JP6143166B2

JP6143166B2 - Dog clutch gear

Info

Publication number: JP6143166B2
Application number: JP2013071743A
Authority: JP
Inventors: 松永　直也; 直也松永; 嗣人稲山
Original assignee: Honda Motor Co Ltd
Current assignee: Honda Motor Co Ltd
Priority date: 2013-03-29
Filing date: 2013-03-29
Publication date: 2017-06-07
Anticipated expiration: 2033-03-29
Also published as: JP2014196753A

Description

本発明は、回転軸に支持される円筒状のボス部と、該ボス部を同軸に囲むとともに外周に歯部が形成される環状のリム部と、前記ボス部および前記リム部間を連結する環状壁部と、前記ボス部および前記リム部間を結んで放射状に延びるとともに前記リム部側に向かうにつれて幅広になるように形成されて前記環状壁部から前記回転軸の軸方向に***する複数の係止リブとを一体に有し、前記回転軸の周方向両側に臨む前記係止リブの両側面の一方に雄型のドグと当接する平坦な当接面が形成され、前記係止リブの前記両側面および前記ボス部の連設部に形成される内側隅曲面部よりも曲率半径の大きな外側隅曲面部が前記係止リブの前記両側面および前記リム部の連設部にそれぞれ形成されるドグクラッチ用ギヤに関する。 The present invention connects a cylindrical boss part supported by a rotating shaft, an annular rim part coaxially surrounding the boss part and having teeth formed on the outer periphery, and the boss part and the rim part. A plurality of annular wall portions, extending radially from the boss portion and the rim portion, and formed so as to increase in width toward the rim portion side, and project from the annular wall portion in the axial direction of the rotating shaft. A flat contact surface that contacts a male dog on one of both side surfaces of the locking rib facing both sides in the circumferential direction of the rotating shaft, and the locking rib. Outer corner curved surface portions having a larger radius of curvature than the inner corner curved surface portions formed on the both side surfaces and the continuous portion of the boss portion are formed on the both side surfaces of the locking rib and the continuous portion of the rim portion, respectively. The present invention relates to a dog clutch gear.

このようなドグクラッチは、特許文献１で既に知られており、このものでは、係止リブの一側面に雄型のドグが当接する際の応力集中を避ける目的で、係止リブがリム部側に向かうにつれて幅広となるように形成されるとともに、係止リブの両側面およびボス部の連設部に内側隅曲面部が形成され、係止リブの両側面およびリム部の連設部に外側隅曲面部が形成されている。 Such a dog clutch is already known from Patent Document 1, and in this case, the locking rib is on the rim portion side in order to avoid stress concentration when the male dog abuts against one side surface of the locking rib. The inner corner curved surface portion is formed on both side surfaces of the locking rib and the connecting portion of the boss portion, and the outside is formed on both side surfaces of the locking rib and the continuous portion of the rim portion. A corner curved surface portion is formed.

特開２００９−２０９９５０号公報JP 2009-209950 A

ところで、ドグは係止リブの側面のボス部寄りの部分に当接するので、内側隅曲面部の曲率半径は小さくせざるを得ず、それに対して外側隅曲面部は係止リブの側面への前記ドグの当接部から離れるので曲率半径を比較的大きくすることができる。このためボス部側の内側隅曲面部には外側隅曲面部に比べて応力集中が発生し易くなっとり、剛性の高い材質を用いたり、剛性を高める処理を施したりしているが、応力を分散し得るような形状の開発が望まれている。 By the way, the dog abuts against the portion of the side surface of the locking rib close to the boss portion, so the radius of curvature of the inner corner curved surface portion must be reduced, whereas the outer corner curved surface portion is directed to the side surface of the locking rib. Since it is away from the contact portion of the dog, the radius of curvature can be made relatively large. For this reason, stress concentration is more likely to occur in the inner corner curved surface portion on the boss side than in the outer corner curved surface portion, and a material having high rigidity is used or a process for increasing rigidity is applied. It is desired to develop a shape that can be dispersed.

本発明は、かかる事情に鑑みてなされたものであり、係止リブ全体に応力を分散し得る形状を有するドグクラッチ用ギヤを提供することを目的とする。 The present invention has been made in view of such circumstances, and an object of the present invention is to provide a dog clutch gear having a shape capable of dispersing stress over the entire locking rib.

上記目的を達成するために、本発明は、回転軸に支持される円筒状のボス部と、該ボス部を同軸に囲むとともに外周に歯部が形成される環状のリム部と、前記ボス部および前記リム部間を連結する環状壁部と、前記ボス部および前記リム部間を結んで放射状に延びるとともに前記リム部側に向かうにつれて幅広になるように形成されて前記環状壁部から前記回転軸の軸方向に***する複数の係止リブとを一体に有し、前記回転軸の周方向両側に臨む前記係止リブの両側面の一方に雄型のドグと当接する平坦な当接面が形成され、前記係止リブの前記両側面および前記ボス部の連設部に形成される内側隅曲面部よりも曲率半径の大きな外側隅曲面部が前記係止リブの前記両側面および前記リム部の連設部にそれぞれ形成されるドグクラッチ用ギヤにおいて、前記外側隅曲面部に、該外側隅曲面部から前記周方向に***する***部が、該***部の両側が前記ボス部側の第１曲面ならびに前記リム部側の第２曲面で前記外側隅曲面部に連なるようにして、一体に形成されることを第１の特徴とする。 In order to achieve the above object, the present invention provides a cylindrical boss portion supported by a rotating shaft, an annular rim portion coaxially surrounding the boss portion and having teeth formed on the outer periphery, and the boss portion. And an annular wall portion that connects the rim portions, and extends radially from the boss portion and the rim portion, and is formed so as to become wider toward the rim portion side, and is rotated from the annular wall portion. A flat contact surface that has a plurality of locking ribs that protrude in the axial direction of the shaft, and that contacts a male dog on one of both side surfaces of the locking rib that faces both sides of the rotating shaft in the circumferential direction The outer corner curved surface portion having a larger radius of curvature than the inner corner curved surface portion formed on the both side surfaces of the locking rib and the connecting portion of the boss portion is formed on the both side surfaces and the rim of the locking rib. Dog clutch gears respectively formed on the continuous connecting portion In the outer corner curved surface portion, the protruding portion that protrudes in the circumferential direction from the outer corner curved surface portion is the first curved surface on the boss portion side and the second curved surface on the rim portion side on both sides of the raised portion. A first feature is that the outer corner curved surface portion is integrally formed.

また本発明は、第１の特徴の構成に加えて、第１曲面の曲率半径が第２曲面の曲率半径よりも小さく設定されることを第２の特徴とする。 In addition to the configuration of the first feature, the present invention has a second feature that the radius of curvature of the first curved surface is set smaller than the radius of curvature of the second curved surface.

本発明は、第１または第２の特徴の構成に加えて、記ボス部の外周面および前記環状壁部の連設部に第３曲面が形成され、前記回転軸の回転方向から見たときに第３曲面と同一の曲率半径となる第４曲面が、前記***部および前記環状壁部の連設部に形成されることを第３の特徴とする。 In the present invention, in addition to the configuration of the first or second feature, a third curved surface is formed on the outer peripheral surface of the boss portion and the connecting portion of the annular wall portion, and when viewed from the rotation direction of the rotary shaft A third feature is that a fourth curved surface having the same radius of curvature as the third curved surface is formed at the connecting portion of the raised portion and the annular wall portion.

本発明は、第１〜第３の特徴の構成のいずれかに加えて、前記係止リブの側面および前記環状壁部の連設部に第５曲面が形成され、前記係止リブの長手方向から見たときに第５曲面よりも大きな曲率半径となる第６曲面が前記***部および前記環状壁部の連設部に形成されることを第４の特徴とする。 In the present invention, in addition to any one of the first to third features, a fifth curved surface is formed on the side surface of the locking rib and the connecting portion of the annular wall portion, and the longitudinal direction of the locking rib A fourth feature is that a sixth curved surface having a radius of curvature larger than that of the fifth curved surface when viewed from the above is formed in the joint portion of the raised portion and the annular wall portion.

本発明は、第１〜第４の特徴の構成のいずれかに加えて、前記ボス部の外周面および前記環状壁部の連設部に第３曲面が形成され、前記回転軸の回転方向から見たときに第３曲面よりも大きな曲率半径となる第７曲面が、前記リム部の内周面および前記環状壁部の連設部に形成されることを第５の特徴とする。 According to the present invention, in addition to any one of the first to fourth features, a third curved surface is formed on the outer peripheral surface of the boss portion and the connecting portion of the annular wall portion, and the rotational axis of the rotating shaft is A fifth feature is that a seventh curved surface having a radius of curvature larger than the third curved surface when viewed is formed on the inner peripheral surface of the rim portion and the continuous portion of the annular wall portion.

本発明は、第１〜第５の特徴の構成のいずれかに加えて、前記係止リブの前記環状壁部とは反対側の先端面および前記リム部の内周面の連設部に、前記リム部の内周面に滑らかに連なる第８曲面と、その第８曲面の前記ボス部側の一部を切除して成る段差部とが形成されることを第６の特徴とする。 In addition to any of the configurations of the first to fifth features of the present invention, the front end surface of the locking rib opposite to the annular wall portion and the continuous portion of the inner peripheral surface of the rim portion, A sixth feature is that an eighth curved surface smoothly connected to the inner peripheral surface of the rim portion and a stepped portion formed by cutting a part of the eighth curved surface on the boss portion side are formed.

本発明は、第６の特徴の構成に加えて、前記回転軸の中心軸線を中心とする第１の仮想円に沿って延びる前記段差部が、前記係止リブの前記リム部側端部に形成される２つの前記***部間に跨がって形成されることを第７の特徴とする。 According to the present invention, in addition to the configuration of the sixth feature, the stepped portion extending along the first virtual circle centered on the central axis of the rotation shaft is formed on the rim portion side end portion of the locking rib. A seventh feature is that the two ridges are formed so as to straddle.

さらに本発明は、第１〜第７の特徴の構成のいずれかに加えて、前記係止リブの前記リム部側端部に形成される２つの前記***部の頂部を通るとともに前記回転軸の中心軸線を中心とする第２の仮想円に沿う前記２つの***部の頂部間の長さが、第２の仮想円上での前記係止リブの幅のほぼ２倍に設定されることを第８の特徴とする。 Furthermore, in addition to any of the configurations of the first to seventh features, the present invention passes through the tops of the two raised portions formed at the rim portion side end portions of the locking ribs, and the rotation shaft. The length between the tops of the two raised portions along the second virtual circle centered on the central axis is set to be approximately twice the width of the locking rib on the second virtual circle. The eighth feature.

本発明の第１の特徴によれば、***部が曲面を介してリム部側の外側隅曲面部に連なるようにして外側隅曲面部に一体に形成されることにより、ボス部側の内側隅曲面部に集中し易かった応力をリム部側に分散させることが可能となり、係止リブ全体への応力の均衡化を図ることができ、形状を変えるだけで剛性を高めることができる。 According to the first feature of the present invention, the ridge portion is formed integrally with the outer corner curved surface portion so as to be connected to the outer corner curved surface portion on the rim portion side through the curved surface, whereby the inner corner on the boss portion side is formed. It is possible to disperse the stress, which was easily concentrated on the curved surface portion, to the rim portion side, to balance the stress on the entire locking rib, and to increase the rigidity only by changing the shape.

また本発明の第２の特徴によれば、***部および外側隅曲面部間の曲面のうちボス部側の第１曲面の曲率半径がリム部側の第２曲面の曲率半径よりも小さいので、係止リブに作用する応力をより***部側に分散させることができる。 Further, according to the second feature of the present invention, the curvature radius of the first curved surface on the boss portion side of the curved surface between the raised portion and the outer corner curved surface portion is smaller than the curvature radius of the second curved surface on the rim portion side. The stress acting on the locking rib can be further distributed to the raised portion side.

本発明の第３の特徴によれば、ボス部の外周面および環状壁部の連設部に形成される第３曲面と回転軸の回転方向から見たときに同一の曲率半径となる第４曲面が***部および環状壁部の連設部に形成されるので、係止リブのボス部側および***部側で環状壁部の連設部の剛性を同等とすることができ、係止リブに作用する応力を***部側に分散させ易くすることができる。 According to the third feature of the present invention, the third curved surface formed on the outer peripheral surface of the boss portion and the continuous portion of the annular wall portion and the fourth curvature having the same radius of curvature when viewed from the rotational direction of the rotary shaft. Since the curved surface is formed in the connecting portion of the raised portion and the annular wall portion, the rigidity of the connecting portion of the annular wall portion can be made equal on the boss portion side and the raised portion side of the locking rib. It is possible to easily disperse the stress acting on the ridge portion side.

本発明の第４の特徴によれば、係止リブの長手方向から見たときに係止リブの側面および環状壁部の連設部に形成される第５曲面よりも大きな曲率半径の第６曲面が***部および環状壁部の連設部に形成されるので、雄型のドグが当接しない***部および環状壁部間の第６曲面の曲率半径を比較的大きくし、特に負荷がかかる外周の歯部に近い側で環状壁部の厚みを増して剛性を高めることができる。 According to the 4th characteristic of this invention, when it sees from the longitudinal direction of a latching rib, the 6th of a curvature radius larger than the 5th curved surface formed in the side surface of a latching rib and the connection part of an annular wall part is provided. Since the curved surface is formed in the continuous portion of the raised portion and the annular wall portion, the radius of curvature of the sixth curved surface between the raised portion and the annular wall portion where the male dog does not contact is relatively large, and particularly a load is applied. Rigidity can be increased by increasing the thickness of the annular wall portion on the side closer to the outer peripheral tooth portion.

本発明の第５の特徴によれば、回転軸の回転方向から見たときにボス部の外周面および環状壁部間の第３曲面よりも大きな曲率半径の第７曲面がリム部の内周面および環状壁部の連設部に形成されるので、特に負荷がかかる外周の歯部に近い側で環状壁部の厚みを増して剛性を高めることができる。 According to the fifth feature of the present invention, the seventh curved surface having a larger radius of curvature than the third curved surface between the outer peripheral surface of the boss portion and the annular wall portion when viewed from the rotational direction of the rotating shaft is the inner periphery of the rim portion. Since it is formed in the connection part of a surface and an annular wall part, the thickness of an annular wall part can be increased on the side near the tooth part of the outer periphery where especially a load is applied, and rigidity can be improved.

本発明の第６の特徴によれば、係止リブの先端面およびリム部の内周面の連設部に、第８曲面と、その第８曲面のボス部側の一部を切除して成る段差部とが形成されるので、係合対象のドグと相対回転しながら係合する際に、第８曲面へのドグの端部のエッジ当たりが生じることを回避し、エッジ当たりによる摩耗が発生する可能性を排除することができる。 According to the sixth feature of the present invention, the eighth curved surface and a part of the eighth curved surface on the boss portion side are cut off at the connecting portion of the distal end surface of the locking rib and the inner peripheral surface of the rim portion. Therefore, when engaging with the dog to be engaged while rotating relatively, the edge of the edge of the dog against the eighth curved surface is avoided and wear due to the edge is prevented. The possibility of occurring can be eliminated.

本発明の第７の特徴によれば、段差部が２つの***部間に跨がって形成されるので、***部を形成することによって係止リブの幅が大きくなるので、ドグとのエッジ当たりが生じる可能性がある範囲が長くなるが、そのエッジ当たりが生じないようにして摩耗の発生を抑制することができる。 According to the seventh feature of the present invention, since the step portion is formed across the two raised portions, the width of the locking rib is increased by forming the raised portion, so that the edge with the dog Although the range in which the hit may occur becomes longer, the occurrence of wear can be suppressed by preventing the hit of the edge.

さらに本発明の第８の特徴によれば、２つの***部の頂部間の長さが係止リブのほぼ２倍に設定されるので、***部が形成されることで係止リブの幅が大きくなり過ぎて重量増加が生じることを抑制しながら、***部を形成することによる応力分散を適度な幅で効果的に得ることができる。 Furthermore, according to the eighth feature of the present invention, since the length between the tops of the two raised portions is set to almost twice the length of the locking rib, the width of the locking rib is reduced by forming the raised portion. While suppressing the increase in weight due to being too large, the stress distribution due to the formation of the raised portion can be effectively obtained with an appropriate width.

内燃機関の要部断面図である。It is principal part sectional drawing of an internal combustion engine. 図１の２矢示部拡大図である。FIG. 2 is an enlarged view of a portion indicated by an arrow 2 in FIG. 1. 図２の３−３線矢視方向から見た第２速用被動ギヤの正面図である。It is a front view of the 2nd speed driven gear seen from the 3-3 arrow direction of FIG. 図３の４−４線拡大断面図である。FIG. 4 is an enlarged sectional view taken along line 4-4 of FIG. 図３の５矢示部拡大図である。FIG. 5 is an enlarged view of a part indicated by an arrow 5 in FIG. 3. 図３の６−６線拡大断面図である。FIG. 6 is an enlarged sectional view taken along line 6-6 of FIG. 図４の要部拡大図である。It is a principal part enlarged view of FIG. 係止リブの応力分布を示す図である。It is a figure which shows the stress distribution of a latching rib.

本発明の実施の形態について図１〜図８を参照しながら説明すると、先ず図１において、たとえば自動二輪車に搭載される２気筒の内燃機関のクランクケース１１には、クランクシャフト１３が回転自在に支承され、シリンダブロック１２が有する２つのシリンダボア１４，１４に摺動自在に嵌合されるピストン１５…が前記クランクシャフト１３に連接される。 An embodiment of the present invention will be described with reference to FIGS. 1 to 8. First, in FIG. 1, for example, a crankshaft 13 is rotatable in a crankcase 11 of a two-cylinder internal combustion engine mounted on a motorcycle. Pistons 15 that are supported and are slidably fitted to the two cylinder bores 14, 14 of the cylinder block 12 are connected to the crankshaft 13.

前記クランクケース１１の左側面には、前記クランクケース１１との間に発電機室１６を形成する発電機カバー２０が結合され、発電機室１６内に収容される発電機１７のロータ１８が、発電機室１６内に突入した前記クランクシャフト１３の端部に固定され、発電機１７のステータ１９は、前記ロータ１８で囲繞されるようにして発電機カバー２０に固定される。 A generator cover 20 forming a generator chamber 16 is coupled to the left side surface of the crankcase 11 with the crankcase 11, and a rotor 18 of a generator 17 accommodated in the generator chamber 16 is provided. The stator 19 of the generator 17 is fixed to the generator cover 20 so as to be surrounded by the rotor 18. The stator 19 is fixed to the end of the crankshaft 13 that has entered the generator chamber 16.

またクランクケース１１に固定されるスタータモータ（図示せず）からの動力を伝達する減速ギヤ列２１の一部を構成する被動ギヤ２２が、一方向クラッチ２３を介して前記ロータ１８に連結される。 A driven gear 22 constituting a part of a reduction gear train 21 that transmits power from a starter motor (not shown) fixed to the crankcase 11 is connected to the rotor 18 via a one-way clutch 23. .

前記クランクケース１１の右側面には、該クランクケース１１との間にクラッチ室２４を形成するクラッチカバー２５が結合され、前記クラッチ室２４内で前記クランクシャフト１３の端部にはパルサ２６が固着されており、このパルサ２６の外周に対向するようにして前記クラッチ室２４内に配置される回転速センサ２７がクラッチカバー２５に固定される。 A clutch cover 25 that forms a clutch chamber 24 is connected to the right side surface of the crankcase 11 and the crankcase 11 is fixed to the end of the crankshaft 13 in the clutch chamber 24. A rotation speed sensor 27 disposed in the clutch chamber 24 is fixed to the clutch cover 25 so as to face the outer periphery of the pulsar 26.

前記クランクケース１１内には、前記クランクシャフト１３と平行な軸線を有して該クランクケース１１で回転自在に支承される第１メインシャフト２８ならびに第２メインシャフト２９と、カウンタシャフト３０との間に選択的に確立可能な複数変速段のギヤ列たとえば第１速〜第６速ギヤ列Ｇ１〜Ｇ６が設けられて成る変速機Ｍが収容される。 In the crankcase 11, there is a first main shaft 28 and a second main shaft 29 that have an axis parallel to the crankshaft 13 and are rotatably supported by the crankcase 11, and a countershaft 30. A transmission M having a gear train of a plurality of shift stages that can be selectively established, for example, first to sixth gear trains G1 to G6 is housed.

第１および第２メインシャフト２８，２９は、第１のメインシャフト２８を第２のメインシャフト２９内に相対回転可能に嵌入するようにして同軸に配置されており、クランクケース１１の右側壁を回転自在に貫通する第１メインシャフト２８の一端部はクランクケース１１の左側壁に回転自在に支承され、この第１メインシャフト２８の他端部は前記クラッチカバー２５で回転自在に支承される。また第２メインシャフト２９は、第１メインシャフト２８を同軸に囲繞して前記クランクケース１１の右側壁を回転自在に支承されつつ貫通するものであり、第１および第２メインシャフト２８，２９間には複数のニードルベアリング３１，３１…が介装される。 The first and second main shafts 28 and 29 are arranged coaxially so that the first main shaft 28 is fitted into the second main shaft 29 so as to be relatively rotatable, and the right side wall of the crankcase 11 is arranged. One end portion of the first main shaft 28 penetrating rotatably is rotatably supported on the left side wall of the crankcase 11, and the other end portion of the first main shaft 28 is rotatably supported by the clutch cover 25. The second main shaft 29 coaxially surrounds the first main shaft 28 and passes through the right side wall of the crankcase 11 while being rotatably supported, and between the first and second main shafts 28 and 29. Are provided with a plurality of needle bearings 31, 31.

前記クランクシャフト１３からの回転動力は、一次減速装置３２、ダンパばね３５および第１多板クラッチ３３を介して第１メインシャフト２８に伝達可能であり、また一次減速装置３２、ダンパばね３５および第２多板クラッチ３４を介して第２メインシャフト２９に伝達可能である。 The rotational power from the crankshaft 13 can be transmitted to the first main shaft 28 via the primary reduction gear 32, the damper spring 35 and the first multi-plate clutch 33, and the primary reduction gear 32, the damper spring 35 and the first It can be transmitted to the second main shaft 29 via the two-multiplate clutch 34.

前記カウンタシャフト３０の一端部は、クランクケース１１の左側壁を回転自在にかつ気密に貫通して該クランクケース１１の左側壁後部から突出され、またカウンタシャフト３０の他端部はクランクケース１１の右側壁に回転自在に支承される。 One end portion of the countershaft 30 penetrates the left side wall of the crankcase 11 in a rotatable and airtight manner and protrudes from the rear portion of the left side wall of the crankcase 11, and the other end portion of the countershaft 30 is connected to the crankcase 11. It is rotatably supported on the right side wall.

前記クランクケース１１の左側壁から突出した前記カウンタシャフト３０の一端部には駆動スプロケット３６が固定されており、この駆動スプロケット３６に巻き掛けられる無端状のチェーン（図示せず）により、変速機Ｍから出力される回転動力が図示しない後輪に伝達される。 A drive sprocket 36 is fixed to one end portion of the countershaft 30 protruding from the left side wall of the crankcase 11, and a transmission M is provided by an endless chain (not shown) wound around the drive sprocket 36. Is transmitted to a rear wheel (not shown).

第１メインシャフト２８およびカウンタシャフト３０間には、複数変速段たとえば第１速ギヤ列Ｇ１、第３ギヤ列Ｇ３および第５速ギヤ列Ｇ５が設けられ、第２メインシャフト２９およびカウンタシャフト３０間には、第１メインシャフト２８およびカウンタシャフト３０間とは異なる複数変速段たとえば第２速ギヤ列Ｇ２、第４速ギヤ列Ｇ４および第６速ギヤ列Ｇ６が設けられる。 Between the first main shaft 28 and the counter shaft 30, a plurality of speed stages, for example, a first speed gear train G1, a third gear train G3, and a fifth speed gear train G5 are provided, and between the second main shaft 29 and the counter shaft 30. Are provided with a plurality of speed stages different from those between the first main shaft 28 and the counter shaft 30, for example, a second speed gear train G2, a fourth speed gear train G4, and a sixth speed gear train G6.

図２において、第１速ギヤ列Ｇ１は、第１メインシャフト２８に一体に形成される第１速用駆動ギヤ４１と、前記カウンタシャフト３０に軸方向相対移動を不能として相対回転可能に支承される第１速用被動ギヤ４２とから成り、第３速ギヤ列Ｇ３は、第１メインシャフト２８に軸方向相対移動を可能として相対回転不能に支承される第３速用駆動ギヤ４３と、前記カウンタシャフト３０に軸方向相対移動を不能として相対回転可能に支承される第３速用被動ギヤ４４とから成り、第５速ギヤ列Ｇ５は、第１メインシャフト２８に軸方向相対移動を不能として相対回転可能に支承される第５速用駆動ギヤ４５と、前記カウンタシャフト３０に軸方向相対移動を可能として相対回転不能に支承される第５速用被動ギヤ４６とから成る。 In FIG. 2, the first speed gear train G1 is supported by the first speed drive gear 41 formed integrally with the first main shaft 28 and the countershaft 30 so as to be relatively rotatable while disabling relative axial movement. A third-speed drive gear 43, which is supported by the first main shaft 28 so as to be capable of relative movement in the axial direction and not to be rotatable relative to the first main shaft 28; The counter gear 30 includes a third-speed driven gear 44 that is supported so that relative movement in the axial direction relative to the countershaft 30 is disabled. The fifth-speed gear train G5 disables relative movement in the axial direction relative to the first main shaft 28. The fifth-speed drive gear 45 is supported so as to be capable of relative rotation, and the fifth-speed driven gear 46 is supported so as to be capable of relative movement in the axial direction on the countershaft 30 so as not to be capable of relative rotation.

第２速ギヤ列Ｇ２は、第２メインシャフト２８に一体に形成される第２速用駆動ギヤ４７と、前記カウンタシャフト３０に軸方向相対移動を不能として相対回転可能に支承される第２速用被動ギヤ４８とから成り、第４速ギヤ列Ｇ４は、第２メインシャフト２８に軸方向相対移動を可能として相対回転不能に支承される第４速用駆動ギヤ４９と、前記カウンタシャフト３０に軸方向相対移動を不能として相対回転可能に支承される第４速用被動ギヤ５０とから成り、第６速ギヤ列Ｇ６は、第２メインシャフト２８に軸方向相対移動を不能として相対回転可能に支承される第６速用駆動ギヤ５１と、前記カウンタシャフト３０に軸方向相対移動を可能として相対回転不能に支承される第６速用被動ギヤ５２とから成る。 The second speed gear train G2 is a second speed drive gear 47 formed integrally with the second main shaft 28, and a second speed supported on the countershaft 30 so as to be relatively rotatable while disabling relative movement in the axial direction. The fourth speed gear train G4 is composed of a driven gear 48, and a fourth speed drive gear 49 supported on the second main shaft 28 so as to be capable of relative movement in the axial direction and not to rotate relative to the second main shaft 28. The fourth-speed driven gear 50 is supported so that relative movement in the axial direction is disabled and relative rotation is possible, and the sixth gear train G6 is relatively rotatable in the axial direction relative to the second main shaft 28. It comprises a sixth speed drive gear 51 that is supported and a sixth speed driven gear 52 that is supported on the countershaft 30 so as to be capable of relative movement in the axial direction but not to be relatively rotatable.

第４速用駆動ギヤ４９および第５速用駆動ギヤ４５間で第１メインシャフト２８には、軸方向相対移動を可能とした第１のドグ部材５３が相対回転不能に支承されており、この第１のドグ部材５３に第３速用駆動ギヤ４３が一体に形成される。また第１のドグ部材５３は、その第５速用駆動ギヤ４５に対向する側面に配置される雄型の第１のドグ５４…を有するものであり、第５速用駆動ギヤ４５には第１のドグ５４…を係脱可能に係合させる第１の係合凹部５５…が形成される。また第６速用駆動ギヤ５１を第２速用駆動ギヤ４７との間に挟む位置で第２メインシャフト２８には、軸方向相対移動を可能とした第２のドグ部材５６が相対回転不能に支承されており、この第２のドグ部材５６に第４速用駆動ギヤ４９が一体に形成される。また第２のドグ部材５６は、その第６速用駆動ギヤ５１に対向する側面に配置される雄型の第２のドグ５７…を有するものであり、第６速用駆動ギヤ５１には第２のドグ歯５７…を係脱可能に係合させる第２の係合凹部５８…が形成される。 Between the fourth speed drive gear 49 and the fifth speed drive gear 45, the first main shaft 28 is supported by a first dog member 53 that is capable of relative movement in the axial direction so as not to be relatively rotatable. A third speed drive gear 43 is formed integrally with the first dog member 53. The first dog member 53 has a male first dog 54 disposed on the side surface facing the fifth speed drive gear 45, and the fifth speed drive gear 45 includes a first dog member 54. The first engaging recesses 55 are formed to engage the dogs 54 in a detachable manner. In addition, the second dog member 56 that can move in the axial direction relative to the second main shaft 28 at a position where the sixth-speed drive gear 51 is sandwiched between the second-speed drive gear 47 and the second-speed drive gear 47 becomes relatively non-rotatable. The fourth dog drive gear 49 is integrally formed with the second dog member 56. Further, the second dog member 56 has male second dogs 57 arranged on the side surface facing the sixth speed drive gear 51, and the sixth speed drive gear 51 includes the second dog member 57. Second engagement recesses 58 are formed to engage the two dog teeth 57 in a releasable manner.

第１速用被動ギヤ４２および第３速用被動ギヤ４４間で前記カウンタシャフト３０には、軸方向相対移動を可能とした第３のドグ部材５９が相対回転不能に支承されており、この第３のドグ部材５９に第５速用被動ギヤ４６が一体に形成される。また第３のドグ部材５９は、その第１速用被動ギヤ４２に対向する側面に配置される雄型の第３のドグ６０…ならびに第３速用被動ギヤ４４に対向する側面に配置される雄型の第４のドグ６１…を有するものであり、第１速用被動ギヤ４２には第３のドグ６０…を係脱可能に係合させる第３の係合凹部６２…が形成され、第３速用被動ギヤ４４には第４のドグ６１…を係脱可能に係合させる第４の係合凹部６３…が形成される。 Between the first speed driven gear 42 and the third speed driven gear 44, a third dog member 59 capable of relative movement in the axial direction is supported on the countershaft 30 so as not to be relatively rotatable. The third gear member 59 is integrally formed with the third dog member 59. The third dog member 59 is disposed on the side surface facing the male third dog 60... Disposed on the side surface facing the first speed driven gear 42 and the third speed driven gear 44. There are male fourth dogs 61... The first speed driven gear 42 is formed with third engagement recesses 62 for releasably engaging the third dogs 60. The third-speed driven gear 44 is formed with fourth engagement recesses 63 that detachably engage the fourth dogs 61.

第２速用被動ギヤ４８および第４速用被動ギヤ５０間で前記カウンタシャフト３０には、軸方向相対移動を可能とした第４のドグ部材６４が相対回転不能に支承されており、この第４のドグ部材６４に第６速用被動ギヤ５２が一体に形成される。また第４のドグ部材６４は、その第２速用被動ギヤ４８に対向する側面に配置される雄型の第５のドグ６５…ならびに第４速用被動ギヤ５０に対向する側面に配置される雄型の第６のドグ６６…を有するものであり、第２速用被動ギヤ４８には第５のドグ６５…を係脱可能に係合させる第５の係合凹部６７…が形成され、第４速用被動ギヤ５０には第６のドグ６６…を係脱可能に係合させる第６の係合凹部６８…が形成される。 Between the second speed driven gear 48 and the fourth speed driven gear 50, a fourth dog member 64 is mounted on the countershaft 30 so as to be capable of relative movement in the axial direction. A fourth gear driven gear 52 is formed integrally with the fourth dog member 64. The fourth dog member 64 is disposed on the side surface facing the male fifth dog 65... Disposed on the side surface facing the second speed driven gear 48 and the fourth speed driven gear 50. The second engaging gear 48 is formed with fifth engaging recesses 67 for releasably engaging the fifth dogs 65, and so on. The fourth gear driven gear 50 is formed with sixth engaging recesses 68 for detachably engaging the sixth dogs 66.

第１のドグ部材５３の第１のドグ５４…および第５速用駆動ギヤ４５の第１の係合凹部５５…は、第１のドグ部材５３の軸方向移動によって第１メインシャフト２８および第５速駆動ギヤ４５間の動力伝達の断・接を切換える第１のドグクラッチＣ１を構成し、第２のドグ部材５６の第２のドグ５７…および第６速駆動ギヤ５１の第２の係合凹部５８…は、第２のドグ部材５６の軸方向移動によって第２メインシャフト２９および第６速駆動ギヤ５１間の動力伝達の断・接を切換える第２のドグクラッチＣ２を構成する。また第３のドグ部材５９の第３のドグ６０…および第１速用被動ギヤ４２の第３の係合凹部６２…は、第３のドグ部材５９の軸方向移動によって第１速用被動ギヤ４２およびカウンタシャフト３０間の動力伝達の断・接を切換える第３のドグクラッチＣ３を構成し、第３のドグ部材５９の第４のドグ６１…および第３速用被動ギヤ４４の第３の係合凹部６２…は、第３のドグ部材５９の軸方向移動によって第３速用被動ギヤ４４およびカウンタシャフト３０間の動力伝達の断・接を切換える第４のドグクラッチＣ４を構成する。さらに第４のドグ部材６４の第５のドグ６５…および第２速用被動ギヤ４８の第５の係合凹部６７…は、第４のドグ部材６４の軸方向移動によって第２速被動ギヤ４８およびカウンタシャフト３０間の動力伝達の断・接を切換える第５のドグクラッチＣ５を構成し、第４のドグ部材６４の第６のドグ６６…および第４速被動ギヤ５０の第６の係合凹部６８…は第４のドグ部材６４の軸方向移動によって第４速被動ギヤ５０およびカウンタシャフト３０間の動力伝達の断・接を切換える第６のドグクラッチＣ６を構成する。 The first dog 54 of the first dog member 53 and the first engaging recess 55 of the fifth gear 45 are driven by the axial movement of the first dog member 53 and the first main shaft 28. A first dog clutch C1 for switching between power transmission / reception between the fifth speed drive gear 45 and the second engagement of the second dog 57 ... of the second dog member 56 and the sixth speed drive gear 51 is provided. The recesses 58 ... constitute a second dog clutch C2 that switches between power connection and disconnection between the second main shaft 29 and the sixth speed drive gear 51 by the axial movement of the second dog member 56. Further, the third dog 60 of the third dog member 59 and the third engaging recess 62 of the first speed driven gear 42 are moved by the axial movement of the third dog member 59. The third dog clutch C3 for switching the power transmission / reception between the motor 42 and the countershaft 30 is configured, and the fourth dog 61... Of the third dog member 59 and the third engagement of the third speed driven gear 44 are configured. The combined recesses 62 ... constitute a fourth dog clutch C4 that switches between power transmission / disconnection between the third speed driven gear 44 and the countershaft 30 by the axial movement of the third dog member 59. Furthermore, the fifth dog 65 of the fourth dog member 64 and the fifth engagement recess 67 of the second speed driven gear 48 are moved by the second speed driven gear 48 by the axial movement of the fourth dog member 64. And the fifth dog clutch C5 for switching the power transmission between the counter shaft 30 and the sixth dog 66... Of the fourth dog member 64 and the sixth engagement recess of the fourth speed driven gear 50. 68 ... constitutes a sixth dog clutch C6 for switching the power transmission / reception between the fourth speed driven gear 50 and the countershaft 30 by the axial movement of the fourth dog member 64.

このような変速機Ｍでは、第１〜第４のドグ部材５３，５６，６０，６４の軸方向位置を制御して第１〜第６のドグクラッチＣ１〜Ｃ６の断・接を切換えることによって、第１〜第６速ギヤ列Ｇ１〜Ｇ６が択一的に確立することになる。 In such a transmission M, the axial positions of the first to fourth dog members 53, 56, 60, and 64 are controlled to switch the connection / disconnection of the first to sixth dog clutches C1 to C6. The first to sixth speed gear trains G1 to G6 are alternatively established.

第１〜第６のドグクラッチＣ１〜Ｃ６において第５速駆動ギヤ４５、第６速駆動ギヤ５１、第１速被動ギヤ４２、第３速被動ギヤ４４、第２速被動ギヤ４８および第４速被動ギヤ５０は、本発明のドグクラッチ用ギヤとして形成されるものであり、基本的には同様の形状を有しており、代表して第２速被動ギヤ４８の形状について以下に詳細に説明し、第５速駆動ギヤ４５、第６速駆動ギヤ５１、第１速被動ギヤ４２、第３速被動ギヤ４４および第４速被動ギヤ５０の形状についての詳細な説明は省略する。 In the first to sixth dog clutches C1 to C6, the fifth speed driving gear 45, the sixth speed driving gear 51, the first speed driven gear 42, the third speed driven gear 44, the second speed driven gear 48, and the fourth speed driven. The gear 50 is formed as a dog clutch gear of the present invention, and basically has the same shape. As a representative example, the shape of the second speed driven gear 48 will be described in detail below. Detailed descriptions of the shapes of the fifth speed driving gear 45, the sixth speed driving gear 51, the first speed driven gear 42, the third speed driven gear 44, and the fourth speed driven gear 50 are omitted.

図３および図４において、第２速被動ギヤ４８は、回転軸であるカウンタシャフト３０に支持される円筒状のボス部７０と、該ボス部７０を同軸に囲むとともに外周に歯部７４が形成される環状のリム部７１と、前記ボス部７０および前記リム部７１間を連結する環状壁部７２と、前記ボス部７０および前記リム部７１間を結んで放射状に延びるとともに前記リム部７１側に向かうにつれて幅広になるように形成されて前記環状壁部７２から前記回転軸の軸方向に***する複数の係止リブ７３，７３…とを一体に有し、前記ボス部７０および前記リム部７１間であって相互に隣接する係止リブ７３，７３間に第５の係合凹部６７が形成される。 3 and 4, the second speed driven gear 48 includes a cylindrical boss portion 70 supported by the counter shaft 30 that is a rotation shaft, and a boss portion 70 coaxially surrounding the boss portion 70 and a tooth portion 74 formed on the outer periphery. An annular rim portion 71, an annular wall portion 72 connecting the boss portion 70 and the rim portion 71, and a rim portion 71 side extending radially and connecting the boss portion 70 and the rim portion 71. Are integrally formed with a plurality of locking ribs 73, 73... Which are formed so as to become wider toward the center of the annular wall 72 and protrude from the annular wall portion 72 in the axial direction of the rotation shaft. A fifth engaging recess 67 is formed between the locking ribs 73 adjacent to each other between 71 and 71.

図５を併せて参照して、前記カウンタシャフト３０の周方向両側に臨む前記係止リブ７３の両側面の一方に、前記カウンタシャフト３０の回転方向に沿う後方に臨むようにして平坦な当接面７５が形成され、前記係止リブ７３の前記両側面および前記ボス部７０の連設部には内側隅曲面部７７，７７がそれぞれ形成され、前記係止リブ７３の前記両側面および前記リム部７１の連設部には外側隅曲面部７８，７８がそれぞれ形成される。しかも外側隅曲面部７８の曲率半径ＲＢは内側隅曲面部７７の曲率半径ＲＡよりも大きく設定される。 Referring also to FIG. 5, a flat contact surface 75 facing one side of both sides of the locking rib 73 facing both sides of the countershaft 30 in the circumferential direction so as to face rearward along the rotation direction of the countershaft 30. Inner corner curved surface portions 77 and 77 are formed on the both side surfaces of the locking rib 73 and the connecting portion of the boss portion 70, respectively, and the both side surfaces of the locking rib 73 and the rim portion 71. Outer corner curved surface portions 78 and 78 are respectively formed in the continuous portions. Moreover, the radius of curvature RB of the outer corner curved surface portion 78 is set larger than the radius of curvature RA of the inner corner curved surface portion 77.

また前記外側隅曲面部７８には、該外側隅曲面部７８から前記周方向に***する***部７９が、該***部７９の両側が前記ボス部７０側の第１曲面８１ならびに前記リム部７１側の第２曲面８２で前記外側隅曲面部７８に連なるようにして、一体に形成され、第１曲面８１の曲率半径Ｒ１が第２曲面８２の曲率半径Ｒ２よりも小さく設定される。 Further, the outer corner curved surface portion 78 has a raised portion 79 protruding from the outer corner curved surface portion 78 in the circumferential direction, and both sides of the raised portion 79 are the first curved surface 81 on the boss portion 70 side and the rim portion 71. The second curved surface 82 is formed integrally with the outer corner curved surface portion 78 so that the curvature radius R1 of the first curved surface 81 is set smaller than the curvature radius R2 of the second curved surface 82.

前記ボス部７０の外周面および前記環状壁部７２の連設部には第３曲面８３が形成され、前記カウンタシャフト３０の回転方向７６から見たときに第３曲面８３の曲率半径Ｒ３と同一の曲率半径Ｒ４となる第４曲面８４が、前記***部７９および前記環状壁部７２の連設部に形成される。 A third curved surface 83 is formed on the outer peripheral surface of the boss portion 70 and the connecting portion of the annular wall portion 72, and is the same as the radius of curvature R3 of the third curved surface 83 when viewed from the rotation direction 76 of the countershaft 30. A fourth curved surface 84 having a radius of curvature R4 is formed in the protruding portion 79 and the continuous portion of the annular wall portion 72.

図６において、前記係止リブ７３の側面および前記環状壁部７２の連設部には第５曲面８５が形成され、前記係止リブ７３の長手方向から見たときに第５曲面８５の曲率半径Ｒ５よりも大きな曲率半径Ｒ６となる第６曲面８６が前記***部７９および前記環状壁部７２の連設部に形成される。 In FIG. 6, a fifth curved surface 85 is formed on the side surface of the locking rib 73 and the continuous portion of the annular wall portion 72, and the curvature of the fifth curved surface 85 when viewed from the longitudinal direction of the locking rib 73. A sixth curved face 86 having a radius of curvature R6 larger than the radius R5 is formed at the connecting portion of the raised portion 79 and the annular wall portion 72.

前記リム部７１の内周面および前記環状壁部７２の連設部には、前記ボス部７０の外周面および前記環状壁部７２の連設部に形成される第３曲面８３の曲率半径Ｒ３よりも、前記カウンタシャフト３０の回転方向７６から見たときに大きな曲率半径Ｒ７となる第７曲面８７が形成される。 A radius of curvature R3 of a third curved surface 83 formed on the outer peripheral surface of the boss portion 70 and the continuous portion of the annular wall portion 72 is provided on the inner peripheral surface of the rim portion 71 and the continuous portion of the annular wall portion 72. A seventh curved surface 87 having a large radius of curvature R7 when viewed from the rotational direction 76 of the countershaft 30 is formed.

図７を併せて参照して、前記係止リブ７３の前記環状壁部７２とは反対側の先端面および前記リム部７１の内周面の連設部には、前記リム部７１の内周面に滑らかに連なる第８曲面８８と、その第８曲面８８の前記ボス部７０側の一部を切除して成る段差部８９とが形成される。 Referring also to FIG. 7, the inner peripheral surface of the rim portion 71 is connected to the front end surface of the locking rib 73 opposite to the annular wall portion 72 and the inner peripheral surface of the rim portion 71. An eighth curved surface 88 that is smoothly connected to the surface, and a stepped portion 89 that is formed by cutting a part of the eighth curved surface 88 on the boss portion 70 side are formed.

また前記カウンタシャフト３０の中心軸線を中心とする第１の仮想円ＩＣ１に沿って延びる前記段差部８９が、前記係止リブ７３の前記リム部７１側端部に形成される２つの前記***部７９，７９間に跨がって形成される。 Further, the two raised portions formed at the end portion of the locking rib 73 on the rim portion 71 side, the stepped portion 89 extending along the first virtual circle IC1 centering on the central axis of the countershaft 30. It is formed across 79 and 79.

さらに前記係止リブ７３の前記リム部７１側端部に形成される２つの前記***部７９の頂部を通るとともに前記カウンタシャフト３０の中心軸線を中心とする第２の仮想円ＩＣ２に沿う前記２つの***部７９，７９の頂部間の長さＬが、第２の仮想円ＩＣ２上での前記係止リブ７３の幅ｄのほぼ２倍に設定される。 Further, the 2 of the locking rib 73 along the second virtual circle IC2 passing through the tops of the two raised portions 79 formed at the end of the rim portion 71 and centering on the central axis of the countershaft 30. The length L between the tops of the two raised portions 79, 79 is set to approximately twice the width d of the locking rib 73 on the second virtual circle IC2.

次にこの実施の形態の作用について説明すると、第２速被動ギヤ４８にいて、カウンタシャフト３０の周方向両側に臨む前記係止リブ７３の両側面の一方に、前記カウンタシャフト３０の回転方向７６に沿う後方に臨むようにして平坦な当接面７５が形成され、前記係止リブ７３の前記両側面および前記ボス部７０の連設部には内側隅曲面部７７，７７がそれぞれ形成され、前記係止リブ７３の前記両側面および前記リム部７１の連設部には外側隅曲面部７８，７８がそれぞれ形成され、外側隅曲面部７８の曲率半径ＲＢは内側隅曲面部７７の曲率半径ＲＡよりも大きく設定され、前記外側隅曲面部７８に、該外側隅曲面部７８から前記周方向に***する***部７９が、該***部７９の両側が前記ボス部７０側の第１曲面８１ならびに前記リム部７１側の第２曲面８２で前記外側隅曲面部７８に連なるようにして、一体に形成されるので、ボス部７０側の内側隅曲面部７７に集中し易かった応力をリム部７１側に分散させることが可能となり、係止リブ７３全体への応力の均衡化を図ることができ、形状を変えるだけで剛性を高めることができる。 Next, the operation of this embodiment will be described. In the second speed driven gear 48, the rotation direction 76 of the countershaft 30 is provided on one of both side surfaces of the locking rib 73 facing both sides of the countershaft 30 in the circumferential direction. A flat abutting surface 75 is formed so as to face rearward along the inner side, and inner corner curved surface portions 77, 77 are formed on the both side surfaces of the locking rib 73 and the connecting portion of the boss portion 70, respectively. Outer corner curved surface portions 78 and 78 are respectively formed on the both side surfaces of the retaining rib 73 and the connecting portion of the rim portion 71, and the curvature radius RB of the outer corner curved surface portion 78 is larger than the curvature radius RA of the inner corner curved surface portion 77. Is set to be large, and the outer corner curved surface portion 78 is provided with a protruding portion 79 protruding from the outer corner curved surface portion 78 in the circumferential direction, the first curved surface 81 on both sides of the protruding portion 79 on the boss portion 70 side, and the Re Since the second curved surface 82 on the portion 71 side is continuous with the outer corner curved surface portion 78, the stress is easily concentrated on the inner corner curved surface portion 77 on the boss portion 70 side on the rim portion 71 side. It is possible to disperse, and it is possible to balance the stress on the entire locking rib 73, and it is possible to increase the rigidity only by changing the shape.

このような第２速被動ギヤ４８の係止リブ７３に作用する応力分布の演算によれば、斜線相互の間隔が狭いほうが応力が強いものとして表すと、図８で示すような結果が得られており、係止リブ７３の全体に応力が分散することを確認できる。 According to the calculation of the stress distribution acting on the locking rib 73 of the second speed driven gear 48 as described above, the result shown in FIG. Thus, it can be confirmed that the stress is dispersed throughout the locking rib 73.

また第１曲面８１の曲率半径Ｒ１が第２曲面８２の曲率半径Ｒ２よりも小さく設定されるので、係止リブ７３に作用する応力をより***部７９側に分散させることができる。 Further, since the radius of curvature R1 of the first curved surface 81 is set smaller than the radius of curvature R2 of the second curved surface 82, the stress acting on the locking rib 73 can be further distributed to the raised portion 79 side.

また前記ボス部７０の外周面および前記環状壁部７２の連設部に第３曲面８３が形成され、前記カウンタシャフト３０の回転方向７６から見たときに第３曲面８３と同一の曲率半径となる第４曲面８４が、前記***部７９および前記環状壁部７２の連設部に形成されるので、係止リブ７３のボス部７０側および***部７９側で環状壁部７２の連設部の剛性を同等とすることができ、係止リブ７３に作用する応力を***部７９側に分散させ易くすることができる。 A third curved surface 83 is formed on the outer peripheral surface of the boss portion 70 and the connecting portion of the annular wall portion 72, and has the same radius of curvature as the third curved surface 83 when viewed from the rotation direction 76 of the countershaft 30. Since the fourth curved surface 84 is formed in the continuous portion of the raised portion 79 and the annular wall portion 72, the continuous portion of the annular wall portion 72 on the boss portion 70 side and the raised portion 79 side of the locking rib 73. Can be made equal, and the stress acting on the locking rib 73 can be easily distributed to the raised portion 79 side.

また前記係止リブ７３の側面および前記環状壁部７２の連設部に第５曲面８５が形成され、前記係止リブ７３の長手方向から見たときに第５曲面８５よりも大きな曲率半径となる第６曲面８６が前記***部７９および前記環状壁部７２の連設部に形成されるので、雄型の第５のドグ６５が当接しない***部７９および環状壁部７２間の第６曲面８６の曲率半径Ｒ６を比較的大きくし、特に負荷がかかる外周の歯部７４に近い側で環状壁部７２の厚みを増して剛性を高めることができる。 Further, a fifth curved surface 85 is formed on the side surface of the locking rib 73 and the continuous portion of the annular wall portion 72, and has a larger radius of curvature than the fifth curved surface 85 when viewed from the longitudinal direction of the locking rib 73. Since the sixth curved face 86 is formed in the connecting portion of the raised portion 79 and the annular wall portion 72, the sixth curved face 86 between the raised portion 79 and the annular wall portion 72 where the male fifth dog 65 does not contact is formed. The curvature radius R6 of the curved surface 86 can be made relatively large, and the rigidity of the annular wall 72 can be increased by increasing the thickness of the annular wall 72 on the side close to the outer peripheral tooth 74 where the load is applied.

また前記カウンタシャフト３０の回転方向７６から見たときに第３曲面８３よりも大きな曲率半径となる第７曲面８７が、前記リム部７１の内周面および前記環状壁部７２の連設部に形成されるので、特に負荷がかかる外周の歯部７４に近い側で環状壁部７２の厚みを増して剛性を高めることができる。 A seventh curved surface 87 having a radius of curvature larger than that of the third curved surface 83 when viewed from the rotation direction 76 of the countershaft 30 is provided on the inner peripheral surface of the rim portion 71 and the connecting portion of the annular wall portion 72. Since it is formed, the rigidity of the annular wall portion 72 can be increased by increasing the thickness of the annular wall portion 72 on the side close to the outer peripheral tooth portion 74 where the load is applied.

また前記係止リブ７３の前記環状壁部７２とは反対側の先端面および前記リム部７１の内周面の連設部に、前記リム部７１の内周面に滑らかに連なる第８曲面８８と、その第８曲面８８の前記ボス部７０側の一部を切除して成る段差部８９とが形成されるので、第５のドグ６５と相対回転しながら係合する際に、第８曲面８８への前記ドグ６５の端部のエッジ当たりが生じることを回避し、エッジ当たりによる摩耗が発生する可能性を排除することができる。 Further, an eighth curved surface 88 smoothly connected to the inner peripheral surface of the rim portion 71 is connected to the front end surface of the locking rib 73 opposite to the annular wall portion 72 and the inner peripheral surface of the rim portion 71. And a stepped portion 89 formed by cutting away a part of the eighth curved surface 88 on the boss portion 70 side, the eighth curved surface is used when engaging with the fifth dog 65 while rotating relatively. It is possible to avoid the occurrence of edge contact at the end of the dog 65 to 88 and eliminate the possibility of wear due to edge contact.

また前記カウンタシャフト３０の中心軸線を中心とする第１の仮想円ＩＣ１に沿って延びる前記段差部８９が、前記係止リブ７３の前記リム部７１側端部に形成される２つの前記***部７９，７９間に跨がって形成されるので、***部７９，７９を形成することによって係止リブ７３の幅が大きくなるので、ドグ７６５とのエッジ当たりが生じる可能性がある範囲が長くなるが、そのエッジ当たりが生じないようにして摩耗の発生を抑制することができる。 Further, the two raised portions formed at the end portion of the locking rib 73 on the rim portion 71 side, the stepped portion 89 extending along the first virtual circle IC1 centering on the central axis of the countershaft 30. 79, 79. Since the width of the locking rib 73 is increased by forming the raised portions 79, 79, the range in which the edge contact with the dog 765 may occur is long. However, the occurrence of wear can be suppressed so that the edge contact does not occur.

さらに前記係止リブ７３の前記リム部７１側端部に形成される２つの前記***部７９，７９の頂部を通るとともに前記カウンタシャフト３０の中心軸線を中心とする第２の仮想円ＩＣ２に沿う前記２つの***部７９，７９の頂部間の長さＬが、第２の仮想円ＩＣ２上での前記係止リブ７３の幅ｄのほぼ２倍に設定されるので、***部７９，７９が形成されることで係止リブ７３の幅が大きくなり過ぎて重量増加が生じることを抑制しながら、***部７９…を形成することによる応力分散を適度な幅で効果的に得ることができる。 Further, it passes through the tops of the two raised portions 79, 79 formed at the end of the locking rib 73 on the rim portion 71 side, and is along the second virtual circle IC 2 centering on the central axis of the countershaft 30. Since the length L between the tops of the two raised portions 79, 79 is set to approximately twice the width d of the locking rib 73 on the second virtual circle IC2, the raised portions 79, 79 are As a result, it is possible to effectively obtain a stress distribution with an appropriate width by forming the raised portions 79... While suppressing an increase in weight due to an excessive increase in the width of the locking rib 73.

以上、本発明の実施の形態について説明したが、本発明は上記実施の形態に限定されるものではなく、特許請求の範囲に記載された本発明を逸脱することなく種々の設計変更を行うことが可能である。 Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various design changes can be made without departing from the present invention described in the claims. Is possible.

３０・・・回転軸であるカウンタシャフト
６５・・・ドグ
７０・・・ボス部
７１・・・リム部
７２・・・環状壁部
７３・・・係止リブ
７４・・・歯部
７５・・・当接面
７６・・・回転方向
７７・・・内側隅曲面部
７８・・・外側隅曲面部
７９・・・***部
８１・・・第１曲面
８２・・・第２曲面
８３・・・第３曲面
８４・・・第４曲面
８５・・・第５曲面
８６・・・第６曲面
８７・・・第７曲面
８８・・・第８曲面
８９・・・段差部
ＩＣ１・・・第１の仮想円
ＩＣ２・・・第２の仮想円 30 ... Countershaft 65 which is a rotating shaft ... Dog 70 ... Boss part 71 ... Rim part 72 ... Annular wall 73 ... Locking rib 74 ... Tooth part 75 ... · Contact surface 76 · · · rotation direction 77 · · · inner corner curved surface portion 78 · · · outer corner curved surface portion 79 · · · raised portion 81 · · · first curved surface 82 · · · second curved surface 83 · · · Third curved surface 84 ... fourth curved surface 85 ... fifth curved surface 86 ... sixth curved surface 87 ... seventh curved surface 88 ... eighth curved surface 89 ... stepped portion IC1 ... first Virtual circle IC2 ... second virtual circle

Claims

回転軸（３０）に支持される円筒状のボス部（７０）と、該ボス部（７０）を同軸に囲むとともに外周に歯部（７４）が形成される環状のリム部（７１）と、前記ボス部（７０）および前記リム部（７１）間を連結する環状壁部（７２）と、前記ボス部（７０）および前記リム部（７１）間を結んで放射状に延びるとともに前記リム部（７１）側に向かうにつれて幅広になるように形成されて前記環状壁部（７２）から前記回転軸（３０）の軸方向に***する複数の係止リブ（７３）とを一体に有し、前記回転軸（３０）の周方向両側に臨む前記係止リブ（７３）の両側面の一方に雄型のドグ（６５）と当接する平坦な当接面（７５）が形成され、前記係止リブ（７３）の前記両側面および前記ボス部（７０）の連設部に形成される内側隅曲面部（７７）よりも曲率半径の大きな外側隅曲面部（７８）が前記係止リブ（７３）の前記両側面および前記リム部（７１）の連設部にそれぞれ形成されるドグクラッチ用ギヤにおいて、前記外側隅曲面部（７８）に、該外側隅曲面部（７８）から前記周方向に***する***部（７９）が、該***部（７９）の両側が前記ボス部（７０）側の第１曲面（８１）ならびに前記リム部（７１）側の第２曲面（８２）で前記外側隅曲面部（７８）に連なるようにして、一体に形成されることを特徴とするドグクラッチ用ギヤ。 A cylindrical boss portion (70) supported by the rotating shaft (30), an annular rim portion (71) that coaxially surrounds the boss portion (70) and has a tooth portion (74) formed on the outer periphery; An annular wall portion (72) for connecting the boss portion (70) and the rim portion (71), and a rim portion (72) extending radially from the boss portion (70) and the rim portion (71). 71) integrally formed with a plurality of locking ribs (73) formed so as to increase in width toward the side and projecting from the annular wall (72) in the axial direction of the rotating shaft (30), A flat contact surface (75) that contacts a male dog (65) is formed on one of both side surfaces of the locking rib (73) facing both sides in the circumferential direction of the rotating shaft (30), and the locking rib Inner corner bends formed on both side surfaces of (73) and the continuous portion of the boss portion (70) In the dog clutch gear, the outer corner curved surface portion (78) having a larger radius of curvature than the portion (77) is formed on the both side surfaces of the locking rib (73) and the continuous portion of the rim portion (71), respectively. The outer corner curved surface portion (78) has a raised portion (79) protruding from the outer corner curved surface portion (78) in the circumferential direction, and both sides of the raised portion (79) are located on the boss portion (70) side. A dog clutch gear characterized by being formed integrally with one curved surface (81) and a second curved surface (82) on the rim portion (71) side so as to be connected to the outer corner curved surface portion (78).

第１曲面（８１）の曲率半径が第２曲面（８２）の曲率半径よりも小さく設定されることを特徴とする請求項１記載のドグクラッチ用ギヤ。 The dog clutch gear according to claim 1, wherein the radius of curvature of the first curved surface (81) is set smaller than the radius of curvature of the second curved surface (82).

前記ボス部（７０）の外周面および前記環状壁部（７２）の連設部に第３曲面（８３）が形成され、前記回転軸（３０）の回転方向（７６）から見たときに第３曲面（８３）と同一の曲率半径となる第４曲面（８４）が、前記***部（７９）および前記環状壁部（７２）の連設部に形成されることを特徴とする請求項１または２記載のドグクラッチ用ギヤ。 A third curved surface (83) is formed on the outer peripheral surface of the boss portion (70) and the continuous portion of the annular wall portion (72), and the third curved surface (83) is viewed when viewed from the rotation direction (76) of the rotation shaft (30). The fourth curved surface (84) having the same radius of curvature as that of the three curved surface (83) is formed in a continuous portion of the raised portion (79) and the annular wall portion (72). Or the gear for dog clutches of 2.

前記係止リブ（７３）の側面および前記環状壁部（７２）の連設部に第５曲面（８５）が形成され、前記係止リブ（７３）の長手方向から見たときに第５曲面（８５）よりも大きな曲率半径となる第６曲面（８６）が前記***部（７９）および前記環状壁部（７２）の連設部に形成されることを特徴とする請求項１〜３のいずれか１項に記載のドグクラッチ用ギヤ。 A fifth curved surface (85) is formed on the side surface of the locking rib (73) and the continuous portion of the annular wall portion (72), and the fifth curved surface when viewed from the longitudinal direction of the locking rib (73). The sixth curved surface (86) having a larger radius of curvature than (85) is formed in the connecting portion of the raised portion (79) and the annular wall portion (72). The dog clutch gear according to any one of the preceding claims.

前記ボス部（７０）の外周面および前記環状壁部（７２）の連設部に第３曲面（８３）が形成され、前記回転軸（３０）の回転方向（７６）から見たときに第３曲面（８３）よりも大きな曲率半径となる第７曲面（８７）が、前記リム部（７１）の内周面および前記環状壁部（７２）の連設部に形成されることを特徴とする請求項１〜４のいずれか１項に記載のドグクラッチ用ギヤ。 A third curved surface (83) is formed on the outer peripheral surface of the boss portion (70) and the continuous portion of the annular wall portion (72), and the third curved surface (83) is viewed when viewed from the rotation direction (76) of the rotation shaft (30). A seventh curved surface (87) having a radius of curvature larger than the three curved surfaces (83) is formed on the inner peripheral surface of the rim portion (71) and the connecting portion of the annular wall portion (72). The gear for a dog clutch according to any one of claims 1 to 4.

前記係止リブ（７３）の前記環状壁部（７２）とは反対側の先端面および前記リム部（７１）の内周面の連設部に、前記リム部（７１）の内周面に滑らかに連なる第８曲面（８８）と、その第８曲面（８８）の前記ボス部（７０）側の一部を切除して成る段差部（８９）とが形成されることを特徴とする請求項１〜５のいずれか１項に記載のドグクラッチ用ギヤ。 On the inner peripheral surface of the rim portion (71), the front end surface of the locking rib (73) opposite to the annular wall portion (72) and the continuous portion of the inner peripheral surface of the rim portion (71) 8. An eighth curved surface (88) smoothly connected and a stepped portion (89) formed by cutting a part of the eighth curved surface (88) on the boss portion (70) side are formed. Item 6. The dog clutch gear according to any one of Items 1 to 5.

前記回転軸（３０）の中心軸線を中心とする第１の仮想円（ＩＣ１）に沿って延びる前記段差部（８９）が、前記係止リブ（７３）の前記リム部（７１）側端部に形成される２つの前記***部（７９）間に跨がって形成されることを特徴とする請求項６記載のドグクラッチ用ギヤ。 The step portion (89) extending along the first virtual circle (IC1) centering on the central axis of the rotation shaft (30) is the end portion on the rim portion (71) side of the locking rib (73). The dog clutch gear according to claim 6, wherein the dog clutch gear is formed to straddle between the two raised portions (79).

前記係止リブ（７３）の前記リム部（７１）側端部に形成される２つの前記***部（７９）の頂部を通るとともに前記回転軸（３０）の中心軸線を中心とする第２の仮想円（ＩＣ２）に沿う前記２つの***部（７９）の頂部間の長さが、第２の仮想円（ＩＣ２）上での前記係止リブ（７３）の幅のほぼ２倍に設定されることを特徴とする請求項１〜７のいずれか１項に記載のドグクラッチ用ギヤ。
A second centered on the central axis of the rotating shaft (30) while passing through the tops of the two raised portions ( 79) formed at the rim (71) side end of the locking rib (73). The length between the tops of the two raised portions (79) along the virtual circle (IC2) is set to be approximately twice the width of the locking rib (73) on the second virtual circle (IC2). The dog clutch gear according to any one of claims 1 to 7, wherein the dog clutch gear is provided.