JPS6135806Y2

JPS6135806Y2 -

Info

Publication number: JPS6135806Y2
Application number: JP1980091748U
Authority: JP
Priority date: 1980-06-30
Filing date: 1980-06-30
Publication date: 1986-10-17
Also published as: JPS5716056U

Description

【考案の詳細な説明】この考案は例えば農用トラクタに装着したロー
タリにて耕耘作業を行うとき、耕土の性質等に起
因する耕耘抵抗の変動に応じて走行速度をわづか
に高低に夫々、容易に切替できるように、遊星ギ
ヤ機構を用いて構成した多板摩擦クラツチ式変速
装置に関するもので、遊星ギヤ機構の遊星ギヤを
軸支するために腕であるキヤリヤへ嵌入した固定
軸の固定手段を簡易にして、占有空間の小さいも
のに改良した変速装置を提案するものである。[Detailed explanation of the invention] This invention allows, for example, when plowing with a rotary attached to an agricultural tractor, the running speed can be slightly increased or decreased in response to fluctuations in tilling resistance caused by the properties of the cultivated soil, etc. This relates to a multi-plate friction clutch type transmission configured using a planetary gear mechanism so as to be able to switch between the two. The present invention proposes an improved transmission that is simplified and occupies less space.

次にこの考案の構成を図示の如き農用トラクタ
に適用した１実施例にもとづいて説明すれば、第
１図にその動力伝導係統図として示したように、
原動機１によるクランク軸２の回転をフロントミ
ツシヨンケース３に軸支した入力軸４へメインク
ラツチ５を介して伝達し、又、フロントミツシヨ
ンケース３に軸支しているPTO軸６と主変速軸
７に夫々装架した主変速ギヤ列８によつてこの主
変速軸７から所望の回転速度が得られるように構
成している。そこでこの考案においては遊星ギヤ
機構９とクラツチ部１０及びブレーキ部１１とか
らなる変速装置１２をこの農用トラクタの後車輪
１３が軸支されているリヤミツシヨンケース１４
内に設けて主変速軸７からこの変速装置１２に伝
達される回転動力を変速装置１２の出力軸部１５
へ直結状態で出力し、或いは、この直結時の回転
速度に対していくらか減速された回転速度にて出
力軸部１５へ出力するように設け、この農用トラ
クタの後輪駆動ギヤ部１６を回転駆動するようリ
ヤミツシヨンケース１４に軸支した副変速軸１７
とPTO軸６に夫々装架した副変速ギヤ列１８に
よつて出力軸部１５からの回転動力を更に変速し
て副変速軸１７に伝達するものである。そして、
この考案の変速装置の詳細な縦断面図を第２図に
示して、以下に詳述すれば、ベアリング１９にて
フロントミツシヨンケース３に軸支した主変速軸
７の後部に内歯ギヤ７ａを設け、両端を開口した
中空筒状の支え枠２０の１端に端蓋２１をボルト
２２…にて取付け、内歯ギヤ７ａに外嵌するよう
にこの支え枠２０をフロントミツシヨンケース３
の壁部３ａへボルト２３…にて取付けて、後部に
歯部１５ａを設けた出力軸部１５の前端はベアリ
ング２４を介して主変速軸７の後部に軸支し、端
壁２１に取付けたベアリング２５に出力軸部１５
の後端を軸支する。そして出力軸部１５にボス部
２６ａを嵌着したキヤリヤ２６には第３図のよう
にアーム２６ｂ…を延設し、このアーム２６ｂの
先端附近は夫々、空洞状に形成し、小径部２７ａ
と大径部２７ｂを備えた固定軸２７をこの空洞内
を貫通するようにしながら小径部２７ａは後側の
アーム２６ｂに、又、大径部２７ｂは前側のアー
ム２６ｂに夫々、嵌入し、ベアリング２８を介し
て上記空洞内にて回転自在となるよう、夫々の固
定軸２７の大径部２７ｂに嵌入した遊星ギヤ２９
…を内歯ギヤ７ａに噛合せる。そして内歯ギヤ７
ａを支持しているフランジ部７ｂに接近した固定
軸２７の大径部２７ｂの端部は、出力軸部１５の
軸芯に近い部分を切欠２７ｃし、キヤリヤ２６の
ボス部２６ａに遊嵌できる孔３０ａを備えた押え
板３０の外周には押え部３０ｂ…を夫々、形成
し、孔３０ａをボス部２６ａに嵌挿してボス部２
６ａへ挿着した止輪３１にてこの押え板３０の軸
方向移動を止めれば、押え部３０ｂが固定軸２７
の夫々の切欠２７ｃに係合することになつて、こ
れらの固定軸２７は、小径部２７ａと押え板３０
によつて軸方向に抜けが阻止されると共に、切欠
２７ｃに係合する押え部３０ｂによつて軸芯廻り
の回動を阻止されるようにする。そしてクラツチ
部１０とブレーキ部１１の摩擦板などを装着する
ためのハウジング３２のボス部３２ａをベアリン
グ３３，３４を介して出力軸部１５へ遊嵌し、ボ
ス部３２ａに形成した太陽ギヤ３２ｂを遊星ギヤ
２７…に噛合せ、ハウジング３２の中仕切壁３２
ｃとボス部３２ａとの間に形成したシリンダ室に
はリング状のクラツチピストン３５とブレーキピ
ストン３６を密嵌し、ハウジング３２の外筒部分
に設けた溝３２ｄ…，３２ｅ…に摩擦板３７…の
溝部を嵌合し、キヤリヤ２６のスプラインボス部
２６ｃに嵌合する摩擦板３８を上記クラツチ部１
０の側の摩擦板３７…の夫々の間に挿入し、端蓋
２１のスプラインボス部２１ａに嵌合する摩擦板
３８を上記ブレーキ部１１の側の摩擦板３７…の
夫々の間に挿入し、クラツチ部１０とブレーキ部
１１の互に最も近い摩擦板３７，３７′をばね３
９を介して連結ピン４０にて相互に連結する。そ
して原動機１にて駆動される図示外のポンプの圧
力油は図示外の変速レバーにて切替えされる切替
弁４１を介して送油管４２，４３から端蓋２１と
出力軸部１５及びハウジング３２に夫々設けた油
路を通つてクラツチピストン３５又はブレーキピ
ストン３６の背面に導入されるように設け、クラ
ツチピストン３５が第２図の矢線Ａ方向に押動さ
れるときはクラツチ部１０の摩擦板３７，３８が
合着されてハウジング３２とキヤリヤ２６は合体
するので、出力軸部１５は主変速軸７に直結され
て１体に回転することになるが、ブレーキピスト
ン３６を反矢線Ａ方向に押動するときは、ハウジ
ング３２に係合している摩擦板３７が端蓋２１に
係合して常に静止している摩擦板３７に合着する
ため、太陽ギヤ３２ｂも静止して主変速軸７の回
転は太陽ギヤ３２ｂの廻りを公転しながら内歯ギ
ヤ７ａと噛合つて自転する遊星ギヤ２９によつて
減速されてキヤリヤ２６と１体の出力軸部１５に
伝達されるように構成している。 Next, the configuration of this invention will be explained based on an example in which it is applied to an agricultural tractor as shown in the figure.As shown in the power transmission diagram in Figure 1,
The rotation of the crankshaft 2 by the prime mover 1 is transmitted via the main clutch 5 to the input shaft 4 which is pivotally supported in the front transmission case 3, and is also connected to the PTO shaft 6 which is pivotally supported in the front transmission case 3 and the main transmission. The main transmission gear train 8 mounted on each shaft 7 is configured so that a desired rotational speed can be obtained from the main transmission shaft 7. Therefore, in this invention, a transmission 12 consisting of a planetary gear mechanism 9, a clutch part 10, and a brake part 11 is attached to a rear transmission case 14 on which a rear wheel 13 of this agricultural tractor is pivotally supported.
The rotational power transmitted from the main transmission shaft 7 to the transmission 12 is transferred to the output shaft portion 15 of the transmission 12.
The rear wheel drive gear section 16 of this agricultural tractor is rotatably driven by outputting the output to the output shaft section 15 in a directly coupled state, or at a rotation speed that is somewhat reduced compared to the rotation speed when directly coupled. An auxiliary transmission shaft 17 is supported on the rear transmission case 14 so as to
The rotational power from the output shaft section 15 is further changed in speed by a sub-transmission gear train 18 mounted on the PTO shaft 6 and the PTO shaft 6, respectively, and transmitted to the sub-transmission shaft 17. and,
A detailed longitudinal cross-sectional view of the transmission of this invention is shown in FIG. An end cover 21 is attached to one end of a hollow cylindrical support frame 20 with both ends open using bolts 22, and this support frame 20 is attached to the front transmission case 3 so as to fit onto the internal gear 7a.
It is attached to the wall 3a with bolts 23..., and the front end of the output shaft section 15, which has teeth 15a at the rear, is pivotally supported at the rear of the main transmission shaft 7 via a bearing 24, and is attached to the end wall 21. Output shaft portion 15 to bearing 25
Pivotally supports the rear end of. As shown in FIG. 3, arms 26b are extended from the carrier 26 with the boss 26a fitted to the output shaft 15, and the vicinity of the tip of each arm 26b is formed into a hollow shape, and the small diameter portion 27a
The fixed shaft 27, which has a large diameter part 27b, is inserted into this cavity, and the small diameter part 27a is fitted into the rear arm 26b, and the large diameter part 27b is fitted into the front arm 26b, and the bearing is inserted. A planetary gear 29 is fitted into the large diameter portion 27b of each fixed shaft 27 so as to be rotatable within the cavity via the planetary gear 29.
... mesh with the internal gear 7a. and internal gear 7
The end of the large diameter portion 27b of the fixed shaft 27 that is close to the flange portion 7b that supports the output shaft portion 15 has a notch 27c in a portion close to the axis of the output shaft portion 15, and can be loosely fitted into the boss portion 26a of the carrier 26. Holding portions 30b are formed on the outer periphery of the holding plate 30 provided with the holes 30a, and the holes 30a are fitted into the boss portions 26a to form the boss portions 2.
If the retaining ring 31 inserted into the retaining ring 6a stops the axial movement of the presser plate 30, the presser portion 30b will move to the fixed shaft 27.
These fixed shafts 27 are engaged with the respective notches 27c of the small diameter portion 27a and the holding plate 30.
This prevents it from coming off in the axial direction, and the holding portion 30b that engages with the notch 27c prevents rotation about the axis. Then, the boss portion 32a of the housing 32 for mounting the friction plates of the clutch portion 10 and the brake portion 11 is loosely fitted to the output shaft portion 15 via the bearings 33 and 34, and the sun gear 32b formed on the boss portion 32a is fitted. meshing with the planetary gear 27..., partition wall 32 of the housing 32
A ring-shaped clutch piston 35 and a brake piston 36 are tightly fitted into the cylinder chamber formed between the boss portion 32a and the ring-shaped clutch piston 35, and friction plates 37 are fitted in grooves 32d, 32e, provided in the outer cylinder portion of the housing 32. The friction plate 38, which fits into the groove portion of the clutch portion 1 and which fits into the spline boss portion 26c of the carrier 26, is attached to the clutch portion 1.
A friction plate 38 that is inserted between each of the friction plates 37 on the side of 0 and that fits into the spline boss part 21a of the end cover 21 is inserted between each of the friction plates 37 on the side of the brake part 11. , the friction plates 37, 37' of the clutch part 10 and the brake part 11 that are closest to each other are connected to the spring 3.
9 and are connected to each other by a connecting pin 40. Pressurized oil from a pump (not shown) driven by the prime mover 1 is supplied to the end cover 21, output shaft portion 15, and housing 32 from oil pipes 42, 43 via a switching valve 41 that is switched by a gear lever (not shown). The oil is introduced into the rear surface of the clutch piston 35 or the brake piston 36 through respective oil passages, and when the clutch piston 35 is pushed in the direction of the arrow A in FIG. 37 and 38 are joined, and the housing 32 and carrier 26 are combined, so the output shaft portion 15 is directly connected to the main transmission shaft 7 and rotates as one body. When the friction plate 37 that is engaged with the housing 32 engages with the end cover 21 and is always stationary, the sun gear 32b is also stationary and the main gear is shifted. The rotation of the shaft 7 is configured to be decelerated by the planetary gear 29, which rotates while meshing with the internal gear 7a while revolving around the sun gear 32b, and is transmitted to the output shaft portion 15, which is integrated with the carrier 26. ing.

そしてこの減速時の回転速度比Ｎは、内歯ギヤ
７ａの歯数をZ₇、太陽ギヤ３２ｂの歯数をZ₃₂と
すれば、Ｎ＝Ｚ_７／Ｚ_７＋Ｚ_３２＜１となる。 The rotation speed ratio N during this deceleration is N=Z ₇ /Z ₇ +Z ₃₂ <1, where Z ₇ is the number of teeth of the internal gear 7a and Z ₃₂ is the number of teeth of the sun gear 32b.

この考案に係る多板摩擦クラツチ式変速装置は
上述のように構成しているので、例えば耕耘作業
においては切替弁４１の切替レバー４１ａを運転
席附近に設けた図示外の変速レバーにてクラツチ
ピストン３５の背面に圧力油が導入されるよう操
作すれば、クラツチピストン３５は第２図の矢線
Ａ方向に移動してクラツチ部１０の摩擦板３７，
３８を圧接することになつて、ハウジング３２と
キヤリヤ２６は１体となり、このため、遊星運動
はできなくなつて出力軸部１５はキヤリヤ２６を
介して主変速軸７に直結されて比較的高速にてこ
の農用トラクタが耕耘走行をすることになる。 Since the multi-disc friction clutch type transmission device according to this invention is constructed as described above, for example, during plowing work, the switching lever 41a of the switching valve 41 can be used to shift the clutch piston by using a shift lever (not shown) installed near the driver's seat. 35, the clutch piston 35 moves in the direction of the arrow A in FIG.
38, the housing 32 and carrier 26 become one body, and as a result, planetary motion is no longer possible, and the output shaft portion 15 is directly connected to the main transmission shaft 7 via the carrier 26, allowing relatively high speed operation. This agricultural tractor will be used for plowing.

そして、この耕耘走行中に例えば土質の硬い圃
場区間に到達したために耕耘抵抗がやや大きくな
つたようなときには、この変速装置１２のブレー
キピストン３６の背面に圧力油が供給されるよう
に切替弁４１を切替操作することにより、このピ
ストン３６が反矢線Ａ方向に移動してブレーキ部
１１の摩擦板３７，３８は互に圧接することにな
り、端蓋２１に係合して常に静止している摩擦板
３８…のためにハウジング３２及び太陽ギヤ３２
ｂは静止するので、主変速軸７の回転は太陽ギヤ
３２ｂの廻りを公転しながら内歯ギヤ７ａと噛合
つて自転する遊星ギヤ２９によつて減速されてキ
ヤリヤ２３と１体の出力軸部１２に伝達される
が、今、例えば、内歯ギヤ７ａの歯数Z₇に対する
太陽ギヤ３２ｂの歯数Z₃₂の比、即ち、Z₇：Z₃₂＝
９：１としておけば前述の算式によつてＮ＝９／１０となつて主変速軸７の回転速度の１割減の回転速度
にて出力軸部１５は回転することになり、したが
つて農用トラクタの耕耘走行速度はわづかに低下
することになつて、ロータリや、エンジン、変速
装置などに過大な負荷を与えること無く安定した
作業を続けることができるものであり、しかもこ
の減速切替操作にあたつて変速ギヤの入換操作の
如きわづらわしい手数を必要としないのである。
そして、遊星ギヤ２９…をキヤリヤ２６へ軸支し
ている固定軸２７は、キヤリヤ２６のアーム２６
ｂに嵌入した小径部２７ａとボス部２６ａに嵌入
した押え板３０によつて軸方向の抜けが阻止さ
れ、又、切欠２７ｃに係合する押え部３０ｂによ
つて軸芯廻りの回動も同時に阻止されるのであ
り、このように固定軸２７を固定するための押え
板３０は、キヤリヤ２６のボス部２６ａに挿着す
る止輪３１によつて固定されるので、厚みのうす
いこの止輪３１は、押え板３０又は固定軸２７の
夫々の端面と内歯ギヤ７ａのフランジ部７ｂとの
隙間Ｓを極めて小さくすることができるので、変
速装置１２の軸長方向の寸法が大きくなるのを良
く防止できるものであり、又、このように固定軸
２７は圧入でなく単にキヤリヤ２６に遊嵌挿入す
る構造であつて、押え板３０と止輪３１とによつ
て固定するものであるので、加工及び組込操作に
おいても簡易なものとすることができたのであ
る。 When the tilling resistance becomes a little large during this tilling run, for example because the field section has hard soil, the changeover valve 41 is turned on so that pressure oil is supplied to the back of the brake piston 36 of the transmission 12. By switching the piston 36, the piston 36 moves in the direction opposite to the arrow A, and the friction plates 37 and 38 of the brake part 11 come into pressure contact with each other, engaging with the end cover 21 and always remaining stationary. The housing 32 and the sun gear 32 for the friction plate 38...
Since b is stationary, the rotation of the main transmission shaft 7 is decelerated by the planetary gear 29, which rotates around the sun gear 32b and meshes with the internal gear 7a, so that the rotation of the main transmission shaft 7 is reduced by the output shaft portion 12, which is integrated with the carrier 23. For example, the ratio of the number of teeth Z ₃₂ of the sun gear 32b to the number Z ₇ of the internal gear 7a, that is, Z ₇ :Z ₃₂ =
If the ratio is set to 9:1, N=9/10 according to the above formula, and the output shaft portion 15 will rotate at a rotational speed that is 10% less than the rotational speed of the main transmission shaft 7. Therefore, The plowing speed of the agricultural tractor is slightly reduced, allowing stable work to continue without putting an excessive load on the rotary, engine, transmission, etc., and this deceleration switching operation This eliminates the need for troublesome operations such as switching gears.
The fixed shaft 27 that pivotally supports the planetary gears 29 to the carrier 26 is connected to the arm 26 of the carrier 26.
The small diameter part 27a fitted in the small diameter part 27a and the holding plate 30 fitted in the boss part 26a prevent the pin from coming off in the axial direction, and the holding part 30b engaged in the notch 27c also prevents rotation around the axis at the same time. The retaining plate 30 for fixing the fixed shaft 27 in this way is fixed by the retaining ring 31 inserted into the boss portion 26a of the carrier 26, so the thin retaining ring 31 Since the gap S between the end face of the holding plate 30 or the fixed shaft 27 and the flange portion 7b of the internal gear 7a can be made extremely small, it is possible to prevent the axial dimension of the transmission 12 from increasing. In addition, since the fixed shaft 27 is not press-fitted but is simply loosely inserted into the carrier 26, and is fixed by the retaining plate 30 and retaining ring 31, processing is not required. This also made it possible to simplify the installation process.

この考案は叙述せる実施例に於て詳述したよう
に、固定軸の外端に切欠部が形成されているの
で、機械加工が極めて容易であり、更に、キヤリ
ヤのボス部に外嵌固着した押え板の外周部で、同
時に複数の固定軸を係止できるので、分解組立が
迅速容易にできるのである。 As described in detail in the embodiment described, this invention has a notch formed at the outer end of the fixed shaft, so machining is extremely easy. Since a plurality of fixed shafts can be locked at the same time on the outer periphery of the holding plate, disassembly and assembly can be performed quickly and easily.

[Brief explanation of the drawing]

第１図はこの考案を適用した農用トラクタの動
力伝達経路図、第２図は同上考案の１実施例を示
す縦断面図、第３図は第２図における遊星ギヤ機
構の要部正面図である。符号説明、１……原動機、２……クランク軸、
３……フロントミツシヨンケース、３ａ……壁
部、４……入力軸、５……メインクラツチ、６…
…PTO軸、７……主変速軸、７ａ……内歯ギ
ヤ、７ｂ……フランジ部、８……主変速ギヤ列、
９……遊星ギヤ機構、１０……クラツチ部、１１
……ブレーキ部、１２……変速装置、１３……後
車輪、１４……リヤミツシヨンケース、１５……
出力軸部、１５ａ……歯部、１６……後輪駆動ギ
ヤ部、１７……副変速軸、１８……副変速ギヤ
列、１９，２４，２５，２８，３３……ベアリン
グ、２０……支え枠、２１……端蓋、２２，２３
……ボルト、２６……キヤリヤ、２６ａ，３２ａ
……ボス部、２６ｂ……アーム、２１ａ，２６ｃ
……スプラインボス部、２７……固定軸、２７ａ
……小径部、２７ｂ……大径部、２７ｃ……切
欠、３０……押え板、２９……遊星ギヤ、３０ａ
……孔、３０ｂ……押え部、３１……止輪、３２
……ハウジング、３２ｂ……太陽ギヤ、３２ｃ…
…中仕切壁、３２ｄ，３２ｅ……溝、３５……ク
ラツチピストン、３６……ブレーキピストン、３
７，３８……摩擦板、３９……ばね、４０……連
結ピン、４１……切替弁、４１ａ……切替レバ
ー、４２，４３……送油管、Ｓ……隙間。 Figure 1 is a power transmission path diagram of an agricultural tractor to which this invention is applied, Figure 2 is a longitudinal sectional view showing an embodiment of the same invention, and Figure 3 is a front view of the main parts of the planetary gear mechanism in Figure 2. be. Symbol explanation, 1... Prime mover, 2... Crankshaft,
3...Front transmission case, 3a...Wall, 4...Input shaft, 5...Main clutch, 6...
... PTO shaft, 7 ... Main transmission shaft, 7a ... Internal gear, 7b ... Flange part, 8 ... Main transmission gear train,
9... Planetary gear mechanism, 10... Clutch portion, 11
... Brake section, 12 ... Transmission device, 13 ... Rear wheel, 14 ... Rear transmission case, 15 ...
Output shaft portion, 15a... Tooth portion, 16... Rear wheel drive gear portion, 17... Sub-transmission shaft, 18... Sub-transmission gear train, 19, 24, 25, 28, 33... Bearing, 20... Support frame, 21...End cover, 22, 23
...Bolt, 26...Carrier, 26a, 32a
...Boss part, 26b...Arm, 21a, 26c
... Spline boss part, 27 ... Fixed shaft, 27a
...small diameter part, 27b...large diameter part, 27c...notch, 30...pressing plate, 29...planetary gear, 30a
...hole, 30b...presser section, 31...retaining ring, 32
...Housing, 32b...Sun gear, 32c...
...Inner partition wall, 32d, 32e...Groove, 35...Clutch piston, 36...Brake piston, 3
7, 38... Friction plate, 39... Spring, 40... Connection pin, 41... Switching valve, 41a... Switching lever, 42, 43... Oil feed pipe, S... Gap.

Claims

[Scope of utility model registration request]

A plurality of fixed shafts are arranged and fixed in the circumferential direction on a carrier fitted to the output shaft part, and a planetary gear is loosely fitted onto the fixed shafts so as to mesh with the internal gear on the input side which is rotationally driven. The output shaft portion is provided so that it can be integrally coupled with the sun gear that meshes with the planetary gear, or separated from the sun gear by means of a clutch portion, and the output shaft portion can be connected to the sun gear that meshes with the planetary gear, and can be separated from the sun gear by means of a clutch portion. In the transmission device, a brake section is provided, and the clutch section and the brake section are formed of multi-plate friction plates.
A multi-plate friction clutch type transmission in which the outer periphery of a presser plate externally fitted and fixed to the boss portion of the carrier is engaged with a notch formed from the outer end of these fixed shafts.