JP2918395B2 - Vehicle transmission - Google Patents
Vehicle transmissionInfo
- Publication number
- JP2918395B2 JP2918395B2 JP4150915A JP15091592A JP2918395B2 JP 2918395 B2 JP2918395 B2 JP 2918395B2 JP 4150915 A JP4150915 A JP 4150915A JP 15091592 A JP15091592 A JP 15091592A JP 2918395 B2 JP2918395 B2 JP 2918395B2
- Authority
- JP
- Japan
- Prior art keywords
- gear
- transmission
- clutch
- shaft
- transmission shaft
- 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.)
- Expired - Fee Related
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
- 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
-
- 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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/04—Combinations of toothed gearings only
- F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
- F16H37/043—Combinations of toothed gearings only change gear transmissions in group arrangement without gears having orbital motion
- F16H2037/045—Combinations of toothed gearings only change gear transmissions in group arrangement without gears having orbital motion comprising a separate gearing unit for shifting between high and low ratio range
Description
【０００１】[0001]
【産業上の利用分野】本発明は、車輌の変速装置に関す
るものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission for a vehicle.
【０００２】[0002]
【従来の技術】従来例として、図５にトラクタのトラン
スミッションを示す。同図において、1 はミッションケ
ース2 内に収容された主変速装置で、前部には走行系伝
動軸3に一体回転自在に設けられたシングルコーンシン
クロメッシュ式の高低切換クラッチ4 が配置されてい
る。この高低切換クラッチ4 の前側には、第１ギヤ5
が、後側には第２ギヤ6 が夫々配置されて、伝動軸3 上
に遊転自在に設けられている。また、伝動軸3 と平行に
設けられたカウンタ軸7 前部には、第１ギヤ5 に歯合す
る大径ギヤ8aと第２ギヤ6 に歯合する小径ギヤ8bとを有
する中間ギヤ体8 が遊転自在に設けられている。そし
て、第１ギヤ5 には、フライホイール9 、主クラッチ1
0、推進軸11、前後進切換装置12を順次経てエンジンの
動力が伝達されるようになっており、高低切換クラッチ
4 を、そのシフタを前方へシフトして、第１ギヤ5 に連
結させることで、動力が第１ギヤ5 から伝動軸3 へ同速
状態で伝達され、高低切換クラッチ4 を、そのシフタを
後方へシフトして、第２ギヤ6 に連結させることで、動
力が第１ギヤ5 から中間ギヤ体8 、第２ギヤ6 を経て減
速されて伝動軸3 へ伝達されるようになっている。2. Description of the Related Art As a conventional example, FIG. 5 shows a tractor transmission. Referring to FIG. 1, reference numeral 1 denotes a main transmission accommodated in a transmission case 2, and a single-cone synchromesh type high / low switching clutch 4 which is rotatably provided integrally with a traveling system transmission shaft 3 is disposed at a front portion. I have. The front side of the high-low changeover clutch 4, the first gear 5
However, a second gear 6 is disposed on the rear side, and is freely rotatably provided on the transmission shaft 3. An intermediate gear body 8 having a large-diameter gear 8a meshing with the first gear 5 and a small-diameter gear 8b meshing with the second gear 6 is provided at the front of a counter shaft 7 provided in parallel with the transmission shaft 3. Are provided so as to freely rotate. The first gear 5 has a flywheel 9 and a main clutch 1
0, the power of the engine is transmitted through the propulsion shaft 11 and the forward / reverse switching device 12 in this order.
4 by shifting its shifter forward and connecting it to the first gear 5, power is transmitted from the first gear 5 to the transmission shaft 3 at the same speed, and the high / low switching clutch 4 is moved backward by the shifter. By shifting to the second gear 6, the power is reduced from the first gear 5 through the intermediate gear body 8 and the second gear 6 and transmitted to the transmission shaft 3.
【０００３】また、カウンタ軸7 には、その後部に、シ
ングルコーンシンクロメッシュ式の第１クラッチ13が、
中間部で中間ギヤ体8 の後側に、シングルコーンシンク
ロメッシュ式の第２クラッチ14が夫々一体回転自在に設
けられ、第1 クラッチ13の前後には、伝動軸3 からカウ
ンタ軸7 へ、第１クラッチ13を介して動力を伝達する第
１の伝動ギヤ系列15,16 と第２の伝動ギヤ系列17,18 と
が、伝動軸3 、カウンタ軸7 に配設されている。また、
第２クラッチ14の後側には、伝動軸3 からカウンタ軸7
へ、第２クラッチ14を介して動力を伝達する第３の伝動
ギヤ系列19,20が、伝動軸3 、カウンタ軸7 に配設され
ている。第１、２、３の伝動ギヤ系列15,16,17,18,19,2
0 の内、伝動軸3 上に設けられるギヤ15,17,19は伝動軸
3 にスプライン嵌合され、カウンタ軸7 上に設けられる
ギヤ16,18,20はカウンタ軸7 に遊転自在に外嵌されてい
る。そして、カウンタ軸7 から後輪デフ装置等を介して
後輪に動力が伝達されるようになっている。[0003] A single cone synchromesh type first clutch 13 is provided at the rear of the counter shaft 7.
A single cone synchromesh type second clutch 14 is provided at the intermediate portion behind the intermediate gear body 8 so as to be integrally rotatable, and before and after the first clutch 13, a second shaft 14 is provided from the transmission shaft 3 to the counter shaft 7. A first transmission gear train 15, 16 and a second transmission gear train 17, 18 for transmitting power via one clutch 13 are arranged on the transmission shaft 3 and the counter shaft 7. Also,
Behind the second clutch 14, the transmission shaft 3 to the counter shaft 7
Third transmission gear trains 19 and 20 for transmitting power via the second clutch 14 are arranged on the transmission shaft 3 and the counter shaft 7. First, second and third transmission gear trains 15, 16, 17, 18, 19, 2
0, gears 15, 17, and 19 provided on transmission shaft 3 are transmission shafts.
The gears 16, 18, and 20 provided on the counter shaft 7 are spline-fitted to 3, and the gears 16, 18, and 20 are fitted around the counter shaft 7 so as to freely rotate. Further, power is transmitted from the counter shaft 7 to the rear wheels via a rear wheel differential device or the like.
【０００４】そして、１本の主変速レバーの操作によっ
て、高低切換クラッチ4 が動かされた後、第１クラッチ
13又は第２クラッチ14が択一的に動かされるようになっ
ていて、第１クラッチ13を第１の伝動ギヤ系列15,16 に
連結することで１速或いは４速が得られ、第１クラッチ
13を第２の伝動ギヤ系列17,18 に連結することで２速或
いは５速が得られ、第３クラッチ14を第３の伝動ギヤ系
列19,20 に連結することで、３速或いは６速が得られる
ようになっている。After the high / low switching clutch 4 is operated by operating one main shift lever, the first clutch
The first or fourth clutch 13 or the second clutch 14 is selectively operated, and the first or fourth speed is obtained by connecting the first clutch 13 to the first transmission gear trains 15, 16.
The second or fifth speed can be obtained by connecting the third clutch 13 to the second transmission gear trains 17 and 18, and the third or sixth speed can be obtained by connecting the third clutch 14 to the third transmission gear trains 19 and 20. Is obtained.
【０００５】[0005]
【発明が解決しようとする課題】農用トラクタにあって
は、多種の作業機が装着され、また、作業内容が多種あ
り、そのため、作業機或いは作業内容に応じた車速を適
宜選択できるよう前記主変速装置に加えて副変速装置、
デュアル変速装置（高低の２段変速装置）及びクリープ
変速装置等を組み合わせて、多段変速できるように構成
されているが、さらに、ユーザの要望に応えるべく、よ
り一層の主変速装置の多段変速化が計画されている。In the agricultural tractor, various types of work machines are mounted, and there are many types of work. Therefore, the main tractor is designed to be able to appropriately select the work machine or the vehicle speed according to the work contents. Auxiliary transmission in addition to the transmission,
By combining the dual transmission (two-stage transmission high and low) and creep transmission, etc., are configured to so that you to multi-speed, further, to meet the demands of users, multistage more of the main transmission unit A shift is planned.
【０００６】しかしながら、単にギヤの枚数を増やすと
主変速装置が大型化し、また、ギヤを組込むスペースも
無い。そこで本発明は、変速装置を軸方向に大きくする
ことなく変速段数を増やすことができるよう考慮するこ
とを目的とする。However, if the number of gears is simply increased, the size of the main transmission is increased, and there is no space for incorporating the gears. Therefore, an object of the present invention is to consider so that the number of gears can be increased without increasing the transmission in the axial direction.
【０００７】[0007]
【課題を解決するための手段】本発明が前記目的を達成
するために講じた技術的手段は、伝動軸3 上に、高低切
換クラッチ4 を設けると共に、この高低切換クラッチ4
の伝動軸軸方向前後に、該高低切換クラッチ4 に係脱自
在に係合する第１ギヤ5 と第２ギヤ6 とを配設し、伝動
軸3 に対して平行に配置されると共に車輪に動力を伝達
するカウンタ軸7 上に、前記第１ギヤ5 、第２ギヤ6 に
歯合するギヤ8a,8b を有する中間ギヤ体8 を遊転自在に
設け、高低切換クラッチ4 を第１ギヤ5 又は第２ギヤ6
に係合させることで、第１ギヤ5 、第２ギヤ6 、中間ギ
ヤ体8 を介して伝動軸3 にエンジンの動力が高低２段に
変速されて伝達されるように構成し、前記中間ギヤ体8
後方のカウンタ軸7 上に、前記伝動軸3 上に一体回転自
在に設けたギヤ19に歯合すると共にカウンタ軸7 上に遊
転自在に設けたギヤ20に係脱自在に係合するクラッチ14
を一体回転自在に設けた車輌の変速装置において、前記
伝動軸3 上に、エンジンの動力が伝達される筒軸21を遊
転自在に設け、この筒軸21に、高低切換クラッチ4 を一
体回転自在に設けると共に第１ギヤ5 を遊転自在に設
け、第２ギヤ6 を伝動軸3 に一体回転自在に設け、中間
ギヤ体8 に前記クラッチ14に係脱自在に係合する係合部
22を設けた点にある。The technical means taken by the present invention to achieve the above object is to provide a high-low switching clutch 4 on a transmission shaft 3 and a high- low switching clutch 4.
Before and after transmission axial direction of, and disposed between the first gear 5 engaging the disengageably to the height switching clutch 4 and the second gear 6, the wheels while being arranged parallel to the transmission shaft 3 on the counter shaft 7 for transmitting power, the first gear 5, the gear 8a meshing with the second gear 6, an intermediate gear member 8 having 8b freely idle, the level switching clutch 4 first gear 5 Or the second gear 6
The first gear 5, the second gear 6, and the intermediate gear
The power of the engine is transmitted to the transmission shaft 3 via the
The intermediate gear body 8 is configured to be transmitted while being shifted.
A clutch 14 meshes with a gear 19 provided on the rear counter shaft 7 so as to be integrally rotatable on the transmission shaft 3 and is removably engaged with a gear 20 provided on the counter shaft 7 so as to freely rotate.
In the transmission of a vehicle, the cylinder shaft 21 to which the power of the engine is transmitted is freely rotatably provided on the transmission shaft 3, and the high / low switching clutch 4 is integrally rotated with the cylinder shaft 21. The first gear 5 is freely rotatable, the second gear 6 is rotatably provided on the transmission shaft 3, and the intermediate gear body 8 is engaged with the clutch 14 so as to be freely engaged with and disengaged from the clutch 14.
22.
【０００８】[0008]
【作用】筒軸21に伝達されたエンジンからの動力は、高
低切換クラッチ4 を介して、第１ギヤ5 、中間ギヤ体8
、第２ギヤ6 を順次経て伝動軸3 へと伝達されるか、
或いは、第２ギヤ6 のみを経て伝動軸3 へと伝達され、
この伝動軸3 から複数の伝動ギヤ系列の内選択された１
つの伝動ギヤ系列を通してカウンタ軸7 に動力が伝達さ
れ、カウンタ軸7 から車輪に動力が伝達される。[Function] The power transmitted from the engine to the cylinder shaft 21 is high.
The first gear 5, the intermediate gear body 8, via the low switching clutch 4
Is transmitted to the transmission shaft 3 through the second gear 6 sequentially,
Alternatively, it is transmitted to the transmission shaft 3 only through the second gear 6,
From this transmission shaft 3, one of a plurality of transmission gear trains is selected.
Power is transmitted to the counter shaft 7 through the two transmission gear trains, and power is transmitted from the counter shaft 7 to the wheels.
【０００９】そして、クラッチ14を中間ギヤ体8 に設け
た係合ギヤ22に係合させることで、第１ギヤ5 から中間
ギヤ体8 、係合部22、クラッチ14を経てカウンタ軸7 に
動力が伝達されるか、或いは、第２ギヤ6 から中間ギヤ
体8 、係合部22、クラッチ14を経てカウンタ軸7 に動力
が伝達され、新たに２系統の変速経路が増加されること
となり、変速段数を増やすことができ、しかも、クラッ
チ14、中間ギヤ体8 等を利用しているので、変速装置の
軸方向の大きさも大きくはならない。By engaging the clutch 14 with the engagement gear 22 provided on the intermediate gear body 8, power is transmitted from the first gear 5 to the counter shaft 7 via the intermediate gear body 8, the engagement portion 22, and the clutch 14. Or the power is transmitted from the second gear 6 to the counter shaft 7 via the intermediate gear body 8, the engaging portion 22, and the clutch 14, and the speed change paths of the two systems are newly increased. Since the number of gear stages can be increased and the clutch 14, the intermediate gear body 8 and the like are used, the size of the transmission in the axial direction does not increase.
【００１０】[0010]
【実施例】以下、本発明の実施例を図面に基づいて説明
する。図１は第１実施例を示し、トラクタのトランスミ
ッションの走行系主変速装置を示し、以下、従来例との
相違点を述べる。同図において、走行系伝動軸3 の前部
には筒軸21がベアリングを介して遊転自在に外嵌されて
おり、この筒軸21の前部は前後進切換装置12の出力部12
a にスプライン嵌合され、筒軸21の後部には高低切換ク
ラッチ4 が一体回転自在に設けられている。そして、高
低切換クラッチ4 前方の第１ギヤ5 は前記筒軸21に遊転
自在に設けられていると共に、高低切換クラッチ4 後方
の第２ギヤ6 は伝動軸3 にスプライン嵌合されている。
したがって、高低切換クラッチ4 のシフタ4aを前方へシ
フトして、該高低切換クラッチ4 を第１ギヤ5 に連結さ
せると、動力は、筒軸21から第１ギヤ5 、中間ギヤ体8
、第２ギヤ6 を順次経て減速されて伝動軸3に伝達さ
れ、高低切換クラッチ4 のシフタ4bを後方へシフトし
て、該高低切換クラッチ4 を第２ギヤ6 に連結させると
動力は、筒軸21から第２ギヤ6 を介して同速状態で伝動
軸3 に伝達されるようになっている。Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 shows a first embodiment, which shows a traveling main transmission of a tractor transmission. Hereinafter, differences from the conventional example will be described. In the figure, a cylindrical shaft 21 is fitted around a front portion of a traveling system transmission shaft 3 through a bearing so as to freely rotate via a bearing. The front portion of the cylindrical shaft 21 is connected to an output portion 12 of a forward / reverse switching device 12.
a, a height switching clutch 4 is integrally rotatably provided at the rear of the cylinder shaft 21. The first gear 5 in front of the high / low switching clutch 4 is freely rotatably provided on the cylindrical shaft 21, and the second gear 6 behind the high / low switching clutch 4 is spline-fitted to the transmission shaft 3.
Therefore, when the shifter 4a of the high / low switching clutch 4 is shifted forward and the high / low switching clutch 4 is connected to the first gear 5, the power is transferred from the cylinder shaft 21 to the first gear 5 and the intermediate gear body 8.
The gears are sequentially decelerated and transmitted to the transmission shaft 3 through the second gear 6 to shift the shifter 4b of the high / low switching clutch 4 backward and connect the high / low switching clutch 4 to the second gear 6, so that the power is The power is transmitted from the shaft 21 to the transmission shaft 3 at the same speed via the second gear 6.
【００１１】また、中間ギヤ体8 の第２クラッチ14対向
側には、第２クラッチ14のシフタ14a に歯み合う係合ギ
ヤ22（係合部）が設けられており、第２クラッチ14のシ
フタ14a を前方にシフトして第２クラッチ14を歯合ギヤ
22に連結させることにより、動力が、筒軸21から第１ギ
ヤ5 、中間ギヤ体8 を経てカウンタ軸7 に伝達されるか
或いは、筒軸21から第２ギヤ6 、中間ギヤ体8 を経てカ
ウンタ軸7 に伝達されるようになっている。An engaging gear 22 (engaging portion) meshing with a shifter 14a of the second clutch 14 is provided on a side of the intermediate gear body 8 opposite to the second clutch 14. Shift the shifter 14a forward to shift the second clutch 14
The power is transmitted from the cylinder shaft 21 to the counter shaft 7 via the first gear 5 and the intermediate gear body 8, or from the cylinder shaft 21 to the counter gear 7 via the second gear 6 and the intermediate gear body 8. It is transmitted to the counter shaft 7.
【００１２】したがって、図１に示す主変速装置1 の構
成にあっては、高低切換クラッチ4を第１ギヤ5 或いは
第２ギヤ6 に連結した状態で、第１クラッチ13を第１の
伝動ギヤ系列15,16 に連結することで１速或いは５速が
得られ、第１クラッチ13を第２の伝動ギヤ系列17,18 に
連結することで２速或いは６速が得られ、第２クラッチ
14を第３の伝動ギヤ系列19,20 に連結することで３速或
いは７速が得られ、第２クラッチ14を係合ギヤ22に連結
することで４速或いは８速が得られるようになってい
る。Therefore, in the structure of the main transmission 1 shown in FIG. 1, the first clutch 13 is connected to the first transmission gear while the height switching clutch 4 is connected to the first gear 5 or the second gear 6. The first or fifth speed can be obtained by connecting to the trains 15 and 16, and the second or sixth speed can be obtained by connecting the first clutch 13 to the second transmission gear trains 17 and 18.
The third or seventh speed can be obtained by connecting the second clutch 14 to the third transmission gear trains 19 and 20, and the fourth or eighth speed can be obtained by connecting the second clutch 14 to the engagement gear 22. ing.
【００１３】このように、主変速装置1 は従来の６段変
速より２段多い８段変速とされ、特に、図例のようにシ
ンクロメッシュ式のクラッチを採用したものにあって
は、同期させる前のクラッチ側と被伝達側のギヤとの周
速の差が小さくなり、これによって、同期時間が短くな
ると共に、変速操作力が低減されて操作性が向上すると
いう利点を有する。As described above, the main transmission 1 is an eight-speed transmission which is two more stages than the conventional six-speed transmission. In particular, in the case where a synchromesh type clutch is employed as shown in FIG. The difference in peripheral speed between the previous clutch side and the transmission side gear is reduced, which has the advantage of shortening the synchronization time and reducing the shifting operation force to improve operability.
【００１４】図２は第２実施例を示し、第１クラッチ13
としてダブルコーンシンクロメッシュ式のものを採用
し、且つ、第１クラッチ13を伝動軸3 上に一体回転自在
に設けたものであり、そのため、第１伝動ギヤ系列15,1
6 及び第２伝動ギヤ系列17,18の内、伝動軸3 上のギヤ1
5,17 は該伝動軸3 に対して遊転自在とされ、カウンタ
軸7 上のギヤ16,18 は該カウンタ軸7 と一体回転自在と
されている。これによって、変速切換の操作力の低減化
が図られている。FIG. 2 shows a second embodiment, in which the first clutch 13
Of the double-cone synchromesh type, and the first clutch 13 is provided on the transmission shaft 3 so as to be rotatable integrally therewith.
6 and the second transmission gear train 17, 18, the gear 1 on the transmission shaft 3
The gears 5, 17 are freely rotatable with respect to the transmission shaft 3, and the gears 16, 18 on the counter shaft 7 are rotatable integrally with the counter shaft 7. As a result, the operation force for gear shifting is reduced.
【００１５】図３及び図４は比較例を示している。図３
に示すものは、従来のものと同様、第１ギヤ5 は前記実
施例における筒軸に一体形成されており、高低切換クラ
ッチ4 は伝動軸3 と一体回転自在とされ、第２ギヤ6 は
伝動軸3 に遊転自在に設けられている。その他は、第１
実施例と同様に構成されている。また、図４に示すもの
は、第１クラッチ13が、第２実施例と同様伝動軸3 上に
設けられている点が、図３のものと相違するだけであ
る。FIGS. 3 and 4 show a comparative example. FIG.
The first gear 5 is formed integrally with the cylinder shaft in the above embodiment, the height change clutch 4 is rotatable integrally with the transmission shaft 3, and the second gear 6 is The shaft 3 is freely rotatable. Others are the first
The configuration is the same as that of the embodiment. 4 is different from that of FIG. 3 only in that the first clutch 13 is provided on the transmission shaft 3 as in the second embodiment.
【００１６】前記図３、図４の構成のものでは、第２ク
ラッチ14を係合ギヤ22に連結させた状態では、動力は、
常に、第１ギヤ5 から中間ギヤ体8 を経てしか伝達され
なく、主変速装置1 は７段変速となるものであり、変速
段数のバリエーションの少ないものである。In the configuration shown in FIGS. 3 and 4, when the second clutch 14 is connected to the engagement gear 22, the power is
The transmission is always transmitted only from the first gear 5 via the intermediate gear body 8, so that the main transmission 1 is a seven-speed shift, and the variation in the number of shift steps is small.
【００１７】[0017]
【発明の効果】本発明によれば、伝動軸3 上に、エンジ
ンの動力が伝達される筒軸21を遊転自在に設け、この筒
軸21に、高低切換クラッチ4 を一体回転自在に設けると
共に第１ギヤ5 を遊転自在に設け、第２ギヤ6 を伝動軸
3 に一体回転自在に設け、中間ギヤ体8 に前記クラッチ
14に係脱自在に係合する係合部22を設けたことから、高
低切換クラッチ4 、第１ギヤ5 、第２ギヤ6 、中間ギヤ
体8 、クラッチ14等を利用して、新たに２段の変速段数
を増やすことができ、多種の作業機又は多種の作業内容
に対応させることができしかも、伝動軸3 、カウンタ軸
7 上に新たに伝動ギヤを組込む必要がなく、変速装置が
軸方向に大きくなることもない。According to the present invention, a cylinder shaft 21 to which the power of the engine is transmitted is freely rotatably provided on the transmission shaft 3, and a height switching clutch 4 is provided on this cylinder shaft 21 so as to be integrally rotatable. In addition, the first gear 5 is freely rotatably provided, and the second gear 6 is connected to the transmission shaft.
3 and the intermediate gear body 8
Since the provision of the engagement portion 22 which engages disengageably to 14, high
By using the low switching clutch 4, the first gear 5, the second gear 6, the intermediate gear body 8, the clutch 14, etc., the number of two-speed gears can be newly increased, and various types of work machines or various types of work contents can be provided. And transmission shaft 3, counter shaft
7 There is no need to install a new transmission gear on top, and the transmission does not grow in the axial direction.
【図１】第１実施例を示す変速装置の断面図である。FIG. 1 is a cross-sectional view of a transmission according to a first embodiment.
【図２】第２実施例を示す変速装置の断面図である。FIG. 2 is a sectional view of a transmission according to a second embodiment.
【図３】比較例を示す変速装置の断面図である。FIG. 3 is a sectional view of a transmission showing a comparative example.
【図４】比較例を示す変速装置の断面図である。FIG. 4 is a sectional view of a transmission showing a comparative example.
【図５】従来例を示す変速装置の断面図である。FIG. 5 is a cross-sectional view of a transmission showing a conventional example.
３ 走行系伝動軸 ４ 高低切換クラッチ ５ 第１ギヤ ６ 第２ギヤ ７ カウンタ軸 ８ 中間ギヤ体 8a 大径ギヤ 8b 小径ギヤ 14 第２クラッチ 19 ギヤ 20 ギヤ 21 筒軸 22 係合ギヤ（係合部） Reference Signs List 3 traveling system transmission shaft 4 height switching clutch 5 first gear 6 second gear 7 counter shaft 8 intermediate gear body 8a large diameter gear 8b small diameter gear 14 second clutch 19 gear 20 gear 21 cylinder shaft 22 engaging gear (engaging portion) )
───────────────────────────────────────────────────── フロントページの続き (58)調査した分野(Int.Cl.6，ＤＢ名) F16H 3/00 - 3/42 B60K 17/08 ──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int.Cl. 6 , DB name) F16H 3/00-3/42 B60K 17/08
Claims (1)
を設けると共に、この高低切換クラッチ(4) の伝動軸軸
方向前後に、該高低切換クラッチ(4) に係脱自在に係合
する第１ギヤ(5) と第２ギヤ(6) とを配設し、伝動軸
(3) に対して平行に配置されると共に車輪に動力を伝達
するカウンタ軸(7) 上に、前記第１ギヤ(5) 、第２ギヤ
（6)に歯合するギヤ(8a)(8b)を有する中間ギヤ体(8) を
遊転自在に設け、高低切換クラッチ(4) を第１ギヤ(5)
又は第２ギヤ(6) に係合させることで、第１ギヤ(5) 、
第２ギヤ(6) 、中間ギヤ体(8) を介して伝動軸(3) にエ
ンジンの動力が高低２段に変速されて伝達されるように
構成し、前記中間ギヤ体(8) 後方のカウンタ軸(7) 上
に、前記伝動軸(3) 上に一体回転自在に設けたギヤ(19)
に歯合すると共にカウンタ軸(7) 上に遊転自在に設けた
ギヤ(20)に係脱自在に係合するクラッチ(14)を一体回転
自在に設けた車輌の変速装置において、 前記伝動軸(3) 上に、エンジンの動力が伝達される筒軸
(21)を遊転自在に設け、この筒軸(21)に、高低切換クラ
ッチ(4) を一体回転自在に設けると共に第１ギヤ(5) を
遊転自在に設け、第２ギヤ(6) を伝動軸(3) に一体回転
自在に設け、中間ギヤ体(8) に前記クラッチ(14)に係脱
自在に係合する係合部(22)を設けたことを特徴とする車
輌の変速装置。1. A high / low switching clutch (4) on a transmission shaft (3).
The provided with this back and forth transmission axis direction of the high and low switching clutch (4), distribution of the first and gear (5) and the second gear (6) which engages disengageably to the height switching clutch (4) Transmission shaft
Gears (8a) and (8b) meshed with the first gear (5) and the second gear (6) on a counter shaft (7) arranged in parallel with (3) and transmitting power to the wheels. An intermediate gear body (8) having free rotation is provided, and a high / low switching clutch (4) is connected to the first gear (5).
Alternatively, by engaging with the second gear (6), the first gear (5),
The second gear (6) and the intermediate gear (8) are connected to the transmission shaft (3) by air.
Engine power is now transmitted in two stages, high and low
Configured, the intermediate gear member (8) behind the counter shaft on (7), said transmission shaft (3) gear (19) which is provided to be rotatable together on
A transmission for a vehicle, which is provided with a clutch (14) integrally engaged with a gear (20) rotatably provided on a counter shaft (7) so as to be freely rotatable on the counter shaft (7). (3) The cylinder shaft to which the power of the engine is transmitted
(21) is freely rotatable, and a height change clutch (4) is rotatably provided integrally with the cylindrical shaft (21), a first gear (5) is freely rotatable, and a second gear (6) is provided. A transmission shaft (3) rotatably provided integrally with the transmission shaft (3), and an intermediate gear body (8) provided with an engaging portion (22) for engaging and disengaging the clutch (14). apparatus.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4150915A JP2918395B2 (en) | 1992-06-10 | 1992-06-10 | Vehicle transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4150915A JP2918395B2 (en) | 1992-06-10 | 1992-06-10 | Vehicle transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH05346144A JPH05346144A (en) | 1993-12-27 |
| JP2918395B2 true JP2918395B2 (en) | 1999-07-12 |
Family
ID=15507181
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4150915A Expired - Fee Related JP2918395B2 (en) | 1992-06-10 | 1992-06-10 | Vehicle transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2918395B2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5557980A (en) * | 1992-12-08 | 1996-09-24 | Getrag Gears Of North America, Inc. | One-piece gear rattle prevention for countershaft transmission |
-
1992
- 1992-06-10 JP JP4150915A patent/JP2918395B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH05346144A (en) | 1993-12-27 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |