrical member fitted around the shaft member;
One member of the cylindrical member and the shaft member is configured to transmit the torque between the one member and the other member of the cylindrical member and the shaft member. A hydraulic passage for pressing the peripheral surface of the second member against the peripheral surface of the other member,
The hydraulic passage extends in a substantially axial direction of the one member,
The one member is
An annular first member;
An annular second member facing the first member via the hydraulic passage,
The first member and the second member are welded and joined by an annular first welded portion at one end side of the hydraulic passage, while an annular second weld is made at the other end side of the hydraulic passage. Welded and joined by parts
In the first welded portion, the first member and the second member overlap with each other in the axial direction of the one member.

本発明によれば、上記第１溶接部において、上記第１部材と上記第２部材とは、上記一方の部材の軸方向に重なっているから、従来の構成、すなわち、第１溶接部において、第１部材と第２部材とが、径方向のみに重なっていて軸方向に重なっていない構成と比較して、略上記軸方向に延在する油圧通路の径方向の拡張に基づく径方向の引っ張り応力が、上記第１溶接部に作用しにくくて、第１溶接部において径方向の股裂き効果を緩和することができる。したがって、上記第１溶接部の破壊を抑制することができる。   According to the present invention, in the first welded portion, the first member and the second member overlap in the axial direction of the one member, so in the conventional configuration, that is, in the first welded portion, Compared with a configuration in which the first member and the second member overlap only in the radial direction and do not overlap in the axial direction, the radial tension is based on the radial expansion of the hydraulic passage extending substantially in the axial direction. The stress hardly acts on the first welded portion, and the radial crotch tearing effect can be mitigated at the first welded portion. Therefore, destruction of the first welded portion can be suppressed.

また、一実施形態では、
上記第１溶接部において、上記第１部材において上記第２部材に対向する面は、略上記一方の部材の径方向に広がっているか、または、上記一方の部材の径方向に上記液圧通路から離れるにしたがって、上記軸方向に上記液圧通路の他端側に傾斜している。 In one embodiment,
In the first welded portion, the surface of the first member that faces the second member extends substantially in the radial direction of the one member, or from the hydraulic passage in the radial direction of the one member. As it leaves, it inclines to the other end side of the fluid pressure passage in the axial direction.

上記実施形態によれば、第１溶接部において、第１部材において第２部材に対向する対向面が、略上記一方の部材の径方向に広がっているか、または、上記一方の部材の径方向に上記液圧通路から離れるにしたがって、上記軸方向に上記液圧通路の他端側に傾斜しているから、上記軸方向に延在する油圧通路の径方向の拡張に基づく股裂き方向である径方向の引っ張り応力が、上記第１溶接部に殆ど作用することがない。したがって、上記第１溶接部の股裂効果を格段に緩和できる。   According to the embodiment, in the first welded portion, the opposing surface of the first member that faces the second member extends substantially in the radial direction of the one member, or in the radial direction of the one member. A diameter that is a crotch tearing direction based on a radial expansion of the hydraulic passage extending in the axial direction because the hydraulic passage is inclined toward the other end side of the hydraulic passage in the axial direction as it is separated from the hydraulic passage. Directional tensile stress hardly acts on the first welded portion. Therefore, the crotch cracking effect of the first weld can be remarkably mitigated.

また、一実施形態では、
上記第１溶接部は、上記一方の部材の径方向において、上記液圧通路に対して上記一方の部材の上記周面側とは反対側に位置し、上記第２溶接部は、上記径方向において、上記液圧通路に対して上記液圧通路の上記一方の部材の上記周面側に位置している。 In one embodiment,
The first welded portion is located on a side opposite to the peripheral surface side of the one member with respect to the hydraulic passage in the radial direction of the one member, and the second welded portion is in the radial direction. And the fluid pressure passage is located on the peripheral surface side of the one member of the fluid pressure passage.

上記実施形態によれば、第１部材と第２部材とを互いに容易に組み付けることができて、溶接を容易に行うことができる。   According to the said embodiment, a 1st member and a 2nd member can be assembled | attached easily mutually and welding can be performed easily.

また、本発明のトルクリミッタは、
本発明の軸連結装置を備え、
上記液圧通路に封入した液体により上記液圧通路を上記一方の部材の径方向に拡張することにより、上記軸部材と上記筒部材とを摩擦係合する一方、上記液圧通路に封入された液体を除去することにより、上記軸部材が上記筒部材に対して相対回転することを特徴としている。 The torque limiter of the present invention is
Comprising the shaft coupling device of the present invention,
By expanding the hydraulic pressure passage in the radial direction of the one member with the liquid enclosed in the hydraulic pressure passage, the shaft member and the cylindrical member are frictionally engaged, while being enclosed in the hydraulic pressure passage. By removing the liquid, the shaft member rotates relative to the cylindrical member.

本発明によれば、従来のトルクリミッタと比較して、油圧通路の両側の溶接部の破壊を抑制することができ、寿命を長くすることができ、信頼性を高くすることができる。   According to the present invention, as compared with a conventional torque limiter, it is possible to suppress breakage of the welded portions on both sides of the hydraulic passage, to extend the life, and to improve the reliability.

本発明の軸連結装置によれば、第１溶接部において、第１部材と第２部材とが、筒部材および軸部材のうちの一方の部材の軸方向に重なっているから、従来の構成、すなわち、第１溶接部において、第１部材と第２部材とが、径方向のみに重なっている構成と比較して、略上記軸方向に延在する油圧通路の径方向の拡張に基づく径方向の引っ張り応力が、上記第１溶接部に作用しにくくて、第１溶接部において径方向の股裂き効果を緩和することができ、第１溶接部の破壊を抑制することができる。   According to the shaft coupling device of the present invention, in the first welded portion, the first member and the second member overlap in the axial direction of one of the cylindrical member and the shaft member. That is, in the first welded portion, the radial direction based on the radial expansion of the hydraulic passage extending substantially in the axial direction as compared with the configuration in which the first member and the second member overlap only in the radial direction. The tensile stress is less likely to act on the first welded portion, so that the radial crotch tearing effect can be mitigated at the first welded portion, and the breakage of the first welded portion can be suppressed.

また、本発明のトルクリミッタによれば、従来のトルクリミッタと比較して、油圧通路の両側の溶接部の破壊を抑制することができ、寿命を長くすることができ、信頼性を高くすることができる。   Further, according to the torque limiter of the present invention, it is possible to suppress the breakage of the welded portions on both sides of the hydraulic passage, to extend the life, and to increase the reliability, as compared with the conventional torque limiter. Can do.

以下、本発明を図示の形態により詳細に説明する。   Hereinafter, the present invention will be described in detail with reference to the drawings.

図１および図２は、本発明の軸連結装置において、液圧通路の溶接部の破壊が起こりにくい原理を説明する模式図である。   FIG. 1 and FIG. 2 are schematic diagrams for explaining the principle that the welded portion of the hydraulic passage is less likely to break in the shaft coupling device of the present invention.

詳しくは、図１は、本発明の軸連結装置において採用される第１部材２および第２部材３の溶接部３０,３１についての概略を説明する模式図である。また、図２は、従来の軸連結装置において採用されている第１部材６０２および第２部材６０３の溶接部についての概略を説明する模式図である。   Specifically, FIG. 1 is a schematic diagram for explaining the outline of the welded portions 30 and 31 of the first member 2 and the second member 3 employed in the shaft coupling device of the present invention. FIG. 2 is a schematic diagram for explaining the outline of the welded portions of the first member 602 and the second member 603 employed in the conventional shaft coupling device.

以下、図１および図２を用いて、本発明の軸連結装置が溶接部の耐破壊性に優れる理由を説明する。尚、説明は、図１に示すように、例として、筒部材１が、第１および第２部材２,３を有する構成に基づいて行うことにする（軸部材が、第１および第２部材を有する構成である場合にも、同様の説明が成立する）。   Hereinafter, the reason why the shaft coupling device of the present invention is excellent in the fracture resistance of the welded portion will be described with reference to FIGS. As shown in FIG. 1, the description will be made based on a configuration in which the tubular member 1 includes first and second members 2 and 3 (the shaft member is the first and second members). The same description holds true even in the case of a configuration with

図１にしめすように、筒部材１は、断面Ｌ字状の第１部材２と、断面Ｌ字状の第２部材３とを有する。   As shown in FIG. 1, the cylindrical member 1 includes a first member 2 having an L-shaped cross section and a second member 3 having an L-shaped cross section.

上記第１部材２は、軸方向に延在する筒状部１１と、リング部１２とからなる。上記リング部１２は、環状であって、筒状部１１の軸方向の他端部の内周側から径方向の内方に突出している。上記筒状部１１の内周面は、その中央部に環状の凹部２３を有する。   The first member 2 includes a cylindrical portion 11 extending in the axial direction and a ring portion 12. The ring portion 12 is annular and protrudes inward in the radial direction from the inner peripheral side of the other end portion in the axial direction of the cylindrical portion 11. The inner peripheral surface of the cylindrical portion 11 has an annular recess 23 at the center.

上記第２部材３は、軸方向に延在する筒状部２１と、リング部２２とからなる。上記リング部２２は、環状であって、筒状部２１の軸方向の一端部の外周側から径方向の外方に突出している。上記筒状部２１の外周面は、その中央部に環状の凹部３３を有する。   The second member 3 includes a cylindrical portion 21 that extends in the axial direction and a ring portion 22. The ring portion 22 is annular, and protrudes outward in the radial direction from the outer peripheral side of one end portion in the axial direction of the tubular portion 21. The outer peripheral surface of the cylindrical part 21 has an annular recess 33 at the center.

上記第１部材２の軸方向のリング部１２側とは反対側の端面は、第２部材３のリング部２２の軸方向の端面に当接し、第２部材３の軸方向のリング部２２側とは反対側の端面は、第１部材２のリング部１２の軸方向の端面に当接している。上記第１部材２の筒状部１１の内周面の軸方向の寸法は、第２部材３の筒状部２１の外周面の軸方向の寸法と、略一致し、第１部材２の環状凹部２３の軸方向の寸法と、第２部材３の環状凹部３３の軸方向の寸法とは、略一致している。上記第１部材２の環状凹部２３の全体と、第２部材３の環状凹部３３の全体とは、径方向に重なっている。上記第１部材２の環状凹部２３と、第２部材３の環状凹部３３とは、相俟って環状の液圧通路２７を構成している。上記液圧通路２７は、筒部材１の軸方向に延在している。上記第１部材２の筒状部１１の内周面と、第２部材３の筒状部２１の外周面とは、液圧通路２７の両側で、当接している。   The end surface of the first member 2 opposite to the ring portion 12 side in the axial direction is in contact with the end surface in the axial direction of the ring portion 22 of the second member 3, and the axial direction ring portion 22 side of the second member 3. The end surface on the opposite side is in contact with the axial end surface of the ring portion 12 of the first member 2. The axial dimension of the inner peripheral surface of the cylindrical portion 11 of the first member 2 substantially coincides with the axial dimension of the outer peripheral surface of the cylindrical portion 21 of the second member 3, and the annular shape of the first member 2. The dimension in the axial direction of the recess 23 and the dimension in the axial direction of the annular recess 33 of the second member 3 are substantially the same. The entire annular recess 23 of the first member 2 and the entire annular recess 33 of the second member 3 overlap in the radial direction. The annular recess 23 of the first member 2 and the annular recess 33 of the second member 3 together constitute an annular hydraulic passage 27. The hydraulic pressure passage 27 extends in the axial direction of the cylindrical member 1. The inner peripheral surface of the cylindrical portion 11 of the first member 2 and the outer peripheral surface of the cylindrical portion 21 of the second member 3 are in contact with both sides of the hydraulic pressure passage 27.

上記第１部材２の軸方向のリング部１２側とは反対側の端面と、第２部材３のリング部２２の軸方向の端面とは、溶接により結合されている。また、上記第２部材３の軸方向のリング部２２側とは反対側の端面と、第１部材２のリング部１２の軸方向の端面とは、溶接により結合されている。   The end surface of the first member 2 opposite to the axially ring portion 12 side and the axially end surface of the ring portion 22 of the second member 3 are joined by welding. Further, the end surface of the second member 3 opposite to the ring portion 22 side in the axial direction and the end surface in the axial direction of the ring portion 12 of the first member 2 are joined by welding.

図１において、３０は、第１部材２の軸方向のリング部１２側とは反対側の端面と、第２部材３のリング部２２の軸方向の端面との溶接部を示し、３１は、第２部材３の軸方向のリング部２２側とは反対側の端面と、第１部材２のリング部１２の軸方向の端面との溶接部を示している。   In FIG. 1, reference numeral 30 denotes a welded portion between the end surface of the first member 2 opposite to the axial ring portion 12 side and the axial end surface of the ring portion 22 of the second member 3. The welding part of the end surface on the opposite side to the ring part 22 side of the axial direction of the 2nd member 3 and the end surface of the axial direction of the ring part 12 of the 1st member 2 is shown.

上記二つの溶接部３０,３１の両方において、第１部材２と第２部材３は、軸方向に対向している（軸方向に重なっている）。   In both of the two welded portions 30 and 31, the first member 2 and the second member 3 face each other in the axial direction (overlapping in the axial direction).

一方、図２に示すように、従来の軸連結装置においては、筒部材６０１は、円筒状の第１部材６０２と、円筒状の第２部材６０３とからなっている。上記第１部材６０２の内周面の中央部には、環状凹部６２３が形成されている一方、第２部材６０３の外周面の中央部には、環状凹部６３３が形成されている。   On the other hand, as shown in FIG. 2, in the conventional shaft coupling device, the cylindrical member 601 includes a cylindrical first member 602 and a cylindrical second member 603. An annular recess 623 is formed in the central portion of the inner peripheral surface of the first member 602, while an annular recess 633 is formed in the central portion of the outer peripheral surface of the second member 603.

上記第１部材６０２の環状凹部６２３の全体と、第２部材６０３の環状凹部６３３の全体とは、径方向に重なっている。上記第１部材６０２の環状凹部６２３と、第２部材３の環状凹部６３３とは、相俟って環状の液圧通路６２７を構成している。   The entire annular recess 623 of the first member 602 and the entire annular recess 633 of the second member 603 overlap in the radial direction. The annular recess 623 of the first member 602 and the annular recess 633 of the second member 3 together constitute an annular hydraulic pressure passage 627.

上記液圧通路６２７は、筒部材６０１の軸方向に延在している。上記第１部材６０２の内周面と、第２部材６０３の外周面とは、液圧通路６２７の両側で、当接している。   The hydraulic pressure passage 627 extends in the axial direction of the cylindrical member 601. The inner peripheral surface of the first member 602 and the outer peripheral surface of the second member 603 are in contact with each other on both sides of the hydraulic pressure passage 627.

上記第１部材６０２の内周面の軸方向の一端部と、第２部材６０３の外周面の軸方向の一端部とは、溶接により結合され、また、上記第１部材６０２の内周面の軸方向の他端部と、第２部材６０３の外周面の軸方向の他端部とは、溶接により結合されている。   One end portion in the axial direction of the inner peripheral surface of the first member 602 and one end portion in the axial direction of the outer peripheral surface of the second member 603 are coupled by welding, and the inner peripheral surface of the first member 602 is The other end portion in the axial direction and the other end portion in the axial direction of the outer peripheral surface of the second member 603 are coupled by welding.

図２において、６３０は、第１部材６０２の内周面の軸方向の一端部と、第２部材６０３の外周面の軸方向の一端部との溶接部を示し、６３１は、上記第１部材６０２の内周面の軸方向の他端部と、第２部材６０３の外周面の軸方向の他端部との溶接部を示している。   In FIG. 2, reference numeral 630 denotes a welded portion between one axial end portion of the inner peripheral surface of the first member 602 and one axial end portion of the outer peripheral surface of the second member 603, and 631 denotes the first member. The welding part of the axial direction other end part of the internal peripheral surface of 602 and the axial direction other end part of the outer peripheral surface of the 2nd member 603 is shown.

上記本発明および従来の筒部材１,６０１の構成において、上記筒部材１では、二つの溶接部３０,３１が、液圧通路２７に、軸方向に重なる箇所に位置していなくて、液圧通路２７の延在方向に重なっていなくて、二つの溶接部３０,３１において、第１部材２と第２部材３が、軸方向に重なっているから、液圧通路２７に所定量の液体が封入されて、液圧通路２７が、図１に矢印Ａで示す方向に拡張し、第２部材３が矢印Ａで示す方向に膨らんだ場合において、二つの溶接部３０,３１が、液圧通路２７が径方向に拡張することに起因して生成される径方向の力である股裂き方向の力の影響を大きく受けることがない。   In the configuration of the present invention and the conventional cylindrical member 1, 601, in the cylindrical member 1, the two welded portions 30, 31 are not located at a position overlapping with the hydraulic pressure passage 27 in the axial direction. Since the first member 2 and the second member 3 overlap each other in the axial direction in the two welded portions 30 and 31 without overlapping in the extending direction of the passage 27, a predetermined amount of liquid flows in the hydraulic passage 27. When the hydraulic passage 27 is expanded in the direction indicated by the arrow A in FIG. 1 and the second member 3 swells in the direction indicated by the arrow A, the two welded portions 30 and 31 are connected to the hydraulic passage. 27 is not greatly affected by the force in the crotch tearing direction, which is the radial force generated due to the radial expansion of 27.

一方、上記従来の筒部材６０１では、二つの溶接部６３０,６３１が、液圧通路６２７に軸方向に重なる箇所に位置し、液圧通路６２７の延在方向に重なっていなくて、かつ、溶接部６３０,６３１において、第１部材６０２と第２部材６０３とが、径方向に対向しているから、液圧通路６２７に所定の液体が封入されて、液圧通路６２７が、図２に矢印Ｂで示す方向に拡張し、第２部材６０３が矢印Ｂで示す方向に膨らんだ場合において、二つの溶接部６３０,６３１が、液圧通路２７が径方向に拡張することに起因して生成される径方向の力である股裂き方向の力の影響を大きく受けて、溶接部６３０,６３１が、破壊し易くなるのである。   On the other hand, in the conventional cylindrical member 601, the two welded portions 630 and 631 are located at a position overlapping the hydraulic passage 627 in the axial direction, do not overlap the extending direction of the hydraulic passage 627, and are welded. In the portions 630 and 631, the first member 602 and the second member 603 are opposed to each other in the radial direction, so that a predetermined liquid is sealed in the hydraulic pressure passage 627 and the hydraulic pressure passage 627 is indicated by an arrow in FIG. When the second member 603 expands in the direction indicated by B and the second member 603 swells in the direction indicated by arrow B, the two welds 630 and 631 are generated due to the expansion of the hydraulic pressure passage 27 in the radial direction. The welds 630 and 631 are easily broken by being greatly affected by the force in the crotch tearing direction, which is the radial force.

以下、図３〜図６を用いて、本発明のトルクリミッタの第１乃至第４実施形態８を説明することにする。   Hereinafter, the first to fourth embodiments of the torque limiter according to the present invention will be described with reference to FIGS.

（第１実施形態）
図３は、本発明の第１実施形態のトルクリミッタの軸方向の断面図である。 (First embodiment)
FIG. 3 is a sectional view in the axial direction of the torque limiter according to the first embodiment of the present invention.

このトルクリミッタは、軸部材１０１と、筒部材１０２と、シャーバルブ１０６と、玉軸受１１７および玉軸受１１８とを有する。   The torque limiter includes a shaft member 101, a cylindrical member 102, a shear valve 106, a ball bearing 117 and a ball bearing 118.

上記軸部材１０１は、周面としての略円筒状の外周面１２０を有する本体部１０８と、本体部１０８の外面から突出する断面略Ｌ字形状の係止部１０９とを有する。上記軸部材１０１の外周面１２０は、一つの螺旋形状の油封止防止用の溝１３５を有している。この螺旋形状の溝１３５は、軸部材１０１と筒部材１０２との摩擦係合部分の軸方向の両側に開口している。上記螺旋形状の溝１３５のピッチは、軸部材１０１の軸径（外径）の１／１０以上１／５以下になっている。   The shaft member 101 includes a main body portion 108 having a substantially cylindrical outer peripheral surface 120 as a peripheral surface, and a locking portion 109 having a substantially L-shaped cross section protruding from the outer surface of the main body portion 108. The outer peripheral surface 120 of the shaft member 101 has one spiral-shaped groove 135 for preventing oil sealing. The spiral groove 135 is open on both axial sides of the frictional engagement portion between the shaft member 101 and the cylindrical member 102. The pitch of the spiral groove 135 is 1/10 or more and 1/5 or less of the shaft diameter (outer diameter) of the shaft member 101.

上記筒部材１０２は、第１の筒部材１１０と、第２の筒部材１１１とからなっている。上記第１の筒部材１１０は、周面としての略円筒状の内周面１２１を有している。この内周面１２１は、動力の伝達時において軸部材１０１の外周面１２０に摩擦結合するようになっている。トルク伝達面である軸部材１０１の外周面（溝１３５の表面も含む）１２０と筒部材１０２の内周面１２１とは、処理温度が４００度以上４２０度以下の低温窒化処理が施されて硬化されており、軸部材１０１の外周面１２０（溝１３５の表面も含む）を含む表層部は、窒化物層になっており、また、筒部材１０２の内周面１２１を含む表層部は、窒化物層になっている。これら二つの窒化物層の層厚は、ともに２μｍ以上３μｍ以下になっている。また、これら二つの窒化物層の硬さは、略同じ硬さで、これら二つの窒化物層のビッカース硬さＨｖは、ともに６００Ｈｖ以上になっている。   The cylinder member 102 includes a first cylinder member 110 and a second cylinder member 111. The first cylindrical member 110 has a substantially cylindrical inner peripheral surface 121 as a peripheral surface. The inner peripheral surface 121 is frictionally coupled to the outer peripheral surface 120 of the shaft member 101 when power is transmitted. The outer peripheral surface (including the surface of the groove 135) 120 of the shaft member 101, which is a torque transmission surface, and the inner peripheral surface 121 of the cylindrical member 102 are subjected to a low-temperature nitriding process at a processing temperature of 400 degrees to 420 degrees and cured. The surface layer portion including the outer peripheral surface 120 (including the surface of the groove 135) of the shaft member 101 is a nitride layer, and the surface layer portion including the inner peripheral surface 121 of the cylindrical member 102 is nitrided. It is a material layer. The thicknesses of these two nitride layers are both 2 μm or more and 3 μm or less. Further, the hardness of these two nitride layers is substantially the same, and the Vickers hardness Hv of these two nitride layers is 600 Hv or more.

上記軸部材１０１の外周面１２０と、筒部材１０２の内周面１２１との間には、焼付き防止用の潤滑油であるタービンオイルやトラクションオイルが充填されている。このトラクションオイルとしては、例えば、シクロペンチル基、シクロヘキシル基、シクロヘプチル基などの脂環族の官能基や、これら官能基の一部を不飽和結合としたものや、上記官能基の一部の炭素原子を、酸素原子、硫黄原子、窒素原子で置き換えた官能基、さらには、これらの官能基を架橋して形成された官能基や、これらの官能基を縮合した縮合環を有する官能基や、または、これらの官能基を用いて形成された多環式の芳香族の官能基、を有するナフテン系合成油やナフテン系鉱油がある。また、上記トラクションオイルの他の例としては、例えば、分岐型アルキルベンゼンやアルキルナフタレンや、または、フェニル基やシクロヘキシル基を含むポリオルガノシロキサンがある。また、上記トラクションオイルの更なる例としては、例えば、α−アルキルスチレン二量体やα−アルキルスチレン二量体の水素化物があり、また、Ｆ−（ＣＦ（ＣＦ３）ＣＦ２Ｏ）ｎ−Ｃ２Ｆ５の構造式で表されるパーフルオロポリエーテルやこのパーフルオロポリエーテルの誘導体がある。 Between the outer peripheral surface 120 of the shaft member 101 and the inner peripheral surface 121 of the cylindrical member 102, turbine oil or traction oil, which is lubricating oil for preventing seizure, is filled. Examples of the traction oil include alicyclic functional groups such as a cyclopentyl group, a cyclohexyl group, and a cycloheptyl group, those having a part of these functional groups as an unsaturated bond, and some carbons of the above functional groups. Functional groups in which atoms are replaced with oxygen atoms, sulfur atoms, nitrogen atoms, further functional groups formed by crosslinking these functional groups, functional groups having condensed rings obtained by condensing these functional groups, Alternatively, there are naphthenic synthetic oils and naphthenic mineral oils having a polycyclic aromatic functional group formed using these functional groups. Other examples of the traction oil include branched alkylbenzene and alkylnaphthalene, or polyorganosiloxane containing a phenyl group and a cyclohexyl group. Further examples of the traction oil include, for example, α-alkylstyrene dimers and hydrides of α-alkylstyrene dimers, and F- (CF (CF 3 ) CF 2 O) n. There are perfluoropolyethers represented by the structural formula of —C 2 F 5 and derivatives of this perfluoropolyether.

また、これらのトラクションオイルを、パラフィン系鉱油、ポリαオレフィン油など炭化水素系合成油、ジエステルやポリオールエステルなどエステル油、ポリアルキルグリコール油、アルキルジフェニルエーテル油、シリコーン油、パーフルオロアルキルポリエーテル油等、公知の潤滑油と混合したものも使用できる。   In addition, these traction oils can be used as hydrocarbon synthetic oils such as paraffinic mineral oils and poly-alpha olefin oils, ester oils such as diesters and polyol esters, polyalkyl glycol oils, alkyl diphenyl ether oils, silicone oils, perfluoroalkyl polyether oils, etc. A mixture with a known lubricating oil can also be used.

また、実用性を更に向上する目的で、酸化防止剤、防錆剤、清浄分散剤、流動点降下剤、粘度指数向上剤、極圧剤、耐摩耗添加剤、腐食防止剤、消泡剤、金属不活性化剤、着色剤等の添加剤を適量添加しても良い。   In addition, for the purpose of further improving practicality, antioxidants, rust inhibitors, detergent dispersants, pour point depressants, viscosity index improvers, extreme pressure agents, antiwear additives, corrosion inhibitors, antifoaming agents, An appropriate amount of additives such as a metal deactivator and a colorant may be added.

また、これらのトラクションオイルのうちでも、圧力粘度指数が大きいトラクションオイルを使用することが好ましい。本用途では、１８ＧＰａ−１ （４０℃）以上が好ましく、２５ＧＰａ−１ （４０℃）以上が更にこのましく、３２ＧＰａ−１ （４０℃）以上が更に好ましい。このようなトラクションオイルは、軸とスリーブとの間の接触面圧によりガラス化しやすく、駆動力を伝え易い。また、このようなトラクションオイルは、軸とスリーブとの直接接触を減少させ、軸とスリーブの固着を防ぎ、油圧室の油圧が低下し液状になると、トルク開放を容易になすことができる。 Of these traction oils, it is preferable to use a traction oil having a large pressure viscosity index. In this application, preferably 18GPa -1 (40 ℃) above, 25GPa -1 (40 ℃) or more Preferably, 32GPa -1 (40 ℃) or higher is more preferable. Such traction oil is easily vitrified by the contact surface pressure between the shaft and the sleeve, and easily transmits the driving force. Further, such traction oil reduces the direct contact between the shaft and the sleeve, prevents the shaft and the sleeve from sticking, and can easily release the torque when the hydraulic pressure in the hydraulic chamber decreases and becomes liquid.

上記第２の筒部材１１１は、第１の筒部材１１０の略円筒状の外周面１２３に当接する略円筒状の内周面１２４を有している。上記第２の筒部材１１１は、シャーバルブ取付穴１３０と、環状の油圧通路１２６を有する。上記油圧通路１２６は、第２の筒部材１１１の内部に形成されている。上記油圧通路１２６は、第２の筒部材１１１の内周面１２４の軸方向の所定長さに亘って略軸部材１０１の軸方向に延在している。   The second cylindrical member 111 has a substantially cylindrical inner peripheral surface 124 that contacts the substantially cylindrical outer peripheral surface 123 of the first cylindrical member 110. The second cylindrical member 111 has a shear valve mounting hole 130 and an annular hydraulic passage 126. The hydraulic passage 126 is formed in the second cylindrical member 111. The hydraulic passage 126 extends substantially in the axial direction of the shaft member 101 over a predetermined axial length of the inner peripheral surface 124 of the second cylindrical member 111.

上記第２の筒部材１１１は、筒状の第１部材１７０と、筒状の第２部材１７１とを有する。上記第１部材１７０と第２部材１７１とは、油圧通路１２６を介して径方向に対向している。   The second cylindrical member 111 includes a cylindrical first member 170 and a cylindrical second member 171. The first member 170 and the second member 171 are opposed to each other in the radial direction via the hydraulic passage 126.

上記第１部材１７０は、軸方向に延在する筒状部１８０と、リング部１８１とからなる。上記リング部１８１は、環状であって、筒状部１８０の軸方向の他端部の内周側から径方向の内方に突出している。上記筒状部１８０の内周面は、その中央部に環状の凹部を有する。   The first member 170 includes a cylindrical portion 180 extending in the axial direction and a ring portion 181. The ring portion 181 is annular and protrudes inward in the radial direction from the inner peripheral side of the other end portion in the axial direction of the cylindrical portion 180. The inner peripheral surface of the cylindrical portion 180 has an annular recess at the center.

上記第２部材１７１は、断面略Ｌ字状の形状を有している。上記第２部材１７１は、軸方向に延在する筒状部１９０と、リング部１９１とからなる。上記リング部１９１は、環状であって、筒状部１９０の軸方向の一端部の外周側から径方向の外方に突出している。上記筒状部１９０の外周面は、その中央部に環状の凹部を有している。   The second member 171 has a substantially L-shaped cross section. The second member 171 includes a cylindrical portion 190 extending in the axial direction and a ring portion 191. The ring portion 191 is annular and protrudes outward in the radial direction from the outer peripheral side of one end portion of the cylindrical portion 190 in the axial direction. The outer peripheral surface of the cylindrical portion 190 has an annular recess at the center.

上記第１部材１７０の軸方向のリング部１８１側とは反対側の端面１８４は、第２部材１７１のリング部１９１の軸方向の端面１８５に当接し、第２部材１７１の軸方向のリング部１９１側とは反対側の端面１８６は、第１部材１７０のリング部１８１の軸方向の端面１８７に当接している。   The end surface 184 of the first member 170 opposite to the axial ring portion 181 side abuts on the axial end surface 185 of the ring portion 191 of the second member 171, and the axial ring portion of the second member 171. The end surface 186 opposite to the 191 side is in contact with the axial end surface 187 of the ring portion 181 of the first member 170.

上記第１部材１７０の筒状部１８０の内周面の軸方向の寸法は、第２部材１７１の筒状部１９０の外周面の軸方向の寸法と略一致し、第１部材１７０の環状凹部の軸方向の寸法は、第２部材１７１の環状凹部の軸方向の寸法と略一致している。上記第１部材１７０の環状凹部の全体と、第２部材１７１の環状凹部の全体とは、径方向に重なっている。上記第１部材１７０の環状凹部と、第２部材１７１の環状凹部とは、相俟って環状の油圧通路１２６を構成している。   The axial dimension of the inner peripheral surface of the cylindrical part 180 of the first member 170 substantially matches the axial dimension of the outer peripheral surface of the cylindrical part 190 of the second member 171, and the annular recess of the first member 170 The axial dimension is substantially the same as the axial dimension of the annular recess of the second member 171. The entire annular recess of the first member 170 and the entire annular recess of the second member 171 overlap in the radial direction. The annular recess of the first member 170 and the annular recess of the second member 171 together constitute an annular hydraulic passage 126.

上記油圧通路１２６は、一方の部材としての筒部材１０２の軸方向に延在している。上記第１部材１７０と、第２部材１７１とは、油圧通路１２６の一端側において、環状の溶接部によって溶接接合される一方、油圧通路１２６の他端側において、環状の溶接部によって溶接接合されている。   The hydraulic passage 126 extends in the axial direction of the cylindrical member 102 as one member. The first member 170 and the second member 171 are welded and joined at one end side of the hydraulic passage 126 by an annular welded portion, and are welded and joined at the other end side of the hydraulic passage 126 by an annular welded portion. ing.

詳細には、上記第１部材１７０の軸方向のリング部１８１側とは反対側の端面１８４と、第２部材１７１のリング部１９１の軸方向の端面１８５とは、径方向の上方の端部において、溶接により結合されている。また、上記第２部材１７１の軸方向のリング部１９１側とは反対側の端面１８６と、第１部材１７０のリング部１８１の軸方向の端面１８７とは、径方向の下方の端部において、溶接により結合されている。   Specifically, an end surface 184 opposite to the axial ring portion 181 side of the first member 170 and an axial end surface 185 of the ring portion 191 of the second member 171 are radially upper end portions. In FIG. In addition, an end surface 186 opposite to the axial ring portion 191 side of the second member 171 and an axial end surface 187 of the ring portion 181 of the first member 170 are at the lower end in the radial direction. They are joined by welding.

図３において、１９８は、第１部材１７０の軸方向のリング部１８１側とは反対側の端面１８４と、第２部材１７１のリング部１９１の軸方向の端面１８５との溶接部（以下、この溶接部を第１溶接部という）を示し、１９９は、第２部材１７１の軸方向のリング部１９１側とは反対側の端面１８６と、第１部材１７０のリング部１８１の軸方向の端面１８７との溶接部（以下、この溶接部を第２溶接部という）を示している。   In FIG. 3, reference numeral 198 denotes a welded portion between the end surface 184 of the first member 170 opposite to the axial ring portion 181 side and the axial end surface 185 of the ring portion 191 of the second member 171 (hereinafter referred to as this part). 199 indicates an end surface 186 of the second member 171 opposite to the axial ring portion 191 side, and an axial end surface 187 of the ring portion 181 of the first member 170. (Hereinafter, this weld is referred to as a second weld).

上記二つの溶接部１９８,１９９の両方において、第１部材１７０と第２部材１７１は、略軸方向に対向している。上記二つの溶接部１９８,１９９の両方において、第１部材１７０と第２部材１７１は、軸方向に重なっている。上記二つの溶接部１９８,１９９の両方において、第１部材１７０において第２部材１７１に対向している対向面は、略第１部材１７０の径方向に広がっている。   In both of the two welds 198 and 199, the first member 170 and the second member 171 are substantially opposed to each other in the axial direction. In both of the two welded portions 198 and 199, the first member 170 and the second member 171 overlap in the axial direction. In both of the two welded portions 198 and 199, the facing surface of the first member 170 facing the second member 171 extends substantially in the radial direction of the first member 170.

上記第１溶接部１９８は、一方の部材としての筒部材１０２の径方向において、油圧通路１２６に対して筒部材１０２の摩擦係合面である内周面１２１側とは反対側に位置し、第２溶接部１９９は、径方向において、油圧通路１２６に対して筒部材１０２の上記内周面１２１側に位置している。   The first welded portion 198 is located on the opposite side to the inner circumferential surface 121 side that is the friction engagement surface of the cylindrical member 102 with respect to the hydraulic passage 126 in the radial direction of the cylindrical member 102 as one member. The second welded portion 199 is located on the inner peripheral surface 121 side of the cylindrical member 102 with respect to the hydraulic passage 126 in the radial direction.

上記シャーバルブ１０６は、シャーバルブ取付穴１３０に嵌入されている。上記シャーバルブ１０６がシャーバルブ取付穴１３０に嵌入されている状態で、シャーバルブ１０６の一端部は、第２の筒部材１１１の外周面よりも径方向の外方に突出している。また、上記断面略Ｌ字形状の係止部１０９は、略径方向に延びると共に、第２の筒部材１１１の端面に軸方向に対向する径方向延在部と、この径方向延在部につながっていると共に、第２の筒部材１１１の外周面に沿って軸方向に延在する軸方向延在部とを有している。上記シャーバルブ１０６の上記一端部は、係止部１０９の軸方向延在部によって、係止されている。   The shear valve 106 is fitted in the shear valve mounting hole 130. In a state where the shear valve 106 is fitted in the shear valve mounting hole 130, one end portion of the shear valve 106 protrudes outward in the radial direction from the outer peripheral surface of the second cylindrical member 111. In addition, the locking portion 109 having a substantially L-shaped cross section extends in a substantially radial direction, and extends in a radial direction facing the end surface of the second cylindrical member 111 in the axial direction. It is connected and has an axially extending portion extending in the axial direction along the outer peripheral surface of the second cylindrical member 111. The one end portion of the shear valve 106 is locked by an axially extending portion of the locking portion 109.

上記シャーバルブ１０６は、一端のみが開口したチューブ１２７を有している。このチューブ１２７は、シャーバルブ１０６がシャーバルブ取付穴１３０に嵌入されている状態で、略軸部材１０１の径方向に延在している。また、シャーバルブ１０６がシャーバルブ取付穴１３０に嵌入されている状態でチューブ１２７の閉鎖側の一端部は、第２の筒部材１１１の外周面よりも径方向の外方に突出している。また、上記チューブ１２７の閉鎖側とは反対側の開口は、油圧通路１２６の一端に連通している。上記油圧通路１２６のシャーバルブ１０６側は、密封空間になっている。   The shear valve 106 has a tube 127 that is open only at one end. The tube 127 extends substantially in the radial direction of the shaft member 101 in a state where the shear valve 106 is fitted in the shear valve mounting hole 130. In addition, in a state where the shear valve 106 is fitted in the shear valve mounting hole 130, one end portion on the closed side of the tube 127 protrudes outward in the radial direction from the outer peripheral surface of the second cylindrical member 111. The opening of the tube 127 opposite to the closed side communicates with one end of the hydraulic passage 126. The shear valve 106 side of the hydraulic passage 126 is a sealed space.

上記玉軸受１１７は、軸部材１０１の外面に外嵌固定された内輪１４０と、第２の筒部材１１１の内面に内嵌固定された外輪１４１と、内輪１４０の軌道面と外輪１４１の軌道面と間に配置された玉１４２とを有している。また、上記玉軸受１１８は、軸部材１０１の外面に外嵌固定された内輪１４４と、第１の筒部材１１０の内面に内嵌固定された外輪１４５と、内輪１４４の軌道面と外輪１４５の軌道面と間に配置された玉１４６とを有している。上記玉軸受１１７および１１８は、軸部材１０１が筒部材１０２に対して相対回転しているとき、軸部材１０１を筒部材１０２に対して回転自在に支持するようになっている。   The ball bearing 117 includes an inner ring 140 fitted and fixed to the outer surface of the shaft member 101, an outer ring 141 fitted and fixed to the inner surface of the second cylindrical member 111, a raceway surface of the inner ring 140, and a raceway surface of the outer ring 141. And a ball 142 disposed between them. The ball bearing 118 includes an inner ring 144 fitted and fixed to the outer surface of the shaft member 101, an outer ring 145 fitted and fixed to the inner surface of the first cylindrical member 110, a raceway surface of the inner ring 144, and an outer ring 145. And a ball 146 disposed between the raceway surfaces. The ball bearings 117 and 118 are configured to rotatably support the shaft member 101 with respect to the cylindrical member 102 when the shaft member 101 rotates relative to the cylindrical member 102.

上記構成において、軸部材１０１または筒部材１０２に所定値以下の負荷（トルクの伝達を行う範囲の負荷）がかかっている場合には、図示しないカプラを介して油圧通路１２６に注入されたのち密封された油圧拡張用の油で、第１の筒部材１１０の内周面１２１を縮径して内周面１２１を軸部材１０１の外周面１２０に押し付けて、軸部材１０１と筒部材１０２とを摩擦結合して、軸部材１０１と筒部材１０２との間でトルクを伝達するようになっている。   In the above configuration, when a load of a predetermined value or less (load in a range where torque is transmitted) is applied to the shaft member 101 or the cylindrical member 102, the shaft member 101 or the cylindrical member 102 is sealed after being injected into the hydraulic passage 126 via a coupler (not shown). With the oil for expanding hydraulic pressure, the inner peripheral surface 121 of the first cylindrical member 110 is reduced in diameter, and the inner peripheral surface 121 is pressed against the outer peripheral surface 120 of the shaft member 101, so that the shaft member 101 and the cylindrical member 102 are A torque is transmitted between the shaft member 101 and the cylindrical member 102 by frictional coupling.

一方、軸部材１０１または筒部材１０２に所定値以上の負荷（トルクの伝達を行う範囲よりも大きな負荷）がかかって、軸部材１０１の外周面１２０が、第１の筒部材１１０の内周面１２１に対してスリップして、軸部材１０１と筒部材１０２の軸回りの位置が変化した場合、係止部１０９がシャーバルブ１０６の上記一端部を切断して、油圧通路１２６内の油圧拡張用の油を、一端部が切断されたシャーバルブ１０６を介して外部に排出するようになっている。このようにして、第１の筒部材１１０の内周面１２１の軸部材１０１の外周面１２０に対する押圧力をなくして、軸部材１０１と筒部材１０２の摩擦結合を解いて、トルクの伝達を遮断するようになっている。このようにして、軸部材１０１または筒部材１０２に過負荷が生じた場合において、トルクの伝達を遮断して、トルクリミッタ装置に連結されている高価な機械を保護している。   On the other hand, the shaft member 101 or the cylindrical member 102 is subjected to a load greater than a predetermined value (a load larger than the range in which torque is transmitted), and the outer peripheral surface 120 of the shaft member 101 is the inner peripheral surface of the first cylindrical member 110. When the position of the shaft member 101 and the cylindrical member 102 about the axis changes due to slipping with respect to the shaft 121, the locking portion 109 cuts the one end portion of the shear valve 106 to expand the hydraulic pressure in the hydraulic passage 126. This oil is discharged to the outside through a shear valve 106 with one end cut off. In this manner, the pressing force of the inner peripheral surface 121 of the first cylindrical member 110 against the outer peripheral surface 120 of the shaft member 101 is eliminated, the frictional coupling between the shaft member 101 and the cylindrical member 102 is released, and torque transmission is interrupted. It is supposed to be. In this way, when an overload occurs in the shaft member 101 or the cylinder member 102, the transmission of torque is interrupted to protect the expensive machine connected to the torque limiter device.

尚、上記油封止防止用の溝１３５は、軸部材１０１または第１の筒部材１１０に過大な負荷がかかっていない通常のトルク伝達時に、油圧通路１２６に封入された油圧拡張用の油によって発生する第１の筒部材１１０の内周面１２１が軸部材１０１の外周面１２０を押圧する面圧によって、軸部材１０１と第１の筒部材１１０との間に存在する余剰（余分）な焼付き防止用の潤滑油を、その油封止防止用の溝３５の開口を介して外部に排出する役割を担っている。   The oil sealing prevention groove 135 is generated by oil for hydraulic expansion enclosed in the hydraulic passage 126 during normal torque transmission when no excessive load is applied to the shaft member 101 or the first cylindrical member 110. The surplus (excess) seizure that exists between the shaft member 101 and the first tube member 110 due to the surface pressure that the inner surface 121 of the first tube member 110 presses against the outer surface 120 of the shaft member 101. The prevention lubricating oil is discharged to the outside through the opening of the groove 35 for preventing oil sealing.

このようにして、軸部材１０１と第１の筒部材１１０との間に存在している焼付き防止用の潤滑油が、過剰に軸部材１０１の外周面１２０と第１の筒部材１１０の内周面１２１との間で滞留、密封されて、第１の筒部材１１０が軸部材１０１をクランプする力を所定値（設計値）以下に弱めることを防止し、リリーストルクが所定値より大きく低下することを防止している。   In this manner, the seizure prevention lubricating oil existing between the shaft member 101 and the first cylindrical member 110 is excessively contained in the outer peripheral surface 120 of the shaft member 101 and the first cylindrical member 110. The first cylinder member 110 is retained and sealed with the peripheral surface 121 to prevent the clamping force of the shaft member 101 from being reduced below a predetermined value (design value), and the release torque is greatly reduced below the predetermined value. To prevent it.

上記第１実施形態のトルクリミッタによれば、上記第１溶接部１９８において、第１部材１７０と第２部材１７１とが、軸方向に重なっているから、従来の構成、すなわち、溶接部において、上記第１部材と第２部材とが、径方向に重なって軸方向に重なっていない構成と比較して、略上記軸方向に延在する油圧通路１２６の径方向の拡張に基づく径方向の引っ張り応力が、第１溶接部１７１に作用しにくくて、第１溶接部１９８に、その引っ張り応力に起因する股裂き力が作用することを低減できる。したがって、上記第１溶接部１９８の破壊を抑制することができる。また、同様の理由で、第２溶接部１９９の破壊を抑制することができる。   According to the torque limiter of the first embodiment, since the first member 170 and the second member 171 overlap in the axial direction in the first welded portion 198, in the conventional configuration, that is, in the welded portion, Compared with a configuration in which the first member and the second member overlap in the radial direction and do not overlap in the axial direction, the radial tension is based on the radial expansion of the hydraulic passage 126 extending substantially in the axial direction. The stress hardly acts on the first welded portion 171, and it is possible to reduce the crotch tearing force due to the tensile stress acting on the first welded portion 198. Therefore, destruction of the first welded portion 198 can be suppressed. In addition, for the same reason, the breakage of the second welded portion 199 can be suppressed.

また、上記第１実施形態のトルクリミッタによれば、上記第１溶接部１９８において、第１部材１７０において第２部材１７１に対向する対向面が、略第１部材１７０の径方向に広がっているから、軸方向に延在する油圧通路１２６の径方向の拡張に基づく径方向の引っ張り応力が、第１溶接部１９８に殆ど作用することがない。したがって、上記第１溶接部１９８の股裂が原因となる破壊が発生することがない。また、同様の理由により、第２溶接部１９９の股裂きが原因となる破壊が発生することがない。   Further, according to the torque limiter of the first embodiment, in the first welded portion 198, the facing surface of the first member 170 that faces the second member 171 extends substantially in the radial direction of the first member 170. Therefore, the tensile stress in the radial direction based on the radial expansion of the hydraulic passage 126 extending in the axial direction hardly acts on the first welded portion 198. Therefore, the breakage caused by the crotch of the first welded portion 198 does not occur. Further, for the same reason, the breakage caused by the crotch tear of the second welded portion 199 does not occur.

また、上記第１実施形態のトルクリミッタによれば、上記第１溶接部１９８は、径方向において、液圧通路１２６に対して筒部材１０２の摩擦係合面である内周面１２１側とは反対側に位置し、第２溶接部１９９は、径方向において、液圧通路１２６に対して筒部材１０２の内周面１２１側に位置しているから、第１部材１７０と第２部材１７１とを互いに容易に組み付けることができて、溶接を容易に行うことができる。   Further, according to the torque limiter of the first embodiment, the first welded portion 198 is different from the inner peripheral surface 121 side that is the friction engagement surface of the cylindrical member 102 with respect to the hydraulic pressure passage 126 in the radial direction. The second welded portion 199 is located on the opposite side, and is located on the inner peripheral surface 121 side of the cylindrical member 102 with respect to the hydraulic pressure passage 126 in the radial direction. Therefore, the first member 170 and the second member 171 Can be easily assembled with each other and welding can be easily performed.

（第２実施形態）
図４は、本発明の第２実施形態のトルクリミッタの軸方向の断面図である。 (Second Embodiment)
FIG. 4 is a sectional view in the axial direction of the torque limiter according to the second embodiment of the present invention.

第２実施形態のトルクリミッタは、筒部材２０２の第２の筒部材２１１の構造のみが、第１実施形態のトルクリミッタと異なる。   The torque limiter of the second embodiment differs from the torque limiter of the first embodiment only in the structure of the second cylinder member 211 of the cylinder member 202.

第２実施形態のトルクリミッタでは、第１実施形態のトルクリミッタの構成部と同一構成部には同一参照番号を付して説明を省略することにする。また、第２実施形態のトルクリミッタでは、第１実施形態のトルクリミッタと共通の作用効果および変形例については説明を省略することにし、第１実施形態のトルクリミッタと異なる構成、作用効果および変形例についてのみ説明を行うことにする。   In the torque limiter of the second embodiment, the same components as those of the torque limiter of the first embodiment are denoted by the same reference numerals, and the description thereof is omitted. In the torque limiter according to the second embodiment, the description of the operation and effect common to the torque limiter according to the first embodiment will be omitted, and the configuration, operation and effect different from those of the torque limiter according to the first embodiment will be omitted. Only an example will be described.

第２実施形態において、第２の筒部材２１１は、筒状の第１部材２７０と、筒状の第２部材２７１とを有する。上記第１部材２７０と第２部材２７１とは、油圧通路２２６を介して径方向に対向している。   In the second embodiment, the second cylindrical member 211 includes a cylindrical first member 270 and a cylindrical second member 271. The first member 270 and the second member 271 are opposed to each other in the radial direction via the hydraulic passage 226.

上記第１部材２７０は、軸方向に延在する筒状部２８０と、リング部２８１とからなる。上記リング部２８１は、環状であって、筒状部２８０の軸方向の他端部の内周側から径方向の内方に突出している。上記筒状部２８０の内周面は、その中央部に環状の凹部を有している。   The first member 270 includes a cylindrical portion 280 extending in the axial direction and a ring portion 281. The ring portion 281 is annular and protrudes inward in the radial direction from the inner peripheral side of the other end portion in the axial direction of the cylindrical portion 280. The inner peripheral surface of the cylindrical portion 280 has an annular recess at the center.

上記第２部材２７１は、断面略Ｌ字状の形状を有している。上記第２部材２７１は、軸方向に延在する筒状部２９０と、リング部２９１とからなる。上記リング部２９１は、環状であって、筒状部２９０の軸方向の一端部の外周側から径方向の外方に突出している。上記筒状部２９０の外周面は、その中央部に環状の凹部を有している。   The second member 271 has a substantially L-shaped cross section. The second member 271 includes a cylindrical part 290 extending in the axial direction and a ring part 291. The ring portion 291 is annular and protrudes outward in the radial direction from the outer peripheral side of one end portion of the cylindrical portion 290 in the axial direction. The outer peripheral surface of the cylindrical part 290 has an annular recess at the center.

上記第１部材２７０の軸方向のリング部２８１側とは反対側の端面２８４は、第２部材２７１のリング部２９１の軸方向の端面２８５に当接し、第２部材２７１の軸方向のリング部２９１側とは反対側の端面２８６は、第１部材２７０のリング部２８１の軸方向の端面２８７に当接している。   The end surface 284 of the first member 270 opposite to the axial ring portion 281 side abuts on the axial end surface 285 of the ring portion 291 of the second member 271, and the axial ring portion of the second member 271. The end surface 286 opposite to the 291 side is in contact with the axial end surface 287 of the ring portion 281 of the first member 270.

上記第１部材２７０の筒状部２８０の内周面の軸方向の寸法は、第２部材２７１の筒状部２９０の外周面の軸方向の寸法と略一致し、第１部材２７０の環状凹部の軸方向の寸法は、第２部材２７１の環状凹部の軸方向の寸法と略一致している。上記第１部材２７０の環状凹部の全体と、第２部材２７１の環状凹部の全体とは、径方向に重なっている。上記第２部材２７０の環状凹部と、第２部材２７１の環状凹部とは、相俟って環状の油圧通路２２６を構成している。   The axial dimension of the inner peripheral surface of the cylindrical portion 280 of the first member 270 substantially matches the axial dimension of the outer peripheral surface of the cylindrical portion 290 of the second member 271, and the annular recess of the first member 270. The axial dimension is substantially the same as the axial dimension of the annular recess of the second member 271. The entire annular recess of the first member 270 and the entire annular recess of the second member 271 overlap in the radial direction. The annular recess of the second member 270 and the annular recess of the second member 271 together constitute an annular hydraulic passage 226.

上記油圧通路２２６は、一方の部材としての筒部材２０２の軸方向に延在している。上記第１部材２７０と、第２部材２７１とは、油圧通路２２６の一端側において、環状の溶接部によって溶接接合される一方、油圧通路２２６の他端側において、環状の溶接部によって溶接接合されている。   The hydraulic passage 226 extends in the axial direction of the cylindrical member 202 as one member. The first member 270 and the second member 271 are welded and joined by an annular welded portion at one end side of the hydraulic passage 226, and are welded and joined by an annular welded portion at the other end side of the hydraulic passage 226. ing.

詳細には、上記第１部材２７０の軸方向のリング部２８１側とは反対側の端面２８４と、第２部材２７１のリング部２９１の軸方向の端面２８５とは、溶接により結合されている。また、上記第２部材２７１の軸方向のリング部２９１側とは反対側の端面２８６と、第１部材２７０のリング部２８１の軸方向の端面２８７とは、溶接により結合されている。   Specifically, the end surface 284 of the first member 270 opposite to the axial ring portion 281 side and the end surface 285 of the second member 271 in the axial direction of the ring portion 291 are joined by welding. Further, the end surface 286 opposite to the side of the ring portion 291 in the axial direction of the second member 271 and the end surface 287 of the first member 270 in the axial direction of the ring portion 281 are joined by welding.

図４において、２９８は、第１部材２７０の軸方向のリング部２８１側とは反対側の端面２８４と、第２部材２７１のリング部２９１の軸方向の端面２８５との溶接部（以下、この溶接部を、第１溶接部という）を示し、２９９は、第２部材２７１の軸方向のリング部２９１側とは反対側の端面２８６と、第１部材２７０のリング部２８１の軸方向の端面２８７との溶接部（以下、この溶接部を、第２溶接部という）を示している。上記二つの溶接部２９８,２９９の両方において、第１部材２７０と第２部材２７１は、軸方向に重なっている。   In FIG. 4, reference numeral 298 denotes a welded portion between the end surface 284 opposite to the axial ring portion 281 side of the first member 270 and the axial end surface 285 of the ring portion 291 of the second member 271 (hereinafter referred to as “this”). 299 indicates an end surface 286 of the second member 271 opposite to the axial ring portion 291 side, and an axial end surface of the ring portion 281 of the first member 270. A welded portion with 287 (hereinafter, this welded portion is referred to as a second welded portion) is shown. In both of the two welded portions 298 and 299, the first member 270 and the second member 271 overlap in the axial direction.

上記第１溶接部２９８は、一方の部材としての筒部材２０２の径方向において、油圧通路２２６に対して筒部材２０２の摩擦係合面である内周面１２１側とは反対側に位置し、第２溶接部２９９は、径方向において、油圧通路２２６に対して筒部材２０２の上記内周面１２１側に位置している。   The first welded portion 298 is located on the side opposite to the inner circumferential surface 121 side that is the friction engagement surface of the cylindrical member 202 with respect to the hydraulic passage 226 in the radial direction of the cylindrical member 202 as one member. The second welded portion 299 is located on the inner peripheral surface 121 side of the cylindrical member 202 with respect to the hydraulic passage 226 in the radial direction.

上記第１部材２７０の軸方向のリング部２８１側とは反対側の端面２８４は、油圧通路２２６から離れるにしたがって、すなわち、径方向の外方にいくにしたがって、軸方向において、第１部材２７０のリング部２８１側（油圧通路の他端側）に傾斜している。また、同様に、上記第２部材２７１のリング部２９１の軸方向の端面２８５は、油圧通路２２６から離れるにしたがって、すなわち、径方向の外方にいくにしたがって、軸方向において、第１部材２７０のリング部２８１側（油圧通路の他端側）に傾斜している。   The end surface 284 of the first member 270 opposite to the axial ring portion 281 side is separated from the hydraulic passage 226, that is, as it goes outward in the radial direction, the first member 270 in the axial direction. Is inclined toward the ring portion 281 side (the other end side of the hydraulic passage). Similarly, the end face 285 in the axial direction of the ring portion 291 of the second member 271 is further away from the hydraulic passage 226, that is, as it goes outward in the radial direction, the first member 270 in the axial direction. Is inclined toward the ring portion 281 side (the other end side of the hydraulic passage).

また、図４に示すように、上記第２部材２７１の軸方向のリング部２９１側とは反対側の端面２８６は、油圧通路２２６から離れるにしたがって、すなわち、径方向の内方にいくにしたがって、軸方向において、第２部材２７１のリング部２９１側（油圧通路の一端側）に傾斜している。また、同様に、上記第１部材２７０のリング部２８１の軸方向の端面２８７は、油圧通路２２６から離れるにしたがって、すなわち、径方向の内方にいくにしたがって、軸方向において、第２部材２７１のリング部２９１側（油圧通路の一端側）に傾斜している。   As shown in FIG. 4, the end surface 286 of the second member 271 opposite to the axial ring portion 291 side is separated from the hydraulic passage 226, that is, as it goes inward in the radial direction. In the axial direction, the second member 271 is inclined toward the ring portion 291 side (one end side of the hydraulic passage). Similarly, the axial end surface 287 of the ring portion 281 of the first member 270 moves away from the hydraulic passage 226, that is, inward in the radial direction, the second member 271 in the axial direction. It is inclined to the ring portion 291 side (one end side of the hydraulic passage).

上記第２実施形態のトルクリミッタによれば、上記第１溶接部２９８において、第１部材２７０において第２部材２７１に対向する対向面（端面２８４）が、径方向に油圧通路２２６から離れるにしたがって、軸方向において、第１部材２７０のリング部２８１側（液圧通路２２６の他端側）に傾斜しているから、軸方向に延在する油圧通路２２６の径方向の拡張に基づく径方向の引っ張り応力が、第１溶接部２９８に殆ど作用することがない。したがって、上記第１溶接部２９８の股裂破壊を格段に緩和できる。   According to the torque limiter of the second embodiment, in the first welded portion 298, the opposing surface (end surface 284) facing the second member 271 in the first member 270 is separated from the hydraulic passage 226 in the radial direction. In the axial direction, since the first member 270 is inclined toward the ring portion 281 side (the other end side of the hydraulic pressure passage 226), the radial direction is based on the radial expansion of the hydraulic passage 226 extending in the axial direction. The tensile stress hardly acts on the first welded portion 298. Therefore, the crotch fracture of the first welded portion 298 can be remarkably mitigated.

また、同様に、上記第２溶接部２９９において、第２部材２７１において第１部材２７０に対向する対向面（端面２８６）が、径方向に油圧通路２２６から離れるにしたがって、軸方向において、第２部材２７１のリング部２９１側（液圧通路２２６の一端側）に傾斜しているから、第１溶接部２９９の股裂破壊を格段に緩和できる。   Similarly, in the second welded portion 299, the second member 271 has a second opposing surface (end surface 286) that faces the first member 270 in the axial direction as the second surface 286 moves away from the hydraulic passage 226 in the radial direction. Since the member 271 is inclined toward the ring portion 291 side (one end side of the hydraulic pressure passage 226), the crotch fracture of the first welded portion 299 can be remarkably mitigated.

上記第１実施形態および第２実施形態では、油圧通路１２６,２２６を筒部材１０２,２０２に形成した。しかしながら、油圧通路は、以下の第３実施形態および第４実施形態のように、軸部材に形成されても良い。   In the first and second embodiments, the hydraulic passages 126 and 226 are formed in the cylindrical members 102 and 202. However, the hydraulic passage may be formed in the shaft member as in the following third and fourth embodiments.

（第３実施形態）
図５は、本発明の第３実施形態のトルクリミッタの軸方向の断面図である。 (Third embodiment)
FIG. 5 is a sectional view in the axial direction of the torque limiter according to the third embodiment of the present invention.

第３実施形態のトルクリミッタでは、環状の油圧通路３２６を、軸部材３０１に形成し、油圧通路３２６が径方向に拡張することで、軸部材３０１の外周面３２３が筒部材３０２の内周面３２４に摩擦係合することが第１実施形態のトルクリミッタと異なる。また、軸方向の両側に開口した油封止防止用の溝３３５を筒部材３０２に形成した点が、第１実施形態のトルクリミッタと異なる。第２実施形態のトルクリミッタでは、第１実施形態のトルクリミッタと共通の構成、作用効果および変形例については説明を省略することにする。   In the torque limiter of the third embodiment, an annular hydraulic passage 326 is formed in the shaft member 301 and the hydraulic passage 326 expands in the radial direction so that the outer peripheral surface 323 of the shaft member 301 becomes the inner peripheral surface of the cylindrical member 302. It differs from the torque limiter of the first embodiment in that it is frictionally engaged with 324. Moreover, the point which formed the groove | channel 335 for oil sealing prevention opened on the both sides of an axial direction in the cylinder member 302 differs from the torque limiter of 1st Embodiment. In the torque limiter according to the second embodiment, the description of the configuration, operational effects, and modifications common to those of the torque limiter according to the first embodiment will be omitted.

第３実施形態のトルクリミッタは、軸部材３０１と、筒部材３０２と、シャーバルブ３０６と、玉軸受１１７および玉軸受１１８とを有する。   The torque limiter according to the third embodiment includes a shaft member 301, a cylindrical member 302, a shear valve 306, a ball bearing 117 and a ball bearing 118.

上記軸部材３０１は、略円筒状の外周面３２０を有する軸本体３６１と、第１環状部材３１０と、第２環状部材３１１とを有する。第１環状部材３１０の内周面３２１は、軸本体３６１の外周面３２０と嵌め合わされている。上記第１環状部材３１０の端面は、ボルト３４５によって軸本体３６１の軸方向の端面に係止されて固定されている。上記第２環状部材３１１の内周面は、第１環状部材３１０の外周面に当接している。上記第２環状部材３１１は、周面としての略円筒状の外周面３２３を有している。   The shaft member 301 includes a shaft main body 361 having a substantially cylindrical outer peripheral surface 320, a first annular member 310, and a second annular member 311. The inner peripheral surface 321 of the first annular member 310 is fitted with the outer peripheral surface 320 of the shaft main body 361. The end face of the first annular member 310 is locked and fixed to the end face in the axial direction of the shaft main body 361 by a bolt 345. The inner peripheral surface of the second annular member 311 is in contact with the outer peripheral surface of the first annular member 310. The second annular member 311 has a substantially cylindrical outer peripheral surface 323 as a peripheral surface.

上記第１環状部材３１０は、筒状の第１部材３７１と、筒状の第２部材３７２とを有する。上記第１部材３７１と第２部材３７２とは、油圧通路３２６を介して径方向に対向している。   The first annular member 310 includes a cylindrical first member 371 and a cylindrical second member 372. The first member 371 and the second member 372 are opposed to each other in the radial direction via the hydraulic passage 326.

上記第１部材３７１は、軸方向に延在する筒状部３８０と、環状のリング部３８１とからなる。上記リング部３８１は、環状であって、筒状部３８０の軸方向の他端部の外周側から径方向の外方に突出している。上記筒状部３８０の外周面は、その中央部に環状の凹部を有する。   The first member 371 includes a cylindrical portion 380 extending in the axial direction and an annular ring portion 381. The ring portion 381 is annular and protrudes outward in the radial direction from the outer peripheral side of the other end portion of the cylindrical portion 380 in the axial direction. The outer peripheral surface of the cylindrical part 380 has an annular recess at the center.

上記第２部材３７２は、断面略Ｌ字状の形状を有している。上記第２部材３７２は、軸方向に延在する筒状部３９０と、リング部３９１とからなる。上記リング部３９１は、環状であって、筒状部３９０の軸方向の一端部の内周側から径方向の内方に突出している。上記筒状部３９０の内周面は、その中央部に環状の凹部を有している。   The second member 372 has a substantially L-shaped cross section. The second member 372 includes a cylindrical portion 390 extending in the axial direction and a ring portion 391. The ring portion 391 is annular and protrudes radially inward from the inner peripheral side of one axial end of the tubular portion 390. The inner peripheral surface of the cylindrical portion 390 has an annular recess at the center.

上記第１部材３７１の軸方向のリング部３８１側とは反対側の端面３８４は、第２部材３７２のリング部３９１の軸方向の端面３８５に当接し、第２部材３７２の軸方向のリング部３９１側とは反対側の端面３８６は、第１部材３７１のリング部３８１の軸方向の端面３８７に当接している。   An end surface 384 of the first member 371 opposite to the axial ring portion 381 side abuts on an axial end surface 385 of the ring portion 391 of the second member 372, and the axial ring portion of the second member 372. The end surface 386 opposite to the 391 side is in contact with the axial end surface 387 of the ring portion 381 of the first member 371.

上記第１部材３７１の筒状部３８０の外周面の軸方向の寸法は、第２部材３７２の筒状部３９０の内周面の軸方向の寸法と略一致し、第１部材３７１の環状凹部の軸方向の寸法は、第２部材３７２の環状凹部の軸方向の寸法と略一致している。上記第１部材３７１の環状凹部の全体と、第２部材３７２の環状凹部の全体とは、径方向に重なっている。上記第１部材３７１の環状凹部と、第２部材３７２の環状凹部とは、相俟って環状の油圧通路３２６を構成している。   The axial dimension of the outer peripheral surface of the cylindrical part 380 of the first member 371 is substantially the same as the axial dimension of the inner peripheral surface of the cylindrical part 390 of the second member 372, and the annular recess of the first member 371. The axial dimension is substantially the same as the axial dimension of the annular recess of the second member 372. The entire annular recess of the first member 371 and the entire annular recess of the second member 372 overlap in the radial direction. The annular recess of the first member 371 and the annular recess of the second member 372 together constitute an annular hydraulic passage 326.

上記油圧通路３２６は、一方の部材としての軸部材３０１の軸方向に延在している。上記第１部材３７１と、第２部材３７２とは、油圧通路３２６の一端側において、環状の溶接部によって溶接接合される一方、油圧通路３２６の他端側において、環状の溶接部によって溶接接合されている。   The hydraulic passage 326 extends in the axial direction of a shaft member 301 as one member. The first member 371 and the second member 372 are welded and joined by an annular welded portion at one end of the hydraulic passage 326, and are welded and joined by an annular welded portion at the other end of the hydraulic passage 326. ing.

詳細には、上記第１部材３７１の軸方向のリング部３８１側とは反対側の端面３８４と、第２部材３７２のリング部３９１の軸方向の端面３８５とは、溶接により結合されている。また、上記第２部材３７２の軸方向のリング部３９１側とは反対側の端面３８６と、第１部材３７１のリング部３８１の軸方向の端面３８７とは、溶接により結合されている。   Specifically, the end surface 384 opposite to the axial ring portion 381 side of the first member 371 and the axial end surface 385 of the ring portion 391 of the second member 372 are joined by welding. Further, the end surface 386 opposite to the ring portion 391 side in the axial direction of the second member 372 and the end surface 387 in the axial direction of the ring portion 381 of the first member 371 are joined by welding.

図５において、３９８は、上記第１部材３７１の軸方向のリング部３８１側とは反対側の端面３８４と、第２部材３７２のリング部３９１の軸方向の端面３８５との溶接部（以下、この溶接部を、第１溶接部という）を示し、３９９は、第２部材３７２の軸方向のリング部３９１側とは反対側の端面３８６と、第１部材３７１のリング部３８１の軸方向の端面３８７との溶接部（以下、この溶接部を、第２溶接部という）を示している。上記二つの溶接部３９８,３９９の両方において、第１部材３７１と第２部材３７２は、軸方向に重なっている。   In FIG. 5, reference numeral 398 denotes a welded portion (hereinafter referred to as an axial end surface 385 of the ring portion 391 of the second member 372 and the end surface 384 of the second member 372 opposite to the axial ring portion 381 side). This welded portion is referred to as a first welded portion) 399 indicates an end surface 386 of the second member 372 opposite to the axial ring portion 391 side, and an axial direction of the ring portion 381 of the first member 371. A welded portion with the end surface 387 (hereinafter, this welded portion is referred to as a second welded portion) is shown. In both of the two welds 398 and 399, the first member 371 and the second member 372 overlap in the axial direction.

上記第１部材３７１の端面３８４、第２部材３７２の端面３８５、第２部材３７２の端面３８６、および、第１部材３７１の端面３８７の夫々は、略第１部材の径方向に広がっている。   Each of the end surface 384 of the first member 371, the end surface 385 of the second member 372, the end surface 386 of the second member 372, and the end surface 387 of the first member 371 extends substantially in the radial direction of the first member.

上記第１溶接部３９８は、一方の部材としての軸部材３０１の径方向において、油圧通路３２６に対して軸部材３０１の摩擦係合面である外周面３２３側とは反対側に位置し、第２溶接部３９９は、径方向において、油圧通路３２６に対して軸部材３０２の上記外周面３２３側に位置している。   The first welded portion 398 is located on the opposite side of the outer peripheral surface 323 that is the friction engagement surface of the shaft member 301 with respect to the hydraulic passage 326 in the radial direction of the shaft member 301 as one member. The two welded portions 399 are located on the outer peripheral surface 323 side of the shaft member 302 with respect to the hydraulic passage 326 in the radial direction.

上記筒部材３０２は、上記筒部材３０２の外面から突出する係止部３０９を有すると共に、周面としての内周面３２４を有する。上記筒部材３０２の内周面３２４は、螺旋形状の油封止防止用の溝３３５を有している。この螺旋形状の溝３３５は、軸部材３０１と筒部材３０２との摩擦係合部分の軸方向の両側に開口している。また、上記螺旋形状の溝３３５のピッチは、軸部材３０１の軸径（外径）の１／１０以上１／５以下になっている。   The cylindrical member 302 has a locking portion 309 protruding from the outer surface of the cylindrical member 302 and an inner peripheral surface 324 as a peripheral surface. The inner peripheral surface 324 of the cylindrical member 302 has a spiral groove 335 for preventing oil sealing. The spiral groove 335 is open on both sides in the axial direction of the friction engagement portion between the shaft member 301 and the cylindrical member 302. The pitch of the spiral groove 335 is 1/10 or more and 1/5 or less of the shaft diameter (outer diameter) of the shaft member 301.

上記筒部材３０２の略円筒状の内周面３２４は、トルクの伝達時において、軸部材３０１（詳しくは第２環状部材３１１）の外周面３２３と摩擦結合するようになっている。上記軸部材３０１の外周面３２３と、筒部材３０２の内周面３２４との間には、焼付き防止用の潤滑油である、タービンオイル、トラクションオイル、または、トラクションオイルの混合物が塗布されている。   The substantially cylindrical inner peripheral surface 324 of the cylindrical member 302 is frictionally coupled to the outer peripheral surface 323 of the shaft member 301 (specifically, the second annular member 311) during torque transmission. Between the outer peripheral surface 323 of the shaft member 301 and the inner peripheral surface 324 of the cylinder member 302, turbine oil, traction oil, or a mixture of traction oil, which is a lubricant for preventing seizure, is applied. Yes.

上記第１環状部材３１０は、シャーバルブ取付穴３３０と、油圧通路３２６とを有し、油圧通路３２６は、第２環状部材３１１の外周面３２３の軸方向の所定長さに亘って略軸部材３０１の軸方向に延在している。   The first annular member 310 has a shear valve mounting hole 330 and a hydraulic passage 326, and the hydraulic passage 326 is a substantially axial member over a predetermined axial length of the outer peripheral surface 323 of the second annular member 311. 301 extends in the axial direction.

上記シャーバルブ３０６は、シャーバルブ取付穴３３０に嵌入されている。上記シャーバルブ３０６がシャーバルブ取付穴３３０に嵌入されている状態で、シャーバルブ３０６の一端部は、第１環状部材３１０の端面よりも軸方向の外方に突出している。上記係止部３０９は、第１環状部材３１０の端面に沿って径方向に延在している。上記シャーバルブ３０６の上記一端部は、係止部３０９によって、係止されている。   The shear valve 306 is fitted into the shear valve mounting hole 330. In a state where the shear valve 306 is fitted in the shear valve mounting hole 330, one end portion of the shear valve 306 protrudes outward in the axial direction from the end surface of the first annular member 310. The locking portion 309 extends in the radial direction along the end surface of the first annular member 310. The one end portion of the shear valve 306 is locked by a locking portion 309.

上記シャーバルブ３０６は、一端のみが開口したチューブ３２７を有している。このチューブ３２７は、シャーバルブ３０６がシャーバルブ取付穴３３０に嵌入されている状態で、略軸部材３０１の軸方向に延在している。上記シャーバルブ３０６がシャーバルブ取付穴３３０に嵌入されている状態で、チューブ３２７の閉鎖側の一端部は、第１環状部材３１０の端面よりも軸方向の外方に突出している。また、上記チューブ３２７の閉鎖側とは反対側の開口は、油圧通路３２６の一端に連通している。上記油圧通路３２６のシャーバルブ３０６側は、密封空間になっている。   The shear valve 306 has a tube 327 that is open only at one end. The tube 327 extends substantially in the axial direction of the shaft member 301 in a state where the shear valve 306 is fitted in the shear valve mounting hole 330. In a state where the shear valve 306 is fitted into the shear valve mounting hole 330, one end portion on the closed side of the tube 327 protrudes outward in the axial direction from the end surface of the first annular member 310. The opening of the tube 327 opposite to the closed side communicates with one end of the hydraulic passage 326. The shear passage 306 side of the hydraulic passage 326 is a sealed space.

第３実施形態のトルクリミッタでは、トルク伝達面である第２環状部材３１１の外周面（溝３３５の表面も含む）３２３の表層部と、筒部材３０２の内周面３２４の表層部とには、第１実施形態のトルクリミッタと同様の低温窒化処理が施されている。上記第２環状部材３１０の外周面（溝３３５の表面も含む）３２３の表層部と、筒部材３０２の内周面３２４の表層部とは、窒化物層になっている。第３実施形態のトルクリミッタの窒化物層の層厚や硬さは、第１実施形態のトルクリミッタの窒化物層と同一である。このトルクリミッタの窒化物層によって、第３実施形態においても、第１実施形態のトルクリミッタの窒化物層と同様の作用効果を獲得できるようになっている。   In the torque limiter of the third embodiment, the outer surface of the second annular member 311 (including the surface of the groove 335) 323, which is a torque transmission surface, and the surface layer of the inner surface 324 of the cylindrical member 302 are provided. The same low temperature nitriding treatment as that of the torque limiter of the first embodiment is performed. The surface layer portion of the outer peripheral surface (including the surface of the groove 335) 323 of the second annular member 310 and the surface layer portion of the inner peripheral surface 324 of the cylindrical member 302 are nitride layers. The thickness and hardness of the nitride layer of the torque limiter of the third embodiment are the same as the nitride layer of the torque limiter of the first embodiment. With the nitride layer of the torque limiter, the third embodiment can obtain the same operational effects as the nitride layer of the torque limiter of the first embodiment.

上記玉軸受１１７は、軸本体３６１の外面に外嵌固定された内輪と、筒部材３０２の内面に内嵌固定された外輪と、内輪の軌道面と外輪の軌道面と間に配置された玉とを有している。また、上記玉軸受１１８は、第１環状部材３１０の外面に外嵌固定された内輪と、筒部材３０２の内面に内嵌固定された外輪と、内輪の軌道面と外輪の軌道面と間に配置された玉とを有している。上記玉軸受１１７および１１８は、軸部材３０１が筒部材３０２に対して相対回転しているとき、軸部材３０１を筒部材３０２に対して回転自在に支持するようになっている。   The ball bearing 117 includes an inner ring that is fitted and fixed to the outer surface of the shaft body 361, an outer ring that is fitted and fixed to the inner surface of the cylindrical member 302, and a ball disposed between the raceway surface of the inner ring and the raceway surface of the outer ring. And have. The ball bearing 118 includes an inner ring that is fitted and fixed to the outer surface of the first annular member 310, an outer ring that is fitted and fixed to the inner surface of the cylindrical member 302, and a raceway surface of the inner ring and a raceway surface of the outer ring. And arranged balls. The ball bearings 117 and 118 are configured to rotatably support the shaft member 301 with respect to the cylindrical member 302 when the shaft member 301 rotates relative to the cylindrical member 302.

上記構成において、軸部材３０１および筒部材３０２に所定値以下の負荷（トルクの伝達を行う範囲の負荷）がかかっている場合には、図示しないカプラを介して油圧通路３２６に注入された後、密封された油圧拡張用の油で、第２環状部材３１１の外周面３２３を拡径して、外周面３２３を筒部材３０２の内周面３２４に押し付けて、軸部材３０１と筒部材３０２とを摩擦結合して、軸部材３０１と筒部材３０２との間でトルクを伝達するようになっている。   In the above configuration, when a load less than a predetermined value is applied to the shaft member 301 and the cylindrical member 302 (load in a range where torque is transmitted), after being injected into the hydraulic passage 326 via a coupler (not shown), With the sealed oil for hydraulic expansion, the outer peripheral surface 323 of the second annular member 311 is expanded in diameter, the outer peripheral surface 323 is pressed against the inner peripheral surface 324 of the cylindrical member 302, and the shaft member 301 and the cylindrical member 302 are connected. A torque is transmitted between the shaft member 301 and the cylindrical member 302 by frictional coupling.

一方、上記軸部材３０１または筒部材３０２に所定値以上の負荷（トルクの伝達を行う範囲よりも大きな負荷）がかかって、軸部材３０１の外周面３２３が、筒部材３０２の内周面３２４に対してスリップして、軸部材３０１と筒部材３０２の軸回りの位置が変化した場合には、係止部３０９がシャーバルブ３０６の一端部を切断して、チューブ３２７の閉鎖側の一端部を破壊して、油圧通路３２６内の油圧拡張用の油を、この破壊されたチューブ３２７の側から外部に排出するようになっている。   On the other hand, the shaft member 301 or the cylindrical member 302 is subjected to a load greater than a predetermined value (a load larger than the range in which torque is transmitted), and the outer peripheral surface 323 of the shaft member 301 is applied to the inner peripheral surface 324 of the cylindrical member 302. When the shaft member 301 and the cylindrical member 302 change their positions around the axis due to slipping, the locking portion 309 cuts one end portion of the shear valve 306, and the one end portion on the closed side of the tube 327 is The oil for hydraulic expansion in the hydraulic passage 326 is discharged and discharged from the broken tube 327 side to the outside.

このようにして、筒部材３０２の内周面３２４に対する第２環状部材３１１の外周面３２３の押圧力をなくして、軸部材３０１と筒部材３０２との摩擦結合を解いて、トルクの伝達を遮断するようになっている。このようにして、軸部材３０１または筒部材３０２に過負荷がかかった場合において、トルクの伝達を遮断して、トルクリミッタ装置に連結されている高価な機械を保護している。   In this way, the pressing force of the outer circumferential surface 323 of the second annular member 311 against the inner circumferential surface 324 of the cylindrical member 302 is eliminated, the frictional coupling between the shaft member 301 and the cylindrical member 302 is released, and torque transmission is interrupted. It is supposed to be. In this way, when the shaft member 301 or the cylindrical member 302 is overloaded, the transmission of torque is interrupted to protect the expensive machine connected to the torque limiter device.

上記第３実施形態のトルクリミッタにおいても、第１のトルクリミッタと同様、二つの溶接部３９８および３９９において、第１部材３７１と第２部材３７２とが軸方向に重なっているから、溶接部３９８,３９９の股裂き破壊を抑制できる。   Also in the torque limiter of the third embodiment, since the first member 371 and the second member 372 overlap in the axial direction in the two welded portions 398 and 399, similarly to the first torque limiter, the welded portion 398 is provided. , 399 crotch tear failure can be suppressed.

また、特に、第３実施形態のトルクリミッタによれば、二つの溶接部３９８および３９９において、第１部材３７１と第２部材３７２との当接面が、略径方向に広がっているから、溶接部３９８,３９９の破壊抑制効果を格段に大きくすることができて、寿命および信頼性を格段に向上させることができる。   In particular, according to the torque limiter of the third embodiment, in the two welded portions 398 and 399, the contact surfaces of the first member 371 and the second member 372 are spread in a substantially radial direction. The effect of suppressing the destruction of the parts 398 and 399 can be greatly increased, and the life and reliability can be significantly improved.

（第４実施形態）
図６は、本発明の第４実施形態のトルクリミッタの軸方向の断面図である。 (Fourth embodiment)
FIG. 6 is a sectional view in the axial direction of the torque limiter according to the fourth embodiment of the present invention.

第４実施形態のトルクリミッタは、筒部材４０１の第１環状部材４１０の構造のみが、第３実施形態のトルクリミッタと異なる。   The torque limiter of the fourth embodiment is different from the torque limiter of the third embodiment only in the structure of the first annular member 410 of the tubular member 401.

第４実施形態のトルクリミッタでは、第３実施形態のトルクリミッタの構成部と同一構成部には同一参照番号を付して説明を省略することにする。また、第４実施形態のトルクリミッタでは、第１および第３実施形態のトルクリミッタと共通の作用効果および変形例については説明を省略することにし、第１および第３実施形態のトルクリミッタと異なる構成、作用効果および変形例についてのみ説明を行うことにする。   In the torque limiter of the fourth embodiment, the same components as those of the torque limiter of the third embodiment are denoted by the same reference numerals, and the description thereof is omitted. Further, in the torque limiter of the fourth embodiment, the description of the operations and effects common to the torque limiter of the first and third embodiments is omitted, and is different from the torque limiter of the first and third embodiments. Only the configuration, operational effects, and modifications will be described.

第４実施形態では、第１環状部４１０は、筒状の第１部材４７１と、筒状の第２部材４７２とを有する。上記第１部材４７１と第２部材４７２とは、油圧通路４２６を介して径方向に対向している。   In the fourth embodiment, the first annular portion 410 includes a cylindrical first member 471 and a cylindrical second member 472. The first member 471 and the second member 472 are opposed to each other in the radial direction via the hydraulic passage 426.

上記第１部材４７１は、軸方向に延在する筒状部４８０と、リング部４８１とからなる。上記リング部４８１は、環状であって、筒状部４８０の軸方向の他端部の外周側から径方向の外方に突出している。上記筒状部４８０の外周面は、その中央部に環状の凹部を有している。   The first member 471 includes a cylindrical portion 480 extending in the axial direction and a ring portion 481. The ring portion 481 is annular, and protrudes outward in the radial direction from the outer peripheral side of the other end portion in the axial direction of the cylindrical portion 480. The outer peripheral surface of the cylindrical portion 480 has an annular recess at the center.

上記第２部材４７２は、断面略Ｌ字状の形状を有している。上記第２部材４７２は、軸方向に延在する筒状部４９０と、リング部４９１とからなる。上記リング部４９１は、環状であって、筒状部４９０の軸方向の一端部の内周側から径方向の内方に突出している。上記筒状部４９０の内周面は、その中央部に環状の凹部を有している。   The second member 472 has a substantially L-shaped cross section. The second member 472 includes a cylindrical portion 490 extending in the axial direction and a ring portion 491. The ring portion 491 is annular and protrudes inward in the radial direction from the inner peripheral side of one end portion of the cylindrical portion 490 in the axial direction. The inner peripheral surface of the cylindrical portion 490 has an annular recess at the center.

上記第１部材４７１の軸方向のリング部４８１側とは反対側の端面４８４は、第２部材４７２のリング部４９１の軸方向の端面４８５に当接し、第２部材４７２の軸方向のリング部４９１側とは反対側の端面４８６は、第１部材４７１のリング部４８１の軸方向の端面４８７に当接している。   The end surface 484 of the first member 471 opposite to the axial ring portion 481 side abuts on the axial end surface 485 of the ring portion 491 of the second member 472, and the axial ring portion of the second member 472. The end surface 486 opposite to the 491 side is in contact with the axial end surface 487 of the ring portion 481 of the first member 471.

上記第１部材４７１の筒状部４８０の内周面の軸方向の寸法は、第２部材４７２の筒状部４９０の外周面の軸方向の寸法と略一致し、第１部材４７１の環状凹部の軸方向の寸法は、第２部材４７２の環状凹部の軸方向の寸法と略一致している。上記第１部材４７１の環状凹部の全体と、第２部材４７２の環状凹部の全体とは、径方向に重なっている。上記第１部材４７１の環状凹部と、第２部材４７２の環状凹部とは、相俟って環状の油圧通路４２６を構成している。   The axial dimension of the inner circumferential surface of the cylindrical portion 480 of the first member 471 substantially matches the axial dimension of the outer circumferential surface of the cylindrical portion 490 of the second member 472, and the annular recess of the first member 471. The axial dimension is substantially the same as the axial dimension of the annular recess of the second member 472. The entire annular recess of the first member 471 and the entire annular recess of the second member 472 overlap in the radial direction. The annular recess of the first member 471 and the annular recess of the second member 472 together constitute an annular hydraulic passage 426.

上記油圧通路４２６は、一方の部材としての軸部材４０１の軸方向に延在している。上記第１部材４７１と、第２部材４７２とは、油圧通路４２６の一端側において、環状の溶接部によって溶接接合される一方、油圧通路４２６の他端側において、環状の溶接部によって溶接接合されている。   The hydraulic passage 426 extends in the axial direction of a shaft member 401 as one member. The first member 471 and the second member 472 are welded and joined at one end side of the hydraulic passage 426 by an annular welded portion, and are welded and joined at the other end side of the hydraulic passage 426 by an annular welded portion. ing.

詳細には、上記第１部材４７１の軸方向のリング部４８１側とは反対側の端面４８４と、第２部材４７２のリング部４９１の軸方向の端面４８５とは、径方向の内方の周面において、溶接により結合されている。また、上記第２部材４７２の軸方向のリング部４９１側とは反対側の端面４８６と、第１部材４７１のリング部４８１の軸方向の端面４８７とは、径方向の外方の周面において、溶接により結合されている。   Specifically, the end surface 484 opposite to the axial ring portion 481 side of the first member 471 and the axial end surface 485 of the ring portion 491 of the second member 472 are radially inward. The surfaces are joined by welding. Further, an end surface 486 opposite to the axial ring portion 491 side of the second member 472 and an axial end surface 487 of the ring portion 481 of the first member 471 are on the outer circumferential surface in the radial direction. Are joined by welding.

図６において、４９８は、上記第１部材４７１の軸方向のリング部４８１側とは反対側の端面４８４と、第２部材４７２のリング部４９１の軸方向の端面４８５との溶接部（以下、この溶接部を、第１溶接部という）を示し、４９９は、上記第２部材４７２の軸方向のリング部４９１側とは反対側の端面４８６と、第１部材４７１のリング部４８１の軸方向の端面４８７との溶接部（以下、この溶接部を、第２溶接部という）を示している。上記二つの溶接部４９８,４９９の両方において、第１部材４７１と第２部材４７２は、軸方向に重なっている。   In FIG. 6, reference numeral 498 denotes a welded portion (hereinafter referred to as an axial end surface 485 of the ring portion 491 of the second member 472 and an end surface 484 opposite to the axial ring portion 481 side of the first member 471. This welded portion is referred to as a first welded portion), and 499 is an end surface 486 opposite to the ring portion 491 side in the axial direction of the second member 472 and the axial direction of the ring portion 481 of the first member 471. 2 shows a welded portion with the end surface 487 (hereinafter, this welded portion is referred to as a second welded portion). In both of the two welded portions 498 and 499, the first member 471 and the second member 472 overlap in the axial direction.

上記第１溶接部４９８は、一方の部材としての軸部材４０１の径方向において、油圧通路４２６に対して軸部材２０１の摩擦係合面である外周面４２３側とは反対側に位置し、第２溶接部４９９は、径方向において、油圧通路４２６に対して軸部材４０１の上記外周面４２３側に位置している。   The first welded portion 498 is located on the opposite side of the outer peripheral surface 423 that is the friction engagement surface of the shaft member 201 with respect to the hydraulic passage 426 in the radial direction of the shaft member 401 as one member. The two welded portions 499 are located on the outer peripheral surface 423 side of the shaft member 401 with respect to the hydraulic passage 426 in the radial direction.

上記第１部材４７１の軸方向のリング部４８１側とは反対側の端面４８４は、油圧通路４２６から離れるにしたがって、すなわち、径方向の内方にいくにしたがって、軸方向において、第１部材４７１のリング部４８１側（油圧通路の他端側）に傾斜している。また、同様に、上記第２部材４７２のリング部４９１の軸方向の端面４８５は、油圧通路４２６から離れるにしたがって、すなわち、径方向の内方にいくにしたがって、軸方向において、第１部材４７１のリング部４８１側（油圧通路の他端側）に傾斜している。   An end surface 484 of the first member 471 opposite to the axial ring portion 481 side is separated from the hydraulic passage 426, that is, inward in the radial direction, the first member 471 in the axial direction. Is inclined toward the ring portion 481 side (the other end side of the hydraulic passage). Similarly, the axial end surface 485 of the ring portion 491 of the second member 472 moves away from the hydraulic passage 426, that is, inward in the radial direction, the first member 471 in the axial direction. Is inclined toward the ring portion 481 side (the other end side of the hydraulic passage).

また、図６に示すように、上記第２部材４７２の軸方向のリング部４９１側とは反対側の端面４８６は、油圧通路４２６から離れるにしたがって、すなわち、径方向の外方にいくにしたがって、軸方向において、第２部材４７２のリング部４９１側（油圧通路の一端側）に傾斜している。また、同様に、上記第１部材４７１のリング部４８１の軸方向の端面４８７は、油圧通路４２６から離れるにしたがって、すなわち、径方向の外方にいくにしたがって、軸方向において、第２部材４７２のリング部４９１側（油圧通路の一端側）に傾斜している。   Further, as shown in FIG. 6, the end surface 486 of the second member 472 opposite to the axial ring part 491 side is separated from the hydraulic passage 426, that is, as it goes outward in the radial direction. In the axial direction, the second member 472 is inclined toward the ring portion 491 side (one end side of the hydraulic passage). Similarly, the axial end surface 487 of the ring portion 481 of the first member 471 moves away from the hydraulic passage 426, that is, as it goes radially outward, the second member 472 in the axial direction. Is inclined to the ring portion 491 side (one end side of the hydraulic passage).

上記第４実施形態のトルクリミッタによれば、上記第１溶接部４９８において、第１部材４７１において第２部材４７２に対向する対向面が、径方向に油圧通路４２６から離れるにしたがって、軸方向において第１部材４７１のリング部４８１側（液圧通路４２６の他端側）に傾斜しているから、軸方向に延在する油圧通路４２６の径方向の拡張に基づく径方向の引っ張り応力が、第１溶接部４９８に殆ど作用することがない。したがって、上記第１溶接部４９８の股裂破壊を格段に緩和することができる。   According to the torque limiter of the fourth embodiment, in the first welded portion 498, in the axial direction, the opposing surface of the first member 471 that faces the second member 472 moves away from the hydraulic passage 426 in the radial direction. Since the first member 471 is inclined toward the ring portion 481 side (the other end side of the hydraulic pressure passage 426), the radial tensile stress based on the radial expansion of the hydraulic passage 426 extending in the axial direction is the first. 1 There is almost no effect on the welded portion 498. Therefore, the crotch fracture of the first welded portion 498 can be remarkably mitigated.

また、同様に、上記第２溶接部４９９において、第２部材４７２において第１部材４７１に対向する対向面が、径方向に油圧通路４２６から離れるにしたがって、軸方向において、第２部材４７２のリング部４９１側（液圧通路４２６の一端側）に傾斜しているから、第１溶接部４９９の股裂破壊を格段に緩和することができる。   Similarly, in the second welded portion 499, as the opposing surface of the second member 472 facing the first member 471 moves away from the hydraulic passage 426 in the radial direction, the ring of the second member 472 in the axial direction. Since it is inclined toward the portion 491 side (one end side of the hydraulic pressure passage 426), the crotch fracture of the first welded portion 499 can be remarkably mitigated.

尚、上記第１乃至第４実施形態では、液圧通路が、油圧通路であって、液圧通路を径方向に拡張するのに使用する液体が油であったが、この発明では、液圧通路を径方向に拡張するのに使用する液体は、水等、油以外の如何なる液体であっても良い。   In the first to fourth embodiments, the hydraulic passage is a hydraulic passage, and the liquid used to expand the hydraulic passage in the radial direction is oil. The liquid used to expand the passage in the radial direction may be any liquid other than oil, such as water.

また、上記実施形態では、軸連結装置を、トルクリミッタに使用したが、この発明の軸連結装置は、例えば、液圧通路の径方向の拡張を用いて、二つのフランジ部を摩擦係合する装置等に使用することができる。   Moreover, in the said embodiment, although the shaft coupling device was used for the torque limiter, the shaft coupling device of this invention frictionally engages two flange parts, for example, using expansion of the hydraulic pressure passage in the radial direction. It can be used for devices.

本発明の軸連結装置において採用される第１部材および第２部材の溶接について、概略を説明する模式図である。It is a mimetic diagram explaining an outline about welding of the 1st member and the 2nd member adopted in a shaft connecting device of the present invention. 従来の軸連結装置において採用されている第１部材および第２部材の溶接について、概略を説明する模式図である。It is a mimetic diagram explaining an outline about welding of the 1st member and the 2nd member adopted in the conventional shaft connecting device. 本発明の第１実施形態のトルクリミッタの軸方向の断面図である。It is sectional drawing of the axial direction of the torque limiter of 1st Embodiment of this invention. 本発明の第２実施形態のトルクリミッタの軸方向の断面図である。It is sectional drawing of the axial direction of the torque limiter of 2nd Embodiment of this invention. 本発明の第３実施形態のトルクリミッタの軸方向の断面図である。It is sectional drawing of the axial direction of the torque limiter of 3rd Embodiment of this invention. 本発明の第４実施形態のトルクリミッタの軸方向の断面図である。It is sectional drawing of the axial direction of the torque limiter of 4th Embodiment of this invention.

符号の説明Explanation of symbols

１,１０２,２０２,３０２ 筒部材
２,１７０,２７０,３７１,４７１ 第１部材
３,１７１,２７１,３７２,４７２ 第２部材
２７,１２６,２２６,３２６,４２６ 油圧通路
９８,９９,１９８,１９９,２９８,２９８,３９８,３９９,４９８,４９９ 溶接部 1,102,202,302 Tube member 2,170,270,371,471 First member 3,171,271,372,472 Second member 27,126,226,326,426 Hydraulic passage 98,99,198, 199,298,298,398,399,498,499 welds

Claims (4)

軸部材と、
この軸部材に外嵌した筒部材と
を備え、
上記筒部材および上記軸部材のうちの一方の部材は、その一方の部材と、上記筒部材および上記軸部材のうちの他方の部材との間でトルクの伝達を行うときに、上記一方の部材の周面を上記他方の部材の周面に押し付けるための液圧通路を有し、
上記液圧通路は、上記一方の部材の略軸方向に延在し、
上記一方の部材は、
環状の第１部材と、
上記第１部材に上記液圧通路を介して対向する環状の第２部材と
を有し、
上記第１部材と、上記第２部材とは、上記液圧通路の一端側において、環状の第１溶接部によって溶接接合される一方、上記液圧通路の他端側において、環状の第２溶接部によって溶接接合され、
上記第１溶接部において、上記第１部材と上記第２部材とは、上記一方の部材の軸方向に重なっていることを特徴とする軸連結装置。 A shaft member;
A cylindrical member fitted around the shaft member;
One member of the cylindrical member and the shaft member is configured to transmit the torque between the one member and the other member of the cylindrical member and the shaft member. A hydraulic passage for pressing the peripheral surface of the second member against the peripheral surface of the other member,
The hydraulic passage extends in a substantially axial direction of the one member,
The one member is
An annular first member;
An annular second member facing the first member via the hydraulic passage,
The first member and the second member are welded and joined by an annular first welded portion at one end side of the hydraulic passage, while an annular second weld is made at the other end side of the hydraulic passage. Welded and joined by parts
In the first welding part, the first member and the second member overlap each other in the axial direction of the one member. 請求項１に記載の軸連結装置において、
上記第１溶接部において、上記第１部材において上記第２部材に対向する面は、略上記一方の部材の径方向に広がっているか、または、上記一方の部材の径方向に上記液圧通路から離れるにしたがって、上記軸方向に上記液圧通路の他端側に傾斜していることを特徴とする軸連結装置。 The shaft coupling device according to claim 1,
In the first welded portion, the surface of the first member that faces the second member extends substantially in the radial direction of the one member, or from the hydraulic passage in the radial direction of the one member. The shaft coupling device is inclined in the axial direction toward the other end side of the hydraulic passage as it leaves. 請求項２に記載の軸連結装置において、
上記第１溶接部は、上記一方の部材の径方向において、上記液圧通路に対して上記一方の部材の上記周面側とは反対側に位置し、上記第２溶接部は、上記径方向において、上記液圧通路に対して上記液圧通路の上記一方の部材の上記周面側に位置していることを特徴とする軸連結装置。 The shaft coupling device according to claim 2,
The first welded portion is located on a side opposite to the peripheral surface side of the one member with respect to the hydraulic passage in the radial direction of the one member, and the second welded portion is in the radial direction. The shaft coupling device according to claim 1, wherein the shaft coupling device is located on the peripheral surface side of the one member of the hydraulic pressure passage with respect to the hydraulic pressure passage. 請求項１乃至３のいずれか１つに記載の軸連結装置を備え、
上記液圧通路に封入した液体により上記液圧通路を上記一方の部材の径方向に拡張することにより、上記軸部材と上記筒部材とを摩擦係合する一方、上記液圧通路に封入された液体を除去することにより、上記軸部材が上記筒部材に対して相対回転することを特徴とするトルクリミッタ。 A shaft coupling device according to any one of claims 1 to 3, comprising:
By expanding the hydraulic pressure passage in the radial direction of the one member with the liquid enclosed in the hydraulic pressure passage, the shaft member and the cylindrical member are frictionally engaged, while being enclosed in the hydraulic pressure passage. A torque limiter wherein the shaft member rotates relative to the cylindrical member by removing the liquid.
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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011163501A (en) * 2010-02-12 2011-08-25 Jtekt Corp Shaft coupling device and torque limiter
JP2011185401A (en) * 2010-03-10 2011-09-22 Jtekt Corp Shaft connector and torque limiter
JP2013217420A (en) * 2012-04-06 2013-10-24 Jtekt Corp Shaft coupling device and torque limiter
JP2016142406A (en) * 2015-02-05 2016-08-08 株式会社ジェイテクト Torque limiter

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5582809A (en) * 1978-12-11 1980-06-21 Olsson Hans Otto Hydraulic pressure coupling assembly
JPH07269528A (en) * 1994-03-31 1995-10-17 Sumitomo Metal Ind Ltd Fluid pressure joint

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5582809A (en) * 1978-12-11 1980-06-21 Olsson Hans Otto Hydraulic pressure coupling assembly
JPH07269528A (en) * 1994-03-31 1995-10-17 Sumitomo Metal Ind Ltd Fluid pressure joint

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011163501A (en) * 2010-02-12 2011-08-25 Jtekt Corp Shaft coupling device and torque limiter
JP2011185401A (en) * 2010-03-10 2011-09-22 Jtekt Corp Shaft connector and torque limiter
CN102207136A (en) * 2010-03-10 2011-10-05 株式会社捷太格特 Shaft connector and torque limiter
JP2013217420A (en) * 2012-04-06 2013-10-24 Jtekt Corp Shaft coupling device and torque limiter
JP2016142406A (en) * 2015-02-05 2016-08-08 株式会社ジェイテクト Torque limiter

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