JPH03135833A - Structure of clutch attaching portion for transmission device - Google Patents
Structure of clutch attaching portion for transmission deviceInfo
- Publication number
- JPH03135833A JPH03135833A JP1274276A JP27427689A JPH03135833A JP H03135833 A JPH03135833 A JP H03135833A JP 1274276 A JP1274276 A JP 1274276A JP 27427689 A JP27427689 A JP 27427689A JP H03135833 A JPH03135833 A JP H03135833A
- Authority
- JP
- Japan
- Prior art keywords
- clutch
- transmission
- clutch housing
- friction plate
- gear
- 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.)
- Granted
Links
- 230000005540 biological transmission Effects 0.000 title claims abstract description 78
- 239000003921 oil Substances 0.000 description 7
- 230000000994 depressogenic effect Effects 0.000 description 4
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、多板式の摩擦クラッチを設けると共に、この
摩擦クラッチを構成するクラッチハウジングに伝動用ギ
アを一体回転可能に備えてある伝動装置のクラッチ取付
部構造に関する。[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to a transmission device which is provided with a multi-plate friction clutch and has a transmission gear rotatably integrated with a clutch housing constituting the friction clutch. Regarding clutch mounting structure.
上記伝動装置において、従来、例えば実開昭６３−１８
２９３１号公報に示されるように、クラッチハウジング
に断接される方の摩擦板が取付られているスリーブの支
軸にクラッチハウジングが取付けられていた。すなわち
、クラッチハウジングをスリーブ支軸が支持するように
なっている。In the above-mentioned transmission device, conventionally, for example,
As shown in Japanese Patent No. 2931, a clutch housing was attached to a support shaft of a sleeve to which a friction plate that is connected and disconnected to the clutch housing was attached. That is, the clutch housing is supported by the sleeve support shaft.
従来、クラッチハウジングがスリーブ支軸に対して傾斜
することの抑制を図ると、スリーブ支軸による支持スパ
ンが長くなるように、クラッチハウジングのスリーブ支
軸に外嵌するボス部の軸芯方向長さを長くする必要があ
り、またクラッチハウジングには摩擦板取付けのための
ハウジング部を前記ボス部と回転軸芯方向に位置する状
態で備えさせる必要があることから、クラッチハウジン
グの回転軸芯方向での長さが長くなると共に、この長尺
化のために大型化したクラッチハウジングの収納ができ
るようにミッションケースも大型化せねばならない不都
合があった。Conventionally, in order to prevent the clutch housing from inclining with respect to the sleeve support shaft, the length in the axial direction of the boss portion that fits onto the sleeve support shaft of the clutch housing is increased so that the support span by the sleeve support shaft becomes longer. It is necessary to increase the length of the clutch housing, and the clutch housing needs to be provided with a housing part for attaching the friction plate, which is located in the direction of the rotational axis of the clutch housing. As the length of the transmission case increases, the transmission case also has to be increased in size to accommodate the larger clutch housing due to the increased length.
本発明の目的は、クラッチハウジングの傾斜抑制が小型
化を図りながらできるようにすることにある。An object of the present invention is to suppress the inclination of the clutch housing while reducing the size of the clutch housing.
本発明による伝動装置のクラッチ取付部構造にあっては
、目的達成のために、前記クラッチハウジングの前記伝
動用ギアに対して摩擦板取付部とは反対側に位置する箇
所にベアリング取付筒部を備えさせ、このベアリング取
付筒部に付設のベアリングと、前記摩擦板取付部に外嵌
する筒ブシュとを介して回転自在に支持される状態でミ
ッションケースに取付けてある。In order to achieve the purpose of the clutch mounting part structure of the transmission device according to the present invention, a bearing mounting cylinder part is provided at a location of the clutch housing on the opposite side of the friction plate mounting part with respect to the transmission gear. The transmission case is rotatably supported via a bearing attached to the bearing mounting cylindrical portion and a cylindrical bushing externally fitted to the friction plate mounting portion.
前記筒ブシュは単一部品であってもよいのであるが、油
路形成用貫通孔を有する内筒ブシュと外筒ブシュとで形
成すれば有利である。Although the cylindrical bushing may be a single component, it is advantageous to form it with an inner cylindrical bushing and an outer cylindrical bushing having a through hole for forming an oil passage.
ミッションケースに支持されるように取付ける支持専用
部分としてのベアリング取付部の回転軸芯方向長さを従
来のボス部長さより小に形成しても、ミッションケース
がクラッチハウジングをベアリング取付部と摩擦板取付
部の両箇所にて支持することから、支持スパン長さを従
来の支持スパン長さと同一またはそれより長いようにす
ることが可能となる。Even if the length of the bearing mounting part, which is a support-only part that is installed to be supported by the transmission case, is smaller than the length of the conventional boss part, the mission case does not allow the clutch housing to be attached to the bearing mounting part and the friction plate mounting part. Since the support is provided at both locations, it is possible to make the support span length the same as or longer than the conventional support span length.
筒ブシュを外筒ブシュと油路付き内筒ブシュとで作成す
れば、外筒ブシュと内筒ブシュの間で相対回動するよう
にし、そして、クラッチ人り圧のために油がクラッチハ
ウジング内から摩擦板取付部の摩擦板係止用切欠き、内
筒ブシュの油路を通して内筒ブシュと外筒ブシュの間に
供給されるようにし、その割には、内筒ブシュには貫通
孔不在部がブシュの周方向に全周にわたって連続する環
状状態で形成され、この環状孔不在部のために、内筒ブ
シュの貫通孔周囲のエツジ作用によるブシュ摩滅が発生
しにくい状態に両ブシュが接触するようにすることが可
能になる。すなわち、クラッチハウジングやミ、ソショ
ンケースに摩滅や焼付きが生じにくいようにし、しかも
、ブシュ自体の摩滅や焼付きも生じにくいようにするこ
とが可能になる。If the cylindrical bushing is made of an outer cylindrical bushing and an inner cylindrical bushing with an oil passage, relative rotation will occur between the outer cylindrical bushing and the inner cylindrical bushing, and oil will flow inside the clutch housing due to the clutch pressure. The oil is supplied between the inner bushing and the outer bushing through the friction plate locking notch in the friction plate mounting part and the oil passage in the inner bushing.However, there is no through hole in the inner bushing. The part is formed in an annular state that continues all around the circumferential direction of the bushing, and because of this annular hole-free part, both bushes are in contact with each other in a state where it is difficult for the bushes to be worn out due to the edge action around the through-hole of the inner cylinder bushing. It becomes possible to do so. That is, it is possible to prevent the clutch housing, the clutch housing, and the solution case from being easily worn out or seized, and also to prevent the bushing itself from being easily worn out or seized.
クラッチハウジングの支持スパンを長くし、クラッチハ
ウジングとスリーブの軸芯ずれが発生しにくくてクラッ
チがスムーズに作動すると共に伝動を確実にする信頼性
の高いものにすることが可能になった。By increasing the support span of the clutch housing, misalignment between the clutch housing and sleeve is less likely to occur, allowing the clutch to operate smoothly and ensuring transmission with high reliability.
しかも、クラッチハウジングの回転軸芯方向長さを極力
小にし、クラッチハウジングの小型化を図って伝動装置
をコンパクトに得ることが可能になった。Moreover, the length of the clutch housing in the direction of the rotational axis is minimized, and the clutch housing is made smaller, thereby making it possible to obtain a compact transmission device.
筒ブシュを内外側ブシュで作成することにより、クラッ
チハウジング及びミッションケースのみならずブシュ自
体をも摩滅したり、しにくいように保護して耐久性の優
れたものにすることができる。By making the cylindrical bushing with inner and outer bushings, not only the clutch housing and transmission case but also the bushing itself can be protected from wear and tear, making it highly durable.
次に実施例を示す。 Next, examples will be shown.
第１図に示すように、エンジン出力を、中立を挾んで前
進側と後進側に切換え可能な油圧式無段変速装置（Ｍｌ
）及び入力軸（１）を介してミッションケース（２）に
伝達し、そして、入力軸（１）の回動力を、シフトギア
部材（３）の摺動操作によって３段に切換え可能な走行
用副変速装置（Ｍ２）に伝達すると共に、この走行用副
変速装置（Ｍ２）の回転出力を機体操向装置（Ａ）を介
して左右のクローラ式走行装置（４）、（４）夫々のク
ローラ駆動軸（５）に伝達するように構成して、コンパ
イン用の走行用伝動構造を構成しである。As shown in Figure 1, a hydraulic continuously variable transmission (Ml
) and the input shaft (1) to the transmission case (2), and the rotational force of the input shaft (1) can be switched to three stages by sliding the shift gear member (3). In addition to transmitting the rotational output of the auxiliary transmission for traveling (M2) to the transmission (M2), the rotational output of the traveling sub-transmission (M2) is transmitted to the left and right crawler type traveling devices (4), (4), respectively, through the aircraft direction device (A). It is configured to transmit data to the shaft (5), thereby configuring a traveling transmission structure for a compine.
機体操向装置（Ａ）を構成するに、左右走行装置（４）
、 （４）の夫々に対して第１図及び第２図に示すよう
に構成しである。The left and right traveling device (4) constitutes the aircraft direction device (A).
, (4) are constructed as shown in FIGS. 1 and 2.
すなわち、ミッションケース（２）に支軸（６）を介し
て支持されるように取付けた前進伝動ギア（７）を、走
行用副変速装置（Ｍ２）の出力軸ギア（８）に直接に咬
合させることによって常に支軸（６）の軸芯（Ｐ）の周
りで回動駆動されるように構成し、支軸（６）の一端側
に前記軸芯（Ｐ）の周りで回動するように配置した後進
伝動ギア（９）を逆転伝動ギア機構（１０）を介して走
行用副変速装置（Ｍ２）の出力軸ギア（１１）に連動さ
せることによって常に前進伝動ギア（７）と同一の軸芯
周りで前進伝動ギア（７）とは逆の回転方向に回動する
よう駆動されるように構成すると共に、支軸（６）の前
進伝動ギア（７）と後進伝動ギア（９）の間に位置する
箇所に伝動ギア部材（１２）を相対回動及び摺動自在に
取付けてある。伝動ギア部材（１２）にクラッチギア部
（１３）を前進伝動ギア（７）のボス部ギアに係脱する
ように形成して備えさせることにより、前進伝動ギア（
７）から伝動ギア部材（１２）に両者の咬合によって回
動力伝達するように、かつ、伝動ギア部材（１２）の摺
動に伴って入り切り変化するように前進用クラッチ（Ｆ
Ｃ）を構成しである。後進用伝動ギア（９）にクラッチ
ハウジング（１４）を一体部品に形成することによって
一体に回動するように備えると共に、伝動ギア部材（１
２）に一体形成のために共に摺動するように備えさせた
筒形出力部材（１５）をクラッチハウジング（１４）の
内部に同芯状に配置し、そして、クラッチハウジング（
１４）と出力部材（１５）の間に複数枚の摩擦板（１６
）・・を有したクラッチ本体を設けると共に、クラッチ
操作部（１７）をクラッチ本体に押圧作用したり作用解
除するように形成して伝動ギア部材（１２）に備えさせ
ることにより、後進伝動ギア（９）の回動力が伝動ギア
部材（１２）に摩擦伝達されるように、かつ、伝動ギア
部材（１２）の摺動に伴って入り切り変化するように多
板式の後進用摩擦クラッチ（ＲＣ）を構成しである。伝
動ギア部材（１２）はギア伝動機構（１８）を介してク
ローラ駆動軸（５）に連動すると共に摺動如何にかかわ
らずギア伝動機構（１８）のギア（１８ａ）との咬合を
維持するように形成しであること、及び、クラッチギア
部（１３）及びクラッチ操作部（１７）を一体に摺動す
るように備えていることにより、走行装置（４）に連動
されたままで軸芯（Ｐ）の方向に摺動して前進用クラッ
チ（ＦＣ）と後進用摩擦クラッチ（ＲＣ）をいずれもが
切りになると共にいずれか一方のみが入りになる状態に
操作するように構成しである。また、伝動ギア部材（１
２）は出力部材（１５）に作用させである前進付勢スプ
リング（１９）によって前進用クラッチ入り操作位置に
摺動付勢されるように構成すると共に、揺動フォーク（
２０）、フォーク支軸（２１）、第３図に示す如き揺動
リンク（２２）及び操作ワイヤ（２３）を介して操向ペ
ダル（２４）により後進用クラッチ入り側に人為操作す
るように構成しである。That is, the forward transmission gear (7) attached to the mission case (2) so as to be supported via the support shaft (6) is directly engaged with the output shaft gear (8) of the auxiliary transmission for traveling (M2). The structure is such that the support shaft (6) is always rotated around the axis (P) by rotating the support shaft (6). By interlocking the reverse transmission gear (9) arranged in It is configured to be driven to rotate in the opposite rotational direction to the forward transmission gear (7) around the axis, and the forward transmission gear (7) and the reverse transmission gear (9) of the support shaft (6). A transmission gear member (12) is attached to a location located between the two so as to be relatively rotatable and slidable. By forming the clutch gear part (13) in the transmission gear member (12) so as to engage with and disengage from the boss gear of the forward transmission gear (7), the forward transmission gear (
7) to the transmission gear member (12) by engagement between the two, and the forward clutch (F
C). The clutch housing (14) is formed as an integral part in the reverse transmission gear (9) so that the clutch housing (14) rotates together with the transmission gear member (1).
2) is arranged concentrically inside the clutch housing (14) with a cylindrical output member (15) provided to slide together for integral formation;
A plurality of friction plates (16) are arranged between the output member (14) and the output member (15).
)..., and the transmission gear member (12) is provided with a clutch operating portion (17) formed to press or release the clutch body, thereby making it possible to operate the reverse transmission gear ( A multi-disc reverse friction clutch (RC) is installed so that the rotational force of 9) is frictionally transmitted to the transmission gear member (12) and is turned on and off as the transmission gear member (12) slides. It is composed. The transmission gear member (12) is interlocked with the crawler drive shaft (5) via the gear transmission mechanism (18), and maintains engagement with the gear (18a) of the gear transmission mechanism (18) regardless of whether it is slid or not. By forming the clutch gear part (13) and the clutch operating part (17) so as to slide together, the shaft center (P ) to operate the forward clutch (FC) and reverse friction clutch (RC) so that both are disengaged and only one of them is engaged. In addition, a transmission gear member (1
2) is configured to be slidably biased to the forward clutch engaged operating position by a forward biasing spring (19) acting on the output member (15), and the swing fork (
20), configured to be manually operated to the reverse clutch engagement side by a steering pedal (24) via a fork support shaft (21), a swing link (22) as shown in FIG. 3, and an operation wire (23). It is.
要するに、左右一対の操向ペダル（２４）、 （２４）
のいずれもを直進位置（Ｓ）に操作すると、一対の前進
用クラッチ（ＦＣ）、 （ＦＣ）のいずれもが入りにな
って前進伝動ギア（７）の回動力を一方の伝動ギア部材
（１２）によりギア伝動機構（１８）を介して一方のク
ローラ駆動軸（５）に、かつ、他方の伝動ギア部材（１
２）によりギア伝動機構（１８）を介して他方のクロー
ラ駆動軸（５）に夫々伝達し、機体が直進前進するよう
に左右走行装置（４）、（４）を前進側に駆動するので
ある。そして、一方の操向ペダル（２４）のみを第１旋
回位置（Ｔ１）に踏込み操作すると、その方の前進用ク
ラッチ（ＰＣ）及び後進用クラッチ（ＲＣ）が切りにな
って一方のクローラ駆動軸（５）に対する伝動が停止し
、踏込み操作した操向ペダル（２４）の位置する側に向
かって機体が旋回走行するように左右走行装置（４）。In short, a pair of left and right steering pedals (24), (24)
When both of them are operated to the straight forward position (S), both of the pair of forward clutches (FC), (FC) are engaged, and the rotational force of the forward transmission gear (7) is transferred to one transmission gear member (12). ) to one crawler drive shaft (5) via a gear transmission mechanism (18), and the other transmission gear member (1
2), the power is transmitted to the other crawler drive shaft (5) through the gear transmission mechanism (18), and drives the left and right traveling devices (4), (4) forward so that the aircraft moves straight forward. . When only one steering pedal (24) is depressed and operated to the first turning position (T1), the forward clutch (PC) and reverse clutch (RC) of that side are disengaged, and one crawler drive shaft is (5) so that the transmission to the left and right traveling device (4) is stopped and the aircraft turns toward the side where the depressed steering pedal (24) is located.
（４）の一方を遊転状態にしながら他方を前進側に駆動
するのである。そして、一方の操向ペダル（２４）のみ
を第２旋回位置（Ｔ２）にさらに踏込み操作すると、そ
の方の後進用クラッチ（ＲＣ）が入りになって後進伝動
ギア（９）の回動力を伝動ギア部材（１２）によりギア
伝動機構（１８）を介して一方のクローラ駆動軸（５）
に伝達し、踏込み操作した操向ペダル（２４）の位置す
る側に機体が信地旋回するように左右走行装置（４）、
（４）の一方を後進側に、かつ、他方を前進側に夫々
駆動するのである。(4) While one is in an idle state, the other is driven forward. When only one steering pedal (24) is further depressed to the second turning position (T2), that side's reverse clutch (RC) is engaged and transmits the rotational force of the reverse transmission gear (9). One crawler drive shaft (5) is connected to one crawler drive shaft (5) via a gear transmission mechanism (18) by a gear member (12).
a left-right traveling device (4), so that the aircraft turns to the side where the depressed steering pedal (24) is located;
One of (4) is driven in the reverse direction, and the other is driven in the forward direction.
一対の後進用クラッチ（ＲＣ）、 （ＲＣ）の夫々にお
いて、クラッチハウジング（１４）の摩擦板取付部（１
４ａ）を該箇所に外嵌する筒ブシュ（２５）を介してミ
ッションケース（２）の第１クラッチ支持部（２ａ）に
内嵌させ、そして、クラッチハウジング（１４）の後進
伝動ギア（９）に対して摩擦板取付部（１４ａ）とは反
対側に備えさせたベアリング取付部（１４ｂ）を該箇所
に外嵌するボール式ベアリング（２６）を介してミッシ
ョンケース（２）の第２クラッチ支持部（２ｂ）に内嵌
させることにより、クラッチハウジング（１４）をミッ
ションケース（２）に筒ブシュ（２５）とベアリング（
２６）を介して回転自在に支持されるように取付けてあ
る。つまり、摩擦板取付部（１４ａ）に筒ブシュ（２５
）を介してミッションケース（２）が支持作用し、ベア
リング取付部（１４ｂ）にベアリング（２６）を介して
ミッションケース（２）が支持作用することと、摩擦板
取付部（１４ａ）とベアリング取付部（１４ｂ）が前記
配置関係に在ることのために、クラッチハウジング（１
４）がその回転軸芯方向での長さの割には支持スパンが
長くて出力部材（１５）に対して傾斜しにくい状態でミ
ッションケース（２）によって支持されるように配慮し
である。In each of the pair of reverse clutches (RC), (RC), the friction plate mounting portion (1) of the clutch housing (14) is
4a) is fitted into the first clutch support part (2a) of the transmission case (2) via the cylindrical bushing (25) which is fitted externally to the part, and then the reverse transmission gear (9) of the clutch housing (14) is fitted. The second clutch of the mission case (2) is supported via a ball bearing (26) which is fitted onto a bearing mounting part (14b) provided on the opposite side of the friction plate mounting part (14a). By fitting the clutch housing (14) into the transmission case (2), the cylindrical bushing (25) and the bearing (
26) so as to be rotatably supported. In other words, the cylindrical bushing (25
), the transmission case (2) acts as a support via the bearing attachment part (14b), and the transmission case (2) acts as a support act on the bearing attachment part (14b) through the bearing (26), and the friction plate attachment part (14a) and the bearing attachment part. Because the portion (14b) is in the above arrangement, the clutch housing (14b)
4) has a long support span relative to its length in the rotational axis direction, so that it is supported by the transmission case (2) in a state where it is unlikely to tilt relative to the output member (15).
筒ブシュ（２５）は摩擦板取付部（１４ａ）に圧入によ
って一体に回動するように外嵌する内筒ブシュ（２５ａ
）と、この内筒ブシュ（２５ａ）に相対回動するように
外嵌する外筒ブシュ（２５ｂ）とによって作成しである
。内筒ブシュ（２５ａ）には第４図に示す如く周方向及
び軸芯方向の夫々に分散させた複数個の貫通孔（２７）
・・を備えてあると共に、これら貫通孔（２７）は、摩
擦板（１６）の複数の第５図の如き突部（１６ａ）・・
が摺動のみ可能に入り込むことによって摩擦板（１６）
がクラッチハウジング（１４）に一体回転及び摺動可能
に係止するように形成して、かつ、クラッチハウジング
（１４）の周方向に分散させて摩擦板取付部（１４ａ）
に備えてある複数の摩擦板係止用切欠き（２８）・・の
１つに連通ずる油路を形成するように配置すると共に形
成しである。The cylindrical bushing (25) is fitted with an inner cylindrical bushing (25a) that is press-fitted into the friction plate mounting portion (14a) so as to rotate together with the cylindrical bushing (25).
) and an outer bushing (25b) that is fitted onto the inner bushing (25a) so as to rotate relative to the inner bushing (25a). The inner cylinder bush (25a) has a plurality of through holes (27) distributed in the circumferential direction and the axial direction as shown in FIG.
..., and these through holes (27) are provided with a plurality of protrusions (16a) of the friction plate (16) as shown in FIG.
The friction plate (16) is inserted so that it can only slide.
Friction plate attachment portions (14a) are formed so as to be integrally rotatable and slidably engaged with the clutch housing (14), and are distributed in the circumferential direction of the clutch housing (14).
It is arranged and formed so as to form an oil passage communicating with one of the plurality of friction plate locking notches (28) provided in the.
つまり、摩擦板取付部（１４ａ）と第１クラッチ支持部
（２ａ）の間の相対回動が内筒ブシュ（２５ａ）と外筒
ブシュ（２５ｂ）の間で生じるように構成し、そして、
後進用クラッチ（ＲＣ）の入り作動時に、摩擦板押圧に
伴う操作力のために潤滑油が切欠き（２８）、及び、貫
通孔（２７）による油路を通してハウジング内から内筒
ブシュ（２５ａ）と外筒ブシュ（２５ｂ）の間に供給さ
れることが可能なように構成し、さらには、内筒ブシュ
（２５ａ）が貫通孔（２７）の存在しない部分によりブ
シュ全周にわたって連続して外筒ブシュ（２５ｂ）に接
触して貫通孔周囲のエツジ作用による外筒ブシュ（２５
ｂ）の摩滅を発生しにくくするように配慮することによ
り、摩擦板取付部（１４ａ）及び第１クラッチ支持部（
２ａ）の摩滅防止を図ると共にブシュ自体の摩滅抑制を
も図っている。That is, the structure is configured such that relative rotation between the friction plate mounting portion (14a) and the first clutch support portion (2a) occurs between the inner cylinder bushing (25a) and the outer cylinder bushing (25b), and
When the reverse clutch (RC) is engaged, lubricating oil flows from the inside of the housing to the inner cylinder bushing (25a) through the oil passage formed by the notch (28) and the through hole (27) due to the operating force accompanying the pressing of the friction plate. and the outer cylinder bushing (25b), and furthermore, the inner cylinder bushing (25a) is configured so that it can be supplied between the outer cylinder bushing (25b) and the outer cylinder bushing (25b), and furthermore, the inner cylinder bushing (25a) is continuously connected to the outside over the entire circumference of the bushing by the part where the through hole (27) does not exist. The outer cylinder bush (25b) is in contact with the cylinder bush (25b) due to the edge action around the through hole.
b) By taking measures to prevent wear and tear, the friction plate mounting portion (14a) and the first clutch support portion (
In addition to preventing wear of the bushing 2a), it is also intended to suppress wear of the bush itself.
尚、摩擦クラッチ（ＲＣ）を機体操向を可能にするため
に備えさせる伝動構造の他、単なる伝動断接を可能にす
るために備えさせる伝動構造、さらには、伝動対象を走
行装置以外とする各種伝動構造にも本発明は適用できる
。したがって、後進伝動ギア（９）を伝動用ギア（９）
と称する。In addition to the transmission structure that is equipped with a friction clutch (RC) to enable aircraft direction, there are also transmission structures that are equipped to simply connect and disconnect the transmission, and furthermore, transmission structures that are equipped with a friction clutch (RC) to enable the orientation of the aircraft, and furthermore, the transmission target is other than the traveling device. The present invention can also be applied to various transmission structures. Therefore, the reverse transmission gear (9) is replaced by the transmission gear (9).
It is called.
尚、特許請求の範囲の項に図面との対照を便利にする為
に符号を記すが、該記入により本発明は添付図面の構造
に限定されるものではない。Incidentally, although reference numerals are written in the claims section for convenient comparison with the drawings, the present invention is not limited to the structure shown in the accompanying drawings.
図面は本発明に係る伝動装置のクラッチ取付部構造の実
施例を示し、第１図は走行用伝動構造の断面図、第２図
は後進用伝動部の断面図、第３図は後進用操作系統図、
第４図はブシュの斜視図、第５図は第２図の■−Ｖ線断
面矢視図である。
（２）・・・・・・ミッションケース、（９）・・・・
・・伝動用ギア、（１４）・・・・・・クラッチハウジ
ング、（１４ａ）・・・・・・摩擦板取付部、（１４ｂ
）・・・・・・ベアリング取付部、（２５）・・・・・
・筒ブシュ、（２５ａ）・・・・・・内筒ブシュ、（２
５ｂ）・・・・・・外筒ブシュ、（２６）・・・・・・
ベアリング、（２７）・・・・・・貫通孔、（２８）・
・・・・・摩擦板係止用切欠き、（ＲＣ）・・・・・・
摩擦クラッチ。The drawings show an embodiment of the clutch mounting structure of the transmission device according to the present invention, FIG. 1 is a cross-sectional view of the transmission structure for traveling, FIG. 2 is a cross-sectional view of the reverse transmission section, and FIG. 3 is a cross-sectional view of the reverse transmission structure. System diagram,
FIG. 4 is a perspective view of the bushing, and FIG. 5 is a sectional view taken along the line ■-V in FIG. 2. (2)...Mission case, (9)...
...Transmission gear, (14)...Clutch housing, (14a)...Friction plate mounting part, (14b
)...Bearing mounting part, (25)...
・Cylinder bushing, (25a)...Inner cylinder bushing, (2
5b)...Outer cylinder bushing, (26)...
Bearing, (27)...Through hole, (28)
...Friction plate locking notch, (RC)...
friction clutch.
Claims (1)
の摩擦クラッチ（ＲＣ）を構成するクラッチハウジング
（１４）に伝動用ギア（９）を一体回転可能に備えてあ
る伝動装置のクラッチ取付部構造であって、前記クラッ
チハウジング（１４）の前記伝動用ギア（９）に対して
摩擦板取付部（１４ａ）とは反対側に位置する箇所にベ
アリング取付筒部（１４ｂ）を備えさせ、このベアリン
グ取付筒部（１４ｂ）に付設のベアリング（２６）と、
前記摩擦板取付部（１４ａ）に外嵌する筒ブシュ（２５
）とを介して回転自在に支持される状態でミッションケ
ース（２）に取付けてある伝動装置のクラッチ取付部構
造。 ２、前記筒ブシュ（２５）が前記摩擦板取付部（１４ａ
）に一体回転可能に外嵌する内筒ブシュ（２５ａ）と、
この内筒ブシュ（２５ａ）に外嵌する外筒ブシュ（２５
ｂ）とから成り、前記内筒ブシュ（２５ａ）に前記摩擦
板取付部（１４ａ）の摩擦板係止用切欠き（２８）に連
通する油路を形成する状態で貫通孔（２７）を備えてあ
る請求項１記載の伝動装置のクラッチ取付部構造。[Scope of Claims] 1. A transmission including a multi-disc friction clutch (RC) and a clutch housing (14) constituting the friction clutch (RC) with a transmission gear (9) rotatable integrally with the clutch housing (14). In the clutch mounting part structure of the device, a bearing mounting cylinder part (14b) is located at a location of the clutch housing (14) on the opposite side of the transmission gear (9) from the friction plate mounting part (14a). and a bearing (26) attached to this bearing mounting cylinder part (14b),
A cylindrical bushing (25) that fits onto the friction plate mounting portion (14a)
) A clutch mounting part structure of a transmission device that is rotatably supported through the transmission case (2). 2. The cylindrical bushing (25) is attached to the friction plate mounting portion (14a
);
An outer cylinder bush (25) that fits onto this inner cylinder bush (25a)
b), the inner cylindrical bushing (25a) is provided with a through hole (27) forming an oil passage communicating with the friction plate locking notch (28) of the friction plate mounting portion (14a); 2. A clutch mounting portion structure for a transmission device according to claim 1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1274276A JPH0832505B2 (en) | 1989-10-21 | 1989-10-21 | Clutch mounting structure of transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1274276A JPH0832505B2 (en) | 1989-10-21 | 1989-10-21 | Clutch mounting structure of transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03135833A true JPH03135833A (en) | 1991-06-10 |
| JPH0832505B2 JPH0832505B2 (en) | 1996-03-29 |
Family
ID=17539400
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1274276A Expired - Fee Related JPH0832505B2 (en) | 1989-10-21 | 1989-10-21 | Clutch mounting structure of transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0832505B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2004104451A1 (en) * | 2003-05-22 | 2004-12-02 | Yanmar Co., Ltd. | Axle supporting structure of working machine |
| EP1818570A1 (en) * | 2006-02-14 | 2007-08-15 | CRF Societa'Consortile per Azioni | Arrangement of an idler gear in a gear transmission |
| WO2012029953A1 (en) * | 2010-09-03 | 2012-03-08 | ヤンマー株式会社 | Transmission device for riding-type work vehicle |
| JP2013512829A (en) * | 2010-11-25 | 2013-04-18 | 金華職業技術学院 | Spin turn traveling transmission for rice field combine |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4519394B2 (en) * | 2002-07-25 | 2010-08-04 | 富士重工業株式会社 | Shaft support structure for continuously variable transmission |
-
1989
- 1989-10-21 JP JP1274276A patent/JPH0832505B2/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2004104451A1 (en) * | 2003-05-22 | 2004-12-02 | Yanmar Co., Ltd. | Axle supporting structure of working machine |
| CN100451396C (en) * | 2003-05-22 | 2009-01-14 | 洋马株式会社 | Axle supporting structure of working machine |
| EP1818570A1 (en) * | 2006-02-14 | 2007-08-15 | CRF Societa'Consortile per Azioni | Arrangement of an idler gear in a gear transmission |
| WO2012029953A1 (en) * | 2010-09-03 | 2012-03-08 | ヤンマー株式会社 | Transmission device for riding-type work vehicle |
| JP2012051531A (en) * | 2010-09-03 | 2012-03-15 | Yanmar Co Ltd | Traveling transmission device for riding type work vehicle |
| JP2013512829A (en) * | 2010-11-25 | 2013-04-18 | 金華職業技術学院 | Spin turn traveling transmission for rice field combine |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0832505B2 (en) | 1996-03-29 |
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| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |