JPS6122176B2 - - Google Patents
Info
- Publication number
- JPS6122176B2 JPS6122176B2 JP55105380A JP10538080A JPS6122176B2 JP S6122176 B2 JPS6122176 B2 JP S6122176B2 JP 55105380 A JP55105380 A JP 55105380A JP 10538080 A JP10538080 A JP 10538080A JP S6122176 B2 JPS6122176 B2 JP S6122176B2
- Authority
- JP
- Japan
- Prior art keywords
- meshing
- engagement
- driving body
- recess
- convex portion
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 230000013011 mating Effects 0.000 claims 3
- 230000005540 biological transmission Effects 0.000 description 26
- 230000008094 contradictory effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/089—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
- B62M7/00—Motorcycles characterised by position of motor or engine
- B62M7/02—Motorcycles characterised by position of motor or engine with engine between front and rear wheels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D11/00—Clutches in which the members have interengaging parts
- F16D11/08—Clutches in which the members have interengaging parts actuated by moving a non-rotating part axially
- F16D11/10—Clutches in which the members have interengaging parts actuated by moving a non-rotating part axially with clutching members movable only axially
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/04—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways with a shaft carrying a number of rotatable transmission members, e.g. gears, each of which can be connected to the shaft by a clutching member or members between the shaft and the hub of the transmission member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D11/00—Clutches in which the members have interengaging parts
- F16D2011/004—Clutches in which the members have interengaging parts using an internal or intermediate axially slidable sleeve, coupling both components together, whereby the intermediate sleeve is arranged internally at least with respect to one of the components
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D11/00—Clutches in which the members have interengaging parts
- F16D2011/008—Clutches in which the members have interengaging parts characterised by the form of the teeth forming the inter-engaging parts; Details of shape or structure of these teeth
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Operated Clutches (AREA)
Description
【発明の詳細な説明】
本発明は噛合い易くかつ噛合い後の遊び（ガ
タ）が少ない、新規なドツグクラツチ装置に関す
るものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a novel dog clutch device that is easy to engage and has little play (backlash) after engagement.
同一の回転軸上に、駆動体を一体に、また被動
体を相対回転自在にそれぞれ支承し、それらに設
けた噛合凸部と噛合凹部とを噛脱させてそれら間
の回転力の伝達あるいはその解除を行うようにし
た、所謂ドツグクラツチ装置では前記噛合凸部と
噛合凹部との噛合率を高めるとそれら間の回転方
向の遊び（ガタ）が大きくなつて回転時の衝撃を
大きくし、また騒音の原因にもなり、また前記遊
び（ガタ）を小さくすると噛合率の低下を招き、
結局従来ドツグクラツチ装置では、前記噛合率と
遊びとが相互に相反する関係にあつて前記噛合率
を高め、かつ前記遊びも少なくすることは困難で
ある。 A driving body is integrally supported and a driven body is relatively rotatably supported on the same rotating shaft, and the engaging convex portion and the engaging concave portion provided thereon are engaged and disengaged to transmit or transmit rotational force between them. In a so-called dog clutch device that is designed to release, increasing the engagement ratio between the meshing protrusion and the meshing recess increases the play (backlash) in the rotational direction between them, which increases the impact during rotation and also reduces noise. Also, reducing the play (backlash) will lead to a decrease in the engagement ratio.
After all, in the conventional dog clutch device, the engagement ratio and the play are in a contradictory relationship, and it is difficult to increase the engagement ratio and reduce the play.
そこで本発明は前記噛合率を高めつつ、かつ前
記遊び（ガタ）を可及的に縮小することができる
ようにした、構造簡単なドツグクラツチ装置を提
供することを目的とするものである。 SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a dog clutch device having a simple structure, which is capable of increasing the meshing ratio and reducing the play as much as possible.
かかる目的を達成するために本発明は、回転軸
上に駆動体を一体に回転できるように、また被動
体を相対回転できるようにそれぞれ支承し、それ
ら駆動体及び被動体の相対向する対向面の何れか
一方に複数個の噛合凸部を、その他方にその噛合
凸部と噛脱し得る噛合凹部をそれぞれ回転方向に
等間隔を存して設け、前記駆動体と被動体との軸
方向の相対摺動によつて前記噛合凸部と噛合凹部
を噛脱させ、それら駆動体と被動体間の回転力の
伝達もしくはその解除を行うようにしたドツグク
ラツチ装置において、前記噛合凸部を回転方向に
間隔を存し、かつ軸方向の高さが異なる高，低噛
合凸部よりなる噛合凸部組により構成し、一方前
記噛合凹部を前記噛合凸部組と噛合し得る大きさ
に形成し、前記駆動体と被動体との相対回転時に
前記噛合凸部組の、高噛合凸部がその低噛合凸部
に先行して前記噛合凹部に噛合されることを特徴
とする。 In order to achieve this object, the present invention supports a driving body on a rotating shaft so that they can rotate together and a driven body so that they can rotate relative to each other, and the facing surfaces of the driving body and the driven body that face each other. A plurality of engaging convex portions are provided on one of the two, and a plurality of engaging concave portions that can engage and disengage with the engaging convex portion are provided on the other side at equal intervals in the rotational direction, and the axial direction between the driving body and the driven body is provided. In a dog clutch device in which the engaging protrusion and the engaging recess are engaged and disengaged by relative sliding to transmit or release rotational force between the driving body and the driven body, the engaging convex portion is moved in the direction of rotation. It is constituted by a meshing protrusion set consisting of high and low meshing protrusions with a gap and different heights in the axial direction, and the meshing recess is formed to a size that can mesh with the meshing protrusion set, and When the driving body and the driven body rotate relative to each other, the high engagement convex portion of the engagement convex set is engaged with the engagement concave portion before the low engagement convex portion thereof.
以下、図面により本考案ドツグクラツチ装置を
自動二輪車の動力伝達系に実施した場合の実施例
について説明すると、エンジンＥのクランクケー
ス１と、主ミツシヨンケース２とは、一体に形成
され、前記クランクケース１内にはクランクシヤ
フト３が回転自在に軸架され、また前記主ミツシ
ヨンケース２内には主変速機Tmが収納装備され
ている。この主変速機Tmは主ミツシヨンケース
２に互いに平行に軸架されるプライマリシヤフト
４、メインシヤフト５およびカウンタシヤフト６
とを有し、クランクシヤフト３とプライマリシヤ
フト４とは、それら間に懸回されるチエイン伝動
機構７を介して連動され、またプライマリシヤフ
ト４とメインシヤフト５とは、それら間に設けら
れる伝動歯車機構８およびクラツチ機構９を介し
て連動され、さらにメインシヤフト５とカウンタ
シヤフト６とは、それらに設けられる主変速歯車
群１０を介して連動されている。そしてエンジン
Ｅの動力は、クランクシヤフト３よりチエン伝動
機構７、プライマリシヤフト４、伝動歯車機構
８、クラツチ機構９、メインシヤフト５、変速歯
車群１０を介してカウンタシヤフト６に伝達さ
れ、クランクシヤフト３と、カウンタシヤフト６
間の変速比の変更は前記主変速機Tmの切換操作
によつて通常のように行われる。カウンタシヤフ
ト６の出力端６′は主ミツシヨンケース２より外
部に突出している。 Hereinafter, an embodiment in which the dog clutch device of the present invention is implemented in a power transmission system of a motorcycle will be explained with reference to the drawings. The crankcase 1 of the engine E and the main transmission case 2 are integrally formed, and A crankshaft 3 is rotatably mounted within the main transmission case 1, and a main transmission Tm is housed within the main transmission case 2. This main transmission Tm includes a primary shaft 4, a main shaft 5, and a countershaft 6, which are mounted parallel to each other on a main transmission case 2.
The crankshaft 3 and the primary shaft 4 are interlocked via a chain transmission mechanism 7 suspended between them, and the primary shaft 4 and the main shaft 5 are connected to a transmission gear provided between them. The main shaft 5 and the countershaft 6 are interlocked via a mechanism 8 and a clutch mechanism 9, and the main shaft 5 and countershaft 6 are interlocked via a main transmission gear group 10 provided thereon. The power of the engine E is transmitted from the crankshaft 3 to the countershaft 6 via the chain transmission mechanism 7, the primary shaft 4, the transmission gear mechanism 8, the clutch mechanism 9, the main shaft 5, and the transmission gear group 10. and countershaft 6
Changes in the gear ratio between the two are performed in the usual manner by switching the main transmission Tm. An output end 6' of the countershaft 6 projects outward from the main transmission case 2.
而して前述したクランクシヤフト３からカウン
タシヤフト６に至る動力伝達機構は従来公知の構
成であるので、その詳細な説明を省略する。 Since the power transmission mechanism from the crankshaft 3 to the countershaft 6 described above has a conventionally known configuration, a detailed explanation thereof will be omitted.
前記主ミツシヨンケース２の後部には、第２図
に明瞭に示すように平面よりみて略Ｌ字状をなす
副ミツシヨンケース１１が支持部材１２を介して
取付ボルト１３により着脱自在に取付けられる。
この副ミツシヨンケース１１はケース主体１４
と、このケース主体１４の開口部に取付ボルト１
６により被着されるカバー１５とより構成され、
前記ケース主体１４は、前記ミツシヨンケース２
の一側壁に沿い車体フレームの前後方向にのびる
前半部１７と、その主ミツシヨンケース２の後壁
に沿い車体フレームの左右方向にのびる後半部１
８とを一体に形成して構成され、前記カバー１５
は前記前半部１７に開口される開口部に被着され
ており、その前半部１７とカバー１５とにより歯
車収容空間が形成されている。歯車収容空間内
に、前記カウンタシヤフト６の出力端６′が突出
されてカバー１５に回転自在に支承されている。 As clearly shown in FIG. 2, a sub-mission case 11 having a substantially L-shape when viewed from above is removably attached to the rear of the main transmission case 2 via a support member 12 with a mounting bolt 13. .
This sub-mission case 11 is the main case 14
Then, insert the mounting bolt 1 into the opening of the case main body 14.
a cover 15 attached by 6;
The case main body 14 is the mission case 2
The front half 17 extends in the longitudinal direction of the vehicle body frame along one side wall, and the rear half 1 extends in the left-right direction of the vehicle body frame along the rear wall of the main transmission case 2.
8, and the cover 15
is attached to the opening in the front half 17, and the front half 17 and the cover 15 form a gear housing space. The output end 6' of the countershaft 6 projects into the gear housing space and is rotatably supported by the cover 15.
前記副ミツシヨンケース１１内には、副変速機
Tsが内装されている。以下この副変速機Tsの構
造を、主に第２図を参照して説明すると、カウン
タシヤフト６の出力端６′には、一対の被動体を
構成する第１，第２歯車２１，２２とがそれぞれ
回転自在に遊嵌されるとともにそれらの間にシフ
タボス２３がスプライン嵌合されており、このシ
フタボス２３はカウンタシヤフト６と一体に回転
できる。シフタボス２３の外周にはシフタ２６が
軸方向に摺動可能にスプライン嵌合されている。
前記第１，第２歯車２１，２２のデイスク部およ
び前記シフタ２６の両側には、後に詳述するドツ
グクラツチ装置Ｃがそれぞれ設けられる。 Inside the sub-transmission case 11 is a sub-transmission.
Ts are interior. The structure of this sub-transmission Ts will be explained below mainly with reference to FIG. are loosely fitted in a rotatable manner, and a shifter boss 23 is spline-fitted between them, and the shifter boss 23 can rotate together with the countershaft 6. A shifter 26 is spline-fitted to the outer periphery of the shifter boss 23 so as to be slidable in the axial direction.
Dog clutch devices C, which will be described in detail later, are provided on both sides of the disk portions of the first and second gears 21 and 22 and the shifter 26, respectively.
而してカウンタシヤフト６、各歯車２１，２２
及びシフタ２６は、本発明の回転軸、被動体及び
駆動体をそれぞれ構成している。 Therefore, the countershaft 6, each gear 21, 22
and shifter 26 respectively constitute a rotating shaft, a driven body, and a driving body of the present invention.
前記シフタ２６にはシフトフオーク２９が嵌着
されており、このシフトフオーク２９は図示しな
いシフトレバー等に連動されている。第２図にお
いてシフタ２６が左に動くと、これが前記ドツグ
クラツチ装置Ｃを介して第１歯車２１と噛合し、
またシフタ２６が右に動くと、これが前記ドツグ
クラツチ装置Ｃを介して第２歯車２２と噛合でき
るようになつている。第１，第２歯車２１，２２
の対向面外周には、環状の緩衝用ラバー１９，２
０が焼付けられている。 A shift fork 29 is fitted into the shifter 26, and the shift fork 29 is interlocked with a shift lever or the like (not shown). When the shifter 26 moves to the left in FIG. 2, it meshes with the first gear 21 via the dog clutch device C,
Also, when the shifter 26 moves to the right, it can mesh with the second gear 22 via the dog clutch device C. First and second gears 21, 22
An annular cushioning rubber 19, 2 is provided on the outer periphery of the opposing surface of the
0 is burned in.
前記副ミツシヨンケース１１の後半部１８は自
動二輪車の後車輪Ｗの前方を横切るように車体フ
レームの横方向にのびており、その後半部１８内
には前記カウンタシヤフト６と略平行に配設され
る伝動シヤフト３０が回転自在に支承され、この
伝動シヤフト３０の一端部には、一体化された第
３，第４歯車３１，３２が軸方向への移動不能に
スプライン嵌合されて伝動シヤフト３０と一体に
回転できるようになつている。第３歯車３１は前
記第１歯車２１と、また第４歯車３２は第２歯車
２２にそれぞれ常時噛合されている。 The rear half 18 of the auxiliary transmission case 11 extends in the lateral direction of the vehicle body frame so as to cross the front of the rear wheel W of the motorcycle, and is disposed within the rear half 18 substantially parallel to the countershaft 6. A transmission shaft 30 is rotatably supported, and integrated third and fourth gears 31 and 32 are spline-fitted to one end of the transmission shaft 30 so as to be immovable in the axial direction. It is designed to be able to rotate together with the The third gear 31 and the fourth gear 32 are always meshed with the first gear 21 and the second gear 22, respectively.
前記伝動シヤフト３０の他端には、駆動傘歯車
３４が一体に形成され、また副ミツシヨンケース
１１の他端部（第２図右端部）には、前記伝動シ
ヤフト３０と直交する短い被動シヤフト３６が回
転自在に支承され、この被動シヤフト３６と一体
に形成される被動傘歯車３５は、前記駆動傘歯車
３４と噛合されている。 A driving bevel gear 34 is integrally formed at the other end of the transmission shaft 30, and a short driven shaft perpendicular to the transmission shaft 30 is formed at the other end of the sub-mission case 11 (right end in FIG. 2). 36 is rotatably supported, and a driven bevel gear 35 formed integrally with the driven shaft 36 is meshed with the drive bevel gear 34.
前記伝動シヤフト３０には、第１図に示すよう
に主ミツシヨンケース２を挟んで前記副変速機
Tsと反対側にシヤフトドライブ伝動機構３７が
連結されており、すなわち前記被動シヤフト３６
には、車体フレームの前後方向にのびるドライブ
シヤフト３８の前端が接手を介して連結され、こ
のドライブシヤフト３８の後端は互に噛合される
一対のフアイナル傘歯車３９，４０を介して後車
輪Ｗに連動されている。ドライブシヤフト３８と
フアイナル傘歯車３９，４０は伝動ケース４１内
に収容される。 As shown in FIG.
A shaft drive transmission mechanism 37 is connected to the side opposite to Ts, that is, the driven shaft 36
The front end of a drive shaft 38 extending in the longitudinal direction of the vehicle body frame is connected via a joint, and the rear end of this drive shaft 38 is connected to a rear wheel W via a pair of final bevel gears 39 and 40 that are meshed with each other. is linked to. The drive shaft 38 and final bevel gears 39 and 40 are housed in a transmission case 41.
次に第３，４図を参照してシフタ２６の両側面
および第１，第２歯車２１，２２の対向側面にそ
れぞれ設けられるドツグクラツチ装置Ｃの構造に
ついて説明すると、前記シフタ２６の両側面に
は、軸方向の高さが異なる高、低噛合凸部２４，
２５よりなる複数組の噛合凸部組Ｐが回転方向に
等間隔を存して放射状に突設されている。 Next, the structure of the dog clutch device C provided on both sides of the shifter 26 and the opposite sides of the first and second gears 21 and 22 will be explained with reference to FIGS. 3 and 4. , high and low engagement convex portions 24 with different axial heights,
A plurality of sets of meshing protrusions P consisting of 25 are provided to protrude radially at equal intervals in the rotational direction.
一方前記第１，第２歯車２１，２２の対向側面
には、前記噛合凸部組Ｐ、すなわち一組の高、低
噛合凸部２４，２５と噛合し得る複数個の噛合凹
部２７が等間隔を存して放射状に形成されてい
る。 On the other hand, on the opposing side surfaces of the first and second gears 21 and 22, a plurality of meshing recesses 27 that can mesh with the meshing projection group P, that is, a set of high and low meshing projections 24 and 25 are arranged at equal intervals. It is formed in a radial pattern.
而して噛合凸部組Ｐを構成する高、低噛合凸部
２４，２５の周方向の両側面および、これに係合
する噛合凹部２７の周方向両側はそれぞれ逆テー
パ４２，４３および４４，４５に形成されてい
る。 Both side surfaces in the circumferential direction of the high and low meshing protrusions 24 and 25 constituting the meshing protrusion group P, and both circumferential sides of the meshing recess 27 that engages with these, are reverse tapers 42, 43 and 44, respectively. 45.
シフタ２６が左、あるいは右に摺動されてそこ
に形成される噛合凸部組Ｐが、第１、あるいは第
２歯車２１、あるいは２２の噛合凹部２７に噛合
する過程を第５図を参照して説明すると、いま
噛合凹部２７の回転方向の幅：L1
噛合凹部２７，２７間の回転方向の間隔：L2
噛合凸部組Ｐの回転方向の幅：ｌ
高噛合凸部２４の回転方向の幅：l1
低噛合凸部２５の回転方向の幅：l2
高：低噛合凸部２４，２５間の間隔：l3
噛合凸部組Ｐ間の間隔：l4
高噛合凸部２４の高さ：h1，
低噛合凸部２５の高さ：h2
高：低噛合凸部の高さの差：ｔ（h1―h2）
噛合凹部２７の上面：Ｂ
噛合凹部２７の側面：Ｅ
とすると、シフタ２６が第５図矢印方向に回転さ
れる噛合方向のスラスト荷重をうけると、l1はL1
に対して十分小さいので高噛合凸部２４は噛合凹
部２７に容易に侵入し得る。すなわち第５図に示
すように低噛合凸部２５が上面Ｂ上を滑り終つた
時点では、高噛合凸部２４の高さｔに相当する部
分が側面Ｅに当つて噛合凹部２７内に侵入し、続
いて低噛合凸部２５が噛合凹部２７内に侵入して
噛合凸部ユニツトＰは噛合凹部２７内に噛合され
る。 The process in which the shifter 26 is slid to the left or right and the meshing protrusion set P formed there meshes with the meshing recess 27 of the first or second gear 21 or 22 is shown in FIG. To explain this, the width of the meshing recess 27 in the rotational direction: L 1 The distance between the meshing recesses 27 and 27 in the rotational direction: L 2 The width of the meshing projection group P in the rotational direction: l The rotational direction of the high meshing projection 24 Width: l 1 Width of the low meshing convex portion 25 in the rotation direction: l 2 Height: Distance between the low meshing convex portions 24 and 25: l 3 Distance between the meshing convex group P: l 4 The width of the high meshing convex portion 24 Height: h 1 , Height of low engagement convex portion 25: h 2 Height: Difference in height of low engagement convex portion: t (h 1 - h 2 ) Top surface of engagement recess 27: B Side surface of engagement recess 27: E, when the shifter 26 receives a thrust load in the meshing direction, which is rotated in the direction of the arrow in FIG. 5, l 1 becomes L 1
Since the high engagement convex portion 24 is sufficiently small compared to the engagement convex portion 24, it can easily enter the engagement recess 27. That is, as shown in FIG. 5, when the low engagement convex portion 25 has finished sliding on the upper surface B, a portion of the high engagement convex portion 24 corresponding to the height t hits the side surface E and enters the engagement recess 27. Then, the low engagement protrusion 25 enters into the engagement recess 27, and the engagement protrusion unit P is engaged within the engagement recess 27.
ところでその噛合終了時点ではL1―ｌは十分
小さいので、噛合凸部ユニツトＰと噛合凹部２７
との回転方向の遊び（ガタ）が少ない。 By the way, since L 1 -l is sufficiently small at the end of the engagement, the engagement convex unit P and the engagement recess 27
There is little play (backlash) in the rotational direction.
而して本発明のドツグクラツチ装置の寸法上の
必要条件を列記すると、
L1＞l1 L2＞l3 L2＞l4
また前述のように高、低噛合凸部２４，２５、
および噛合凹部２７の周方向両側面にそれぞれ逆
テーパ４２，４３および４４，４５を形成するこ
とにより、それらが噛合するとき、シフタ２６に
作用する回転力によつて、高、低噛合凸部２４，
２５と噛合凹部２７の噛合面間に互いに引き寄せ
合うスラスト荷重が生じ、これにより高さｔ＝h1
―h2を大きくして側面Ｅへのかゝり代を十分大き
くすることができ、高，低噛合凸部２４，２５に
作用する単位面積当りの荷重を小さくしてその摩
耗を軽減させることができるとともに高、低噛合
凸部２４，２５が外れにくくなる。 The dimensional requirements for the dog clutch device of the present invention are listed as follows: L 1 > l 1 L 2 > l 3 L 2 > l 4 Also, as mentioned above, the high and low engagement convex portions 24, 25,
By forming reverse tapers 42, 43 and 44, 45 on both circumferential sides of the meshing recess 27, when they mesh, the high and low meshing protrusions 24 are ，
A thrust load is generated between the meshing surfaces of the meshing recess 25 and the meshing recess 27, which attracts each other, and this causes the height t=h 1
-By increasing h2 , it is possible to sufficiently increase the amount of contact to the side surface E, and it is possible to reduce the load per unit area acting on the high and low engagement convex portions 24 and 25, thereby reducing their wear. At the same time, the high and low meshing protrusions 24 and 25 become difficult to come off.
尚、上記実施例において、l3＝l4とすれば、シ
フタ２６が逆方向に回転するときも前述の場合と
全く同じ作用で噛合凸部組Ｐと噛合凹部２７とを
噛合させることができる。 In the above embodiment, if l 3 =l 4 , even when the shifter 26 rotates in the opposite direction, the meshing protrusion set P and the meshing recess 27 can be brought into mesh with the same effect as in the case described above. .
尚、また前記実施例では、噛合凸部組Ｐをシフ
タ２６の両側面に、また噛合凹部２７を第１，第
２歯車２１，２２の対向側面にそれぞれ設けたも
のを示したが、上記とは逆にシフタ２６の両側面
に噛合凹部を、また第１，第２歯車２１，２２の
対向側面に噛合凸部組をそれぞれ設けるようにし
てもよい。 Furthermore, in the embodiment described above, the meshing protrusion set P was provided on both sides of the shifter 26, and the meshing recess 27 was provided on the opposing sides of the first and second gears 21 and 22, respectively. Conversely, meshing recesses may be provided on both sides of the shifter 26, and meshing protrusion sets may be provided on opposing sides of the first and second gears 21 and 22, respectively.
尚、また前記実施例では、噛合凸部組Ｐを高さ
の異なる２組の高，低噛合凸部２４，２５より構
成したが、相互に高さの異なる３個以上の高，低
噛合凸部より噛合凸部組Ｐを構成するようにして
もよい。 Furthermore, in the above embodiment, the meshing convex set P is composed of two sets of high and low meshing projections 24 and 25 with different heights, but three or more sets of high and low meshing projections with different heights. The meshing convex part set P may be constructed from the parts.
以上のように本発明によれば、互いに噛脱され
る駆動体及び被動体の相対向する対向面の何れか
一方に、軸方向の高さの異なる高，低噛合凸部よ
りなる噛合凸部組を突設し、またその他方に前記
噛合凸部組と噛合し得る大きさの噛合凹部を形成
し、前記駆動体と被動体との相対回転時に前記噛
合凸部組の、高噛合凸部がその低噛合凸部に先行
して前記噛合凹部に噛合されるので、噛合凸部組
と噛合凹部とは噛合し易く、しかもそれらの噛合
時の回転方向の遊びを可及的に縮小することがで
き、噛合率が高く、しかもガタの少ない、新規な
ドツグクラツチ装置を得ることができるものであ
る。 As described above, according to the present invention, on either one of the opposing surfaces of the driving body and the driven body that engage and disengage from each other, the engaging convex portion is formed of high and low engaging convex portions having different heights in the axial direction. A set is provided protrudingly, and a meshing recess of a size capable of meshing with the meshing projection set is formed on the other side, and the high meshing projection of the meshing projection set is formed when the driving body and the driven body rotate relative to each other. is engaged with the engagement concave portion before the low engagement convex portion, so that the engagement convex set and the engagement concave portion can easily engage with each other, and furthermore, the play in the rotational direction at the time of their engagement is reduced as much as possible. Therefore, it is possible to obtain a novel dog clutch device which has a high meshing ratio and little backlash.
第１図は本発明ドツグクラツチ装置を備えた自
動二輪車の動力伝達系を示す概略平面図、第２図
はその一部の拡大断面図、第３図はシフタ２６の
側面図、第３Ａ図は第３図―線部分図、第４
図は第１，第２歯車の側面図、第５図は本発明ド
ツグクラツチ装置の噛合状態を示す断面図であ
る。
Ｐ…噛合凸部組、６…回転軸としてのカウンタ
シヤフト、２１，２２…被動体としての第１，第
２歯車、２４，２５…高、低噛合凸部、２６…駆
動体としてのシフタ、２７…噛合凹部。
FIG. 1 is a schematic plan view showing the power transmission system of a motorcycle equipped with the dog clutch device of the present invention, FIG. 2 is an enlarged sectional view of a portion thereof, FIG. 3 is a side view of the shifter 26, and FIG. Figure 3 - line segment diagram, 4th
The figure is a side view of the first and second gears, and FIG. 5 is a sectional view showing the meshing state of the dog clutch device of the present invention. P...Meshing convex part set, 6...Countershaft as a rotating shaft, 21, 22...First and second gears as driven bodies, 24, 25...High and low meshing convex parts, 26...Shifter as a driving body, 27...Matching recess.
Claims (1)
に、また被動体を相対回転できるようにそれぞれ
支承し、それら駆動体及び被動体の相対向する対
向面の何れか一方に複数個の噛合凸部を、その他
方にその噛合凸部と噛脱し得る噛合凹部をそれぞ
れ回転方向に等間隔を存して設け、前記駆動体と
被動体との軸方向の相対摺動によつて前記噛合凸
部と噛合凹部を噛脱させ、それら駆動体と被動体
間の回転力の伝達もしくはその解除を行うように
したドツグクラツチ装置において、前記噛合凸部
を回転方向に間隔を存し、かつ軸方向の高さが異
なる高、低噛合凸部よりなる噛合凸部組により構
成し、一方前記噛合凹部を前記噛合凸部組と噛合
し得る大きさに形成し、前記駆動体と被動体との
相対回転時に前記噛合凸部組の、高噛合凸部がそ
の低噛合凸部に先行して前記噛合凹部に噛合され
ることを特徴とするドツグクラツチ装置。1 A driving body is supported on a rotating shaft so that it can rotate integrally, and a driven body is supported so that it can rotate relative to each other, and a plurality of meshing protrusions are provided on one of the facing surfaces of the driving body and the driven body. and a mating concave part that can engage and disengage with the mating convex part is provided on the other side at equal intervals in the rotational direction, and the mating convex part is formed by relative sliding in the axial direction between the driving body and the driven body. In a dog clutch device that transmits or releases rotational force between the driving body and the driven body by engaging and disengaging the engaging concave portion, the engaging convex portion is spaced apart in the rotational direction and has a height in the axial direction. The meshing recess is formed in a size that can mesh with the meshing projection set, and the meshing recess is formed in a size that can mesh with the meshing projection set, and when the driving body and the driven body rotate relative to each other. A dog clutch device characterized in that the high engagement convex portion of the engagement convex set is engaged with the engagement concave portion before the low engagement convex portion thereof.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10538080A JPS5729820A (en) | 1980-07-31 | 1980-07-31 | Dog clutch apparatus |
| GB8123084A GB2081822B (en) | 1980-07-31 | 1981-07-27 | Positive clutch |
| FR8114976A FR2487934B1 (en) | 1980-07-31 | 1981-07-31 | CLUTCH CLUTCH FOR MOTORCYCLE |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10538080A JPS5729820A (en) | 1980-07-31 | 1980-07-31 | Dog clutch apparatus |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2114368A Division JPH03148391A (en) | 1990-04-30 | 1990-04-30 | Saddle type vehicle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5729820A JPS5729820A (en) | 1982-02-17 |
| JPS6122176B2 true JPS6122176B2 (en) | 1986-05-30 |
Family
ID=14406067
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10538080A Granted JPS5729820A (en) | 1980-07-31 | 1980-07-31 | Dog clutch apparatus |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPS5729820A (en) |
| FR (1) | FR2487934B1 (en) |
| GB (1) | GB2081822B (en) |
Families Citing this family (22)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS601427A (en) * | 1983-06-15 | 1985-01-07 | Daikin Mfg Co Ltd | Power switching device for vehicle and the like for industrial machine |
| JPS6158736U (en) * | 1984-08-29 | 1986-04-19 | ||
| JPS61273954A (en) * | 1985-05-30 | 1986-12-04 | ダイセル化学工業株式会社 | Flame-retardant laminated board |
| JPS6225361U (en) * | 1985-07-30 | 1987-02-16 | ||
| US5052535A (en) * | 1987-08-17 | 1991-10-01 | Eaton Corporation | Positive clutch structure |
| JPH01206138A (en) * | 1988-02-10 | 1989-08-18 | Honda Motor Co Ltd | Transmission for automobile |
| JPH03148391A (en) * | 1990-04-30 | 1991-06-25 | Honda Motor Co Ltd | Saddle type vehicle |
| DE19624774C2 (en) * | 1996-06-21 | 2000-06-08 | Blw Praezisionsschmiede Gmbh | Clutch teeth in a manual transmission |
| DE19624772C2 (en) * | 1996-06-21 | 2000-06-29 | Blw Praezisionsschmiede Gmbh | Claw teeth for manual transmissions or the like |
| JP4542809B2 (en) * | 2004-04-23 | 2010-09-15 | 株式会社イケヤフォ−ミュラ | Torque interrupting device |
| US20060027434A1 (en) | 2004-08-04 | 2006-02-09 | Capito Russell T | Positive clutch with staggered teeth height |
| FR2887604B1 (en) * | 2005-06-23 | 2007-07-27 | Renault Sas | CLAMP ARRANGEMENT FOR A CLUTCH GEARBOX |
| JP2007120723A (en) * | 2005-10-31 | 2007-05-17 | Ikeya Formula Kk | Torque interrupter |
| JP4781305B2 (en) * | 2007-03-29 | 2011-09-28 | 本田技研工業株式会社 | Dog clutch structure of continuously meshing gear transmission |
| JP4998728B2 (en) | 2007-09-28 | 2012-08-15 | 本田技研工業株式会社 | Twin clutch transmission |
| JP4998729B2 (en) * | 2007-09-28 | 2012-08-15 | 本田技研工業株式会社 | Twin clutch transmission |
| US7946403B2 (en) * | 2008-03-04 | 2011-05-24 | Honeywell International Inc. | Mechanical disconnect dual-sided interlocking teeth |
| JP5557567B2 (en) * | 2010-03-23 | 2014-07-23 | 本田技研工業株式会社 | Gearbox for internal combustion engine |
| DE102010042799A1 (en) * | 2010-10-22 | 2012-04-26 | Zf Friedrichshafen Ag | Positive switching element |
| CN102155536B (en) * | 2011-04-15 | 2014-04-16 | 力帆实业(集团)股份有限公司 | Engine shifting mechanism |
| JP2015175397A (en) * | 2014-03-13 | 2015-10-05 | 大岡技研株式会社 | Dog clutch and speed change gear |
| IT201700031648A1 (en) * | 2017-03-22 | 2018-09-22 | Piaggio & C Spa | TRANSMISSION CHANGE FOR A MOTOR WHEEL AND ITS MOTORCYCLE THAT INCLUDES SUCH TRANSMISSION CHANGE |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4527134Y1 (en) * | 1968-04-20 | 1970-10-21 |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR494403A (en) * | 1918-11-09 | 1919-09-09 | Serge Kousminsky | Constant mesh gear shifting device |
| CH82113A (en) * | 1918-11-23 | 1920-01-16 | Serge Kousminsky | Clutch device |
| GB328726A (en) * | 1929-03-05 | 1930-05-08 | Maunsell Bowers Jackson | Improvements in or relating to jaw or claw clutches suitable for variable speed gearing |
| GB334649A (en) * | 1929-06-28 | 1930-09-11 | Harold Raymond Morgan | Improved clutch mechanism |
| GB542439A (en) * | 1940-06-05 | 1942-01-09 | Chrysler Corp | Improvements in or relating to power transmissions for driving vehicles |
| FR938769A (en) * | 1943-02-13 | 1948-10-25 | Bendix Aviat Corp | Clutch suitable for application to aircraft autopilot devices |
| CH316497A (en) * | 1949-10-14 | 1956-10-15 | Tunica Ag | Disengageable coupling device of two coaxial rotating elements |
| JPS5136135Y2 (en) * | 1971-05-15 | 1976-09-04 | ||
| JPS6024987Y2 (en) * | 1977-10-27 | 1985-07-26 | ヤマハ発動機株式会社 | dog clutch |
-
1980
- 1980-07-31 JP JP10538080A patent/JPS5729820A/en active Granted
-
1981
- 1981-07-27 GB GB8123084A patent/GB2081822B/en not_active Expired
- 1981-07-31 FR FR8114976A patent/FR2487934B1/en not_active Expired
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4527134Y1 (en) * | 1968-04-20 | 1970-10-21 |
Also Published As
| Publication number | Publication date |
|---|---|
| FR2487934A1 (en) | 1982-02-05 |
| GB2081822B (en) | 1984-05-10 |
| GB2081822A (en) | 1982-02-24 |
| FR2487934B1 (en) | 1987-07-03 |
| JPS5729820A (en) | 1982-02-17 |
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