JPS6229299Y2 - - Google Patents

Description

【考案の詳細な説明】 本考案は、トラクタにおける前後進変速や前進
での高低変速、等を多板式油圧クラツチの択一操
作によつて軽快に行えるようにした油圧クラツチ
変速装置の油圧配管構造に関し、詳しくは、入力
軸と出力軸との間に、多板式油圧クラツチを夫々
備えた一対の回転支軸を並列に支承し、前記回転
支軸の夫々に、前記多板式油圧クラツチに対する
クラツチ作動用油路とクラツチ潤滑用油路とを形
成して、制御バルブに設けたクラツチ作動用接続
部とクラツチ潤滑用接続部とに夫々連通接続し、
前記制御バルブの操作に基づいて択一的に連結状
態に切換えられた多板式油圧クラツチを介して前
記入力軸と出力軸とを連動連結するように構成し
てある油圧クラツチ変速装置の油圧配管構造に関
する。 冒記した油圧クラツチ変速装置の油圧配管構造
において、複数の多板式油圧クラツチの各回転支
軸に形成の油路（クラツチ作動用油路、クラツチ
潤滑用油路）にオイルを供給するに、従来は、特
開昭55−110624号公報に開示の技術に示される如
く、前記各回転支軸の一端側を支承するケース壁
に、前記各回転支軸の油路に連通する油路を形成
して、そのケース壁に形成の内部油路を介して前
記各回転支軸の油路にオイルを供給すべく構成し
たものがあつた。 かかる油圧配管構造によれば、装置全体をコン
パクトに構成できる利点があるが、ケース壁に、
各回転支軸の油路に連通する油路を形成する場合
には、ケースを分割して油路を形成しなければな
らないことから、ケースの成形時に油路を形成し
ておかねばならず、ケースの鋳型が高くつき、ま
た、そのケースの合せ面を高精度に仕上げて油漏
れが生じないようにしなければならず、高度な気
密性が要求されるとともに、各回転支軸の油路に
対してポンプからのオイルを択一的に供給する為
の制御バルブをケース壁に内装して設けたりしな
ければならないので、全体として、複数の多板式
油圧クラツチの各回転支軸に形成の油路に対する
オイル供給構造が高価につくという欠点がある。 これに対して、例えば特公昭35−7302号公報に
記載の伝動機構に使用されているような油圧継手
を回転支軸の軸端に嵌入装着し、この油圧継手と
制御バルブとをパイプで接続する油圧配管構造に
よれば、構造自体が比較的単純であるので、安価
に製作できる利点があるものの、油圧継手と制御
バルブとを接続するパイプが煩雑に錯綜すること
となり、パイプの接続作業に手間がかかるととも
に装置全体が大型化してしまう欠点がある。 本考案は上記実状に鑑みて為されたものであつ
て、油圧継手を使用することによつて、安価に製
作できる利点を生かしながら、パイプの取付構造
を単純化することによつて、パイプの接続作業が
正確かつ容易に行え、しかも、装置全体を比較的
コンパクトに構成できる油圧クラツチ変速装置の
油圧配管構造を提供することを目的とする。 上記目的を達成する為の本考案の特徴構成は、
冒記した油圧クラツチ変速装置の油圧配管構造に
おいて、前記一対の回転支軸を前記入力軸を挾ん
で互いに上下に位置させて支承し、一端が夫々前
記クラツチ作動用油路とクラツチ潤滑用油路との
いずれにも連通可能に開口され、かつ、他端が
夫々回転支軸の軸芯を通る面に対して左右に振分
け配置したパイプ接続口に開口される一対の内部
油路を形成した同一形状の油圧継手を、前記回転
支軸の入力軸を挾む軸端の夫々に嵌入装着すると
ともに、前記両油圧継手を、その夫々に備えさせ
たパイプ接続口が前記入力軸の軸芯と両回転支軸
の軸芯とを結ぶ線分に対して左右に振分け配置さ
れ、かつ、前記入力軸の径方向において、回転支
軸の軸芯よりも外方側に位置する姿勢でケースに
固定し、前記線分を挾んで左右一側方に位置する
上下２個のパイプ接続口に開口する内部油路をク
ラツチ作動用油路に連通させ、他側方に位置する
上下２個のパイプ接続口に開口する内部油路をク
ラツチ潤滑用油路に連通させ、更に、前記左右一
側方に位置するパイプ接続口の上方にクラツチ作
動用接続部を位置させ、前記他側方に位置するパ
イプ接続口の上方にクラツチ潤滑用接続部を位置
させる姿勢で制御バルブを取付け、前記左右一側
方に位置するパイプ接続口とクラツチ作動用接続
部とをクラツチ作動用パイプを介して接続し、前
記他側方に位置するパイプ接続口とクラツチ潤滑
用接続部とをクラツチ潤滑用パイプを介して接続
してある点にあり、かかる構成から次の作用効果
を奏する。 すなわち、多板式油圧クラツチの回転支軸に油
圧継手を装着して、油圧ポンプに接続の制御バル
ブからパイプを介して各回転支軸に形成の油路、
つまり、クラツチ作動用油路とクラツチ潤滑用油
路にオイルを供給すべく構成したものであるか
ら、安価な配管構造を利用して各回転支軸の油路
にオイルを供給することができ、又、油圧継手や
パイプはシール材を使つて容易に気密性をはかる
ことができることから、高精度な製作加工が要求
されず、さらに、パイプによる配管構造にするこ
とによつて、バルブをケース壁内に内装する必要
がなく、バルブの組付け作業が容易に行える。 そして、このように、複数の多板式油圧クラツ
チの回転支軸に形成の油路に対するオイル供給構
造を安価な配管構造を利用して行うものでありな
がら、本考案は特に下記乃至の作用効果を奏
する。 回転支軸の軸端に嵌入装着される油圧継手を
いずれの回転支軸に対しても使用できる同一形
状の共通部材としたので、油圧継手製作上のコ
ストを低廉化できる。 油圧継手に備えさせたパイプ接続口を、いず
れの回転支軸に対しても、入力軸の径方向にお
いて、回転支軸の軸芯よりも外方側に位置する
姿勢で油圧継手をケースに固定するものである
から、制御バルブと上下の油圧継手を迂回して
４本のパイプにて接続する場合に、これら内部
油路とパイプとの接続は入力軸から充分離れた
位置で行われることとなり、その結果、パイプ
組付作業が入力軸の外側において容易に行える
ようになつた。 入力軸と軸芯と両回転支軸の軸芯とを結ぶ線
分に対して、制御バルブに設けられるクラツチ
作動用接続部並びにクラツチ潤滑用接続部と、
各油圧継手に設けられる一対のパイプ接続口と
を左右に振分け、前記線分に対して一方側に位
置する各パイプ接続口とその上方に位置するク
ラツチ作動用接続部とをパイプで接続し、他方
側に位置する各パイプ接続口とその上方に位置
するクラツチ潤滑用接続部とをパイプで接続す
るものであるから、上下左右においてクロス配
管となるのを回避でき、配管接続を誤るおそれ
がない上に配管作業が容易に行える。 更に、クロス配管を回避することによつて、
油圧継手を用いながらも、装置全体をコンパク
トに構成できる。 以下、本考案の実施例を図面に基づいて説明す
る。 図は農用トラクタの伝動構造を示すものであつ
て、エンジン１、主クラツチハウジング２、ミツ
シヨンケース３がこの順序で直列に連結され、エ
ンジン出力をミツシヨンケース３内で適当に変速
して後部両側に突設した後輪駆動軸４，４と後方
に突設したPTO軸５に伝達すべく構成されてい
る。そして、ミツションケース３の前部にはシフ
トギヤ６，７の選択シフトによつて４段の変速を
行う走行系の主ギヤ変速機構８が装備されるとと
もに、ケース後部にはシフトギヤ９ａ，９ｂのシ
フトによつて２段の変速を行う走行系の副ギヤ変
速機構１０と左右後輪駆動軸４，４に対する差動
変速機構１１が装備されている。又、ミツシヨン
ケース３の前後中間にはシフトギヤ１２のシフト
によつて、２段の変速を行うPTO系のギヤ変速
機構１３が装備されている。 又、主クラツチハウジング２の後壁２ａとミツ
シヨンケース３の前壁３ａとの間には中間伝動室
１４が形成されていて、ミツシヨンケース前壁３
ａからこの中間伝動室１４内に走行系の入力軸１
５が突入されるとともに、主クラツチ１６を介し
て動力断続される原動軸１７が中間伝動室１４内
に突入され、且つ中間伝動室１４の上下には油圧
クラツチ１８，１９を装備した回転支軸２０，２
１が主クラツチハウジング後壁２ａとこれに取付
けたブラケツト２２を介して支承されている。 上位の油圧クラツチ１８は、支軸２０に固着さ
れた駆動ドラム２３内に装備したピストン２４を
圧油にて右方にシフトすることによつて前記駆動
ドラム２３と支軸２０に遊嵌された受動ドラム２
５との間に介装した摩擦板２６…，２７…を圧接
させて両ドラム２３，２５間の摩擦動力伝達を行
い、ピストン２４への油圧解除によつてピストン
２４を内装スプリング２８で左方へ復元シフトす
ることによつて摩擦動力伝達を解除するよう構成
されたものであり、前記駆動ドラム２３に形成し
たギヤ２９が前記原動軸１７の軸端に固着のギヤ
３０に咬合されている。そして、受動ドラム２５
に一体成形したギヤ３１が中間伝動室１４内に別
途支軸３２を介して遊転支承したアイドルギヤ３
３を介して前記走行系の入力軸１５の軸端に固着
したギヤ３４に咬合連動されている。又、下位の
油圧クラツチ１９は、前記油圧クラツチ１８と同
様に駆動ドラム３５、受動ドラム３６、ピストン
３７、摩擦板３８…，３９…、及び復帰用スプリ
ング４０からなり、駆動ドラム３５に形成したギ
ヤ４１原動軸ギヤ３０に咬合されるときに、受動
ドラム３６に形成したギヤ４２が走行系入力軸ギ
ヤ３４に直接咬合されている。そして、下位の油
圧クラツチ１９が正転（前進）伝動用に、又、上
位の油圧クラツチ１８が逆転（後進）伝動用とさ
れている。 又、下位の回転支軸２１の後端はミツシヨンケ
ース３内においてPTO系の伝動軸４３にカツプ
リング連結されていて、両油圧クラツチ１８，１
９の入切に関係なく動力が伝達されるようになつ
ている。 前記両油圧クラツチ１８，１９への圧油供給及
び排油は各回転支軸２０，２１の内部油路４４，
４５を介して行われるとともに、両クラツチ１
８，１９の摩擦伝動箇所への潤滑油供給が別の内
部油路４６，４７を介して行われるものである。
そして、これら回転支軸２０，２１の前端は主ク
ラツチハウジング後壁２ａを通して主クラツチ室
４８内に突入され、その突入軸端が前記後壁２ａ
の前面にボルト止めされた油圧継手４９，５０に
夫々嵌入装着されている。又、主クラツチハウジ
ング２の上面には制御バルブ５１が取付けられて
いて、このバルブ５１に備えたクラツチ作動用接
続部５１Ａとクラツチ潤滑用接続部５１Ｂとから
主クラツチ室４８内に延出したパイプ５２，５
３，５４，５５が前記油圧継手４９，５０に形成
した内部油路４４…の開口端に設けたパイプ接続
口１０１，１０２に接続されて、制御バルブ５１
と前記各油路４４…が連通接続されている。 そしてこの場合、第５図に示すようにクラツチ
作動用油路４４，４５に対するパイプ５２，５３
は原動軸１７の横一側（図では左側）に設けられ
るとともに、クラツチ潤滑用油路４６，４７に対
するパイプ５４，５５は原動油の横他側（図では
右側）に設けられている。又、主クラツチハウジ
ング２には主クラツチ操作用レリーズ５６のシフ
トフオーク５７を固着した操作軸５８が横架支承
され、上部油圧クラツチ１８に対するパイプ５
２，５４がこ操作軸５８を囲繞するように迂回彎
曲させて配管されている。 つまり、原動軸１７の軸芯と各回転支軸２０，
２１の軸芯とを結ぶ線分に対して、一方側にクラ
ツチ作動用の配管構造を、他方側にクラツチ潤滑
用の配管構造を振分けて配置してある。 又、上下の油圧継手４９，５０は左右に深さの
異なる内部油路を有した同一のものが上下逆姿勢
で主クラツチハウジング後壁２ａに取付けられて
いて、上位の油圧継手４９においては両油路５
９，６０が回転支軸２０より上方にあり、且つ深
さの小さい左側の内部油路５９が前記クラツチ作
動用油路４４に、又、深さの大きい右側の内部油
路６０がクラツチ潤滑用油路４６に夫々連通接続
されている。これに対して上下反転して取付けら
れた下位の油圧継手４９においては、両油路６
１，６２が回転支軸２１より下方にあり、且つ深
さの小さい右側の内部油路６１がクラツチ潤滑用
油路４７に、又、深さの大きい左側の内部油路６
２がクラツチ作動用油路４５に夫々連通接続さ
れ、もつて、上記のようにクラツチ作動用のパイ
プ５２，５３とクラツチ潤滑用のパイプ５４，５
５が原動軸１７の左右に振分け配置されている。 又、下位の油圧継手５０とレリーズ５６との間
にレリーズ復帰用のバネ６３が張設されている。 第４図は前記油圧クラツチ１８，１９の作動用
油圧回路を示し、前記制御バルブ５１は、前後進
切換え用の３位置切換バルブ６４、クラツチ作動
油圧の立上り特性を制御するためのモジユレーテ
イングリリーフバルブ６５とモジユレーテイング
バルブ６６、各油圧クラツチ１８，１９内への潤
滑油供給用のリリーフバルブ６７、から構成され
ており、この制御バルブ５１のポンプポートがポ
ンプ６８に接続されたフロープライオリテイバル
ブ６９の流量制御ポートに接続されている。前記
３位置切換バルブ６４は手動レバーにて３位置に
回動操作されるロータリ型に構成されていて、中
立位置Ｎではポンプ６８からの圧油をモジユレー
テイングリリーフバルブ６５及びクラツチ潤滑用
リリーフバルブ６７を通じてタンクポートＴに排
油するとともに、リリーフ排油の一部をリリーフ
バルブ６７の上手から油路Ｌを介して両油圧クラ
ツチ１８，１９の摩擦伝動部に供給して摩擦面の
潤滑と冷却が行われる。又、前進位置Ｆもしくは
後進位置Ｒでは圧油を前進用油圧クラツチ１９へ
の油路ｆもしくは後進用油圧クラツチ１８への油
路ｒに供給するとともに、モジユレーテイングバ
ルブ６６への油路ｍにも供給して油圧クラツチ作
動圧の制御を行うようになつている。 前記モジユレーテイングリリーフバルブ６５
は、バネ７０で閉弁方向に付勢されるとともに、
このバネ７０の後端を支えるバネ受け７１がモジ
ユレーテイングバルブ６６のオリフイス７２を通
して供給される圧油によつて変位可能に構成され
ていて、前記オリフイス７２を通しての少量づつ
の圧油供給によつてバネ圧、つまりリリーフ作動
圧が漸次増大するようになつている。従つて、切
換バルブ６４を前進位置Ｆは後進位置Ｒに切換え
ると、前記のようにモジユレーテイングリリーフ
バルブ６５の作動圧が漸次的に増大するので選択
された油圧クラツチ１９又は１８への印加圧も漸
次的に増大し、衝撃のない滑らかなクラツチ入り
作動がもたらされる。 尚、実用新案登録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
本考案は添付図面の構造に限定されるものではな
い。 [Detailed description of the invention] The invention is based on a hydraulic piping structure for a hydraulic clutch transmission that allows a tractor to easily perform forward/reverse gear shifting, forward elevation/low gear shifting, etc. by selectively operating a multi-disc hydraulic clutch. More specifically, a pair of rotary shafts each having a multi-plate hydraulic clutch are supported in parallel between the input shaft and the output shaft, and each of the rotary shafts is provided with a clutch actuator for the multi-plate hydraulic clutch. forming an oil passage for oil supply and a oil passage for clutch lubrication, the oil passage being connected to a clutch actuation connection portion and a clutch lubrication connection portion provided on the control valve, respectively;
A hydraulic piping structure of a hydraulic clutch transmission configured to operatively connect the input shaft and the output shaft via a multi-plate hydraulic clutch that is selectively switched to a connected state based on the operation of the control valve. Regarding. In the hydraulic piping structure of the hydraulic clutch transmission mentioned above, conventional methods are used to supply oil to the oil passages (oil passages for clutch actuation, oil passages for clutch lubrication) formed on each rotating shaft of a plurality of multi-plate hydraulic clutches. As disclosed in the technique disclosed in Japanese Unexamined Patent Publication No. 55-110624, an oil passage communicating with the oil passage of each rotation support shaft is formed in a case wall supporting one end side of each rotation support shaft. In some cases, oil is supplied to the oil passages of the rotating shafts through internal oil passages formed in the case wall. This hydraulic piping structure has the advantage that the entire device can be configured compactly, but there are
When forming an oil passage that communicates with the oil passage of each rotating support shaft, the case must be divided to form the oil passage, so the oil passage must be formed when the case is molded. The mold for the case is expensive, and the mating surfaces of the case must be finished with high precision to prevent oil leakage, which requires a high degree of airtightness. On the other hand, a control valve for selectively supplying oil from the pump must be installed inside the case wall, so as a whole, the oil must be formed on each rotating shaft of the multiple multi-plate hydraulic clutches. The disadvantage is that the oil supply structure for the road is expensive. In contrast, a hydraulic joint, such as that used in the transmission mechanism described in Japanese Patent Publication No. 35-7302, is fitted onto the shaft end of the rotating support shaft, and the hydraulic joint and the control valve are connected with a pipe. According to the hydraulic piping structure, the structure itself is relatively simple, so it has the advantage that it can be manufactured at low cost, but the pipes that connect the hydraulic joint and the control valve are complicated and complicated, making it difficult to connect the pipes. This has the disadvantage that it is time consuming and the entire device becomes larger. The present invention was developed in view of the above-mentioned circumstances, and utilizes the advantage of using hydraulic joints that can be manufactured at low cost while simplifying the pipe mounting structure. It is an object of the present invention to provide a hydraulic piping structure for a hydraulic clutch transmission device that allows connection work to be performed accurately and easily and that allows the entire device to be configured relatively compactly. The characteristic structure of this invention to achieve the above purpose is as follows:
In the hydraulic piping structure of the above-mentioned hydraulic clutch transmission, the pair of rotating support shafts are supported by sandwiching the input shaft and being positioned above and below each other, and one end is connected to the clutch operating oil passage and the clutch lubrication oil passage, respectively. A pair of identical internal oil passages each having a pair of internal oil passages opened so as to be able to communicate with each other, and whose other ends are respectively opened to pipe connection ports distributed on the left and right with respect to the plane passing through the axis of the rotational support shaft. A shaped hydraulic joint is fitted and attached to each of the shaft ends that sandwich the input shaft of the rotary support shaft, and the pipe connection ports provided on each of the hydraulic joints are connected to the axis of the input shaft and both sides. The input shaft is arranged to the left and right with respect to the line segment connecting the axis of the rotation support shaft, and is fixed to the case in a position outward from the axis of the rotation support shaft in the radial direction of the input shaft. , an internal oil passage opened to two upper and lower pipe connection ports located on one left and right side of the line segment is communicated with the clutch actuation oil passage, and an upper and lower two pipe connection port located on the other side. An internal oil passage opened to the clutch lubrication oil passage is connected to the clutch lubrication oil passage, and a clutch actuation connecting portion is located above the pipe connection port located on one of the left and right sides, and a pipe connection located on the other side is provided. The control valve is installed in a position in which the clutch lubrication connection part is positioned above the mouth, and the pipe connection ports located on one of the left and right sides are connected to the clutch operation connection part through the clutch operation pipe, and the other The pipe connection port located on the side and the clutch lubrication connection part are connected via the clutch lubrication pipe, and this structure provides the following effects. In other words, a hydraulic joint is attached to the rotating shaft of the multi-disc hydraulic clutch, and an oil passage is formed from the control valve connected to the hydraulic pump to each rotating shaft via a pipe.
In other words, since it is configured to supply oil to the clutch operating oil passage and the clutch lubrication oil passage, it is possible to supply oil to the oil passage of each rotating shaft using an inexpensive piping structure. In addition, since hydraulic joints and pipes can be easily made airtight using sealing materials, high-precision manufacturing is not required.Furthermore, by creating a piping structure with pipes, the valve can be easily sealed against the case wall. There is no need to install the valve inside the valve, making it easy to assemble the valve. In this way, although the oil supply structure to the oil passages formed on the rotational shafts of the plurality of multi-plate hydraulic clutches is performed using an inexpensive piping structure, the present invention particularly achieves the following effects. play. Since the hydraulic joint fitted into the shaft end of the rotary support shaft is a common member with the same shape that can be used for any rotary support shaft, the manufacturing cost of the hydraulic joint can be reduced. Fix the hydraulic joint to the case in such a way that the pipe connection port provided on the hydraulic joint is positioned outward from the axis of the rotary support shaft in the radial direction of the input shaft with respect to any rotation support shaft. Therefore, when connecting the four pipes bypassing the control valve and the upper and lower hydraulic joints, the connections between these internal oil passages and the pipes must be made at a sufficient distance from the input shaft. As a result, pipe assembly work can now be easily performed outside the input shaft. A clutch actuation connection part and a clutch lubrication connection part provided on the control valve with respect to a line connecting the input shaft, the shaft center, and the shaft centers of both rotational support shafts;
A pair of pipe connection ports provided on each hydraulic joint are divided into left and right sides, and each pipe connection port located on one side with respect to the line segment is connected to a clutch actuation connection portion located above the pipe connection port with a pipe, Since each pipe connection port located on the other side is connected to the clutch lubrication connection located above it with a pipe, it is possible to avoid cross piping on the top, bottom, left and right, and there is no risk of making mistakes in connecting the pipes. Piping work can be easily done on top. Furthermore, by avoiding cross piping,
Even though hydraulic joints are used, the entire device can be configured compactly. Hereinafter, embodiments of the present invention will be described based on the drawings. The figure shows the power transmission structure of an agricultural tractor, in which an engine 1, a main clutch housing 2, and a transmission case 3 are connected in series in this order, and the engine output is appropriately shifted within the transmission case 3 to provide power to the rear of the tractor. It is configured to transmit power to rear wheel drive shafts 4, 4 protruding from both sides and a PTO shaft 5 protruding from the rear. The front part of the transmission case 3 is equipped with a main gear transmission mechanism 8 for the driving system that changes gears in four stages by selective shifting of shift gears 6 and 7, and the rear part of the case is equipped with shift gears 9a and 9b. The vehicle is equipped with an auxiliary gear transmission mechanism 10 for the traveling system that performs two-speed shifting by shifting, and a differential transmission mechanism 11 for the left and right rear wheel drive shafts 4, 4. Furthermore, a PTO-type gear transmission mechanism 13 is installed between the front and rear of the transmission case 3 to perform a two-speed shift by shifting the shift gear 12. Further, an intermediate transmission chamber 14 is formed between the rear wall 2a of the main clutch housing 2 and the front wall 3a of the transmission case 3.
The input shaft 1 of the traveling system is inserted into this intermediate transmission chamber 14 from a.
5 is plunged in, the driving shaft 17 whose power is on/off through the main clutch 16 is thrust into the intermediate transmission chamber 14, and above and below the intermediate transmission chamber 14 are rotating support shafts equipped with hydraulic clutches 18 and 19 . 20,2
1 is supported via a rear wall 2a of the main clutch housing and a bracket 22 attached thereto. The upper hydraulic clutch 18 is fitted loosely between the drive drum 23 and the support shaft 20 by shifting a piston 24 installed in the drive drum 23 fixed to the support shaft 20 to the right using pressure oil. passive drum 2
Friction plates 26..., 27... interposed between drums 5 and 5 are brought into pressure contact to transmit frictional power between both drums 23 and 25, and by releasing hydraulic pressure to the piston 24, the piston 24 is moved to the left by the internal spring 28. A gear 29 formed on the driving drum 23 is engaged with a gear 30 fixed to the shaft end of the driving shaft 17. And passive drum 25
An idle gear 3 in which a gear 31 integrally molded is rotatably supported in the intermediate transmission chamber 14 via a separate support shaft 32.
3, it is interlocked with a gear 34 fixed to the shaft end of the input shaft 15 of the traveling system. Similarly to the hydraulic clutch 18 , the lower hydraulic clutch 19 is composed of a drive drum 35, a passive drum 36, a piston 37, friction plates 38..., 39..., and a return spring 40, and a gear formed on the drive drum 35. 41, when the drive shaft gear 30 is engaged, the gear 42 formed on the passive drum 36 is directly engaged with the traveling system input shaft gear 34. The lower hydraulic clutch 19 is used for normal rotation (forward) transmission, and the upper hydraulic clutch 18 is used for reverse rotation (reverse) transmission. Further, the rear end of the lower rotating support shaft 21 is coupled to a PTO system transmission shaft 43 within the transmission case 3, and both hydraulic clutches 18 , 1
Power is transmitted regardless of whether 9 is on or off. Pressure oil is supplied to and drained from both hydraulic clutches 18 and 19 through internal oil passages 44 and 44 of each rotating support shaft 20 and 21, respectively.
45 and both clutches 1
Lubricating oil is supplied to the friction transmission points 8 and 19 via separate internal oil passages 46 and 47.
The front ends of these rotary support shafts 20 and 21 are thrust into the main clutch chamber 48 through the rear wall 2a of the main clutch housing, and the end of the shaft is thrust into the main clutch chamber 48 through the rear wall 2a of the main clutch housing.
The hydraulic joints 49 and 50 are bolted to the front surface of the hydraulic joints 49 and 50, respectively. A control valve 51 is attached to the upper surface of the main clutch housing 2, and a pipe extends into the main clutch chamber 48 from a clutch actuation connection 51A and a clutch lubrication connection 51B provided on the valve 51. 52,5
3, 54, 55 are connected to pipe connection ports 101, 102 provided at the open ends of the internal oil passages 44 formed in the hydraulic joints 49, 50, and the control valves 51
and the respective oil passages 44 are connected in communication. In this case, as shown in FIG.
is provided on one lateral side of the driving shaft 17 (left side in the drawing), and pipes 54, 55 for clutch lubrication oil passages 46, 47 are provided on the other lateral side of the driving oil (right side in the drawing). Further, an operating shaft 58 to which a shift fork 57 of a release 56 for operating the main clutch is fixed is horizontally supported on the main clutch housing 2, and a pipe 5 connected to the upper hydraulic clutch 18 is supported horizontally.
The pipes 2 and 54 are curved in a detour so as to surround the operating shaft 58. In other words, the axis of the driving shaft 17 and each rotating support shaft 20,
A piping structure for clutch operation is disposed on one side of a line segment connecting the axis of 21, and a piping structure for clutch lubrication is disposed on the other side. Moreover, the upper and lower hydraulic joints 49 and 50 are identical and have internal oil passages with different depths on the left and right sides, and are attached to the main clutch housing rear wall 2a in an upside-down position. Oil road 5
9 and 60 are located above the rotation support shaft 20, and the left inner oil passage 59 with a smaller depth is used as the clutch operating oil passage 44, and the deeper right internal oil passage 60 is used for clutch lubrication. The oil passages 46 are connected to each other in communication. On the other hand, in the lower hydraulic joint 49 installed upside down, both oil passages 6
1 and 62 are located below the rotation support shaft 21, and the inner oil passage 61 on the right side, which has a smaller depth, is the oil passage 47 for clutch lubrication, and the internal oil passage 6, which has a larger depth, on the left side.
2 are connected to the clutch operating oil passage 45, respectively, and as mentioned above, the clutch operating pipes 52, 53 and the clutch lubricating pipes 54, 5
5 are arranged on the left and right sides of the driving shaft 17. Further, a spring 63 for releasing the release is stretched between the lower hydraulic joint 50 and the release 56. FIG. 4 shows a hydraulic circuit for operating the hydraulic clutches 18 and 19 , and the control valve 51 includes a three-position switching valve 64 for switching forward and backward, and a modulating relief for controlling the rise characteristics of the clutch operating oil pressure. It consists of a valve 65, a modulating valve 66, and a relief valve 67 for supplying lubricating oil into each hydraulic clutch 18 , 19 , and the pump port of the control valve 51 is connected to a flow priority valve 68. It is connected to the flow control port of valve 69. The 3-position switching valve 64 is of a rotary type that can be rotated to 3 positions with a manual lever, and in the neutral position N, the pressure oil from the pump 68 is modulated into the relief valve 65 and the clutch lubrication relief valve. 67 to the tank port T, and a part of the relief drain oil is supplied from the top of the relief valve 67 through the oil path L to the friction transmission parts of both hydraulic clutches 18 and 19 to lubricate and cool the friction surfaces. will be held. In the forward position F or reverse position R, pressure oil is supplied to the oil path f to the forward hydraulic clutch 19 or the oil path r to the reverse hydraulic clutch 18 , and is also supplied to the oil path m to the modulating valve 66. is also supplied to control the hydraulic clutch operating pressure. The modulating relief valve 65
is urged in the valve closing direction by a spring 70, and
A spring receiver 71 supporting the rear end of the spring 70 is configured to be able to be displaced by pressure oil supplied through an orifice 72 of the modulating valve 66. As a result, the spring pressure, that is, the relief operating pressure, gradually increases. Therefore, when the switching valve 64 is switched from the forward position F to the reverse position R, the operating pressure of the modulating relief valve 65 gradually increases as described above, so that the applied pressure to the selected hydraulic clutch 19 or 18 increases. The clutch force increases gradually, resulting in smooth clutch engagement without shock. Incidentally, although reference numerals are written in the claims section of the utility model registration for convenience of comparison with the drawings, the present invention is not limited to the structure of the attached drawings by such entry.

【図面の簡単な説明】[Brief explanation of the drawing]

図面は本考案に係る油圧クラツチ変速装置の油
圧配管構造の実施例を示し、第１図は農用トラク
タにおける伝動構造の全体を示す概略側面図、第
２図は要部の縦断側面図、第３図は要部の横断平
面図、第４図は油圧回路図、第５図及び第６図は
夫々第２図における−線断面図、及び−
線断面図である。 １５……出力軸、１７……入力軸、５１Ａ……
クラツチ作動用接続部、５１Ｂ……クラツチ潤滑
用接続部、１０１，１０２……パイプ接続口、１
８，１９……油圧クラツチ、２０，２１……回転
支軸、２……ケース、４４，４５……クラツチ作
動用油路、４６，４７……クラツチ潤滑用油路、
４９，５０……油圧継手、５１……制御バルブ、
５２，５３……クラツチ作動用パイプ、５４，５
５……クラツチ潤滑用パイプ、５９，６０，６
１，６２……内部油路。 The drawings show an embodiment of the hydraulic piping structure of the hydraulic clutch transmission according to the present invention, FIG. 1 is a schematic side view showing the entire transmission structure of an agricultural tractor, FIG. 2 is a vertical side view of the main parts, and FIG. The figure is a cross-sectional plan view of the main part, FIG. 4 is a hydraulic circuit diagram, and FIGS. 5 and 6 are sectional views taken along the - line in FIG. 2, and -
FIG. 15...Output shaft, 17...Input shaft, 51A...
Connection part for clutch operation, 51B... Connection part for clutch lubrication, 101, 102... Pipe connection port, 1
8, 19 ... Hydraulic clutch, 20, 21... Rotating shaft, 2... Case, 44, 45... Oil passage for clutch operation, 46, 47... Oil passage for clutch lubrication,
49, 50...Hydraulic joint, 51...Control valve,
52, 53...Clutch actuation pipe, 54, 5
5...Clutch lubrication pipe, 59, 60, 6
1,62...Internal oil passage.

Claims (1)

【実用新案登録請求の範囲】[Scope of utility model registration request] 入力軸１７と出力軸１５との間に、多板式油圧
クラツチ１８，１９を夫々備えた一対の回転支軸
２０，２１を並列に支承し、前記回転支軸２０，
２１の夫々に、前記多板式油圧クラツチ１８，１
９に対するクラツチ作動用油路４４，４５とクラ
ツチ潤滑用油路４６，４７とを形成して、制御バ
ルブ５１に設けたクラツチ作動用接続部５１Ａと
クラツチ潤滑用接続部５１Ｂとに夫々連通接続
し、前記制御バルブ５１の操作に基づいて択一的
に連結状態に切換えられた多板式油圧クラツチ１
８，１９を介して前記入力軸１７と出力軸１５と
を連動連結するように構成してある油圧クラツチ
変速装置の油圧配管構造において、前記一対の回
転支軸２０，２１を前記入力軸１７を挾んで互い
に上下に位置させて支承し、一端が夫々前記クラ
ツチ作動用油路４４，４５とクラツチ潤滑用油路
４６，４７とのいずれにも連通可能に開口され、
かつ、他端が夫々回転支軸２０，２１の軸芯を通
る面に対して左右に振分け配置したパイプ接続口
１０１，１０２に開口される一対の内部油路５
９，６０，６１，６２を形成した同一形状の油圧
継手４９，５０を、前記回転支軸２０，２１の入
力軸１７を挾む軸端の夫々に嵌入装着するととも
に、前記両油圧継手４９，５０を、その夫々に備
えさせたパイプ接続口１０１，１０２が前記入力
軸１７の軸芯と両回転支軸２０，２１の軸芯とを
結ぶ線分に対して左右に振分け配置され、かつ、
前記入力軸１７の径方向において、回転支軸２
０，２１の軸芯よりも外方側に位置する姿勢でケ
ース２に固定し、前記線分を挾んで左右一側方に
位置する上下２個のパイプ接続口１０１，１０２
に開口する内部油路５９，６２をクラツチ作動用
油路４４，４５に連通させ、他側方に位置する上
下２個のパイプ接続口１０２，１０１に開口する
内部油路６０，６１をクラツチ潤滑用油路４６，
４７に連通させ、更に、前記左右一側方に位置す
るパイプ接続口１０１，１０２の上方にクラツチ
作動用接続部５１Ａを位置させ、前記他側方に位
置するパイプ接続口１０２，１０１の上方にクラ
ツチ潤滑用接続部５１Ｂを位置させる姿勢で制御
バルブ５１を取付け、前記左右一側方に位置する
パイプ接続口１０１，１０２とクラツチ作動用接
続部５１Ａとをクラツチ作動用パイプ５２，５３
を介して接続し、前記他側方に位置するパイプ接
続口１０２，１０１とクラツチ潤滑用接続部５１
Ｂとをクラツチ潤滑用パイプ５４，５５を介して
接続してあることを特徴とする油圧クラツチ変速
装置の油圧配管構造。 A pair of rotary shafts 20, 21 each having a multi-plate hydraulic clutch 18, 19 is supported in parallel between the input shaft 17 and the output shaft 15.
The multi-plate hydraulic clutches 18, 1
9, clutch actuation oil passages 44, 45 and clutch lubrication oil passages 46, 47 are formed, and are connected to a clutch actuation connection portion 51A and a clutch lubrication connection portion 51B provided on a control valve 51, respectively, and a multi-plate hydraulic clutch 1 is selectively switched to an engaged state based on the operation of the control valve 51.
In the hydraulic piping structure of the hydraulic clutch transmission, which is configured to interlock and connect the input shaft 17 and the output shaft 15 via the hydraulic clutch piping structure 18 and 19, the pair of rotary support shafts 20 and 21 are supported by being positioned above and below the input shaft 17, and one end of each of the rotary support shafts 20 and 21 is opened so as to be able to communicate with both of the clutch operating oil passages 44 and 45 and the clutch lubricating oil passages 46 and 47,
The other ends of the pair of internal oil passages 5 are opened to pipe connection ports 101, 102 arranged on the left and right sides of a plane passing through the axial centers of the rotation support shafts 20, 21, respectively.
Hydraulic couplings 49, 50 having the same shape and having hydraulic joints 9, 60, 61, 62 formed thereon are fitted and attached to the shaft ends of the rotary support shafts 20, 21 that sandwich the input shaft 17, respectively, and pipe connection ports 101, 102 equipped with the hydraulic couplings 49, 50 respectively are arranged on the left and right sides of a line segment connecting the axis of the input shaft 17 and the axis of the rotary support shafts 20, 21,
In the radial direction of the input shaft 17, the rotation support shaft 2
The pipe connection ports 101 and 102 are fixed to the case 2 in a position located outside the axis of the axial line 0 and 21, and are located on the upper and lower sides of the line segment.
The internal oil passages 59, 62 opening at the upper and lower pipe connection ports 102, 101 located on the other side are connected to the clutch operating oil passages 44, 45, and the internal oil passages 60, 61 opening at the upper and lower pipe connection ports 102, 101 located on the other side are connected to the clutch lubrication oil passages 46,
The control valve 51 is attached in such a manner that the clutch operating connection portion 51A is located above the pipe connection ports 101, 102 located on the left or right side, and the clutch lubrication connection portion 51B is located above the pipe connection ports 102, 101 located on the other side. The pipe connection ports 101, 102 located on the left or right side and the clutch operating connection portion 51A are connected to the clutch operating pipes 52, 53.
and the pipe connection ports 102, 101 located on the other side and the clutch lubrication connection portion 51
A hydraulic piping structure for a hydraulic clutch and transmission, characterized in that the hydraulic piping structure for a hydraulic clutch and transmission is connected to the hydraulic clutch and transmission through clutch lubrication pipes.