JPS60121122A - Speed change gear - Google Patents
Speed change gearInfo
- Publication number
- JPS60121122A JPS60121122A JP59242079A JP24207984A JPS60121122A JP S60121122 A JPS60121122 A JP S60121122A JP 59242079 A JP59242079 A JP 59242079A JP 24207984 A JP24207984 A JP 24207984A JP S60121122 A JPS60121122 A JP S60121122A
- Authority
- JP
- Japan
- Prior art keywords
- hydraulic clutch
- gear
- shaft
- clutch shaft
- input
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
- F16H2003/0936—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts with multiple countershafts comprising only two idle gears and one gear fixed to the countershaft
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Arrangement Of Transmissions (AREA)
- Structure Of Transmissions (AREA)
Abstract
Description
【発明の詳細な説明】
（イ）産業上の利用分野
本件発明は、コンバインや小形建設機械等のクローラー
式走行装置を持った移動車輌の変速装置に関するもので
ある。DETAILED DESCRIPTION OF THE INVENTION (a) Field of Industrial Application The present invention relates to a transmission device for a mobile vehicle having a crawler type traveling device, such as a combine harvester or a small construction machine.
（ロ）従来技術
これまでも本出願人により、油圧クラッチ式の変速装置
が出願されてきたかぐその多くは、油圧クラッチ式の主
変速装置に対して歯車摺動式の副変速装置を上段に配置
していた。(B) Prior art The present applicant has filed applications for hydraulic clutch type transmissions, but in many cases, a gear sliding type auxiliary transmission is installed in the upper stage of the hydraulic clutch type main transmission. It was placed.
その為に副変速を行なう場合には、ミッションケース外
に設けられたエンジンとの間の主クラツチ装置を断にし
た後に副変速操作を行なう必要があったのである。Therefore, when performing a sub-shift, it was necessary to disconnect the main clutch device between the engine and the transmission case, and then perform the sub-shift operation.
しかし、油圧クラッチ式の変速装置は、主クラツチ装置
の断接操作なしで、変速が行なえる点が利点であるのに
対し、歯車摺動式の副変速の為に主クラツチ装置を断接
しなければならないのは面倒であったのである。However, while a hydraulic clutch type transmission has the advantage of being able to change gears without engaging or disconnecting the main clutch, the gear sliding type sub-shift requires the main clutch to be engaged or disconnected. It was a hassle to have to do so.
（ハ）発明が解決しようとする問題点
本発明の目的は、従来のこのような不具合いを解消すべ
く、油圧クラッチ式の主変速装置を上段に、歯車摺動式
の副変速装置を下段に配置するものであるが、この場合
に上方の油圧クラッチ式の主変速装置と、下方の操向ク
ラッチ装置、操向ブレーキ装置に挟まれた位置に摺動歯
車装置を設ける必要がある為に摺動歯車の十分な摺動空
間を確保することが困難となるのである。(c) Problems to be Solved by the Invention The purpose of the present invention is to solve the above-mentioned problems of the conventional technology by installing a hydraulic clutch type main transmission in the upper stage and a gear sliding type auxiliary transmission in the lower stage. However, in this case, it is necessary to install a sliding gear device between the upper hydraulic clutch type main transmission device and the lower steering clutch device and steering brake device. This makes it difficult to secure sufficient sliding space for the sliding gear.
特に油圧クラッチ装置の人力用遊嵌歯車や、油圧クラッ
チ軸の出力用の歯車がミッションケースの中央近くにあ
ると、これが邪魔になって、副変速用の摺動歯車の摺動
ができなくなるのである。In particular, if the manual loose gear of the hydraulic clutch device or the output gear of the hydraulic clutch shaft are located near the center of the transmission case, this will get in the way and prevent the sliding gear for the auxiliary transmission from sliding. be.
よって本発明においては、油圧クラッチ軸の出力歯車を
ミッションケース側に集めて配置し、下段に設けた摺動
歯車の摺動空間を確保したものである。Therefore, in the present invention, the output gears of the hydraulic clutch shaft are arranged together on the transmission case side to ensure a sliding space for the sliding gears provided at the lower stage.
（ニ）問題を解決するための手段
本発明の目的は以上の如くであり、該目的を達成する為
の構成を説明すると。(d) Means for Solving the Problems The objects of the present invention are as described above, and the configuration for achieving the objects will now be explained.
ミッションケース９の入力軸１の周囲に油圧クラッチ軸
を配置し、′該油圧クラッチ軸上の油圧クラッチ装置の
選択結合により構成される主変速装置の下段に、歯車摺
動式の副変速装置を配置すべく、該油圧クラッチ軸上の
出力歯車を、ミッションケース９の側壁側に集中配置し
、下段の摺動歯車軸５上の同じくミッションケース側壁
側に配置した入力歯車３６へ主変速後の回転を集中入力
したものである。A hydraulic clutch shaft is disposed around the input shaft 1 of the transmission case 9, and a gear sliding type sub-transmission device is installed at the lower stage of the main transmission device configured by selectively coupling the hydraulic clutch devices on the hydraulic clutch shaft. In order to arrange the hydraulic clutch shaft, the output gear on the hydraulic clutch shaft is concentrated on the side wall of the transmission case 9, and the input gear 36 on the lower sliding gear shaft 5, which is also arranged on the side wall of the transmission case, is connected to the output gear after the main shift. This is a concentrated input of rotation.
（ホ）実施例と作用
本発明の目的・構成は以上の如くであり、添付の図面に
示した実施例の構成に基づいて、本発明の詳細な説明す
ると。(E) Embodiments and Functions The objects and structure of the present invention are as described above, and the present invention will be explained in detail based on the structure of the embodiments shown in the attached drawings.
第１図はクローラー式走行装置を備えたコンバインの全
体側面図である。FIG. 1 is an overall side view of a combine harvester equipped with a crawler type traveling device.
本発明の変速装置は、クローラー式の走行装置が主体で
あるが、それに限定されるものではなく、耕耘機等の２
輪形の移動車輌においても用いられるものである。Although the transmission device of the present invention is mainly a crawler-type traveling device, it is not limited thereto, and can be used in two types such as a tiller, etc.
It is also used in ring-shaped mobile vehicles.
クローラー式の走行装置１８を駆動スプロケット１０で
駆動する
ミッションケース９内の変速装置が本発明の要部であり
、該ミッションケース９の両側に突出する左右の駆動軸
８Ｌ・８Ｒに駆動スプロケット０が固設されている。コ
ンバインは各装置が、クローラー式の走行装置の上に搭
載されている。先端に分草板１３が突出し、該分草板１
３にて分草した後に引起し装置１２にて倒伏殻稈を引起
す。それと同時に株元部を刈取装置１５が刈取り、株元
搬送装置１４にて縦搬送装置１６の下位まで搬送する。The transmission device in the mission case 9 that drives the crawler-type traveling device 18 with the drive sprocket 10 is the main part of the present invention, and the drive sprocket 0 is attached to the left and right drive shafts 8L and 8R that protrude on both sides of the mission case 9. It is permanently installed. Each piece of equipment in a combine harvester is mounted on a crawler-type traveling device. A grass dividing plate 13 protrudes from the tip, and the grass dividing plate 1
After the weeds are separated in step 3, the lodging culm is raised by a pulling device 12. At the same time, the reaping device 15 harvests the stock base, and the stock base transport device 14 transports the stock to a lower level of the vertical transport device 16.
縦搬送装置１６にて長短稈調節し乍ら脱穀装置１９のフ
ィードチェーン２７へ受継ぐ。穂先部は上部搬送装置２
３にて、脱穀装置１９の扱胴入口まで運ばれる。脱穀装
置１９内で脱穀し、排稈チェーンにて排稈を排稈処理装
置２１へ運び処理する。The length of the culm is adjusted by the vertical conveyance device 16, and then transferred to the feed chain 27 of the threshing device 19. The tip of the ear is transferred to the upper conveying device 2.
At step 3, the grains are transported to the inlet of the handling drum of the threshing device 19. The husks are threshed in the threshing device 19, and the waste culms are conveyed to the waste culm processing device 21 by the culm removal chain for processing.
第２図は本発明の要部を示すミッションケース９内部の
断面図、第３図は同じく伝動線図、第４図はミッション
ケース９の軸の配置を示す図面、第５図は変速レバー２
２の変速ガイド溝を示す図面である。FIG. 2 is a sectional view of the inside of the mission case 9 showing the main parts of the present invention, FIG. 3 is a transmission line diagram, FIG. 4 is a diagram showing the arrangement of the shafts of the mission case 9, and FIG. 5 is a diagram showing the gear shift lever 2.
2 is a drawing showing a gear shift guide groove of No.
ミッションケース９の上部より突出した入力軸１の端部
に入力プーリー６２が設けられており、該入カブ−１７
−６２へエンジンから■ベルトにより動力が伝えられる
。第４図に示す如く入力軸１の周囲に油圧クラッチ装置
を軸架する油圧クラッチ軸２・３・４が配置される。入
力軸１上に３枚の固設歯車２４・２５・７０が固設され
ており、油圧クラッチ軸２・３・４上の油圧クラッチ装
置の歯車と常時噛合いしている。まず、入力軸上の小径
の固設歯車２５には、油圧クラッチ軸２上の油圧クラッ
チ装置４７の入力嵌装歯車２９と、油圧クラッチ軸３上
の油圧タラソチクラソチ装置４９の入力遊嵌歯車３０と
、油圧クラッチ軸４上の油圧クラッチ装置５１の入力遊
嵌歯車３５と同じ歯数の歯車が常時噛合している。An input pulley 62 is provided at the end of the input shaft 1 protruding from the upper part of the mission case 9.
-Power is transmitted from the engine to -62 by the belt. As shown in FIG. 4, hydraulic clutch shafts 2, 3, and 4 for supporting a hydraulic clutch device are arranged around the input shaft 1. Three fixed gears 24, 25, and 70 are fixedly installed on the input shaft 1, and are constantly meshed with the gears of the hydraulic clutch device on the hydraulic clutch shafts 2, 3, and 4. First, the small-diameter fixed gear 25 on the input shaft is connected to the input fitted gear 29 of the hydraulic clutch device 47 on the hydraulic clutch shaft 2 and the input loosely fitted gear 30 of the hydraulic clutch device 49 on the hydraulic clutch shaft 3. , a gear having the same number of teeth as the input loose fit gear 35 of the hydraulic clutch device 51 on the hydraulic clutch shaft 4 is always in mesh.
又、入力軸１上の中経の固設歯車７０には油圧クラッチ
軸３の油圧クラッチ装置５０の入力嵌装歯車３１と、油
圧クラッチ軸４の油圧クラッチ装置５２の入力嵌装歯車
５３と同じ歯数の歯車が２枚當時噛合している。Moreover, the fixed gear 70 of the middle diameter on the input shaft 1 is the same as the input fitting gear 31 of the hydraulic clutch device 50 of the hydraulic clutch shaft 3 and the input fitting gear 53 of the hydraulic clutch device 52 of the hydraulic clutch shaft 4. Two gears with the same number of teeth are always in mesh.
故に油圧クラッチ軸２・３・４上の４７・４９・５１の
どの油圧クラッチ装置が接続しても同じ回転となり、同
様に油圧クラッチ装置５０・５２の油圧クラッチ装置が
接続しても同じ回転数の同じ方向の回転となる。ただし
、油圧クラソヂ軸２上の油圧クラッチ装置４８への入力
回転は特に速くされている。入力軸１上の３枚の固設歯
車のうち大径の固設歯車２４が１枚だけ油圧クラッチ装
置４８の入力遊嵌歯車２８と常時噛合しており、６個の
油圧クラッチ装置の中では特に速い回転となるように構
成されている。この油圧クラッチ装置は前進第４速の速
度を得るものであり、第５図の図面Ｆ４・１？８の速度
である。Therefore, no matter which hydraulic clutch device 47, 49, or 51 on the hydraulic clutch shafts 2, 3, or 4 is connected, the rotation will be the same, and similarly, even if the hydraulic clutch device 50 or 52 is connected, the rotation speed will be the same. rotation in the same direction. However, the input rotation to the hydraulic clutch device 48 on the hydraulic clasp shaft 2 is particularly fast. Among the three fixed gears on the input shaft 1, only one large-diameter fixed gear 24 is always engaged with the input loose gear 28 of the hydraulic clutch device 48, and among the six hydraulic clutch devices, It is designed for particularly fast rotation. This hydraulic clutch device obtains the speed of the fourth forward speed, which is the speed of drawing F4-1-8 in FIG.
Ｆ４ばＦｌが１．０８０ｋｍ／ｈ 、、Ｆ２が１．３７
９ｋｍ／ｈ 、、Ｆ３が１．８９２ｋｍ／Ｉ＋であるの
に対し、５ 、２２７ｋｍ ／ ｌ＋とＦ３の２．７２
０ｋｍ／ｈ以上の速度に構成され、Ｆ８はＦ５が１．７
３１ｋｍ／ｈ 、Ｆ６が２．２１０ｋｍ／１１、ＦＴが
３．０３３ｋｍ／ｈに対し８．３８０ｋｍ／ｈと２倍以
上の速度を構成している。F4 is 1.080km/h, F2 is 1.37
9km/h, F3 is 1.892km/I+, while 5,227km/l+ and F3's 2.72
Configured for speeds above 0km/h, F8 is F5 is 1.7
31km/h, F6 is 2.210km/11, FT is 8.380km/h, which is more than double the speed of 3.033km/h.
Ｆｌ・Ｆ２・Ｆ３は刈取作業の為の速度であり、Ｆ４は
刈取作業を止めて走行する為の速度にしている。Fl, F2, and F3 are the speeds for reaping work, and F4 is the speed for stopping the reaping work and traveling.
故に刈取作業から走行作業へ移る際に変速レノ＼−によ
り溝を変える必要はなくなり、１本の前後方向の溝の往
復のみで作業が行なえるのである。Therefore, there is no need to change the groove by changing gears when moving from mowing work to traveling work, and the work can be carried out by only reciprocating one groove in the front and back direction.
その他の前進、後進、変速段数を変えているのは油圧ク
ラッチ軸２・３・４の出力歯車２６・３２・３３・３４
である。Other output gears 26, 32, 33, and 34 of hydraulic clutch shafts 2, 3, and 4 change the forward, reverse, and gear stages.
It is.
まず、油圧クラッチ軸３は出力歯車３２が油圧フランチ
軸４上の出力歯車３３と常時噛合しているので、油圧ク
ラッチ軸５に回転が伝えられない時には、油圧クラッチ
軸４が逆転軸の役目をし、油圧クラッチ軸３上の油圧ク
ラッチ装置は後進第１速、第２速となる。即ち、出力歯
車３３・３４が後進用アイドリングギアを兼ねているの
である。First, the output gear 32 of the hydraulic clutch shaft 3 is always in mesh with the output gear 33 on the hydraulic flange shaft 4, so when rotation is not transmitted to the hydraulic clutch shaft 5, the hydraulic clutch shaft 4 acts as a reverse rotation shaft. However, the hydraulic clutch device on the hydraulic clutch shaft 3 is in the first reverse speed and the second reverse speed. That is, the output gears 33 and 34 also serve as reverse idling gears.
又、油圧クラッチ軸２上の出力歯車２６が摺動歯車軸５
の入力歯車３６と常時噛合し、油圧クラッチ軸４上の出
力歯車３４も摺動歯車軸５上の入力歯車３６と常時噛合
しているが、２６の方が大きく３４の方が小さいので油
圧クラッチ軸２上の油圧クラッチ装置４７・４８は前進
第２速第４速、油圧クラッチ軸４上の油圧クラッチ装置
５１・５２ば前進第１速、第３連となる。Further, the output gear 26 on the hydraulic clutch shaft 2 is connected to the sliding gear shaft 5.
The output gear 34 on the hydraulic clutch shaft 4 is also always engaged with the input gear 36 on the sliding gear shaft 5, but since 26 is larger and 34 is smaller, the hydraulic clutch The hydraulic clutch devices 47 and 48 on the shaft 2 serve as the second forward speed and fourth speed, and the hydraulic clutch devices 51 and 52 on the hydraulic clutch shaft 4 serve as the first and third forward speed.
前進第１速は、入力軸１の固設歯車２５より油圧クラッ
チ軸４上の入力Ｍ嵌歯ホ３５へ伝わり、油圧クラッチ装
置５１の接続により、出力歯車３４より摺動歯車軸５上
の固設歯車３６へ伝えられる。The first forward speed is transmitted from the fixed gear 25 of the input shaft 1 to the input M toothed hoop 35 on the hydraulic clutch shaft 4, and by the connection of the hydraulic clutch device 51, the output gear 34 is transmitted to the fixed gear on the sliding gear shaft 5. It is transmitted to the setting gear 36.
前進第２速ば、入力軸１上の固設＠隼２５より油圧クラ
ッチ軸２上の入力遊嵌歯車２９に伝わり、油圧クラッチ
装置４７に接続により出力歯車２６から摺動歯車軸５上
の入力歯車３６へ伝わる。The second forward speed is transmitted from the fixed @Hayabusa 25 on the input shaft 1 to the input loose fit gear 29 on the hydraulic clutch shaft 2, and is transmitted from the output gear 26 to the input on the sliding gear shaft 5 by connecting to the hydraulic clutch device 47. The signal is transmitted to gear 36.
前進第３速は、入力軸１上の固設ｉ￥ｉ ＴＩＥ ７
Ｑより油圧クラッチ軸４上の入力遊嵌歯車５３へ伝わり
、油圧クラッチ装置５２の接続により出力歯車３４から
摺動歯車軸５上の入力歯車３６へ伝えられる。The third forward speed is fixed on the input shaft 1.
The signal is transmitted from Q to the input loose fit gear 53 on the hydraulic clutch shaft 4, and when the hydraulic clutch device 52 is connected, it is transmitted from the output gear 34 to the input gear 36 on the sliding gear shaft 5.
前進第４速は、入力軸１上の固設歯車２４より油圧クラ
ッチ軸上の入力遊嵌歯車２８に伝わり、油圧クラッチ装
置４８の接続により出力歯車２６より、摺動歯車軸５上
の入力歯車３６へ伝えられる。The fourth forward speed is transmitted from the fixed gear 24 on the input shaft 1 to the input loose gear 28 on the hydraulic clutch shaft, and by the connection of the hydraulic clutch device 48, the output gear 26 is transmitted to the input gear on the sliding gear shaft 5. This will be communicated to 36.
後進第１速は、入力軸１上の固設歯ホ２５より油圧クラ
ッチ軸３上の入力遊嵌歯車３０に伝わり、油圧クラッチ
装置４９の伝動により油圧クラッチ軸３上の出力歯車３
２から油圧クラッチ軸４上の出力歯車３３・３４を介し
て油圧クラッチ軸５上の固設歯車３６へ伝えられる。油
圧クラッチ軸４上の出力歯車３３・３４が後進用のアイ
ドリングギアを兼ねているのである。The reverse first speed is transmitted from the fixed teeth 25 on the input shaft 1 to the input loose gear 30 on the hydraulic clutch shaft 3, and is transmitted to the output gear 3 on the hydraulic clutch shaft 3 by transmission from the hydraulic clutch device 49.
2 to the fixed gear 36 on the hydraulic clutch shaft 5 via the output gears 33 and 34 on the hydraulic clutch shaft 4. The output gears 33 and 34 on the hydraulic clutch shaft 4 also serve as idling gears for reverse movement.
後進第２速は、入力軸１上の固設歯車７０より油圧クラ
ソヂ軸３上の入力遊嵌歯車３１へ伝わり、油圧クラッチ
装置５０の接続により油圧クラッチ軸３上の出力歯車３
２から、油圧クラッチ軸４上の出力歯車３３・３４を介
して、摺動歯車軸５上の入力歯車３６へ伝えられる。同
じく油圧クラッチ軸４上の出力歯車３３・３４が後進用
のアイドリングギアを兼ねているのである。The second reverse speed is transmitted from the fixed gear 70 on the input shaft 1 to the input loose gear 31 on the hydraulic clutch shaft 3, and is transmitted to the output gear 3 on the hydraulic clutch shaft 3 by connection of the hydraulic clutch device 50.
2 is transmitted via the output gears 33 and 34 on the hydraulic clutch shaft 4 to the input gear 36 on the sliding gear shaft 5. Similarly, the output gears 33 and 34 on the hydraulic clutch shaft 4 also serve as idling gears for reverse movement.
次に摺動歯車軸５とカウンター軸６の間で副変速装置が
構成されている。Next, a sub-transmission device is constructed between the sliding gear shaft 5 and the counter shaft 6.
摺動歯車軸５上の２連摺動歯車３８・３７のうち小径の
歯車３７がカウンター軸上の２連歯車３９・４ｏのうち
大ｉ￥の方と４０と噛合することにより副変速低が得ら
れ、３８と３９が噛合することにより副変速高が（Ｍら
れる。The smaller diameter gear 37 of the double sliding gears 38 and 37 on the sliding gear shaft 5 meshes with the larger i and 40 of the double gears 39 and 4o on the counter shaft, thereby shifting the sub-shift to low. When 38 and 39 mesh with each other, the sub-shift height is set to (M).
副変速低により、後進２速、前進４速即ち１？１・Ｒ２
・Ｆｌ・Ｆ２・Ｆ３・Ｆ４の変速段が（Ｍられ、副変速
高によりＲ３・Ｒ４・Ｆ５・Ｆ６・Ｆｌ・Ｆ８が１９ら
れる。Due to the low sub-shift, 2 reverse speeds and 4 forward speeds, i.e. 1?1, R2
・The gears of Fl, F2, F3, and F4 are changed to (M), and R3, R4, F5, F6, Fl, and F8 are changed by 19 depending on the sub-shift height.
この副変速の高低を変速レバー２２の左右回動で２連摺
動歯卓３７・３８を摺動すべくし、変速レバー２２の前
後回動により油圧方向制御弁を動かして、６個の油圧ク
ラッチ装置の油路の選択をずべく構成すると、第５図の
如く変速ガイド板を１１形に構成することができる。副
変速が３段の場合には円形４段の場合には円形となる。The height of this sub-shift is set by rotating the gear shift lever 22 left and right to slide the double sliding tooth table 37 and 38, and by rotating the gear shift lever 22 back and forth, the hydraulic directional control valve is moved, and the six hydraulic clutches are controlled. If the oil passages of the device are properly selected, the speed change guide plate can be configured in an 11-shape as shown in FIG. If the sub-shift has three gears, it will be circular; if it has four gears, it will have a circular shape.
カウンター軸上には左右の油圧式操向クラッチ装置兼油
圧ブレーキ装置用の油圧シリンダー６１１゜・６１Ｒが
もうけられており摺動歯車４５Ｌ・４５Ｒを摺動させて
内歯歯車４４Ｌ・４４１？との噛合を断接することによ
り操向クラッチを構成している。Hydraulic cylinders 611° and 61R for left and right hydraulic steering clutch devices and hydraulic brake devices are provided on the counter shaft, and sliding gears 45L and 45R are slid to form internal gears 44L and 441? A steering clutch is constructed by engaging and disengaging the steering clutch.
摺動歯車４５Ｌ・４５Ｒはディスクブレーキ装置の摩擦
板の保持体も兼ねており、油圧シリンダー６１Ｌ ・６
１Ｒの重なる側方への移動により操向クラッチ断のあと
徐々に操向ブレーキ装置４６Ｌ・４６１１が作動する。The sliding gears 45L and 45R also serve as holders for the friction plates of the disc brake device, and the hydraulic cylinders 61L and 6
Due to the overlapping lateral movement of 1R, the steering brake devices 46L and 4611 are gradually activated after the steering clutch is disengaged.
５４は駐車ブレーキ装置である。54 is a parking brake device.
第７軸７上には左右の減速歯車装置４１Ｌ・４１１？・
４２Ｌ・４２Ｒが設げられており、駆動軸である第８
軸８上の最終歯車４３Ｌ・４３Ｒと噛合している。On the seventh axis 7 are left and right reduction gear devices 41L and 411?・
42L and 42R are provided, and the 8th drive shaft
It meshes with the final gears 43L and 43R on the shaft 8.
第４図において示す如く、入力軸１の周囲に油圧クラッ
チ軸２・３・４が配置されており、油圧クラッチ軸３上
の歯車は入力軸１と油圧クラッチ軸４上の歯車と噛合し
ている。摺動歯車軸５上の歯車は、油圧クラッチ軸４と
油圧クラッチ軸２上の歯車と噛合する位置にある。As shown in FIG. 4, hydraulic clutch shafts 2, 3, and 4 are arranged around the input shaft 1, and the gears on the hydraulic clutch shaft 3 mesh with the gears on the input shaft 1 and the hydraulic clutch shaft 4. There is. The gear on the sliding gear shaft 5 is in a position to mesh with the gears on the hydraulic clutch shaft 4 and the hydraulic clutch shaft 2.
第５図は主変速と副変速をワンレバーで操向可能に構成
したものであり、コンバインにおいては操向コラム１７
の側部の変速ガイド板６３の平面図を示している。Figure 5 shows a configuration in which the main gear shift and the auxiliary gear shift can be steered with one lever; in a combine harvester, the steering column 17
2 shows a plan view of the speed change guide plate 63 on the side.
変速レバー２２の１本によりＩ］形に構成すれば前進８
段、後進４段の変速を主クラッチ操作なしで行なうこと
ができ、副変速を３段にすれば円形にすることにより前
進１２段、後進６段が、副変速を４段にすれば円形にす
ることにより、前進１６段、後進８段が主クラッチの操
作なしでやれるのである。If one of the shift levers 22 is configured in an I] shape, forward movement 8 is possible.
4 gears and 4 reverse gears can be performed without operating the main clutch, and if the auxiliary gear is set to 3 gears, it will be circular, resulting in 12 forward gears and 6 reverse gears, and if the auxiliary gear is set to 4 gears, it will be circular. This allows 16 forward speeds and 8 reverse speeds to be achieved without operating the main clutch.
そして、それぞれの前後方向の主変速溝内において、最
も速い速度部分が他の前進速度が構成する作業速度より
も２倍以上速い走行速度に構成されているので、走行時
のみ他の主変速溝へ移動して、副変速の助けを借りて速
度を増す必要がなく常に圃場の状態に合わせて、前後方
向き主変速溝を択ぶだけで後は変速レバーの前後方向の
操作だけで作業が行なえるのである。In each of the main transmission grooves in the longitudinal direction, the fastest speed part is configured to have a running speed that is more than twice as fast as the working speed constituted by the other forward speeds, so only when driving is the other main transmission groove There is no need to increase the speed with the help of an auxiliary transmission, and you can always select the main transmission groove in the longitudinal direction according to the field conditions, and the rest can be done by simply operating the transmission lever in the longitudinal direction. It is.
例えば、湿田と乾田により主変速溝を使い分けたり、殻
稈の成熟具合や、雨上り後の濡れ具合等で主変速溝を択
ぶこともできるのセある。For example, it is possible to use different main transmission grooves for wet fields and dry fields, or to select the main transmission groove according to the maturity of the shell culm, the wetness after rain, etc.
（へ）発明の効果
本発明は以上の如く構成したので次のような効果を奏す
るものである。(F) Effects of the Invention Since the present invention is constructed as described above, it has the following effects.
第１に油圧クラッチ式の主変速装置の下段に歯車摺動式
の変速装置を設けたので、油圧クラッチ式の変速装置を
中立にすれば主クラッチの操作なしで摺動歯車を動かし
て副変速を行なうことができ、主変速と副変速を１本の
変速レバーにて操作することが可能となるのである。First, a gear sliding type transmission is installed below the hydraulic clutch type main transmission, so if the hydraulic clutch type transmission is set to neutral, the sliding gear can be moved without operating the main clutch to shift the auxiliary gear. This makes it possible to operate both the main and sub-shifts using a single shift lever.
第２に上段に設けた油圧クラッチ軸の出力歯車をミッシ
ョンケース側壁側に集中配置したので、油圧クラッチ装
置の下方に余裕の空間を設けることができ、各軸間の間
隔を大きくとらずに副変速用の摺動歯車をミッションケ
ースの中段位置で摺動可能とできたのである。これによ
り、ひいてはミッションケースを小形にすることができ
たちのである。Second, since the output gears of the hydraulic clutch shaft installed in the upper stage are centrally arranged on the side wall of the transmission case, it is possible to provide ample space below the hydraulic clutch device, and the This made it possible for the sliding gear for shifting to slide in the middle position of the transmission case. This allows the mission case to be made smaller.
第１図はクローラー式の走行装置を持った移動車輌のう
ちコンバインの全体側面図。第２図はミッションケース
の断面図、第３図は本件発明の変速装置の伝動線図、第
４図は軸の配置を示すミッションケースの側面図、第５
図は変速ガイド板の平面図である。
１・・・入力軸 ２・３・４・・・油圧クラッチ軸５・
・・摺動歯車 ６・・・カウンター軸９・・・ミッショ
ンケース
２４・２５・７０・・・入力軸上の固設歯車２６−３２
・３３・３４・・・油圧クラッチ軸の出力歯車２８・２
９・３０・３１・３５・５３・・・油圧クラッチ装置の
入力遊嵌両軍
３６・・・摺動歯車軸の入力歯車
３８・３７・・・２連摺動歯車
４７・４８・４９・５０・５１・５２・・・油圧クラッ
チ装置出願人 株式会社神崎高級工機製作所
代理人 弁理士 矢 野 寿 −部Figure 1 is an overall side view of a combine harvester, which is a mobile vehicle with a crawler-type traveling device. Fig. 2 is a sectional view of the transmission case, Fig. 3 is a transmission line diagram of the transmission of the present invention, Fig. 4 is a side view of the mission case showing the arrangement of the shafts, Fig. 5
The figure is a plan view of the speed change guide plate. 1...Input shaft 2.3.4...Hydraulic clutch shaft 5.
...Sliding gear 6...Counter shaft 9...Mission case 24, 25, 70...Fixed gear 26-32 on the input shaft
・33・34...Output gears 28 and 2 of the hydraulic clutch shaft
9, 30, 31, 35, 53... Input loose fitting arm of hydraulic clutch device 36... Input gear of sliding gear shaft 38, 37... Dual sliding gear 47, 48, 49, 50・51・52...Hydraulic clutch device applicant Kanzaki Kokyukoki Seisakusho Co., Ltd. Agent Patent attorney Hisashi Yano - Department
Claims (1)
を配置し、該油圧クラッチ軸上の油圧クラッチ装置の選
択結合により構成される主変速装置の下段に、歯車摺動
式の副変速装置を配置すべく、該油圧クラッチ軸上の出
力歯車を、ミッションケース９の側壁側に集中配置し、
下段の摺動歯車軸５上の同じくミッションケース側壁側
に配置した入力歯車３６へ主変速後の回転を集中入力し
たことを特徴とする変速装置。A hydraulic clutch shaft is arranged around the input shaft 1 of the transmission case 9, and a gear sliding type auxiliary transmission is arranged at the lower stage of the main transmission, which is configured by selectively connecting the hydraulic clutch devices on the hydraulic clutch shaft. In order to achieve this, the output gear on the hydraulic clutch shaft is concentrated on the side wall of the transmission case 9
This transmission is characterized in that the rotation after the main shift is intensively input to the input gear 36 on the lower sliding gear shaft 5, which is also placed on the side wall of the transmission case.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59242079A JPS60121122A (en) | 1984-11-15 | 1984-11-15 | Speed change gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59242079A JPS60121122A (en) | 1984-11-15 | 1984-11-15 | Speed change gear |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP22245084A Division JPS60132157A (en) | 1984-10-22 | 1984-10-22 | Speed change gear |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60121122A true JPS60121122A (en) | 1985-06-28 |
| JPH0123328B2 JPH0123328B2 (en) | 1989-05-02 |
Family
ID=17083969
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP59242079A Granted JPS60121122A (en) | 1984-11-15 | 1984-11-15 | Speed change gear |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60121122A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100808657B1 (en) * | 2006-07-10 | 2008-02-29 | (주)엠에스정밀 | Driveline of transmission |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS50121021A (en) * | 1974-02-28 | 1975-09-22 | ||
| JPS5193021A (en) * | 1975-02-12 | 1976-08-14 |
-
1984
- 1984-11-15 JP JP59242079A patent/JPS60121122A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS50121021A (en) * | 1974-02-28 | 1975-09-22 | ||
| JPS5193021A (en) * | 1975-02-12 | 1976-08-14 |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100808657B1 (en) * | 2006-07-10 | 2008-02-29 | (주)엠에스정밀 | Driveline of transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0123328B2 (en) | 1989-05-02 |
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