JPS6157505B2 - - Google Patents
Info
- Publication number
- JPS6157505B2 JPS6157505B2 JP54021448A JP2144879A JPS6157505B2 JP S6157505 B2 JPS6157505 B2 JP S6157505B2 JP 54021448 A JP54021448 A JP 54021448A JP 2144879 A JP2144879 A JP 2144879A JP S6157505 B2 JPS6157505 B2 JP S6157505B2
- Authority
- JP
- Japan
- Prior art keywords
- gear
- shaft
- drive
- driven
- passive
- 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
Links
- 230000007935 neutral effect Effects 0.000 claims description 11
- 230000033001 locomotion Effects 0.000 claims description 4
- 230000005540 biological transmission Effects 0.000 description 18
- 230000007246 mechanism Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 1
Landscapes
- Structure Of Transmissions (AREA)
Description
【発明の詳細な説明】
本発明は、駆動軸から２個の受動軸に同時に動
力を伝動するための変速装置に係るものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a transmission for simultaneously transmitting power from a drive shaft to two passive shafts.
従来、この種の変速装置においては、第１受動
軸に支持された第１受動ギヤーと、第２受動軸に
支持された第２受動ギヤーとを設け、駆動軸に摺
動自在に支持されて、第１受動ギヤーと係脱自在
に係合する第１駆動ギヤーと、第２受動ギヤーと
係脱自在に係合する第２駆動ギヤーとを一体的に
設けて、この第１駆動ギヤーと第２駆動ギヤーと
を一体的に軸方向に摺動せしめて、それぞれ第１
受動ギヤー、第２受動ギヤーに同時に係合せしめ
て、第１受動軸と第２受動軸とに動力を伝動せし
めていた。しかるに２組のギヤーを同時に係合せ
しめていたために、２組のギヤーの歯の係合位置
が一致することが困難で、係合が中滑に行なわれ
ない欠点があつた。 Conventionally, this type of transmission device includes a first passive gear supported by a first driven shaft and a second passive gear supported by a second driven shaft, which are slidably supported by the drive shaft. , a first drive gear that removably engages with the first driven gear, and a second drive gear that removably engages with the second driven gear are integrally provided, and the first drive gear and the second drive gear are integrally provided. The two drive gears are slid together in the axial direction, and the first and second drive gears are slid together in the axial direction.
The driven gear and the second driven gear were engaged simultaneously to transmit power to the first driven shaft and the second driven shaft. However, since the two sets of gears were engaged at the same time, it was difficult to match the engagement positions of the teeth of the two sets of gears, and there was a drawback that the engagement was not carried out smoothly.
本発明は、第１駆動ギヤー、第２駆動ギヤーの
中立位置において、第１駆動ギヤーと第１受動ギ
ヤーとの軸方向の間隙の寸法を、第２駆動ギヤー
と第２受動ギヤーとの軸方向の間隙の寸法よりも
大なる寸法に設けることにより、第２駆動ギヤー
と第２受動ギヤーが係合しはじめてのち、第１駆
動ギヤーと第１受動ギヤーとを係合めしめて、係
合作動を円滑に行なわしめようとするものであ
る。以下、図面を用いて本発明の１実施例につい
て詳細な説明を行なう。 In the present invention, when the first drive gear and the second drive gear are in a neutral position, the size of the gap in the axial direction between the first drive gear and the first passive gear is changed in the axial direction between the second drive gear and the second passive gear. By providing a dimension larger than the dimension of the gap, after the second drive gear and the second passive gear start to engage, the first drive gear and the first passive gear are engaged and the engagement operation is performed. The aim is to ensure that the process runs smoothly. Hereinafter, one embodiment of the present invention will be described in detail using the drawings.
図において、１はコンバインの機体に固着され
たギヤーケース、３はギヤーケース１に回転自在
に軸支された駆動軸、５は駆動軸３の端部に固着
されたプーリーで、ベルト７を介してエンジン
（図示せず）の動力によつて駆動される。９は第
１受動軸で端部に固着するプーリー１１からベル
ト１３を介して刈取装置（図示せず）に動力を伝
達するものである。１５は駆動軸３の動力を走行
装置（図示せず）に伝達するための第１受動軸
（走行軸）、１７は主変速軸、１９はクラツチ軸、
２１，２３はそれぞれ左側、右側に設けられた車
軸で、それぞれ左側、化側の走行装置（図示せ
ず）を駆動する。駆動軸３、第１受動軸９、第２
受動軸１５、主変速軸１７、クラツチ軸１９、車
軸２１，２３および逆転軸２５は第２図に示すよ
うに関係位置に設けられている。２７，２９，３
１は駆動軸３に、スプライン３３を介して軸方向
に摺動自在に設けられた摺動体３５に一体的に固
着された駆動ギヤーで、左側から右方向に順次配
設され、その大きさはそれぞれ大、小、中の大き
さに設けられている。３７は駆動軸３から第１受
動軸（刈取装置を駆動するための作業軸）に回転
速度を切り換えて動力を伝達するための作業切換
装置で、つぎのように構成されている。すなわ
ち、３９，４１は第１受動軸（作業軸）９に固着
して設けられた第１受動ギヤーで、摺動体３５を
第１図に示す中立位置から右方向の高速位置に移
動したときに、駆動ギヤー２７と第１受動ギヤー
３９が係合して第１受動軸９を高速に切り換え
る。また摺動体３５を第１図の左方向の低速位置
に移動したときに、駆動ギヤー３１と第１受動ギ
ヤー４１が係合して、第１受動軸９を低速に切り
換える。４３は駆動軸３から第２受動軸１５（走
行装置を駆動するための走行軸）に回転速度を切
り換えて動力を伝達するための走行切換装置で、
つぎのように構成されている。すなわち、４５，
４７，４９は第２受動軸（走行軸）１５に固着し
て設けられた第２受動ギヤーで、摺動体３５を第
１図に示す中立位置から右方向に移動して、駆動
ギヤー２７と第１受動ギヤー３９が係合した位置
において、駆動ギヤー３１が第２受動ギヤー４９
と係合して、第２受動軸（走行軸）１５を中速位
置に切り換える。摺動体３５をさらに右方向に移
動せしめると、駆動ギヤー２７と第２受動ギヤー
４５が係合して第２受動軸（走行軸）１５を高速
位置に切り換える。このとき作業切換装置３７は
中立位置となる。摺動体３５を第１図に示す中立
位置から左方向に移動せしめて、駆動ギヤー３１
が第１受動ギヤー４１と係合した位置において、
駆動ギヤー２９が第２受動ギヤー４７と係合し
て、第２受動軸（作業軸）１５を低速位置に切り
換える。なお、説明上、駆動ギヤー２７，３１は
第１受動ギヤー３９，４１にそれぞれ係合する場
合においては第１駆動ギヤーと称し、また駆動ギ
ヤー２９，３１は第２受動ギヤー４７，４９にそ
れぞれ係合する場合においては第２駆動ギヤーと
称することとする。５１，５３は主変速軸１７に
スプライン５４を介して摺動自在に設けた摺動
体、５５，５７は摺動体５１に一体的に設けられ
たギヤーで、摺動体５１が第１図に示す中立位置
から左方向に移動したとき、ギヤー５５は第２受
動ギヤー４７と係合して、第２受動軸１５の動力
を主変速軸１７に高速に伝達し、また摺動体５１
を右方向に移動したとき、ギヤー５７は第２受動
ギヤー４９と係合して、第２駆動軸１５の動力を
主変速軸１７に低速で伝達される。また５９は摺
動体５３に一体的に設けられたギヤーで、摺動体
５３を第１図に示す中立位置から右方向に移動し
たとき、ギヤー５９は第２受動軸１５に固着する
ギヤー６１と係合して第２受動軸１５の動力を主
変速軸１７に中速に伝達する。６３は逆転軸２５
に固着するギヤーで、第２受動軸１５に固着する
ギヤー６５と常時係合している。摺動体５３は第
１図の左方向に移動したとき、ギヤー５９はギヤ
ー６３と係合し、第２受動軸１５の動力は主変速
軸１７に逆転して伝達される。第１図に示す中立
位置において、第１駆動ギヤー２７と第１受動ギ
ヤー３９との軸方向の間隙Ａの寸法は、第２駆動
ギヤー３１と第２受動ギヤー４９との軸方向の間
隙Ｂの寸法よりも大なる寸法に設けられ、また同
様に第１駆動ギヤー３１と第１受動ギヤー４１と
の軸方の間隙Ｃの寸法は、第２駆動ギヤー２９と
第２受動ギヤー４７との間の軸方向の間隙Ｄの寸
法よりも大なる寸法に設けられている。 In the figure, 1 is a gear case fixed to the body of the combine, 3 is a drive shaft rotatably supported by the gear case 1, and 5 is a pulley fixed to the end of the drive shaft 3. and is driven by the power of an engine (not shown). Reference numeral 9 denotes a first driven shaft which transmits power from a pulley 11 fixed to the end thereof to a reaping device (not shown) via a belt 13. 15 is a first passive shaft (traveling shaft) for transmitting the power of the drive shaft 3 to a traveling device (not shown); 17 is a main transmission shaft; 19 is a clutch shaft;
Reference numerals 21 and 23 denote axles provided on the left and right sides, respectively, which drive traveling devices (not shown) on the left and rear sides, respectively. Drive shaft 3, first driven shaft 9, second
The passive shaft 15, the main transmission shaft 17, the clutch shaft 19, the axles 21, 23, and the reversing shaft 25 are provided in related positions as shown in FIG. 27, 29, 3
Reference numeral 1 denotes a drive gear that is integrally fixed to a sliding body 35 provided on the drive shaft 3 via a spline 33 so as to be slidable in the axial direction. They are available in large, small, and medium sizes. Reference numeral 37 denotes a work switching device for switching the rotational speed and transmitting power from the drive shaft 3 to the first passive shaft (work shaft for driving the reaping device), and is configured as follows. That is, 39 and 41 are first passive gears fixed to the first passive shaft (work shaft) 9, and when the sliding body 35 is moved from the neutral position shown in FIG. 1 to the high speed position in the right direction, , the drive gear 27 and the first driven gear 39 engage to switch the first driven shaft 9 at high speed. Further, when the sliding body 35 is moved to the left in FIG. 1 to a low speed position, the drive gear 31 and the first driven gear 41 are engaged to switch the first driven shaft 9 to the low speed position. 43 is a travel switching device for switching the rotational speed and transmitting power from the drive shaft 3 to the second passive shaft 15 (traveling shaft for driving the traveling device);
It is structured as follows. That is, 45,
Reference numerals 47 and 49 are second passive gears fixed to the second passive shaft (traveling shaft) 15, which move the sliding body 35 rightward from the neutral position shown in FIG. At the position where the first driven gear 39 is engaged, the driving gear 31 is engaged with the second driven gear 49.
, and switches the second driven shaft (traveling shaft) 15 to the medium speed position. When the sliding body 35 is further moved to the right, the drive gear 27 and the second driven gear 45 engage with each other, and the second driven shaft (traveling shaft) 15 is switched to the high speed position. At this time, the work switching device 37 is in the neutral position. The sliding body 35 is moved leftward from the neutral position shown in FIG.
At the position where is engaged with the first passive gear 41,
The drive gear 29 engages with the second driven gear 47 to switch the second driven shaft (work shaft) 15 to the low speed position. For the sake of explanation, the drive gears 27 and 31 are referred to as first drive gears when they engage with the first driven gears 39 and 41, respectively, and the drive gears 29 and 31 are referred to as first drive gears when they engage with the second driven gears 47 and 49, respectively. In this case, it will be referred to as the second drive gear. Reference numerals 51 and 53 denote sliding bodies that are slidably provided on the main transmission shaft 17 via a spline 54, and 55 and 57 are gears that are integrally provided with the sliding body 51. When the gear 55 moves to the left from the position, the gear 55 engages with the second passive gear 47 and transmits the power of the second passive shaft 15 to the main transmission shaft 17 at high speed.
When the gear 57 moves to the right, the gear 57 engages with the second passive gear 49, and the power of the second drive shaft 15 is transmitted to the main transmission shaft 17 at a low speed. Further, 59 is a gear provided integrally with the sliding body 53, and when the sliding body 53 is moved rightward from the neutral position shown in FIG. At the same time, the power of the second passive shaft 15 is transmitted to the main transmission shaft 17 at a medium speed. 63 is the reverse rotation shaft 25
The gear 65 is fixed to the second driven shaft 15 and is always engaged with the gear 65 fixed to the second driven shaft 15. When the sliding body 53 moves to the left in FIG. 1, the gear 59 engages with the gear 63, and the power of the second passive shaft 15 is transmitted to the main transmission shaft 17 in reverse. In the neutral position shown in FIG. Similarly, the dimension of the axial gap C between the first drive gear 31 and the first passive gear 41 is larger than the dimension between the second drive gear 29 and the second passive gear 47. The dimension is larger than the dimension of the gap D in the axial direction.
６７はクラツチ軸１９の中央位置に設けたフラ
ンジ部６９に回転自在に嵌合するギヤーで、主変
速軸１７に固着するギヤー７１で常時係合してい
る。７３，７５はクラツチ軸１９の外周に左、右
側にそれぞれ回転自在に嵌合する軸筒で、それぞ
れベアリング７７，７９によりギヤーケース１に
回転自在に支持されている。８１，８３は左、右
のサイドクラツチで、つぎのように構成されてい
る。すなわち、８５，８７は軸筒７３，７５の外
周にそれぞれ回転自在にかつ摺動自在に嵌合する
クラツチヤギヤーで、それぞれ内側方に摺動した
ときに、ギヤー６７の内径部に設けた内歯係止爪
８９に係合する。９１，９３は車軸２１，２３に
それぞれ固着するギヤーで、それぞれギヤー８
７，８９と常時係合している。９５，９７はそれ
ぞれ左、右側の制動装置で、つぎのように構成さ
れている。すなわち、９９，１０１はそれぞれ軸
筒７３，７５の外側端にナツト１０３，１０５に
より固着されたブレーキドラム、１０７はギヤー
ケース１の左側に回動自在に軸支された軸、１０
９は軸１０７に固着するアームで、端部はピン１
１１によりブレーキロツド１１３に連結してい
る。軸１０７はブレーキドラム９９の内方に設け
られたブレーキ部１１５に連動し、ブレーキロツ
ド１１３をひくことによりブレーキ部１１５が作
動してブレーキドラム９９を制動するものであ
る。ブレーキ部１１５は通常用いられるシユーブ
レーキ機構と同じて、ここに詳細な説明を省略す
る。なお、右側の制動装置９７の構成作用につい
ては左側の制動装置９５と同じて、ブレーキ部１
１７によつてブレーキドラム１０１を制動するも
のである。したがつて詳細な説明を省略する。 A gear 67 rotatably fits into a flange portion 69 provided at the center of the clutch shaft 19, and is constantly engaged with a gear 71 fixed to the main transmission shaft 17. Reference numerals 73 and 75 denote shaft cylinders rotatably fitted to the left and right sides of the outer periphery of the clutch shaft 19, respectively, and are rotatably supported by the gear case 1 by bearings 77 and 79, respectively. Reference numerals 81 and 83 denote left and right side clutches, which are constructed as follows. That is, the clutch gears 85 and 87 are rotatably and slidably fitted to the outer peripheries of the shaft cylinders 73 and 75, respectively, and when they slide inward, the clutch gears 85 and 87 engage the inner diameter portion of the gear 67. It engages with the tooth locking pawl 89. 91 and 93 are gears fixed to the axles 21 and 23, respectively, and gear 8, respectively.
7 and 89 are constantly engaged. 95 and 97 are left and right braking devices, respectively, and are constructed as follows. That is, 99 and 101 are brake drums fixed to the outer ends of shaft cylinders 73 and 75 with nuts 103 and 105, respectively; 107 is a shaft rotatably supported on the left side of gear case 1;
9 is an arm that is fixed to the shaft 107, and the end is connected to the pin 1.
11 to a brake rod 113. The shaft 107 is interlocked with a brake section 115 provided inside the brake drum 99, and when the brake rod 113 is pulled, the brake section 115 is activated to brake the brake drum 99. The brake section 115 is the same as a normally used shoe brake mechanism, and detailed description thereof will be omitted here. The structure and function of the right braking device 97 is the same as that of the left braking device 95, and the brake unit 1
17 to brake the brake drum 101. Therefore, detailed explanation will be omitted.
なお、摺動体３５、摺動体５１、摺動体５３は
それぞれ操作レバー（図示せず）に連動して摺動
作動を行なわしめるが、これらの摺動作動機構に
ついては通常の変速装置において用いられる構
成、作動と同じてあるので、ここに説明を省略す
る。 The sliding body 35, the sliding body 51, and the sliding body 53 each perform sliding motion in conjunction with an operating lever (not shown), but these sliding motion mechanisms have a configuration used in a normal transmission. , the operation is the same, so the explanation is omitted here.
以上の構成において、本装置の作用について説
明する。摺動体３５を第１図の左方向に移動せし
めると、駆動ギヤー３１が第１受動ギヤー４１と
係合して、第１受動軸（作業軸）９を低速で回転
せしめるとともに、駆動ギヤー２９が第２受動ギ
ヤー４７と係合して第１受動軸（走行軸）１５を
低速で回転せしめる。つぎに摺動体３５を右方向
に移動せしめると、駆動ギヤー２７が第１受動ギ
ヤー３９と係合して、第１受動軸（作業軸）９を
高速で回転せしめるとともに、駆動ギヤー３１が
第２受動ギヤー４９と係合して第２受動軸（走行
軸）１５を中速で回転せしめる。つぎに摺動体３
５をさらに右方向に移動せしめると、駆動ギヤー
２７が第２受動ギヤー４５と係合して、第２受動
軸（走行軸）１５を高速で回転せしめるが、第１
受動軸（作業軸）９には回転が伝達されない。ま
た摺動体５１を第１図の右方向に移動せしめると
ギヤー５７が第２受動軸４９と係合して、主変速
軸１７を低速で回転せしめる。つぎに摺動体２１
を左方向に移動せしめると、ギヤー５５が第２受
動ギヤー４７と係合して、主変速軸１７を高速で
回転せしめる。摺動体５１を中立位置において、
摺動体５３を第１図の左方向に移動せしめると、
ギヤー５９が第２受動ギヤー６１と係合して主変
速軸１７を中速で回転せしめる。摺動体５３を左
方向に移動せしめると、ギヤー５９が、ギヤー６
３と係合し、第１受動軸１５の動力はギヤー６５
と、ギヤー６３、ギヤー５９を経て、主変速軸１
７を逆転せしめる。主変速軸１７の動力はギヤー
７１からギヤー６７を回転せしめる。 In the above configuration, the operation of the present device will be explained. When the sliding body 35 is moved to the left in FIG. It engages with the second driven gear 47 to rotate the first driven shaft (traveling shaft) 15 at a low speed. Next, when the sliding body 35 is moved to the right, the driving gear 27 engages with the first driven gear 39, causing the first driven shaft (work shaft) 9 to rotate at high speed, and the driving gear 31 It engages with the passive gear 49 to rotate the second passive shaft (traveling shaft) 15 at a medium speed. Next, sliding body 3
5 is further moved to the right, the drive gear 27 engages with the second driven gear 45, causing the second driven shaft (traveling shaft) 15 to rotate at high speed.
No rotation is transmitted to the passive shaft (work shaft) 9. Further, when the sliding body 51 is moved to the right in FIG. 1, the gear 57 engages with the second driven shaft 49, causing the main transmission shaft 17 to rotate at a low speed. Next, the sliding body 21
When the gear 55 is moved to the left, the gear 55 engages with the second passive gear 47, causing the main transmission shaft 17 to rotate at high speed. With the sliding body 51 in the neutral position,
When the sliding body 53 is moved to the left in FIG.
The gear 59 engages with the second passive gear 61 to rotate the main transmission shaft 17 at a medium speed. When the sliding body 53 is moved to the left, the gear 59 is moved to the gear 6.
3, and the power of the first passive shaft 15 is transmitted to the gear 65.
, through gear 63 and gear 59, main transmission shaft 1
Reverse 7. The power of the main transmission shaft 17 causes the gear 71 to rotate the gear 67.
機体を直進走行せしめるには、左、右のクラツ
チレバー（図示せず）を操作して、左、右のクラ
ツチギヤー８５，８７を内歯係止爪８９にともに
係止せしめると、ギヤー６７の動力は、ギヤー８
５からギヤー９１を経て車軸２１を駆動せしめる
とともに、ギヤー８７からギヤー９３を経て車軸
２３を同方向に、かつ同速度で駆動せしめるので
機体は直進する。機体を旋回せしめるにあたつて
は、たとえば左方向に旋回せしめるには、右側の
クラツチギヤー８７は内歯係止爪８９に係止せし
めた状態とし、左側のクラツチギヤー８５を第１
図のＦ方向に移動せしめて、クラツチギヤー８５
を内歯係止爪８９から離脱せしめ、さらに操作杆
（図示せず）によりブレーキロツド１１３を介し
てブレーキ部１１５を作動せしめてブレーキドラ
ム９９を制動すれば、左側の車軸２１は制動さ
れ、右側に車軸２３の駆動により機体は左方向に
旋回するものである。 To make the aircraft travel straight, operate the left and right clutch levers (not shown) to lock both the left and right clutch gears 85 and 87 with the internal locking pawls 89, and the power of the gear 67 is reduced. is gear 8
5 through gear 91 to drive axle 21, and gear 87 through gear 93 to drive axle 23 in the same direction and at the same speed, so the aircraft moves straight. To turn the aircraft, for example, to the left, the right clutch gear 87 should be engaged with the internal locking pawl 89, and the left clutch gear 85 should be in the first position.
Clutch gear 85 by moving it in direction F in the figure.
is released from the internal tooth locking pawl 89, and the brake drum 99 is braked by actuating the brake part 115 via the brake rod 113 using an operation lever (not shown), the left axle 21 is braked, and the right side axle 21 is braked. The aircraft body turns to the left by driving the axle 23.
なお、第１図に示す中立位置において、第１駆
動ギヤー（駆動ギヤ）２７と第１受動ギヤー３９
との軸方向の間隙Ａの寸法を第２駆動ギヤー３１
と第２受動ギヤー４９との軸方向の間隙Ｂの寸法
より大なる寸法に設けてあるので、第２駆動ギヤ
ー３１と第２受動ギヤー４９が係合してのち、第
１駆動ギヤー２７と第１受動ギヤー３９が係合す
るので、切り換え作業が円滑に行なわれるもので
ある。また間隙Ｃと間隙Ｄにおいても同様の効果
を有するものである。 Note that in the neutral position shown in FIG. 1, the first drive gear (drive gear) 27 and the first passive gear 39
The dimension of the axial gap A between the second drive gear 31 and
Since the dimension is larger than the dimension of the axial gap B between the second driven gear 49 and the second driven gear 49, after the second driving gear 31 and the second driven gear 49 are engaged, the first driving gear 27 and the second driven gear 49 are connected. Since the first passive gear 39 is engaged, the switching operation can be performed smoothly. Also, the gap C and the gap D have similar effects.
以上のように本発明は、第１受動軸に支持され
た第１受動ギヤーと、第２受動軸に支持された第
２受動ギヤーとを設け、駆動軸に摺動自在に支持
されて、前記第１受動ギヤーと係脱自在に係合す
る第１駆動ギヤーと、前記第２受動ギヤーと係脱
自在に係合する第２駆動ギヤーとを一体的に設け
て、これを第１駆動ギヤーと第２駆動ギヤーとの
一体的移動操作によつて各対向する第受動１ギヤ
ー、第２受動ギヤーへ同時に噛合せる関係に設
け、前記第１駆動ギヤー、前記第２駆動ギヤーの
中立位置において、前記第１駆動ギヤーと前記第
１受動ギヤーとの軸方向の間隙の寸法を、前記第
２駆動ギヤーと前記第２受動ギヤーとの間隙の寸
法よりも大なる寸法に設けて、これら第１駆動ギ
ヤーと第２駆動ギヤーとを若干のタイミングのず
れで第１受動ギヤー、第２受動ギヤーに噛合せる
変速装置であるから２組のギヤーを同時に係合せ
しめる場合にも、円滑に係合せしめることがで
き、切換作業を容易に行なうことができ、また実
施例のような刈取機の変速装置等にあつては刈取
り作業等の作業の切り換え作動が走行の切り換え
作動より先行することがなく、作業を円滑に行な
うことができるものである。 As described above, the present invention provides a first driven gear supported by a first driven shaft and a second driven gear supported by a second driven shaft, and is slidably supported by a drive shaft. A first drive gear that removably engages with the first driven gear, and a second drive gear that removably engages with the second driven gear are integrally provided, and the first drive gear and the second drive gear are integrally provided. The first driven gear and the second driven gear facing each other are provided in a simultaneous meshing relationship by an integral movement operation with the second driving gear, and when the first driving gear and the second driving gear are in neutral positions, the The dimension of the gap in the axial direction between the first drive gear and the first driven gear is set to be larger than the dimension of the gap between the second drive gear and the second passive gear, so that the first drive gear Since this is a transmission device that meshes the first and second drive gears with the first and second driven gears with a slight timing difference, even when two sets of gears are to be engaged at the same time, they can be engaged smoothly. In addition, in the case of the transmission device of a reaper as in the embodiment, the switching operation for tasks such as reaping does not precede the switching operation for traveling, and the switching operation can be performed easily. This can be done smoothly.
なお、本発明は前述の実施例に限定されるもの
ではなく、他の態様においても実施しうるもので
ある。 It should be noted that the present invention is not limited to the above-mentioned embodiments, but can be implemented in other embodiments as well.
第１図は本発明の１実施例の正断面展開説明
図、第２図はギヤーの配置を示す側面説明図であ
る。
図面の主要な部分を表わす符号の説明、３……
駆動軸、９……第１受動軸、１５……第２受動
軸、２７……第１駆動ギヤー、３１……第２駆動
ギヤー、３９……第１受動ギヤー、４９……第２
受動ギヤー、Ａ，Ｂ……間隙。
FIG. 1 is a front cross-sectional developed explanatory view of one embodiment of the present invention, and FIG. 2 is a side explanatory view showing the arrangement of gears. Explanation of the symbols representing the main parts of the drawing, 3...
Drive shaft, 9...first driven shaft, 15...second driven shaft, 27...first drive gear, 31...second drive gear, 39...first driven gear, 49...second
Passive gear, A, B... gap.
Claims (1)
９と、第２受動軸１５に支持された第２受動ギヤ
ー４９とを設け、駆動軸３に摺動自在に支持され
て、前記第１受動ギヤー３９と係脱自在に係合す
る第１駆動ギヤー２７と、前記第２自動ギヤー４
９と係脱自在に係合する第２駆動ギヤー３１とを
一体的に設けて、これら第１駆動ギヤー２７と第
２駆動ギヤー３１との一体的な移動操作によつて
各対向する第１受動ギヤー３９、第２受動ギヤー
４９へ同時に噛合せる関係に設け、前記第１駆動
ギヤー２７、前記第２駆動ギヤー３１の中立位置
において、前記第１駆動ギヤー２７と前記第１受
動ギヤー３９との軸方向の間隙Ａの寸法を、前記
第２駆動ギヤー３１と前記第２受動ギヤー４９と
の軸方向の間隙Ｂの寸法よりも大なる寸法に設け
て、これら第１駆動ギヤー２７と第２駆動ギヤー
３１とを若干のタイミングのずれで第１受動ギヤ
ー３９、第２受動ギヤー４９に噛合せることを特
徴とする変速装置。1 First passive gear 3 supported by first passive shaft 9
9 and a second driven gear 49 supported by the second driven shaft 15, the first drive is slidably supported by the drive shaft 3 and removably engaged with the first driven gear 39. gear 27 and the second automatic gear 4
9 and a second drive gear 31 that is removably engaged with the first drive gear 27 and the second drive gear 31 are integrally provided, and by the integral movement operation of the first drive gear 27 and the second drive gear 31, each opposing first passive The shafts of the first driving gear 27 and the first driven gear 39 are provided in a relationship that meshes with the gear 39 and the second driven gear 49 at the same time, and when the first driving gear 27 and the second driving gear 31 are in the neutral position, the shafts of the first driving gear 27 and the first driven gear 39 are The dimension of the gap A in the direction is set to be larger than the dimension of the gap B in the axial direction between the second drive gear 31 and the second driven gear 49, so that the first drive gear 27 and the second drive gear 31 and meshes with a first passive gear 39 and a second passive gear 49 with a slight timing lag.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2144879A JPS55115647A (en) | 1979-02-27 | 1979-02-27 | Speed change gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2144879A JPS55115647A (en) | 1979-02-27 | 1979-02-27 | Speed change gear |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS55115647A JPS55115647A (en) | 1980-09-05 |
| JPS6157505B2 true JPS6157505B2 (en) | 1986-12-06 |
Family
ID=12055236
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2144879A Granted JPS55115647A (en) | 1979-02-27 | 1979-02-27 | Speed change gear |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS55115647A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2550933Y2 (en) * | 1991-08-09 | 1997-10-15 | 株式会社クボタ | Mission structure |
-
1979
- 1979-02-27 JP JP2144879A patent/JPS55115647A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS55115647A (en) | 1980-09-05 |
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