JPS58149423A - Forming device for oil passage for hydraulic clutch type transmission - Google Patents

Abstract

PURPOSE:To facilitate the forming of an oil passage and to simplify assembling work by a method wherein a necessary oil passage is formed by combining an oil-passage forming and bearing body supporting one end of a transmission shaft, an oil-passage forming plate, and an intermediate plate with each other. CONSTITUTION:A plurality of oil grooves G1 are formed on the back surface of an oil-passage forming plate 34, while a plurality of oil grooves G2 are formed on the front surface of an oil-passage forming and bearing body 36, and the open- end sides of these oil grooves G1 and G2 are blocked up by an intermediate plate 35. The oil discharging port of a hydraulic pump 46 is communicated with the oil grooves G1 on the back surface of the oil-line forming plate 34 through oil holes in a housing 45 and oil holes in the oil-line forming plate 34, while the oil grooves G1 are communicated with the oil grooves G2 on the front surface of the oil-passage forming and bearing body 36. Moreover, the oil grooves G2 are led to oil-distributing chambers 53F1, 53F2, 53F3 and 53R through oil holes 70 in the oil-passage forming and bearing body 36.

Description

【発明の詳細な説明】 この発明は、農用トラクタ等の車−にお−で油圧クラッ
チの選択的作−により変速を行なう油圧クラッチ式変速
装置用の油路形成装置、より詳しくいうと、パワーシフ
ト軸上に設置され九油田タラツチに対しパワーシフト軸
内に穿設され九油路を介し作−油を供給するように構成
され九油路形成装置に、関すゐものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an oil path forming device for a hydraulic clutch type transmission that changes speed by selective operation of a hydraulic clutch in a vehicle such as an agricultural tractor. This invention relates to a nine oil passage forming device which is installed on the shift shaft and is configured to supply working oil through nine oil passages which are bored in the power shift shaft to nine oil field tarps.

上記のような油路形成装置において、ノ（ワーシ７ト軸
内の油路社パワーシフト軸の回転に伜な一位置を変更さ
れるから、そ、のように位置を変更される油路に対して
位置固定側の油路を接続する丸めの油路ジ肩インドが、
設けられねばならなｉ。In the oil path forming device as described above, the position of the oil path is changed due to the rotation of the power shift shaft in the washi shaft, so the oil path whose position is changed as shown in On the other hand, the rounded oil passage shoulder India that connects the oil passage on the fixed position side is
i must be provided.

オた位置固定側の油路は、油圧配管を極力省略させる態
様で設けるのが望ましい。It is desirable that the oil passage on the fixed position side be provided in such a manner that hydraulic piping is omitted as much as possible.

位置固定側の油路を、油圧配管を極力省略させる態様で
設は九波路形成装置として、例えば喪−昭５１−１０３
２３８号公報に一示されているような油路形成板を用い
丸ものがある。同金報Ｏものは、油圧クラッチ式変速装
置用の位置ＩｉＩ定儒の油路を形成する油路形成板をし
て、油圧タラツチ弐羨遍装置におけるパワーシフト軸を
含めての伝動軸の一端部を支持する軸受体に兼用させ、
パワーシフト軸内の油路に油路形成板内の油路を接続す
るための環状の油分配室は、油路形成板の端面上にパワ
ーシフト軸の一亀部に被嵌される油路受継筒を■定装着
して、パワーシフト軸の一熾部外周面と腋油路受纏筒と
の間に形成している。The oil passage on the fixed position side was installed as a nine-wave passage forming device in a manner that omitted hydraulic piping as much as possible.
There is a round type using an oil passage forming plate as shown in Japanese Patent No. 238. The same gold plate has an oil passage forming plate that forms an oil passage of constant position IiI for a hydraulic clutch type transmission, and is used for one end of a transmission shaft including a power shift shaft in a hydraulic clutch type transmission device. Also serves as a bearing body that supports the
The annular oil distribution chamber for connecting the oil passage in the oil passage forming plate to the oil passage in the power shift shaft is an oil passage that is fitted into one turtle part of the power shift shaft on the end face of the oil passage forming plate. The receiving tube is fixedly attached and is formed between the outer circumferential surface of one part of the power shift shaft and the armpit oil passage receiving tube.

上記のような油路形成板には、複数伝動軸の各一端部を
支承するベアリングの保持部が形成されているが、その
ようなベアリング保持部を避けて単一の油路形成板に多
数の油路を形成することは、油路形状が複雑となること
からして必らずしも容１ではない。また上記した油路受
継筒は、油路形成板を組付ける作業とは別作業で取付け
られる。The oil passage forming plate described above has a holding part for bearings that supports one end of each of the multiple transmission shafts. It is not always easy to form an oil passage because the shape of the oil passage becomes complicated. Further, the oil passage transfer tube described above is installed in a separate operation from the operation for assembling the oil passage forming plate.

この発明の目的とするところは、上で説明した従来のも
のと比較して、油路の形成加工が遥かに容易であると共
Ｋ、組立て作業を簡単化することとしである、油圧クラ
ッチ式変速装置用の新規な波路形成装置を、提供するに
ある。The purpose of this invention is to provide a hydraulic clutch type, which is much easier to form oil passages than the conventional one described above, and which simplifies assembly work. A novel wave path forming device for a transmission is provided.

図示の実施例について、この発明に係る油路形成＠ｔＯ
構成を説明すると、謳１図に示すように、機体前部にエ
ンジンｌを塔載し、このエンジンｌの動力を、前端大径
部２ａ内において主クラッチ３を内蔵するクラッチハウ
ジング２内と、後述する変速伝動機構を内置する書ツシ
曹ンケース４内とを、経て機体最後部を構成するリヤへ
クジンダ５内への伝達し、左右の後輪６を駆動して機体
の走行を行なわせるようにされると共Ｋ、機体よ〉後方
へ嬌出させである作業機部動用０ＰＴＯ軸の回転駆動を
行なうように、構成され先車用トラクタにおいて、この
発明は、次のように実施されている。Regarding the illustrated embodiment, oil channel formation according to the present invention @tO
To explain the configuration, as shown in Figure 1, an engine 1 is mounted on the front of the fuselage, and the power of this engine 1 is transferred to a clutch housing 2 containing a main clutch 3 within a large diameter portion 2a at the front end. The transmission is transmitted from the inside of the bookcase case 4 in which a transmission mechanism, which will be described later, is housed, and then to the rear engine 5, which constitutes the rearmost part of the aircraft, and drives the left and right rear wheels 6 to cause the aircraft to travel. The present invention is implemented in the following manner in a tractor for a leading vehicle, which is configured so as to rotate the 0PTO shaft for moving the working machine part so as to push the machine body backward. There is.

すなわち、図示の農用トラタタにおける走行−力伝導機
構は、第２図に示すように．＃記しえエンジン１に主ク
ラッチ３を介して連動連結しである駆動−８上機体前後
方−に沿わせて設けると共に、こＯ駆−軸８の中途上に
遊嵌して中空＠―軸９を設けて、これらの駆動軸８と中
空伝動軸−との間を適宜の変速比でもって選択的に連動
連曽する走行論力主変適装置である油圧タラツチ式変造
＊１Ｉ１１０を設け、また上記の中空伝動軸９とそれに
平行°させて設けられた伝動軸１１との間に、該両軸９
，１１間を適宜の変速比でもって選択的に連動連結する
走行動力副変速装置である機械式変速装置１２を設け、
走行動力変速部１０．１２の出力軸を構成している上記
伝動軸１１を、傘歯車伝動機構１３を介して左右後輪６
用の差動装置１４へと接続し、この差動装＃１１４の左
右の出力軸１４１をそれぞれ、最終歯車減速装置１５を
介して左右の後輪車軸６ｍへと接続してなるものに、構
成されているのてあシ、上記した油圧クラッチ式変速鋏
ｍｌ　ＯＦｉ、第３図に示すように、千の略半部を１記
クラッチハウジング２内に臨ませて、般けられている。That is, the traveling force transmission mechanism in the illustrated agricultural tractor is as shown in FIG. #Record: The drive shaft 8 is interlocked with the engine 1 through the main clutch 3, and is installed along the front and rear of the upper fuselage. 9, and a hydraulic latch type modification *1I110, which is a travel logic main variable device that selectively interlocks the drive shaft 8 and the hollow transmission shaft with an appropriate gear ratio, is provided. Between the hollow power transmission shaft 9 and the power transmission shaft 11 provided parallel to it, both shafts 9
.
The transmission shaft 11 constituting the output shaft of the traveling power transmission section 10.12 is connected to the left and right rear wheels 6 via a bevel gear transmission mechanism 13.
The left and right output shafts 141 of this differential #114 are respectively connected to the left and right rear wheel axles 6m via the final gear reduction gear 15. As shown in FIG. 3, the hydraulic clutch type transmission scissors ml OFi described above is generally available with approximately half of the arm facing inside the clutch housing 2. As shown in FIG.

油圧クラッチ式変速装置ｌＯは、８２．３．４図に示す
ように、並列配置された２本のパワーシフト軸１６．１
７を備えている。第２．３＠ＩＫ示すように，　１Ｖｌ
ｒ記駆動軸８上には、２伽の変速歯車１８、１９を固定
設置しである。そして、一方のパワーシフト軸１６上に
は、駆動−８上の変速歯車１８に噛合されているＦ１遊
転肯車２０と、遊転自在に支持され駆動軸８上の他の変
速−車１９へと噛合されているＲ中間歯車２３ムに噛合
せであるＲ遊転歯車２３とを、それぞれ遊嵌設置してあ
り、ま九他方のパワーシフト軸１７上には、駆動軸８上
の変速−車１９に噛合せであるＦ，遊転歯車２１と、駆
動軸８上の変速歯車１８に噛合せであるＦ．遊転歯車２
２とを、それヤれ遊嵌設置しである．各パワーシフト軸
１１１．１７上には、上記した各遊転歯車２０．２１．
４２．２３に配してＦ１油圧クラッチ２４、Ｆ，油圧ク
ラッチ２６、Ｖ．油圧クラッチ２６、Ｒ油圧クラッチ２
７を鋏架してあり、これらの各油圧クラッチ２４．１！
．！＠或は２７を選択的に作動させ各遊転歯車２Ｇ．１
１。The hydraulic clutch type transmission lO has two power shift shafts 16.1 arranged in parallel, as shown in Fig. 82.3.4.
It has 7. As shown in Section 2.3 @IK, 1Vl
Two speed change gears 18 and 19 are fixedly installed on the drive shaft 8. On one power shift shaft 16, there is an F1 idling wheel 20 meshed with the speed change gear 18 on the drive shaft 8, and another speed change wheel 19 on the drive shaft 8, which is supported so as to be freely rotatable. The R idle gear 23 which is meshed with the R intermediate gear 23 is loosely fitted to the R intermediate gear 23 which is meshed with the R intermediate gear 23. - F is meshed with the wheel 19; F is meshed with the idler gear 21 and the transmission gear 18 on the drive shaft 8; Idle gear 2
2 and 2 are installed with loose play. On each power shift shaft 111.17, each of the free rotating gears 20.21.
F1 hydraulic clutch 24, F, hydraulic clutch 26, V.42. Hydraulic clutch 26, R hydraulic clutch 2
7 and each of these hydraulic clutches 24.1!
．． ! ＠ or 27 selectively to operate each idler gear 2G. 1
1.

２２或は２３を選択的に各パワーシフト軸１６或は１７
へと選択的に結合し得るように，されてｉる。パワーシ
フト軸１６は麹記の中空伝動輪−に、パワ−シフト軸１
６０後端部Ｋｍ着した歯車２ｓを中空伝動輪９１端部上
の大径歯車２９へと噛合せることで、接続されており、
ｔえ弛方のパワーシフト軸１７は鋏中空伝動軸９に、パ
ワーシフト軸１７の後端部に嵌着した歯車３０を中空伝
動輪９約端部上の小径歯車３１へと噛合せることで、接
続されている。以上により油圧クラッチ式変速＠１１に
１Ｇは、各油圧クラッチ２４．２５．２６戒は２７の選
択作動で各遊転歯車２０．２１．２２或Ｆｉ２３を選択
的に各パワーシフト軸１６戚は１７へと結合することで
、中空伝動軸９に前進ｌ速Ｆ、。22 or 23 can be selectively connected to each power shift shaft 16 or 17.
It is possible to selectively bind to i. The power shift shaft 16 is connected to the hollow transmission wheel of Kojiki.
It is connected by meshing the gear 2s attached at the rear end Km with the large diameter gear 29 on the end of the hollow transmission wheel 91,
The loose power shift shaft 17 is created by meshing the gear 30 fitted on the rear end of the power shift shaft 17 with the small diameter gear 31 on the approximately end of the hollow transmission wheel 9. ,It is connected. As described above, the hydraulic clutch type gear shift @11 to 1G is achieved by selectively operating each hydraulic clutch 24, 25, 26 and 27 to selectively shift each idle gear 20, 21, 22 or Fi 23 to each power shift shaft 16 and 17. By coupling to the hollow transmission shaft 9, the forward l speed F.

＃迩２速Ｆ２、前進３速Ｆ１或は後進１速Ｒの回転数を
選択的に得ることができるものと、されている。# It is possible to selectively obtain the rotational speed of 2nd speed F2, 3rd forward speed F1, or 1st reverse speed R.

第３図に示すように、クラッチハウジング２は後端側を
開放しである本のに、またミッションケース４は前“端
側を開放しであるものに、それぞれ形成されており、こ
れらのクラッチハウジング２と建ツシミ７ケース４間は
、複数個宛の螺杵３２とナツト３８とを利用して締付は
固定するように、なされている。パワーシフト軸１６．
１７の硫端部１まそれぞれ、ミッションケース４の内面
上に集設せる支壁部４ａ、４ｂに回転可能に支持されて
いる。そして特に、やや簿手の油路形成板３４と、薄い
鉄板よりなる間板３５と、肉厚の板状をなす油路形成兼
軸受体３６とを、この願で帥方儒から重畳させて、クラ
ッチハウジング２内に設けてあり、これらの油路形成板
３４と関４［３６と油路形成兼軸受体３６は、＄Ｉ４．
５図に示すように、油路形成兼軸受体３６の背面周端部
分に複数個の連結部３６膳を後方肉色に延出させて一体
形成すると共Ｋ、こＯ連結部３６１０端面Ｋｌｉ合する
複数個の連結部４Ｃをミッションケース４の内面上に突
設形成し、油路形成板３４と間板３ｓと油路形成体３６
とを貫通させ、上記の連結部３＠１を挿通した上でミッ
ションケース４内画上の上記連結部４Ｃへと螺合される
螺杵３７によって、上記０３枚の板３４，３５，３４１
を共締めすると同時にオツシ目ンケース４へと固定連結
されている。竜お油路形成板３４と間板３５と油路形成
兼軸受体３６との間のみを固定連結する螺杵３７′（第
！１ｌｌ）亀、設けられている。As shown in Fig. 3, the clutch housing 2 is formed with an open rear end, and the transmission case 4 is formed with an open front end. A plurality of screw punches 32 and nuts 38 are used to securely tighten the space between the housing 2 and the housing 7 case 4.The power shift shaft 16.
Each of the 17 sulfur end portions 1 is rotatably supported by supporting walls 4a and 4b arranged on the inner surface of the transmission case 4. In particular, the oil passage forming plate 34, which is a little rough, the spacer plate 35 made of a thin iron plate, and the oil passage forming/bearing body 36, which is in the form of a thick plate, are superimposed on each other in this application. The oil passage forming plate 34, the oil passage forming plate 36, and the oil passage forming/bearing body 36 are provided in the housing 2, and the oil passage forming plate 34, the oil passage forming/bearing body 36, and the oil passage forming plate 34 and the oil passage forming/bearing body 36 are provided at a cost of $I4.
As shown in FIG. 5, a plurality of connecting portions 36 are integrally formed on the rear peripheral end portion of the oil passage forming/bearing body 36 so as to extend rearward in flesh color. A plurality of connecting portions 4C are formed protrudingly on the inner surface of the mission case 4, and are connected to the oil passage forming plate 34, the spacer plate 3s, and the oil passage forming body 36.
The three plates 34, 35, 341 are screwed together by the screw 37 which is inserted through the connecting part 3@1 and then screwed into the connecting part 4C on the inside of the mission case 4.
At the same time, they are fixedly connected to the diaper case 4. A screw screw 37' (No. 1ll) is provided to fixedly connect only the oil passage forming plate 34, the intervening plate 35, and the oil passage forming/bearing body 36.

そして、上記のようＫｉミッションケースに固定支持さ
れ九関係とされてｉる油路形成兼軸受体３６に、＃Ｉ３
図に示すようＫ、パワーシフト軸１６゜１７０紡端部を
それぞれ、ベアリング３８．３９を介して軸受けさせて
いる。ま九同機に＠３図に示すようＫ、油圧クラッチ式
変速装ａｉｏの原動側に位置する前記駆動軸８もその中
途を、ベアリング４０を介して上記の油路形成兼輪受体
３６に軸受けされており、さらに、前記したＲ中間歯車
２３Ａの支軸２３Ｂも、上記の３枚の［３４，３５゜３
６に支持させて設けである。なお図示の場合には、走行
動力変速ｇｔｏ、１２の出力軸を構成している前記伝動
輪１１を、同ｍＫ第３−に示すように前方へと延長させ
、図示実用トラクタを四輪駆動層のものに転換する場合
に前輪駆動力を取出す丸めの出カー車４１を、油路形成
板３４よシも前位において該伝動軸１１に嵌着している
。Then, #I3 is attached to the oil passage forming/bearing body 36 which is fixedly supported by the Ki transmission case and has nine connections as described above.
As shown in the figure, the spindle ends of K and power shift shafts 16° and 170 are respectively supported via bearings 38 and 39. In the same machine, as shown in Figure 3, the drive shaft 8 located on the driving side of the hydraulic clutch type transmission AIO is also supported halfway through the bearing 40 by the oil passage forming and wheel bearing body 36. Furthermore, the support shaft 23B of the R intermediate gear 23A is also connected to the three [34, 35°3
It is supported by 6. In the illustrated case, the transmission wheel 11 constituting the output shaft of the traveling power transmission GTO 12 is extended forward as shown in mK No. 3-, and the illustrated practical tractor is converted into a four-wheel drive layer. A round output wheel 41 for extracting the front wheel drive force when converting to a new one is fitted onto the transmission shaft 11 at the front side of the oil passage forming plate 34.

そして、Ｍ３図に示すように、油圧クラッチ式変速装置
１０における駆動−８の後端部側はベアリング４３を介
しミッションケース４頂鷺内面に垂設せる支壁部４ｄＫ
軸受けさせてあり、またなお伝動軸１１０俵端部も上紀
支壁部４ｄＫベアリング４４を介し軸受けされておや、
そしてパワーシフ）軸１６上の変造部材２Ｇ、！３．２
４．１７は油路形成兼軸受体３６と建ツシ曹ンヶース４
内向上の前記支壁部４ａ間で、１１九パワーシフト軸１
７上の変速部材２１．２２．２６．２６は―路形成兼軸
受体３６と２ツシ肩ンケ一ス４内自上０−記支壁部４ｂ
間で、それぞれ各パワーシフト軸１４１．１７上に設置
されてお）、ζ０ようにしてンツシｌンクース４に支持
させえ油圧クララ？ｔ。As shown in Fig. M3, the rear end side of the drive 8 in the hydraulic clutch type transmission 10 is provided with a supporting wall portion 4dK that is suspended from the inner surface of the mission case 4 via a bearing 43.
The bale end of the transmission shaft 110 is also supported via a bearing 44 on the support wall 4dK.
And power shift) modified member 2G on shaft 16,! 3.2
4.17 is the oil passage formation/bearing body 36 and the construction cylinder case 4
119 power shift shaft 1 between the inner support wall portions 4a
The transmission members 21, 22, 26, 26 on 7 are connected to the road forming/bearing body 36 and the two shoulder casings 4, upper and lower 0, supporting wall portions 4b.
The hydraulic clarifiers are installed on each power shift shaft 141. t.

変速装置１０の略鍵中部をクラッチハクジン１２内に、
鍍ハウジング０４ｌｉｉｌｌｌｌ開口から挿入しで、そ
の稜に、＠記の螺杵３２及びナツト３３を利用しクラッ
チハウジング２とζツシ習ンケース４聞〇一定を行なう
ぺく、されている。Put approximately the middle part of the key of the transmission 10 into the clutch cover 12,
It is designed to insert the clutch housing 04 through the opening and tighten the clutch housing 2 and the ζ-synthesis case 4 on its ridge using the screw punch 32 and nut 33 described in @.

＃Ｉ３図に示すように、油路形成１［３４の鍵画上Ｋｉ
ｉ、駆−軸８上とパワーシフト軸１６上とＫｔたからせ
てハウジング４５を鋏着してあに、ζ０ハウジング４５
の略半部をポンプケースとする内接歯車式の油圧ポンプ
４６を、設けである。ζ０油圧ポンプ４６は、駆動軸８
をポンプ軸に兼用事せて構成されており、油圧クラッチ
式変速装置１０における前記油圧クラッチ２４−２７に
対し作動油を供給するためのものと、されている、上記
したハウジング４１０倫の略半部は、１１４７にて前端
開口を閉鎖される円筒状部４５ａＫ形成されており、こ
の円筒状９４５８内にパワーシフト軸１６の前端部を臨
ませである。そして、このノ（ワーシフト軸１６＃ｉ端
１１に形成せる偏平部１６１を利用して該鍵端部上に、
円筒状５４５ｍ内面上の段部４５　ｂＫ対面する摩擦制
動板４８を軸１６と相対回転不能に設け、摩擦制動板４
８の上記段部４５ｂへの圧接係合によりパワーシフト軸
１６を制動するブレーキ４９を構成している。円筒状部
４５８内には、摩擁制動板４１１に対面するピストン５
０と、このピストン５０を介し摩擦制動板４８を段１ｉ
１４５ｂへの圧接方向に移動附勢する圧縮ばね５１とが
、設けられている。プレーヤ４９は、上記し九圧縮ばね
５１の附勢力によって制動作動を行ない、また円筒状部
４５ａ内に形成され九油室５２への油圧作用でピストン
５０の後退を得て制動を４９の機能につｉては、後述す
る。# As shown in Figure I3, oil path formation 1 [Ki on the key picture of 34]
i, attach the housing 45 to the top of the drive shaft 8 and the power shift shaft 16, and attach the housing 45;
An internal gear type hydraulic pump 46 is provided, with approximately half of the pump case serving as a pump case. The ζ0 hydraulic pump 46 is connected to the drive shaft 8
Approximately half of the housing 410 described above is configured to also serve as a pump shaft, and is used to supply hydraulic oil to the hydraulic clutches 24-27 in the hydraulic clutch type transmission 10. A cylindrical portion 45aK is formed whose front end opening is closed at 1147, and the front end of the power shift shaft 16 is exposed within this cylindrical portion 9458. Then, by using the flat part 161 formed on the end 11 of the key shift shaft 16#i,
A friction braking plate 48 facing the stepped portion 45 bK on the inner surface of the cylindrical shape 545 m is provided so as to be unable to rotate relative to the shaft 16.
8 constitutes a brake 49 that brakes the power shift shaft 16 by press-fitting engagement with the stepped portion 45b. Inside the cylindrical portion 458 is a piston 5 facing the friction brake plate 411.
0, and the friction brake plate 48 is moved to stage 1i via this piston 50.
A compression spring 51 is provided which biases the spring 51 to move in the direction of pressure contact with the spring 145b. The player 49 performs the braking operation by the biasing force of the above-mentioned compression spring 51, and also causes the piston 50 to retreat by the hydraulic action on the oil chamber 52 formed in the cylindrical portion 45a, thereby performing braking according to the function of 49. The details will be explained later.

油路形成兼軸受体３６内において、各パワーシフト軸１
１１．１７０周画上には第３図に示すように１該周面に
形成せる環状溝にて形成され九２個宛の油分配室５３Ｆ
’２．５３Ｒ及び５３　Ｆ、、　８３Ｆ。In the oil passage forming/bearing body 36, each power shift shaft 1
11. On the 170th circumferential image, as shown in FIG.
'2.53R and 53F,, 83F.

を設けである。この各油分配ｍ５３Ｆ１，５３１゜５３
Ｆ、、５３Ｆ８Ｆｉ、各パワーシフト軸ｌ・、１ｆに軸
線方向に沿わせ穿設されえ、第４図ＦＣｍ８ｔ）油路５
４Ｆ２，５４Ｒ及び５．４Ｆ、、５４Ｆ、を介して、相
幽する油圧クラッチ２４．１７及び２８．１４の油室２
４ａ１２Ｔ＆及び２１Ｓ畠、２６ｍへと、連通させであ
る。各油圧クラッチ２４．２Ｂ、　２６゜２７は、第３
図ＫＦ１油圧クラッチ２４についてＯみ参照数字を附し
て示すように、各パワーシフト軸Ｉｆ　　１７に固定せ
るクラッチハウジング器ｓと各遊転肯車２０．２１．２
１．２３とに、一方及び他方の摩擦ニレメン）５６．５
７を細動Ｏ＋自在に支持させ、クラッチハウジングｓ！
Ｓ内のビス１１５１１を、上記各油路５４　Ｆ１＃　５
４１１８４　Ｆ＠−５４Ｒを介しての油１１２４ｍ、２
５畠＃　　２６５１９２７１１への油圧作用で前進させ
、これによル摩擦エレメント５ｇ、’５７間を圧接させ
てクラッチ係合を得る、周知の多板式油圧クラッチに構
成されており、・その保合解除Ｌ、上記の油圧作用の解
除でリターンばね５９によりピストン５８の後退を得る
ことで、行なわれる。パワーシフト軸１６゜１７にはま
た、骸軸１６．１７の前方に設は九油１１６０．６１か
ら油圧クラッチ２４．２７及び２５゜２６の摩擦ニレメ
ン）５６．５７部へと潤滑油を供給する潤滑油路６２．
６３も、それぞれ形成されている。この各潤滑油路６２
．６３は纂３図に示すように前記支ｍｓ・４ｍ、４ｂＫ
よるノ（ツーシフト軸１６，１７支承部、つｔり図示の
ようにニードルベアリング６４．６５を備えさせである
支承部へも、潤滑油を供給するようＫ、後方へ延畏させ
である。ｍｓ図において６６は、）（ワーシフト軸１７
前方の油室６１′を前方側から閉鎖するように、油路形
成＠３４の前面に装着して設けたリリーフ弁で、このリ
リーフ弁６６は、潤滑油の油圧を設定させる喪めに設け
られて−る。This is provided. Each oil distribution m53F1,531゜53
F,,53F8Fi,can be drilled along the axial direction of each power shift shaft l, 1f, Fig. 4FCm8t) Oil passage 5
The oil chambers 2 of the hydraulic clutches 24.17 and 28.14 are connected to each other via 4F2, 54R and 5.4F, 54F.
It is connected to 4a12T& and 21S Hatake, 26m. Each hydraulic clutch 24.2B, 26°27 is a third
As shown in Figure KF1 hydraulic clutch 24 with reference numerals, the clutch housing device s fixed to each power shift shaft If 17 and each idler gear 20.21.2
1.23 and one side and the other side friction elm) 56.5
7 is freely supported by fibrillation O+, clutch housing s!
Connect the screw 11511 in S to each oil passage 54 F1#5.
41184 Oil 1124m via F@-54R, 2
It is configured as a well-known multi-disc hydraulic clutch that is moved forward by hydraulic action on # 5 Hatake # 265192711 and thereby pressurizes the friction elements 5g and '57 to obtain clutch engagement, and release the engagement. L. This is accomplished by retracting the piston 58 by means of the return spring 59 upon release of the above-mentioned hydraulic action. The power shift shaft 16.17 is also supplied with lubricating oil from the oil 1160.61 installed in front of the skeleton shaft 16.17 to the friction clutches 24.27 and 25.26 of the hydraulic clutch 56.57. Lubricating oil path 62.
63 are also formed respectively. Each lubricating oil passage 62
．． 63 is the support ms・4m, 4bK as shown in Figure 3.
The two-shift shafts 16 and 17 are also extended rearward to supply lubricating oil to the bearings 16 and 17, which are equipped with needle bearings 64 and 65 as shown.ms In the figure, 66 is ) (war shift shaft 17
A relief valve is installed on the front side of the oil passage forming @ 34 so as to close the front oil chamber 61' from the front side. Teru.

第４図に示すように、ｍ記し九油路形成兼軸受体３６に
上下方向に沿わせて形成しえ弁穴に挿入して、油圧クラ
ッチ式変速装置１０における前記の複数油圧クラッチ２
４−２７への作−油Ｏ論排を切換え制御する切換弁６７
を構成するスプール６８が、設けられている。また同様
に第４１１に示すように、油路形成筆軸受体３６に上下
方向Ｋｌわせて形成し九支承穴に挿入して、上記の複数
―圧りラッチ２４−２７に対・する作用油圧を制御する
調圧弁６９が設けられて−る。As shown in FIG. 4, the plurality of hydraulic clutches 2 in the hydraulic clutch type transmission 10 are inserted into the valve holes marked with m and formed along the vertical direction of the oil passage forming/bearing body 36.
Switching valve 67 that switches and controls the operation to 4-27 and oil O/discharge.
A spool 68 is provided. Similarly, as shown in No. 411, it is formed to be vertically Kl in the oil passage forming brush bearing body 36 and inserted into nine bearing holes to apply hydraulic pressure to the plurality of pressure latches 24-27. A pressure regulating valve 69 is provided to control the pressure.

前記したように、油路形成板３４０ｍＩａＫ俵着しであ
る油圧ポンプ４６社、油圧タラツチ式変連装置ｌＯの油
圧クラッチ２４−２７に対し給油を行なう目的のものと
されているが、ζＯ油圧ポンプ４６の油吐出口からＯｙ
９？要油路は、次のように形成されている。すなわち、
第３−５図に示すように、油路形成板３４の背面には、
適所にそれぞれ配して複数個の油＠Ｇ１を形成してあ）
、ま九―路形成兼軸受体３６０ｍｔｉＫは、適所にそれ
ぞれ配して複数個の油＠Ｇ、管形成してあって、これら
の油溝Ｇ１と油＠Ｇ、とは、前記した間板３５によって
開放端面側（つまり、油＠Ｇ、にりいては板３４背面側
、油溝Ｇｌｌについては板３６１ｉｌｉ面側）を閉鎖さ
れている。そして、油圧ポンプ４６の油吐出口は、前記
ハウジング４５内の油入と油路形成板３４内の油入（以
上、図示せず）とを経て、油路形成板３４背面上のＩＩ
Ｉ！Ｉ＃ｌＧ１に適宜に連らねてあ夛、該油溝Ｇ１をさ
らＫ、間板３５を貫通させて適宜に形成された油入（図
示せず）Ｋより油路形成兼軸受体３６鍵山上の油溝Ｇ、
へと適宜に連らねである。As mentioned above, the hydraulic pumps manufactured by 46 manufacturers are equipped with oil passage forming plates of 340mIaK and are said to be intended for supplying oil to the hydraulic clutches 24-27 of the hydraulic latch-type transmission device lO, but the ζO hydraulic pump Oy from 46 oil outlet
9? The essential oil passages are formed as follows. That is,
As shown in FIG. 3-5, on the back side of the oil passage forming plate 34,
Arrange them in appropriate places to form multiple oils @G1)
, the shaft forming/bearing body 360mtiK has a plurality of oil@G tubes arranged at appropriate locations, and these oil grooves G1 and oil@G are connected to the spacer plate 35 described above. The open end surface side (that is, the back surface side of the plate 34 for oil @G, and the surface side of the plate 361ili for the oil groove Gll) is closed by. The oil discharge port of the hydraulic pump 46 passes through an oil inlet in the housing 45 and an oil inlet in the oil passage forming plate 34 (not shown), and then connects to an oil outlet on the back surface of the oil passage forming plate 34.
I! Connect the oil groove G1 appropriately to I#lG1, extend the oil groove G1, and connect the oil groove (not shown) K formed appropriately by penetrating the spacer plate 35 to form an oil passage and bearing body 36 key thread. Upper oil groove G,
It is connected appropriately.

そしてさらＫ、油溝ｃｓ、ｔｓそれが適宜に切換弁６７
と調圧弁８９に導かれるように形成すると共に、切換弁
６７の二次側ポートを、油＠　Ｇ、と波路形成兼軸受体
３６内の油入（その−例は、第３図に図示の油入７０）
を介して前記の油分配ｍ　５３　Ｆ、。Then, K, oil grooves cs, ts are changed as appropriate to the switching valve 67.
In addition, the secondary side port of the switching valve 67 is formed so as to be guided to the pressure regulating valve 89, and the secondary side port of the switching valve 67 is connected to the oil @ Oil filled 70)
said oil distribution m 53 F, via.

５３　Ｆｌｌ、　５３　Ｆ、、　５３　Ｒへと。、導い
ているのである。ｌｌ圧弁６９のリリーフポートは、上
記とほぼ同様にして前記油１ｉ１６０，６１へと導かれ
ており、また切換弁６７のタンクポートも、上記のほぼ
同様にしてクラッチハウジング２内へと導かれて匹る。53 Fll, 53 F, 53 R. , is guiding. The relief port of the pressure valve 69 is guided to the oil 160, 61 in substantially the same manner as described above, and the tank port of the switching valve 67 is also guided into the clutch housing 2 in substantially the same manner as described above. There are many.

前記したブレーキ４９は、油圧クラッチ式変適装［１０
の中立状態でパワーシフト軸１６を制御し、もって優軸
車軸６ａを制動して、不一の車−発進を防止する機能の
ものとされており、この良め、幀ブレーキ４９の―記油
童６２に対しては、油圧クラッチ式変速装置１０の変適
状簡でＯみ油圧が作用せしめられて、ブレーキ４９調−
作−が解除され、油圧クラッチ弐質適装置１Ｇが中立状
態へと切替えられると自動的に油１１５２への油圧作用
が解除されて、圧縮ばね５１作用でブレーキ４９が鯛−
作動するように、図られてｉる。上記のようにブレーキ
４９作−を自動的に切替え制御すること自体は、特開＠
５Ｂ−４５８３０号企゛報等から公知であるように、油
圧ポンプ４６から切換弁６７へ至る給油回路、フォル切
換弁６γの中立位置では油圧が解除され各作用位置では
油圧が成立する給油回路を、ブレーキ油１１５２へと接
続することで、行なうようにされているが、このえめの
接続波路は、前記ハウジング４５内に形成されている。The brake 49 described above is a hydraulic clutch type modification [10
The function is to control the power shift shaft 16 in the neutral state of the vehicle, thereby braking the dominant axle 6a, and to prevent the vehicle from starting in a wrong direction. On the child 62, O hydraulic pressure is applied to the hydraulic clutch type transmission 10, and the brake is adjusted to 49.
When the action is released and the hydraulic clutch adjustment device 1G is switched to the neutral state, the hydraulic action on the oil 1152 is automatically released and the brake 49 is activated by the action of the compression spring 51.
It is designed to work. Automatically switching and controlling the brake 49 operation as described above is described in Japanese Patent Application Publication No.
5B-45830, etc., the oil supply circuit from the hydraulic pump 46 to the switching valve 67, the oil supply circuit in which the hydraulic pressure is released at the neutral position of the switchover valve 6γ, and the oil pressure is established at each operating position. , to the brake fluid 1152, this connecting wave path being formed within the housing 45.

第６図に示すように、クラッチハウジング２内には、前
記油路形成板３４よりも前方位置においてハウジング２
と一体的な支壁部２ｂを設けてあ〉、前記駆動軸８の前
端ｓｒｉ、との支壁部２ｂＫボールベアリング９３を介
して軸受けされている。As shown in FIG. 6, inside the clutch housing 2, the housing 2 is located at a position forward of the oil passage forming plate 34.
A support wall portion 2b is provided which is integral with the front end sri of the drive shaft 8, and the support wall portion 2bK is supported via a ball bearing 93.

上記の支Ｉ１１部２ｂは、同様に第６図に示すようＫ、
クラッチハウジング２の底壁よりも下方にまで地山させ
てあり、鋏延出部において上記支壁部２ｂに、伝動軸１
１端の鋺記出カー卓４１（第３図）を利用して前輪駆動
力の取出しを行なう場合に動力取出し用の伝動軸を挿通
支持させる筒部２ｃを、一体形成してあ夛、二輪駆動蓋
トラクタのときは、鋏筒部２Ｃ開口鴫を１ｌｉ９４によ
り閉鎖することとしである。第４図に示すように、前記
油路形成兼軸受体３６には、上記の筒部２ｃと同心的な
穴９５であって上記の動力取出し用伝動軸を挿通支持さ
せる穴９５を形成してあり、同様の穴は図示を省略する
が、ｓｔｒ記の油路形成板３４と間板３５とにも穿けら
れている。The above-mentioned support I11 part 2b is also K, as shown in FIG.
The clutch housing 2 is laid down below the bottom wall, and the transmission shaft 1 is attached to the support wall 2b at the scissors extension part.
When extracting the front wheel driving force using the power output car table 41 (Fig. 3) at one end, the cylindrical part 2c through which the transmission shaft for power extraction is inserted and supported is integrally formed. In the case of a driving lid tractor, the opening of the scissor tube portion 2C is closed by 1li94. As shown in FIG. 4, the oil passage forming/bearing body 36 has a hole 95 concentric with the cylindrical portion 2c through which the power extraction transmission shaft is inserted and supported. Although not shown, similar holes are also made in the oil passage forming plate 34 and the spacer plate 35 shown in str.

ｊｌ！＃！Ｊにおいて７１は、油圧クラッチ式変適装置
１０における前記のＦ、遊転−車！１２とパワーシフト
軸１７間に配して設けられ九一方向クラッチで、この一
方向クラッチ７１は、特開昭Ｓ１！−１３１０６５号公
報等から公知であるように、パワーシフト軸１７側から
相対的に正転方向（車輪鋺進方向）Ｋ駆動されると係合
し、？、遊転歯車２雪ヲハワーシフト軸１７に結合して
、工／ジン１０引きが１を容島郷、するものである、そ
して図示の場合には特′に、峡一方向クラッチ７１を、
パワーシフト軸１７に嵌着されている・前記歯車３０の
ボス部の延長部３０１上に配して設け、もって逆に歯車
３０嵌着用のキー７２を長いものにし得るように、図っ
ている。jl! #! In J, 71 is the above-mentioned F in the hydraulic clutch type change device 10, an idling wheel! 12 and the power shift shaft 17. This one-way clutch 71 is a 9-way clutch arranged between the power shift shaft 17 and the JP-A-Sho S1! As is known from Japanese Patent No. 131065 and the like, when the power shift shaft 17 is driven in the forward rotation direction (wheel advance direction) K, the ? , the free rotating gear 2 is connected to the power shift shaft 17, and the gear/engine 10 is connected to the gear 1, and in the illustrated case, the one-way clutch 71 is
It is arranged on an extension 301 of the boss portion of the gear 30 fitted to the power shift shaft 17, so that the key 72 for fitting the gear 30 can be made longer.

次に、図示農用トラクタの他Ｏ１１分の構成について、
概略説明しておくと、前記し九機械式資適装置１２は、
第２．３図に示すように％前記中１伝動軸９上に２個の
変速歯車７３．７４を一体形成すると共に、＃紀伝動輪
１１上に２個０遊転変速歯車７５．７＠を遊嵌して設け
て、大径側の遊転変速歯車７５はこれを中空伝動軸９上
の上記変速−車７３に、また小径側の遊転歯車７６はこ
れを中空伝動輪９上の前記した歯車２９に、それぞれ噛
合せている。伝動軸ｌｌ上にはまえ、スプライン嵌合に
より摺動自在ではあるが軸１１と相対回転不能にシフト
歯車７７を設けてあり、このシフト歯寧７７は、中空伝
動輪９上の変速歯車７４に−合せ得るものに形成されて
いると共に、そのボス部に、上記遊転変速歯車７６０＃
ス部に形成せる係合爪７５ｍに保合可能な係合爪７７１
と、上記遊転変速歯車７６に係合可能な円＊７７ｂとを
、形成しであるものに構成されている。以上により機械
式変速装置１２は、伝動軸１１上でシフト歯車７７を選
択的に摺動変位させ、係合爪７７ｍを係合爪７５８に係
合させ遊転変速−車７５を伝動軸１１に結合することで
１速の変速比で、またシフト歯車７７を中空伝動輪９上
の変速歯車７４に噛合させることで２連の変速比で、さ
らに内−７７ｂを遊転変速−車７６に−合せ諌歯車７６
をれぞれ選択的に中空伝動軸９と伝動軸１１１ｍを連動
連結するものと、されている。Next, regarding the configuration of O11 other than the illustrated agricultural tractor,
To briefly explain, the above-mentioned nine mechanical qualification devices 12 are as follows:
As shown in FIG. 2.3, two speed change gears 73.74 are integrally formed on the middle transmission shaft 9, and two idle speed change gears 75.7@ are formed on the #th generation transmission wheel 11. They are loosely fitted, and the large-diameter free-rotating gear 75 is connected to the above-mentioned speed change wheel 73 on the hollow transmission shaft 9, and the small-diameter free-rotating gear 76 is connected to the above-mentioned speed change wheel 73 on the hollow transmission wheel 9. The gears 29 are meshed with each other. A shift gear 77 is provided on the transmission shaft 11 through spline fitting so that it can slide freely but cannot rotate relative to the shaft 11. This shift gear 77 is connected to the transmission gear 74 on the hollow transmission wheel 9. - The idling speed change gear 760# is formed in a shape that can be matched with the above-mentioned free rotating speed change gear 760# on the boss portion thereof
Engagement claw 771 that can be secured to engagement claw 75m formed on the base part
and a circle *77b that can be engaged with the idle speed change gear 76. As described above, the mechanical transmission 12 selectively slides and displaces the shift gear 77 on the transmission shaft 11, engages the engagement pawl 77m with the engagement pawl 758, and causes the idle speed change wheel 75 to move onto the transmission shaft 11. By coupling, the gear ratio is 1st speed, and by meshing the shift gear 77 with the gear 74 on the hollow transmission wheel 9, the gear ratio is 2 gears, and the inner gear 77b is connected to the idle gear 76. Dowel gear 76
The hollow power transmission shaft 9 and the power transmission shaft 111m are selectively connected to each other.

ま九前記駆動軸８は、建ツ７ｗンケース４内からリヤハ
ウジング５内にオで嬌出させてあり、リヤハウジング器
内において該駆動軸８に、カップリング７８により同心
的な他Ｏ駆動−７・を連結し、この他の駆動軸７９と前
記ＰＴＯ軸７との関に、第２図に示すように、作業機動
力についてＯ変速を行なうＰＴＯ変速鏝置装０を設けて
いる。(9) The drive shaft 8 is projected from the inside of the case 4 into the rear housing 5, and a concentric drive shaft 8 is connected to the drive shaft 8 in the rear housing by a coupling 78. As shown in FIG. 2, a PTO gear shifting device 0 is provided between the other drive shaft 79 and the PTO shaft 7.

このデＴＯ変速装置８０は、駆動軸７９Ｋｍｍｌ定して
設は九３個の変速−車８１，８１８３と、ｒＴＯ軸７に
遊嵌され上記変速歯車８１−８３中の最小径の変速−車
８１に噛合されている遊転歯車８４と、２丁０軸７上Ｋ
１１−のみ自在に設けられた一体的な２個のシフト歯車
８５．８６と、遊転−車８４とシフト歯車８５とのボス
部にそれ（れ噛合爪８７８．８７ｂを形成して鋏両−車
８４゜８５間に介在させ九噛合クラッチ８１とを、備え
ている。そしてこのＰＴＯ変遮装＊ＳＯは、ＰＴ０軸７
上でシフト歯車８５．８６を選択的に摺動変位させ、噛
合爪８７８．８７ｂ間の噛合いによシ噛合クラッチ８７
をクラッチ係合させ遊転−車８４をＰＴＯ軸７に結合す
ることでｌ速の変速比を、歯車８２．８５閣の噛合いに
よｐ２速の変速比を、歯車８３．８６間の噛合いにより
３速の変速比を、それぞれ選択的に得ることができるも
のに、構成きれている。This de-TO transmission 80 has a drive shaft of 79 km, and has 93 speed change wheels 81 and 8183, and a speed change wheel 81 which is loosely fitted to the rTO shaft 7 and has the smallest diameter among the speed change gears 81-83. The free rotating gear 84 meshed with
Two integral shift gears 85 and 86 are freely provided on the idling wheel 84 and the shift gear 85, and engaging pawls 878 and 87b are formed on the boss portions of the idler wheel 84 and the shift gear 85. It is equipped with a nine-tooth clutch 81 interposed between the wheels 84 and 85.This PTO transformation/shield*SO is connected to the PT0 shaft 7.
By selectively slidingly displacing the shift gears 85 and 86 above, the engagement clutch 87 is caused to engage between the engagement claws 878 and 87b.
By engaging the clutch and connecting the idle wheel 84 to the PTO shaft 7, the gear ratio of 1 speed is set, the gear ratio of gear 2 is set by the meshing of gear 82.85, and the gear ratio of gear 2 is set by the meshing of gear 83.86. In particular, the gear ratios of the three speeds can be selectively obtained.

篤１図において、８８は前記切換弁６７を変位操作して
油圧クラッチ式変速装置１０の変速段を切替えるための
主変速レバーで、この主変速レバー８８は、［４図に一
部を示す接続機構８９を介して前記スグール６８へと接
続されている。同様に箒１図において、９０は前記シフ
ト歯車７７を変位操作し機械式変速装置１２の変速段を
切替えるたゆの８ｆ速レバー、９１は前記シフト贈車８
５゜８６を変位操作しＰＴＯ変速装置８０の変速段を切
替えるためのＰＴＯ変速レバーである。ま九第２図にお
いて９２は、前記した各差動装置出力軸１４１に配して
設けられるブレーキである。In Figure 1, reference numeral 88 denotes a main gear shift lever for changing the gear stage of the hydraulic clutch type transmission 10 by displacing the switching valve 67. It is connected to the sugur 68 via a mechanism 89. Similarly, in the drawing of the broom 1, 90 is the 8F speed lever that displaces the shift gear 77 and changes the gear stage of the mechanical transmission 12, and 91 is the shift gear 8.
This is a PTO shift lever for changing the gear stage of the PTO transmission device 80 by displacing 5°86. 9. In FIG. 2, reference numeral 92 denotes a brake disposed on each differential output shaft 141 described above.

以上の実施例について１）＠＠から明らかなように、こ
の発明の油圧クラッチ式変適装置用の油路形成装置は、
パワーシフト軸１６．１７上に設置−ａれ九油圧クラッ
チ２４．２に、２６．１７に対しパワーシフト軸１１１
７内に穿１１された油路５４Ｆ１．５４Ｆ、、５４Ｆ、
、５４１を介して作−柚を供給するように構成され先油
圧タラツチ式変速装置用の油路形成装置であって、油圧
クラッチ式変速装置１０におけるパワーシフト軸を會め
ての伝動軸８．１６．１７１Ｅ）　−１端部を板状Ｏ油
踏彫威兼軸受体３６に支持させると共に、＃油路形成兼
軸受体３６の端面上に油路形成板３４を、むれらＯ油路
形成兼軸受体３６と油路形成板３４とにそれぞれ形成さ
れている油路Ｇ、、　ＧｌＭを接続すｈＩｔめの袖穴を
穿設される薄い間板３ｓｔ介してｌｌＩｌ装定し、前記
したパワーシフト軸１１１．１７内Ｏ油路５４Ｆ１．５
４Ｆ、、５４Ｆ、、５４１を上記し大油路形成兼軸受体
３６内の油路Ｋｍ絖するためＯ環状の油分配＊５３Ｆ、
、５３Ｆ、、５３Ｆ、、ａｌｌを、パワーシフト軸ｔｇ
、ｌｙの一端伽外周画と油路形成兼軸受体３６との間に
形成したことを、特徴としてなるものであって、次のよ
うな長所を備えている。Regarding the above embodiments 1) As is clear from @@, the oil path forming device for the hydraulic clutch type variable device of the present invention is as follows:
Installed on the power shift shaft 16.17 - a nine hydraulic clutch 24.2, 26.17 on the power shift shaft 111
Oil passage 54F1.54F, 54F, bored 11 in 7
, 541 is an oil passage forming device for a hydraulic clutch type transmission, which is configured to supply actuation through the transmission shaft 8. 16.171E) The -1 end is supported by the plate-shaped O oil tread carving and bearing body 36, and the oil passage forming plate 34 is placed on the end face of the #oil passage forming and bearing body 36, and the O oil passage is formed The oil passages G, GlM formed in the bearing body 36 and the oil passage forming plate 34, respectively, are connected to each other through thin intervening plates 3st in which hIt-th armholes are bored, and the above-mentioned power Shift shaft 111.17 internal O oil passage 54F1.5
4F, , 54F, , 541 are described above, and an O-ring shaped oil distribution system is used to form a large oil passage and to form an oil passage Km in the bearing body 36 * 53F,
, 53F, , 53F, , all, power shift axis tg
, ly is formed between one end of the outer periphery and the oil passage forming/bearing body 36, and has the following advantages.

すなわちこの発明の油路形成装置は、油圧クラッチ式変
速装置ｌＯにおける複数油圧クラッチに連らなる位置固
定側の複数油路を形成するのに、油圧クラッチ式変速装
置１０における伝動軸８゜１６．１７の一端部を支承す
る板状の油路形成兼軸受体３６の他に、上記のような油
路形成板３４と間板３５とを用いていて、該三者３４ｉ
、３４゜３５の組合せにより必要な油路を形成するもの
とされていることから、上記した油路形成兼軸受体３６
のみを用いて油路を形成する場合と異なり該油路形成兼
軸受体３６には、軸受用のベアリング保持部を避は友位
置で加工上、無理のない形状で油路を形成加工できると
共に、油路形成兼軸受体３６と油路形成板３４との油路
を薄い間板３５中の油入にて接続する構造で、油路形成
兼軸受体３６の、油路Ｇ２と油路形成板３４の油路Ｇ１
との大部分を路形成兼軸受体３６と油路形成板３４と０
４）鉤造成形時に同時に形成できる合一にて形成でＩゐ
こととなｐｌまた薄い間板３！６には細穴Ｏ穿歇形成を
簡単に行なえることから、最初に述べえような単一の油
路形成板を用いた場合と比較して、油路の形成加工が遥
かに容晶であるもＯとなってｉる。That is, the oil passage forming device of the present invention forms a plurality of oil passages on the fixed position side connected to the plurality of hydraulic clutches in the hydraulic clutch type transmission lO, but the transmission shaft 8° 16. In addition to the plate-shaped oil passage forming/bearing body 36 that supports one end of the oil passage 17, the oil passage forming plate 34 and the spacer plate 35 as described above are used, and the three members 34i
, 34° and 35 to form the necessary oil passage, the above-mentioned oil passage forming/bearing body 36
Unlike the case where the oil passage is formed using a chisel, the oil passage forming/bearing body 36 does not have a bearing holding part for the bearing, so it is possible to form the oil passage in a reasonable shape during machining. , has a structure in which the oil passages between the oil passage forming/bearing body 36 and the oil passage forming plate 34 are connected by oil filling in the thin intervening plate 35, and the oil passage G2 and the oil passage forming of the oil passage forming/bearing body 36 are connected. Oil passage G1 of plate 34
The majority of the passage forming and bearing body 36 and the oil passage forming plate 34
4) It is possible to form the joint by joining which can be formed at the same time as the hook forming.In addition, it is easy to form small holes O in the thin intervening plates 3 and 6. Compared to the case where a single oil passage forming plate is used, the oil passage forming process is much easier.

１１九パワーシフト軸１１１７内の作−油倶鎗油路５４
Ｆ１．５４Ｆ、、５４Ｆ、、５４ｍを位置一定側の油路
に接続する九めＯ１ｌ軟の油分配置１１１３Ｆ、。119 Work in power shift shaft 1117 - Aburakuyari oil road 54
F1.54F, , 54F, , 54m is connected to the oil path on the constant position side with the ninth O1l soft oil arrangement 1113F.

６３Ｆ、５３Ｆ、、５３１をして、パワーシフト軸１６
．１７（）一端部外周面と油路形成兼軸受体ｓ６との関
に形成していることから、最初に述べえような油路受継
筒を用いて上記のようＩｌｌ状の油分配室を形成する場
合と異な９、油路形成兼軸受体３６にパワーシフト軸１
６．１７Ｄ一端部を支承させると直ちに環状の油分配室
５３Ｆ、５３Ｆ、。63F, 53F, 531, power shift shaft 16
．． 17 () Since it is formed at the connection between the outer circumferential surface of one end and the oil passage forming/bearing body s6, the above-mentioned Ill-shaped oil distribution chamber is formed using the oil passage transfer tube mentioned first. 9, the power shift shaft 1 is attached to the oil passage forming/bearing body 36.
6.17D As soon as one end is supported, the annular oil distribution chamber 53F, 53F,.

５３Ｆ、、５３Ｒが形成される仁ととなるから、この発
明の油路形成装置１１Ｍ、層重て作業を簡単化するもの
となっている。Since 53F, 53R are the grooves to be formed, the oil passage forming device 11M of the present invention simplifies the layering work.

第１図はこの発明の一実施例を装備した農用トラクタの
概略側面図、第２図は同トラクタにおける伝動機構を示
す機構図、第３図は同トラクタ要部の一部展開縦断側面
図、第４図Ｆｉ、第３図の■−■線（沿う一部切欠き縦
断正面図、第５図は上記トラクタ要部の部材のみの横断
平面図、第６図は上記トラクタ要部の部材のみの縦断側
面図である。FIG. 1 is a schematic side view of an agricultural tractor equipped with an embodiment of the present invention, FIG. 2 is a mechanical diagram showing the transmission mechanism of the tractor, and FIG. 3 is a partially exploded longitudinal sectional side view of the main parts of the tractor. Fig. 4 Fi, a partially cutaway longitudinal sectional front view along line ■-■ in Fig. 3; Fig. 5 is a cross-sectional plan view of only the main parts of the tractor; Fig. 6 shows only the main parts of the tractor. FIG.

２・・・クラッチハウジング、４・・・ミッションケー
ス、４ｍ、４ｂ、４ｃ・・・連結部、８・・・駆動軸、
９・・・中空伝動軸、１０・・・油圧クラッチ式変速装
置、１１１７・・・パワーシフト軸、１８．１９・・・
変速歯車、２０．２１，２２．２３・・・遊転＠＠、２
４゜２５．２６．２７・・・油圧クラッチ、２８．２９
゜３０．３１・・・歯車、３２・・・螺杵、３３・・・
ナツト、３４・・・油路形成板、３５・・・間板、３６
・・・油路形成兼軸受体、３６ｍ・・・連結部、３７・
・・螺杵、４６・・・油圧ポンプ、５３Ｆ、、５３Ｆ、
、５３Ｆ、、５３Ｒ・・・油分配室、５４　Ｆ、、　　
５４　Ｆ、、　５４　Ｆ、、　５４　Ｒ・・・油路、６
７・・・切換弁、６９・・・調圧弁。2...Clutch housing, 4...Mission case, 4m, 4b, 4c...Connection part, 8...Drive shaft,
9...Hollow transmission shaft, 10...Hydraulic clutch type transmission, 1117...Power shift shaft, 18.19...
Speed change gear, 20.21, 22.23... Idle @@, 2
4゜25.26.27...Hydraulic clutch, 28.29
゜30.31...gear, 32...screw punch, 33...
Nut, 34... Oil path forming plate, 35... Interval plate, 36
...Oil passage formation and bearing body, 36m...Connection part, 37.
... Screwdriver, 46... Hydraulic pump, 53F, 53F,
, 53F, , 53R... Oil distribution room, 54 F, ,
54 F,, 54 F,, 54 R...oil passage, 6
7...Switching valve, 69...Pressure regulating valve.

Claims (1)

【特許請求の範囲】[Claims] パワーシフト軸上に設置された油圧クラッチに対しパワ
ーシフト軸内に穿設され九油路を介して作動油を供給す
るように構成された油圧クラッチ式変速装置用の油路形
成装置であって、油圧クラッチ式変速装置におけるパワ
ーシフト軸を含めての伝動軸の一端部を板状の油路形成
兼軸受体に支持させると共に、骸油路形成兼軸受体の端
面上に油路形成板を、これらの油路形成兼軸受体と油路
形成板とにそれぞれ形成されている油路間を接続するた
めの油穴を穿設される薄い間板を介して固定装着し、鍵
記したパワーシフト軸内の麺路を上記し九波路形成兼軸
受体内の油路に接続するための環状の油分配室を、パワ
ーシフト軸の一熾部外ｊｌＩＴｏと油路形成兼軸受体と
の間に形成し友ことを、特徴とする油路形成装置。An oil passage forming device for a hydraulic clutch type transmission device configured to supply hydraulic oil to a hydraulic clutch installed on the power shift shaft through nine oil passages drilled in the power shift shaft. In a hydraulic clutch type transmission, one end of the transmission shaft including the power shift shaft is supported by a plate-shaped oil passage forming/bearing body, and an oil passage forming plate is provided on the end surface of the oil passage forming/bearing body. It is fixedly attached via a thin plate with oil holes drilled to connect the oil passages formed in these oil passage forming/bearing bodies and the oil passage forming plate, respectively, and the keyed power An annular oil distribution chamber for connecting the oil passage in the shift shaft to the oil passage in the nine wave passage forming and bearing body is provided between one outer part of the power shift shaft and the oil passage forming and bearing body. An oil path forming device that is characterized by being a forming friend.