JPS62147151A - Change gear - Google Patents

Abstract

PURPOSE:To restrict an occupation space in the radial direction of a power transmission shaft by collecting a hydraulic clutch and planetary gear mechanism on the same power transmission shaft, in the case of the change gear of a tractor, etc. CONSTITUTION:A change gear parallelly provides, in the shaft center direction on one power transmission shaft 5, a reciprocal planetary gear mechanism 21 consisting of a carrier 16 parallelly pivoting a pair of planetary gear 18A and 18B, a first sun gear 19 integrated with a power transmission shaft 5 and a second sun gear 20 loosely engaged herewith, and hydraulic clutches 34A and 34B. And the carrier 16, a clutch casing 26 and the second sun gear 20 are integrally rotated when the first hydraulic clutch 34A is operated, and the large diameter planetary gear 18A rotates the power transmission shaft 5 together with the sun gear 19 in the same direction as that of the carrier 16, so the forward condition appears. On the other hand, the casing 26, a mission case 22 and the sun gear 20 are united in a body when the second hydraulic clutch 34B is operated, so the backward condition appears. Thus, the occupation space in the radial direction of the power transmission shaft can be restricted.

Description

【発明の詳細な説明】 〔産業上の利用分野〕 本発明は二りの壮圧クラッチの切換作動に基づいて正逆
切換伝動可能なトラクタ及びコンバイン等に搭載されて
使用される変速装置に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a transmission device that is mounted on a tractor, combine harvester, etc. and is capable of forward and reverse transmission based on the switching operation of two high-pressure clutches.

〔従来の技術〕[Conventional technology]

この種の変速装置において、従来は、エンジンからの動
力を受ける入力軸としての第１伝幼軸に前後進り換用の
二つの油圧クラッチを介装するとともに、この第１伝動
軸と、この第１伝動軸に平行に架設された第２伝動軸と
の間に旧記伯王クラッチのの換によって前後進状窓を現
出可能なギヤ伝！＃機構を介装してあった（例えば実開
昭５８−６３４２９号公報）。In this type of transmission, conventionally, two hydraulic clutches for forward/rearward shifting are interposed on a first transmission shaft serving as an input shaft that receives power from the engine, and two hydraulic clutches are interposed between the first transmission shaft and the first transmission shaft. A gear transmission that can create a forward and backward movement window between the second transmission shaft installed parallel to the first transmission shaft by replacing the old Hakuo clutch! A # mechanism was installed (for example, Japanese Utility Model Application Publication No. 58-63429).

〔発明が解決しようとする問題点〕[Problem that the invention seeks to solve]

しかし、この場合には単純なギヤ伝動機構を採る為に、
二軸に亘って後進伝動側ギヤ機構を設けなければならず
、配置の為の占有スペースが大きくなっていた。However, in this case, in order to adopt a simple gear transmission mechanism,
A reverse transmission side gear mechanism had to be provided over two axes, which required a large amount of space.

本発明の目的はギヤ伝動機構として合理的な機構を選定
することによって占有スペースの削減化を図れるものを
提供する点にある。An object of the present invention is to provide a gear transmission mechanism that can reduce the occupied space by selecting a rational mechanism.

〔問題点を解決するだめの手段〕[Failure to solve the problem]

本発明による特徴構成は、一体作動する一対の遊星ギヤ
を並列枢支したキャリアと、一方の遊星ギヤと咬合状態
にあって伝動軸と一体の第１の太陽ギヤと、他の遊星ギ
ヤと咬合状店にあって第１の太陽ギヤに遊嵌された第２
の太陽ギヤとからなる正逆転用遊星ギヤ機構、及び、キ
ャリアと第２太陽ギヤを一体作動させる正転状態とミッ
ションケースに対して第２太陽ギヤを一体的に固定する
逆転状態とに切換える二つの油圧クラッチとを備えた変
速装置であって、前記遊星ギヤ機構と油圧クラッチとを
同一伝動軸上で軸心方向に並設しである点にあり、その
作用効果は次の通りである。The characteristic configuration according to the present invention includes a carrier in which a pair of planetary gears that operate integrally are supported in parallel, a first sun gear that is in mesh with one of the planetary gears and is integral with the transmission shaft, and a carrier that is in mesh with one of the planetary gears and is integrated with the transmission shaft. The second sun gear is loosely fitted to the first sun gear in the store.
a planetary gear mechanism for forward and reverse rotation consisting of a sun gear; and a planetary gear mechanism for forward and reverse rotation, which switches between a forward rotation state in which the carrier and the second sun gear are operated integrally, and a reverse rotation state in which the second sun gear is integrally fixed with respect to the mission case. The present invention is a transmission equipped with two hydraulic clutches, in which the planetary gear mechanism and the hydraulic clutch are arranged side by side in the axial direction on the same transmission shaft, and the effects thereof are as follows.

〔作　用〕[For production]

つまり、一方の油圧クラッチを作動させると、キャリア
と第２太陽ギヤを一体作動させることができるので、こ
の第２太陽ギヤとこの第２太陽ギヤに咬合する遊星ギヤ
とを一体的に作動させることができ、この遊星ギヤ機構
を介して第１太陽ギヤとともに伝動軸をキャリアと一体
作動させて正転状態を得る。　又、他方の油圧クラッチ
を作動させると、第２太陽ギヤをミッションケース側の
固定系に組込むことができ、この固定された第２太陽ギ
ヤに対して前記遊星ギヤ機構を相対回転させ、この遊星
ギヤ機構と咬合する第１太陽ギヤと伝動軸とをキャリア
と反対方向に回転させ、逆転状態を得る。In other words, when one of the hydraulic clutches is operated, the carrier and the second sun gear can be operated together, so this second sun gear and the planetary gear meshing with this second sun gear can be operated integrally. Through this planetary gear mechanism, the transmission shaft and the first sun gear are operated integrally with the carrier to obtain a normal rotation state. Furthermore, when the other hydraulic clutch is operated, the second sun gear can be assembled into the fixed system on the mission case side, and the planetary gear mechanism is rotated relative to the fixed second sun gear. The first sun gear and the transmission shaft that mesh with the gear mechanism are rotated in the opposite direction to the carrier to obtain a reversed state.

従って、′＠′１太陽ギヤに対して第２の太陽ギヤを遊
嵌し、この第２の太陽ギヤを油圧クラッチの切換゛操作
によって、固定する状態とキャリアと一体化する状係と
に切換える構成を持つ遊星ギヤ機構を採用することによ
って、同一伝動軸上にギヤ機構をまとめることができる
とともに、前記第２太陽ギヤに対して油圧クラッチのゲ
ージング等を連動すればよいので、必然的に遊星ギヤ機
構と油圧クラッチとが−６方向に並設されることになる
。Therefore, the second sun gear is loosely fitted into the first sun gear, and the second sun gear is switched between a fixed state and an integrated state with the carrier by switching the hydraulic clutch. By adopting a planetary gear mechanism with a configuration, the gear mechanisms can be grouped together on the same transmission shaft, and gauging of the hydraulic clutch can be linked to the second sun gear, so it is necessary to use a planetary gear mechanism. The gear mechanism and the hydraulic clutch are arranged in parallel in the -6 direction.

〔発明の効果〕〔Effect of the invention〕

その結果、同一伝動軸上に油圧クラッチと遊星ギヤ機構
をまとめることができ、伝動軸半径方向への占有スペー
スを抑えることができることによって、第２図に示すよ
うに、例えば４輪・２輪切換用クラッチ（ト）の設置ス
ペースヲミッションケースのの拡大化を図ることなく確
保することができ、設計時の許容度が大きい。As a result, the hydraulic clutch and planetary gear mechanism can be combined on the same transmission shaft, and the space occupied in the radial direction of the transmission shaft can be suppressed, making it possible to switch between four wheels and two wheels, for example, as shown in Figure 2. The installation space for the clutch (g) can be secured without enlarging the transmission case, allowing for greater tolerance during design.

但し、遊星ギヤ機構と油圧クラッチとを同一伝動軸上に
投置したものとして、Ｕ、Ｓ、　Ｐａｔｅｎｔ４４６８
９８３　　号に開示されたものがあるが、このものに対
して本発明のものは二つの油圧クラッチも伝動軸心に沿
って並設されているので、半径方向への突出はより小さ
なものであり、より設置スペースの縮小化を図ることが
できる。However, assuming that the planetary gear mechanism and the hydraulic clutch are placed on the same transmission shaft, U, S, Patent 4468
There is a clutch disclosed in No. 983, but the present invention has two hydraulic clutches arranged side by side along the transmission axis, so the protrusion in the radial direction is smaller. , the installation space can be further reduced.

〔実施例〕〔Example〕

農用トラクタに搭載されて使用される変速装置を説明す
る。A transmission device mounted and used on an agricultural tractor will be explained.

第２図に示すように、エンジン（ＥＩ　Ｋ直結されたＰ
ＴＯ伝動軸（１）を後車輪デフケース（２）の後方まで
延出するとともに、減速ギヤ機構（３）を介してＰＴＯ
軸（４）に伝動連結してＰＴＯ出力系を構成しである。As shown in Figure 2, the engine (EI K directly connected P
The TO transmission shaft (1) extends to the rear of the rear wheel differential case (2), and the PTO transmission shaft (1) is extended to the rear of the rear wheel differential case (2), and the PTO
It is transmission connected to the shaft (4) to constitute a PTO output system.

　一方、ＰＴＯ伝幼伝動１）に走行用第１伝動軸（６）
を外嵌支承するとともに、この第１伝動軸（５）とこの
第１伝動軸（５）に平行に架設された第２伝動軸（６）
との間に４段に変速可能なギヤ式主変速装置（７）、第
２伝動軸（６）の後端に略軸心を一致させた状態で設け
られた第３伝動軸（８）と前記ＰＴＯ伝幼伝動１）との
間にギヤ式副変速装置（９）、及び、第３伝動軸（８）
と平行に架設された前輪用駆動軸（１０）との間に超減
速装置（６）を夫々設けである。　又、前記第３伝動軸
（８）の後端に出力用ベベルギヤ（２）を設け、後車輪
用デフ（２）にエンジン出力を伝達するようＫしである
。On the other hand, the first transmission shaft (6) for traveling is attached to the PTO transmission 1).
This first transmission shaft (5) and a second transmission shaft (6) installed parallel to this first transmission shaft (5) are externally supported.
A gear-type main transmission (7) capable of shifting into four stages between the two, and a third transmission shaft (8) provided with its axis substantially aligned with the rear end of the second transmission shaft (6). A gear type auxiliary transmission (9) and a third transmission shaft (8) are provided between the PTO transmission 1).
A super deceleration device (6) is provided between the front wheel drive shaft (10) and the front wheel drive shaft (10) installed parallel to the front wheel. Further, an output bevel gear (2) is provided at the rear end of the third transmission shaft (8) to transmit engine output to the rear wheel differential (2).

前記エンジン（Ｅｌと主変速装置（７）との間には前後
進の換機構α→を設けである。　次のこの前後進の換機
構α滲を説明すると、第１図に示すように、前記第１伝
動軸（５）より入力側でＰＴＯ伝動軸（１）に外嵌支承
された入力軸α均の後端にキャリア（至）をスプライン
嵌着するとともに、このキャリア（ＬＱの突設ビンαη
に大小一対の遊星ギヤ（１８Ａ）（１８Ｂ）を枢支しで
ある。　一方、入力軸０均の後端に対応する第１伝動軸
（５）の前端にはスプライン嵌合された第１の太陽ギヤ
α窃とこの第１の太陽ギヤαりに対して第２の太陽ギヤ
（２０）を遊嵌し、この第１の太陽ギヤα優を大径の遊
星ギヤ（１８Ａ）及び、第２の太陽ギヤ（２０）を小径
の遊星ギヤ（１８Ｂ）と夫々咬合させることによって前
後進用遊星ギヤ機構（２１１を設けである。　前後進用
遊星ギヤ機構［２１１と同軸心で後方にはミッションケ
ース■から一体延出された支持ボス器が第１伝動軸（６
）に遊外嵌される状態に延出され、この延出された支持
ボスコの外周面に油圧クラッチ（至）用クラッチケーシ
ング田が遊嵌されている。　前記クラッチゲージングの
は伝動軸軸心方向に沿った略中間位置に隔壁−を設け、
この隔壁−を隔てて隣接する第１隔室（２８Ａ）と第２
隔室（２８Ｂ）を設けである。　第１隔室（２８Ａ）は
遊星ギヤ機構１２Ｈに近接した方を指す。　前記隔室（
２８Ａ）、（２８Ｂ）内には油圧によって互いに反対方
向に第（第２摩擦多板（２９Ａ）　、　（２９Ｂ）に作
用すべく移動する第（第２ピストン（３０Ａ）　、　（
３０Ｂ）を内装するとともに、前記隔壁−を％１伝動軸
軸心（刈に沿った方向で貫通する連結具■の一例である
ボルトで一体連結しである。　その上に、夫々のピスト
ン（３０Ａ）　、　（３０Ｂ）に対して一端を隔壁−に
埋設した第（第２圧縮スプリング（３１Ａ）　、　（３
１Ｂ）の他端が一体保持され、これら圧縮スプリング（
３１Ａ）　、　（３１Ｂ）が夫々のピストン（３０Ａ）
　、　（３０Ｂ）を互いに遠ざかる方向に付勢するとと
もに、ｄｔＩ記連結具（至）との協働で両ピストン（３
０Ａ）　、　（３０Ｂ）を中立状態に保持させている。A forward/reverse shift mechanism α→ is provided between the engine (El) and the main transmission (7). Next, this forward/reverse shift mechanism α will be explained as shown in FIG. A carrier (to) is spline-fitted to the rear end of the input shaft α which is externally supported on the PTO transmission shaft (1) on the input side of the first transmission shaft (5), and this carrier (LQ protruding Bin αη
A pair of large and small planetary gears (18A) (18B) are pivotally supported. On the other hand, the front end of the first transmission shaft (5) corresponding to the rear end of the input shaft has a spline-fitted first sun gear α and a second sun gear α relative to the first sun gear α. A sun gear (20) is loosely fitted, and the first sun gear α is engaged with the large-diameter planetary gear (18A) and the second sun gear (20) is engaged with the small-diameter planetary gear (18B), respectively. A planetary gear mechanism (211) for forward and backward travel is provided. A support boss device integrally extended from the mission case (6) is coaxial with the planetary gear mechanism (211) for forward and backward travel, and is integrally extended from the mission case (2) at the rear.
), and a clutch casing field for a hydraulic clutch is loosely fitted onto the outer peripheral surface of this extended support boss. The clutch gauging is provided with a partition at a substantially intermediate position along the axial direction of the transmission shaft,
The first compartment (28A) and the second compartment are adjacent to each other across this partition wall.
A compartment (28B) is provided. The first compartment (28A) points closer to the planetary gear mechanism 12H. Said compartment (
Inside 28A) and (28B) are second pistons (30A) and (28B) which are moved in opposite directions by hydraulic pressure to act on the second friction plates (29A) and (29B).
30B) is installed inside, and the partition walls are integrally connected with a bolt, which is an example of a connecting device (2) that passes through the %1 transmission shaft axis in the direction along the cutting. ), (30B), the second (second compression spring (31A), (3
1B) are held together, and these compression springs (
31A) and (31B) are the respective pistons (30A)
, (30B) in the direction away from each other, and both pistons (30B) in cooperation with the dtI connector (to).
0A) and (30B) are maintained in a neutral state.

　第３図に示すように１前記連結具■と第（第２圧縮ス
プリング（３１Ａ）　、　（３１Ｂ）は夫々円周方向で
異った位相位置に配置しである。　前記第１の摩擦多板
（２９Ａ）はキャリア（４）の突設端にスプライン嵌着
され、第２の摩擦多板（２９Ｅ）はミッションケースの
支持ボス［有］に一体固着された円筒部材田にスプライ
ン嵌着しである。　又、クラッチケーシング■の隔壁−
に継る基端部（２７Ａ）は前記第２の太陽ギヤ翰と咬合
している。　以上のように構成された二つの第（第２油
圧クラツチ（３４Ａ）　。As shown in FIG. 3, the first coupling member (1) and the second compression springs (31A) and (31B) are arranged at different phase positions in the circumferential direction. (29A) is spline-fitted to the protruding end of the carrier (4), and the second friction multi-plate (29E) is spline-fitted to the cylindrical member field integrally fixed to the support boss of the transmission case. Yes. Also, the bulkhead of the clutch casing ■
The base end (27A) connected to the second sun gear ridge engages with the second sun gear wing. The two second hydraulic clutches (34A) are constructed as described above.

（３４Ｂ）のうち、第１油圧クラツチ（３４Ａ）を大作
動させると、キャリア（４）とクラッチケーシングの１
とが一体回転する状勺に連結されるとともに、＠２の太
陽ギヤ（イ）も一体連結され、結局キャリア（４）上第
２の太陽ギヤ勾とが一体的に回転作動するので、この太
陽ギヤ翰と小径遊星ギヤ（１８Ｂ）との相対回転がなく
なり、大径遊星ギヤ（１８Ａ）が第１の太陽ギヤａすと
ともに第１伝動軸（５）をキャリア（９）と同方向に回
転させ、前進状態が得られる。　一方、第２油圧クラツ
チ（３４Ｂ）を作動させると、クラッチケーシング玉が
ミッショングースッと一体連結されて固定状態に維持さ
れ、その為に第２の太陽ギヤ翰も固定状態に維持される
ので、第２の太陽ギヤ（１９）に対して小径遊星ギヤ（
１８Ｂ）が相対回転して、第１の太陽ギヤ翰とともに第
１伝動軸（５）をキャリア（ト）と反対方向に回転させ
、後進状態が得られる。(34B), when the first hydraulic clutch (34A) is operated greatly, the carrier (4) and the clutch casing
At the same time, the sun gear (A) of @2 is also integrally connected, and as a result, the second sun gear and the second sun gear on the carrier (4) rotate integrally. The relative rotation between the gear rod and the small diameter planetary gear (18B) is eliminated, and the large diameter planetary gear (18A) rotates the first transmission shaft (5) in the same direction as the carrier (9) together with the first sun gear a. , a forward state is obtained. On the other hand, when the second hydraulic clutch (34B) is operated, the clutch casing ball is firmly connected to the transmission and maintained in a fixed state, and therefore the second sun gear blade is also maintained in a fixed state. The small diameter planetary gear (
18B) rotates relative to each other, and together with the first sun gear wing, the first transmission shaft (5) is rotated in the opposite direction to the carrier (G), so that a reverse traveling state is obtained.

以上のように、遊星ギヤ機構＋２１＋と切換油圧り、７
　ツ＋　（３４Ａ）、　（３４Ｂ）　トラ第ｉ　伝動ａ
（５）上に軸心方向に並設したものでは、第２図に示す
ように４！Ｊ１伝動軸（５）の半径方向への突設が少な
くなるので、この小さくなりた前後進刀換機１１！α→
に対応した前記前輪用駆動軸（１０）部分に油圧クラッ
チ式の４輪・２輪の換クラッチ（至）を介装しである。As mentioned above, the planetary gear mechanism +21+ and the switching hydraulic pressure, 7
+ (34A), (34B) Tiger i Transmission a
(5) In the case of those arranged in parallel in the axial direction on the top, as shown in Fig. 2, there are 4! Since the protrusion of the J1 transmission shaft (5) in the radial direction is reduced, the forward-reverse switching machine 11 becomes smaller! α→
A hydraulic clutch type four-wheel/two-wheel change clutch (to) is interposed in the front wheel drive shaft (10) corresponding to the front wheel drive shaft (10).

〔別実施例〕[Another example]

■　正逆転切換機構α４は前後進用の場合だけでなく、
耕耘ロータリー等の正逆転駆動用として使用してもよい
。■ The forward/reverse switching mechanism α4 is used not only for forward and backward movement, but also for forward and reverse movement.
It may also be used for forward/reverse driving of tillage rotaries and the like.

＠　この種の変速装置は農用トラクタ、コンバイン、耕
耘機等の農用だけでなく、池の一般車に適用してもよい
。@ This type of transmission device can be applied not only to agricultural tractors, combine harvesters, tillers, etc., but also to general pond vehicles.

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

図面は本発明に係る変速装置の実施例を示し、第１図は
油圧クラッチ式前後進り換機構を示す縦断側面図　ｇ　
２図は全体構成図、第３図は第１図のＩＩＩ−ｍ線断面
図である。The drawings show an embodiment of the transmission device according to the present invention, and FIG. 1 is a longitudinal side view showing a hydraulic clutch type forward/backward shifting mechanism.
2 is an overall configuration diagram, and FIG. 3 is a sectional view taken along line III-m in FIG. 1.

Claims (1)

【特許請求の範囲】[Claims] 一体作動する一対の遊星ギヤ（１８Ａ）、（１８Ｂ）を
並列枢支したキャリア（１６）と、一方の遊星ギヤ（１
８Ａ）と咬合状態にあって伝動軸（５）と一体の第１の
太陽ギヤと、他の遊星ギヤ（１８Ｂ）と咬合状態にあっ
て第１の太陽ギヤ（１９）に遊嵌された第２の太陽ギヤ
（２０）とからなる正逆転用遊星ギヤ機構（２１）、及
び、キャリア（１６）と第２太陽ギヤ（２０）を一体作
動させる正転状態とミッションケース（２２）に対して
第２太陽ギヤ（２０）を一体的に固定する逆転状態とに
切換える二つの油圧クラッチ（３４Ａ）、（３４Ｂ）と
を備えた変速装置であって、前記遊星ギヤ機構（２１）
と油圧クラッチ（３４Ａ）、（３４Ｂ）とを同一伝動軸
上で軸心方向に並設してある変速装置。A carrier (16) in which a pair of integrally operated planet gears (18A) and (18B) are supported in parallel, and one planet gear (1
8A) and is integral with the transmission shaft (5), and a first sun gear that is in mesh with the other planetary gear (18B) and is loosely fitted to the first sun gear (19). For the forward and reverse planetary gear mechanism (21) consisting of the second sun gear (20), and for the normal rotation state and mission case (22) in which the carrier (16) and the second sun gear (20) are integrally operated. A transmission device comprising two hydraulic clutches (34A) and (34B) that switch to a reverse state that integrally fixes a second sun gear (20), the planetary gear mechanism (21)
and hydraulic clutches (34A) and (34B) are arranged side by side in the axial direction on the same transmission shaft.