JP4960938B2 - Passenger work vehicle - Google Patents

Passenger work vehicle Download PDF

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JP4960938B2
JP4960938B2 JP2008231060A JP2008231060A JP4960938B2 JP 4960938 B2 JP4960938 B2 JP 4960938B2 JP 2008231060 A JP2008231060 A JP 2008231060A JP 2008231060 A JP2008231060 A JP 2008231060A JP 4960938 B2 JP4960938 B2 JP 4960938B2
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transmission
shaft
transmission mechanism
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case
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健吉 平川
斉 青山
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Kubota Corp
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Description

本発明は、後部に配置したミッションケースに後輪駆動機構を設け、後輪駆動機構から分岐した動力を前輪出力部に出力すべく構成してある乗用型作業車に関する。   The present invention relates to a passenger work vehicle that is configured to provide a rear wheel drive mechanism in a transmission case disposed at a rear portion and output power branched from the rear wheel drive mechanism to a front wheel output portion.

乗用型作業車では例えば特許文献１に開示されているように、エンジン（公報内番号：１）の後方に主クラッチケース（公報内番号：１０）と前輪増速ケース（公報内番号：１１）とを配置し、前輪増速ケース（公報内番号：１１）と後方に配置したミッションケース（公報内番号：５）とに亘って、伝動機構を設けていた。   In a passenger work vehicle, for example, as disclosed in Patent Document 1, a main clutch case (publication number: 10) and a front wheel acceleration case (publication number: 11) are located behind an engine (publication number: 1). And a transmission mechanism was provided across the front wheel acceleration case (publication number: 11) and the rear transmission case (publication number: 5).

つまり、前輪増速ケース内に、エンジン動力を受けて減速する第１伝動機構を設け、前輪増速ケースとミッションケースとに亘って設けた第１伝動軸によって、前記第１伝動機構をミッションケース内の後輪駆動機構に連係してある。
一方、後輪駆動機構から分岐された動力は、ミッションケースと前輪増速ケースとに亘って架設されている第２伝動軸によって前輪増速ケース内の前輪増速機構に連係されている。 That is, a first transmission mechanism that receives engine power and decelerates is provided in the front wheel acceleration case, and the first transmission mechanism is provided in a transmission case by a first transmission shaft that is provided across the front wheel acceleration case and the transmission case. It is linked to the inner rear wheel drive mechanism.
On the other hand, the power branched from the rear wheel drive mechanism is linked to the front wheel speed increasing mechanism in the front wheel speed increasing case by a second transmission shaft that extends between the transmission case and the front wheel speed increasing case.

特公平８−２９６８０号公報（公報第３頁第５欄の第３行〜第２０行、図１，２）Japanese Examined Patent Publication No. 8-29680 (Line 3, page 5, line 5 to line 20, FIGS. 1 and 2)

上記した構成においては、ミッションケースと前輪増速ケースとに亘って架設された第１伝動軸、及び、第２伝動軸として、ユニバーサルジョイントが使用されており、水平方向に対して傾斜した姿勢で伝動軸を配置する構成を採っていた。
そうすると、ユニバーサルジョイントでは使用可能な曲がり角度に一定の制限があるので、このようにユニバーサルジョインを使用した伝動構造を、ホイールベースが短い小型の機種に適応することはできなかった。 In the above-described configuration, the universal joint is used as the first transmission shaft and the second transmission shaft installed between the transmission case and the front wheel acceleration case, and in a posture inclined with respect to the horizontal direction. The structure which has arrange | positioned a transmission shaft was taken.
As a result, there is a certain limit on the bending angle that can be used with universal joints, and thus the transmission structure using universal joins could not be applied to small models with short wheelbases.

本発明の目的は、後ミッションケースから前輪への伝動系にユニバーサルジョントを利用した形態に変更を加えることによって、大小機種間においても適用可能な伝動構造を備えた乗用型作業車を提供する点にある。   An object of the present invention is to provide a passenger-type work vehicle having a transmission structure that can be applied even between large and small models by changing the form using a universal joint to the transmission system from the rear mission case to the front wheels. It is in.

（構成）
請求項１に係る本発明の特徴構成は、エンジン動力を受ける前ミッションケースと、前記前ミッションケースの後方に配置される後ミッションケースと、前記後ミッションケースの前面に装着される静油圧式無段変速装置とを設け、
前記前ミッションケース内に、エンジン動力を後輪出力部に伝達する第１伝動機構と、前記後ミッションケースから戻される動力を受けて前輪出力部へ伝達する第２伝動機構とを設け、
前記後ミッションケース内に、前記静油圧式無段変速装置の油圧モータ軸からの動力伝達を受けて後輪駆動軸に動力伝達する第３伝動機構と、前記第３伝動機構に伝達された動力を前記前ミッションケースへ戻す第４伝動機構とを設け、
前記後輪出力部から前記静油圧式無段変速装置の油圧ポンプ軸に動力伝達する第1伝動軸と、前記第４伝動機構の動力を前記第２伝動機構に伝達する第２伝動軸とを、前記前後ミッションケースに亘って架設し、
前記後輪出力部の出力軸芯と、前記油圧ポンプ軸の入力軸芯と、前記第１伝動軸とを同一軸芯位置に配置し、前記第４伝動機構の出力軸芯と、前記第２伝動機構の入力軸芯と、前記第２伝動軸を同一軸芯位置に配置し、
エンジン動力を、前記第１伝動機構、前記後輪出力部、前記第１伝動軸を介して前記静油圧式無段変速装置の油圧モータ軸に伝達し、前記静油圧式無段変速装置の油圧モータに伝達された動力を、前記第３伝動機構を介して前記後輪駆動軸に伝達し、前記第３伝動機構に伝達された動力を、前記第２伝動軸を介して前記前輪出力部に伝達する点にあり、その作用効果は次の通りである。 (Constitution)
According to a first aspect of the present invention, there is provided a front mission case that receives engine power, a rear mission case that is disposed behind the front mission case, and a hydrostatic type that is mounted on a front surface of the rear mission case. A step transmission and
In the front transmission case, a first transmission mechanism that transmits engine power to the rear wheel output unit and a second transmission mechanism that receives power returned from the rear transmission case and transmits the power to the front wheel output unit are provided.
In the rear transmission case, a third transmission mechanism that receives power transmitted from the hydraulic motor shaft of the hydrostatic continuously variable transmission and transmits power to the rear wheel drive shaft, and power transmitted to the third transmission mechanism. And a fourth transmission mechanism for returning to the previous mission case,
A first transmission shaft that transmits power from the rear wheel output portion to a hydraulic pump shaft of the hydrostatic continuously variable transmission, and a second transmission shaft that transmits power of the fourth transmission mechanism to the second transmission mechanism. , Built over the front and rear mission case,
The output shaft core of the rear wheel output unit, the input shaft core of the hydraulic pump shaft, and the first transmission shaft are arranged at the same axial center position, the output shaft core of the fourth transmission mechanism, and the second The input shaft core of the transmission mechanism and the second transmission shaft are arranged at the same axial center position,
Engine power is transmitted to the hydraulic motor shaft of the hydrostatic continuously variable transmission via the first transmission mechanism, the rear wheel output unit, and the first transmission shaft, and the hydraulic pressure of the hydrostatic continuously variable transmission. The power transmitted to the motor is transmitted to the rear wheel drive shaft via the third transmission mechanism, and the power transmitted to the third transmission mechanism is transmitted to the front wheel output section via the second transmission shaft. The function and effect are as follows.

（作用）
後輪への駆動力は、エンジンから前ミッションケース内の第１伝動機構を通って前輪出力部に伝達され、その前輪出力部から第１伝動軸を介して静油圧式無段変速装置の油圧ポンプに導入される。油圧ポンプに導入された後輪駆動力は油圧モータで変速され、第３伝動機構を介して、後輪伝動機構及び後輪に伝動される。
一方、後輪伝動機構に伝動される駆動力は、第４伝動機構によって分岐されて第２伝動軸を介して前ミッションケース内の第２伝動機構に導入され、第２伝動機構から前輪出力部に伝達され、前輪出力部より前輪に伝達されて前輪駆動に利用される。 (Function)
The driving force to the rear wheels is transmitted from the engine to the front wheel output section through the first transmission mechanism in the front transmission case, and the hydraulic pressure of the hydrostatic continuously variable transmission is transmitted from the front wheel output section through the first transmission shaft. Introduced into the pump. The rear wheel driving force introduced into the hydraulic pump is shifted by a hydraulic motor and transmitted to the rear wheel transmission mechanism and the rear wheel via the third transmission mechanism.
On the other hand, the driving force transmitted to the rear-wheel transmission mechanism is branched by the fourth transmission mechanism and introduced into the second transmission mechanism in the front transmission case via the second transmission shaft, and the front-wheel output section is supplied from the second transmission mechanism. Is transmitted to the front wheels from the front wheel output section and used for front wheel drive.

上記した構成において、前ミッションケースから静油圧式無段変速装置の油圧ポンプ軸に動力伝達するに、前記後輪出力部の出力軸芯と、前記油圧ポンプ軸の入力軸芯と、前記第１伝動軸とを同一軸芯位置に配置して、前ミッションケースから静油圧式無段変速装置への動力伝達は、同一軸芯上に配置した第２伝動軸等で行いつつ、エンジン動力の前ミッションケースへの入力部と後輪出力部との偏芯状態は、前ミッションケース内に配置された第１伝動機構内の動力伝達経路によって行っている。
後ミッションケースから前輪出力部に動力伝達するに、前記第４伝動機構の出力軸芯と、前記第２伝動機構の入力軸芯と、前記第２伝動軸を同一軸芯位置に配置して、後ミッションケースから前ミッションケースへの動力伝達は、同一軸芯上に配置した第２伝動軸等で行いつつ、第２伝動機構の入力軸芯と前輪出力部との偏芯状態は、前ミッションケース内に配置された第２伝動機構内の動力伝達経路によって行っている。 In the above configuration, in order to transmit power from the front transmission case to the hydraulic pump shaft of the hydrostatic continuously variable transmission, the output shaft core of the rear wheel output unit, the input shaft core of the hydraulic pump shaft, and the first The power transmission shaft is arranged at the same axial center position, and power transmission from the previous transmission case to the hydrostatic continuously variable transmission is performed by the second transmission shaft arranged on the same axial core while The eccentric state of the input part to the transmission case and the rear wheel output part is performed by a power transmission path in the first transmission mechanism arranged in the front mission case.
In order to transmit power from the rear transmission case to the front wheel output unit, the output shaft core of the fourth transmission mechanism, the input shaft core of the second transmission mechanism, and the second transmission shaft are arranged at the same axial center position, Power transmission from the rear transmission case to the front transmission case is performed by the second transmission shaft or the like arranged on the same shaft core, while the eccentric state between the input shaft core and the front wheel output portion of the second transmission mechanism is This is performed by a power transmission path in the second transmission mechanism arranged in the case.

以上のように、前後輪の駆動に寄与すべく、前ミッションケースと後ミッションケースとに亘って掛け渡される第１、第２伝動軸が、前ミッションケースと後ミッションケースに形成された入力部と出力部との同一軸芯位置に配置する構成によって、ユニバーサジョイントを使用しない構成を採ることができ、曲がり角度に一定の制限があるユニバーサルジョイントのような設置上の制約がない。  As described above, in order to contribute to driving of the front and rear wheels, the first and second transmission shafts spanned between the front mission case and the rear mission case are input portions formed in the front mission case and the rear mission case. A configuration in which the universal joint is not used can be adopted by the configuration in which the output portion and the output portion are arranged at the same axial center position, and there is no restriction on installation as in the case of a universal joint in which a bending angle is limited.

（発明の効果）
したがって、ホイールベース間の異なる機種に変更する場合には、第１、第２伝動軸として長さの異なるものに変更するだけでよく、ユニバーサルジョイントを使用した場合のように、ホイールベースが短い機種には適用できないということはない。 (The invention's effect)
Therefore, when changing to a different model between the wheelbases, it is only necessary to change the first and second transmission shafts to ones with different lengths. There is no such thing as not applicable.

（構成）
請求項２に係る本発明の特徴構成は、前記後輪出力部と前記前輪出力部を前記前ミッションケース内の下部に配置し、前記静油圧式無段変速装置の油圧ポンプ軸を油圧モータ軸より下方に配置し、
前記後輪出力部から前記油圧ポンプ軸に動力伝達する第１伝動軸と、前記第４伝動機構の動力を前記第２伝動機構に伝達する第２伝動軸とを、前記第２伝動軸が前記第１伝動軸よりも上方に位置する状態で前記前後ミッションケースに亘って架設してある点にあり、その作用効果は次の通りである。 (Constitution)
According to a second aspect of the present invention, the rear wheel output portion and the front wheel output portion are arranged in a lower portion in the front transmission case, and the hydraulic pump shaft of the hydrostatic continuously variable transmission is a hydraulic motor shaft. Placed below,
A first transmission shaft that transmits power from the rear wheel output portion to the hydraulic pump shaft, a second transmission shaft that transmits power of the fourth transmission mechanism to the second transmission mechanism, and the second transmission shaft The operational effect is as follows in that it is installed over the front and rear transmission cases in a state of being located above the first transmission shaft.

（作用効果）
請求項１に係る発明の作用効果に加えて、次のような作用効果を奏する。
つまり、静油圧式無段変速装置における油圧ポンプを油圧モータより下方に位置させる設置形態を採っている。したがって、前ミッションケースでは、上部から取り入れたエンジン駆動力を、一旦第１伝動機構を介して前ミッションケースの下部に導き、第１伝動軸を前ミッションケースの下部より静油圧式無段変速装置の油圧ポンプ軸に向けて延出して、後ミッションケースに導入している。
そして、前輪を駆動する前輪出力部も前ミッションケースの下部に位置するので、第１伝動軸の上方が空き空間となっている。
そこで、第１伝動軸の上方が空き空間となっている点に着目して、第２伝動軸を配置することとした。これによって、第２伝動軸を配置するために専用のスペースを見出す必要は少ない。 (Function and effect)
In addition to the function and effect of the first aspect of the invention, the following function and effect are achieved.
That is, an installation form is adopted in which the hydraulic pump in the hydrostatic continuously variable transmission is positioned below the hydraulic motor. Therefore, in the previous transmission case, the engine driving force taken from the upper part is once guided to the lower part of the previous transmission case via the first transmission mechanism, and the first transmission shaft is hydrostatically continuously variable from the lower part of the previous transmission case. It extends toward the hydraulic pump shaft and is introduced into the rear transmission case.
And since the front-wheel output part which drives a front wheel is also located in the lower part of a front mission case, the upper part of the 1st transmission shaft becomes empty space.
Therefore, the second transmission shaft is arranged by paying attention to the point that the space above the first transmission shaft is an empty space. Thereby, there is little need to find a dedicated space for arranging the second transmission shaft.

（構成）
請求項３に係る本発明の特徴構成は、請求項１又は２記載に係る発明において、前記第３伝動機構が副変速機構であり、前記第３伝動機構が、上方に位置する前記油圧モータ軸から下方に位置する前記後輪出力軸に動力伝達すべく構成してある点にあり、その作用効果は次の通りである。 (Constitution)
The characteristic configuration of the present invention according to claim 3 is the hydraulic motor shaft according to claim 1 or 2, wherein the third transmission mechanism is a sub-transmission mechanism, and the third transmission mechanism is located above. The power transmission is configured to transmit power to the rear wheel output shaft located below from the vehicle. The operation and effect thereof are as follows.

（作用効果）
請求項１又は２に係る発明の作用効果に加えて、次のような作用効果を奏する。
第３伝動機構が副変速機構に兼用されており、この副変速機構を利用して第４伝動機構が構成されているので、機器構成の簡素化が達成できる。また、第３伝動機構での動力伝達の流れが上下方向となっているので、第４伝動機構への動力分岐点を上下方向での何れの高さの位置にも設定でき、前ミッションケースへ動力伝達する上下方向での位置が限定されないものとなる。 (Function and effect)
In addition to the operational effects of the invention according to claim 1 or 2, the following operational effects are provided.
Since the third transmission mechanism is also used as the auxiliary transmission mechanism, and the fourth transmission mechanism is configured by using the auxiliary transmission mechanism, simplification of the device configuration can be achieved. Moreover, since the power transmission flow in the third transmission mechanism is in the vertical direction, the power branch point to the fourth transmission mechanism can be set at any height position in the vertical direction, and the previous transmission case The position in the vertical direction for transmitting power is not limited.

農用トラクタの伝動構造について説明する。図１に示すように、農用トラクタＡは、機体前部にエンジン１、主クラッチケース２、前ミッションケース３を装備し、主クラッチケース２と前ミッションケース３との上面に跨ってパワーステアリング装置用の取付座４を装備し、前ミッションケース３の後方に、静油圧式無段変速装置５、後ミッションケース６を装備して、構成されている。
前ミッションケース３と後ミッションケース６とに亘って運転ステップ兼用のカバーフレーム７が設けてある。パワーステアリング装置用の取付座４を設けて、静油圧式無段変速装置５を使用しないギヤ式変速機構を採用する機種にも兼用できるように構成する。 The transmission structure of the agricultural tractor will be described. As shown in FIG. 1, the agricultural tractor A is equipped with an engine 1, a main clutch case 2, and a front mission case 3 at the front of the machine body, and a power steering device straddling the upper surfaces of the main clutch case 2 and the front mission case 3. For example, and a hydrostatic continuously variable transmission 5 and a rear mission case 6 are provided behind the front mission case 3.
A cover frame 7 serving as an operation step is provided across the front mission case 3 and the rear mission case 6. A mounting seat 4 for the power steering device is provided so that it can also be used for a model that employs a gear-type transmission mechanism that does not use the hydrostatic continuously variable transmission 5.

前ミッションケース内の伝動構造について説明する。図２から図４に示すように、主クラッチケース２より前ミッションケース３の内部にエンジン動力を導入する入力軸８が回転自在に架設してある。入力軸８の下方に中継軸９が架設され、さらに下方に静油圧式無段変速装置５に向かう後輪出力部としての出力軸１０がその後端部１０Ａを前ミッションケース３より突出する状態で設けてある。この出力軸１０の軸芯を、後輪出力部の出力軸芯という。   The transmission structure in the previous mission case will be described. As shown in FIGS. 2 to 4, an input shaft 8 for introducing engine power is rotatably installed in the transmission case 3 in front of the main clutch case 2. A relay shaft 9 is installed below the input shaft 8, and further, an output shaft 10 as a rear wheel output portion heading toward the hydrostatic continuously variable transmission 5 is projected from the front transmission case 3 at the rear end portion 10 </ b> A. It is provided. The shaft center of the output shaft 10 is referred to as the output shaft core of the rear wheel output unit.

入力軸８に第１伝動ギヤ１１を一体回転状態に取付け、中継軸９に第２伝動ギヤ１２をその中継軸９と一体形成し、出力軸１０に第３伝動ギヤ１３を一体回転状態に取付け、これら第１伝動ギヤ１１、第２伝動ギヤ１２、第３伝動ギヤ１３を順番に咬合させて、出力軸１０からエンジン動力を静油圧式無段変速装置５に伝動する、第１伝動機構Ｂを構成している。   The first transmission gear 11 is attached to the input shaft 8 in an integrally rotated state, the second transmission gear 12 is formed integrally with the relay shaft 9 on the relay shaft 9, and the third transmission gear 13 is attached to the output shaft 10 in an integrally rotated state. The first transmission mechanism B, in which the first transmission gear 11, the second transmission gear 12, and the third transmission gear 13 are sequentially engaged to transmit the engine power from the output shaft 10 to the hydrostatic continuously variable transmission 5. Is configured.

図２、図３及び図５に示すように、後ミッションケース６の前面に静油圧式無段変速装置５が装着してあり、静油圧式無段変速装置５の油圧ケース５Ｃの下部には、可変容量型の油圧ポンプ５Ａと、上部には容量固定型の油圧モータ５Ｂとが配置して構成されている。油圧ポンプ５Ａから前ミッションケース３に向けてポンプ軸５ａを延出し、ポンプ軸５ａの前端部と出力軸１０の後端部とをカップリング１４で連結して、第１伝動機構Ｂから静油圧式無段変速装置５の油圧ポンプ５Ａに動力伝達可能に構成してある。
ここに、出力軸１０の前ミッションケース３から突出する後端部１０Ａとカップリング１４とで、後輪出力部から静油圧式無段変速装置５のポンプ軸５ａに動力伝達する第１伝動軸を構成する。 As shown in FIGS. 2, 3, and 5, a hydrostatic continuously variable transmission 5 is mounted on the front surface of the rear transmission case 6, and below the hydraulic case 5 </ b> C of the hydrostatic continuously variable transmission 5. A variable displacement hydraulic pump 5A and a fixed displacement hydraulic motor 5B are arranged at the top. The pump shaft 5a is extended from the hydraulic pump 5A toward the front transmission case 3, the front end portion of the pump shaft 5a and the rear end portion of the output shaft 10 are connected by a coupling 14, and the hydrostatic pressure is supplied from the first transmission mechanism B. The power transmission to the hydraulic pump 5A of the continuously variable transmission 5 is configured.
Here, the first transmission shaft for transmitting power from the rear wheel output portion to the pump shaft 5a of the hydrostatic continuously variable transmission 5 by the rear end portion 10A protruding from the front transmission case 3 of the output shaft 10 and the coupling 14. Configure.

つぎに、後ミッションケース６内の伝動構造について説明する。油圧ケース５Ｃの後端には静油圧式無段変速装置用の油圧ブロック５Ｄが取り付けてあり、油圧ケース５Ｃより油圧ブロック５Ｄを貫通して後ミッションケース６内に臨む油圧モータ出力軸５ｂが延出してある。
後ミッションケース６内には油圧モータ出力軸５ｂの軸芯延長線上に走行入力軸１６が架設されており、油圧モータ出力軸５ｂの突出端部と走行入力軸１６の前端部とがカップリング１５によって連動連結されている。 Next, the transmission structure in the rear mission case 6 will be described. A hydraulic block 5D for a hydrostatic continuously variable transmission is attached to the rear end of the hydraulic case 5C, and a hydraulic motor output shaft 5b extending through the hydraulic block 5D and facing the rear transmission case 6 extends from the hydraulic case 5C. It is out.
In the rear mission case 6, a travel input shaft 16 is installed on the axial extension of the hydraulic motor output shaft 5b, and the protruding end portion of the hydraulic motor output shaft 5b and the front end portion of the travel input shaft 16 are coupled 15 together. Are linked to each other.

図２に示すように、走行入力軸１６の後端部に平行に後輪駆動軸１７が設けてあり、後輪駆動軸１７の後端に後輪デフ機構が設けてある。走行入力軸１６には大小二段ギヤ１６Ａが一体形成してあり、この大小二段ギヤ１６Ａに咬合可能なクラッチギヤ１７Ａが後輪駆動軸１７にスプライン嵌合してある。
以上のような構成によって、高低二段に変速可能な第３伝動機構としての副変速機構Ｃを構成する。尚、この第３伝動機構、後輪デフ機構においては、静油圧式無段変速装置５を使用せず通常のギヤ式主変速機構を使用する機種にも兼用することができる。ただし、ギヤ歯数等の細かい修正は必要である。 As shown in FIG. 2, a rear wheel drive shaft 17 is provided in parallel with the rear end portion of the travel input shaft 16, and a rear wheel differential mechanism is provided at the rear end of the rear wheel drive shaft 17. A large and small two-stage gear 16A is integrally formed with the travel input shaft 16, and a clutch gear 17A that can be engaged with the large and small two-stage gear 16A is spline-fitted to the rear wheel drive shaft 17.
With the above-described configuration, the sub-transmission mechanism C as the third transmission mechanism that can change gears in two levels is configured. In the third transmission mechanism and the rear wheel differential mechanism, the hydrostatic continuously variable transmission device 5 is not used, but can also be used as a model that uses a normal gear-type main transmission mechanism. However, fine corrections such as the number of gear teeth are necessary.

図２及び図３に示すように、後輪駆動軸１７の軸芯を延長した前方側に中継軸１８が延出されるとともに、中継軸１８の横側方に前輪への前輪用伝動軸２１が架設され、中継軸１８の下方にＰＴＯ出力軸２０が架設されている。
一方、静油圧式無段変速装置５のポンプ軸５ａを、油圧ブロック５Ｄを貫通させて後ミッションケース６内に延出するとともに、中継軸１８の前端を油圧ブロック５Ｄに支承し、ポンプ軸５ａの延出端に取り付けた出力ギヤ５ｃと中継軸１８の前端に取り付けた入力ギヤ１８ｃとを常咬式に咬合させて、ポンプ軸５ａから中継軸１８への動力伝達を可能に構成してある。 As shown in FIGS. 2 and 3, the relay shaft 18 is extended to the front side where the shaft center of the rear wheel drive shaft 17 is extended, and the front wheel transmission shaft 21 to the front wheel is laterally lateral to the relay shaft 18. A PTO output shaft 20 is installed under the relay shaft 18.
On the other hand, the pump shaft 5a of the hydrostatic continuously variable transmission 5 extends through the hydraulic block 5D into the rear transmission case 6, and the front end of the relay shaft 18 is supported by the hydraulic block 5D. The output gear 5c attached to the extending end of the shaft and the input gear 18c attached to the front end of the relay shaft 18 are engaged with each other in a normal manner so that power can be transmitted from the pump shaft 5a to the relay shaft 18. .

次に、ＰＴＯ変速機構Ｄについて説明する。図２に示すように、中継軸１８に大小二段ギヤ１８Ａを一体形成し、ＰＴＯ出力軸２０に大小二段のクラッチギヤ２０Ａをスプライン外嵌し、クラッチギヤ２０Ａより前端側に入力ギヤ２０Ｂを遊転支承してある。
一方、中継軸１８の横側方に後記する前輪用伝動軸２１が架設され、この前輪用伝動軸２１に逆転ギヤ２１Ａが遊転支承されている。
逆転ギヤ２１Ａは大小二段ギヤであり、大小二段ギヤのうちの小径ギヤ部２１ａを、中継軸１８に取り付けてある大小二段ギヤ１８Ａの小径ギヤ部１８ａに咬合させるとともに、大径ギヤ部２１ｂをＰＴＯ出力軸２０に装着した入力ギヤ２０Ｂに咬合させている。
ここで、入力ギヤ２０Ｂはクラッチギヤ２０Ａの存在側にスプライン嵌合部を設けてあり、クラッチギヤ２０Ａを入力ギヤ２０Ｂのスプライン嵌合部に嵌合させることによって、逆転ギヤ２１Ａを介した逆転動力をＰＴＯ出力軸２０に導入することが可能である。 Next, the PTO transmission mechanism D will be described. As shown in FIG. 2, a large and small two-stage gear 18A is integrally formed on the relay shaft 18, a large and small two-stage clutch gear 20A is externally fitted to the PTO output shaft 20, and an input gear 20B is connected to the front end side of the clutch gear 20A. There is an idle support.
On the other hand, a front wheel transmission shaft 21 (described later) is installed on the lateral side of the relay shaft 18, and a reverse gear 21 </ b> A is idled on the front wheel transmission shaft 21.
The reverse gear 21A is a large and small two-stage gear. The small-diameter gear portion 21a of the large and small two-stage gear is engaged with the small-diameter gear portion 18a of the large and small two-stage gear 18A attached to the relay shaft 18, and the large-diameter gear portion. 21b is engaged with an input gear 20B mounted on the PTO output shaft 20.
Here, the input gear 20B is provided with a spline fitting portion on the side where the clutch gear 20A is present, and the reverse rotation power via the reverse gear 21A is obtained by fitting the clutch gear 20A to the spline fitting portion of the input gear 20B. Can be introduced into the PTO output shaft 20.

なお、油圧ブロック５Ｄの後方側にＰＴＯ用の支持ケース１９が設けてあり、この支持ケース１９に、前記した中継軸１８の前端、及び、ＰＴＯ出力軸２０の前端がベアリングを介して支持されている。   A support case 19 for PTO is provided on the rear side of the hydraulic block 5D, and the front end of the relay shaft 18 and the front end of the PTO output shaft 20 are supported on the support case 19 via bearings. Yes.

以上の構成より、ＰＴＯ変速構造を纏めると、次のようになる。
（イ） クラッチギヤ２０Ａの小径部２０ａを中継軸１８の大小二段ギヤ１８Ａにおける大径ギヤ部１８ｂに咬合させると、高速駆動状態を現出できる。
（ロ） クラッチギヤ２０Ａの大径部２０ａを中継軸１８の大小二段ギヤ１８Ａにおける小径ギヤ部１８ａに咬合させると、低速駆動状態を現出できる。
（ハ） クラッチギヤ２０Ａを入力ギヤ２０Ｂに咬合させると、逆転駆動状態を現出できる。この場合の逆転動力は、中継軸１８より逆転ギヤ２１Ａを中継して、クラッチギヤ２０Ａを通してＰＴＯ出力軸２０に伝達される。
以上のような構成によって、ＰＴＯ変速構造は、静油圧式無段変速装置５を使用せず通常のギヤ式主変速機構を使用する機種にも兼用することができる。 From the above configuration, the PTO transmission structure can be summarized as follows.
(A) When the small-diameter portion 20a of the clutch gear 20A is engaged with the large-diameter gear portion 18b of the large and small two-stage gear 18A of the relay shaft 18, a high-speed drive state can be revealed.
(B) When the large-diameter portion 20a of the clutch gear 20A is engaged with the small-diameter gear portion 18a of the large and small two-stage gear 18A of the relay shaft 18, a low-speed drive state can appear.
(C) When the clutch gear 20A is engaged with the input gear 20B, a reverse drive state can be obtained. The reverse rotation power in this case is transmitted from the relay shaft 18 to the PTO output shaft 20 through the clutch gear 20A via the reverse gear 21A.
With the above-described configuration, the PTO transmission structure can also be used for a model that uses a normal gear-type main transmission mechanism without using the hydrostatic continuously variable transmission 5.

第２伝動機構としての前輪伝動機構Ｅについて説明する。
図２に示すように、中継軸１８の横側方に前輪用伝動軸２１を架設して、その前輪用伝動軸２１に逆転ギヤ２１Ａを遊嵌する。前輪用伝動軸２１の後端部を後輪駆動軸１７と平行に僅かに延出し、延出端に受動ギヤ２１Ｂを嵌着してある。一方、後輪駆動軸１７の前端部に駆動ギヤ１７Ｂが装着固定してあり、後輪駆動軸１７より前輪用伝動軸２１に動力伝達可能に構成してある。この駆動ギヤ１７Ｂと受動ギヤ２１Ｂとで、第３伝動機構Ｃに伝達された動力を前ミッションケース３へ戻す第４伝動機構Ｆを構成する。ここに、前輪用伝動軸２１の軸芯を、第４伝動機構Ｆの出力軸芯と称する。
第４伝動機構Ｆは、静油圧式無段変速装置５を使用しないギヤ式変速機構を採用する機種にも兼用可能である。 The front wheel transmission mechanism E as the second transmission mechanism will be described.
As shown in FIG. 2, a front wheel transmission shaft 21 is installed on the lateral side of the relay shaft 18, and the reverse gear 21 </ b> A is loosely fitted to the front wheel transmission shaft 21. A rear end portion of the front wheel transmission shaft 21 is slightly extended in parallel with the rear wheel drive shaft 17, and a passive gear 21B is fitted to the extension end. On the other hand, a drive gear 17B is attached and fixed to the front end portion of the rear wheel drive shaft 17 so that power can be transmitted from the rear wheel drive shaft 17 to the front wheel transmission shaft 21. The drive gear 17B and the passive gear 21B constitute a fourth transmission mechanism F that returns the power transmitted to the third transmission mechanism C to the front transmission case 3. Here, the axis of the front wheel transmission shaft 21 is referred to as the output shaft core of the fourth transmission mechanism F.
The fourth transmission mechanism F can also be used in a model that employs a gear-type transmission mechanism that does not use the hydrostatic continuously variable transmission 5.

前輪用伝動軸２１は、油圧ブロック５Ｄ、油圧ケース５Ｃを貫通して前ミッションケース３に向けて延出されている。一方、前ミッションケース３には、前輪用伝動軸２１の軸芯の前方に向けて延出した延長線上に前輪用中間軸２２が架設されるとともに、前輪用中間軸２２の下方で前記した出力軸１０より更に下方に前輪出力部としての前輪出力軸２３が設けてある。
前輪用中間軸２２に出力ギヤ２２Ａが一体形成してあり、前記した静油圧式無段変速装置５へ動力伝達する出力軸１０に中継ギヤ１０Ｂを遊嵌し、更に、下方の前輪出力軸２３に前輪ギヤ２３Ａが一体形成してある。ここに、前輪用中間軸２２の軸芯を第２伝動機構の入力軸芯と称する。
ここに前輪用中間軸２２、出力ギヤ２２Ａ、中継ギヤ１０Ｂ、前輪出力軸２３、前輪ギヤ２３Ａを第２伝動機構としての前輪伝動機構Ｅと称する。 The front wheel transmission shaft 21 extends toward the front transmission case 3 through the hydraulic block 5D and the hydraulic case 5C. On the other hand, the front transmission case 3 is provided with a front wheel intermediate shaft 22 on an extended line extending toward the front of the shaft center of the front wheel transmission shaft 21 and the output described above below the front wheel intermediate shaft 22. A front wheel output shaft 23 as a front wheel output portion is provided further below the shaft 10.
An output gear 22A is integrally formed with the front wheel intermediate shaft 22, and the relay gear 10B is loosely fitted to the output shaft 10 for transmitting power to the hydrostatic continuously variable transmission 5 described above. The front wheel gear 23A is integrally formed. Here, the shaft center of the intermediate shaft 22 for front wheels is referred to as the input shaft core of the second transmission mechanism.
Here, the front wheel intermediate shaft 22, the output gear 22A, the relay gear 10B, the front wheel output shaft 23, and the front wheel gear 23A are referred to as a front wheel transmission mechanism E as a second transmission mechanism.

このような構成によって、出力ギヤ２２Ａから中継ギヤ１０Ｂを介して前輪ギヤ２３Ａに前輪駆動力が伝達される。
一方、前輪用伝動軸２１の前端部と前輪用中間軸２２の後端部とを、繋ぎ軸２４と二つのカップリング２５を介して連動連結している。この伝動軸の構成を、前記第４伝動機構から前記第２伝動機構に動力伝達する第２伝動軸と称する。 With such a configuration, the front wheel driving force is transmitted from the output gear 22A to the front wheel gear 23A via the relay gear 10B.
On the other hand, the front end portion of the front wheel transmission shaft 21 and the rear end portion of the front wheel intermediate shaft 22 are linked and connected via a connecting shaft 24 and two couplings 25. This configuration of the transmission shaft is referred to as a second transmission shaft that transmits power from the fourth transmission mechanism to the second transmission mechanism.

以上のように、後輪出力部の出力軸芯としての出力軸１０の軸芯と、静油圧式無段変速装置５の油圧ポンプ軸５ａの軸芯とが同一軸芯上にあり、出力軸１０と油圧ポンプ軸５ａとを連結する第１伝動軸も同一軸芯上にある。このような構成によって、第１伝動軸としてはユニバーサルジョイントを必要としない構成が可能である。
また、第４伝動機構Ｆの出力軸芯としての前輪用伝動軸２１の軸芯と、第２伝動機構Ｅとしての入力軸芯としての前輪用中間軸２２の軸芯とが同一軸芯上にあり、前輪用伝動軸２１と前輪用中間軸２２とを連結する第２伝動軸も同一軸芯上にある。このような構成によって、第２伝動軸としてはユニバーサルジョイントを必要としない構成が可能である。
第１及び第２伝動軸や、成形が容易な板金製のカバーフレーム７等を、長さの異なるものに変更することによって、主クラッチケース２、前ミッションケース３、静油圧式無段変速装置５及び後ミッションケース６等を余り変更せずに、ホイールベースの異なる機種に対応（生産）することができる。 As described above, the shaft core of the output shaft 10 as the output shaft core of the rear wheel output portion and the shaft core of the hydraulic pump shaft 5a of the hydrostatic continuously variable transmission 5 are on the same shaft core, and the output shaft The first transmission shaft that connects 10 and the hydraulic pump shaft 5a is also on the same axis. With such a configuration, a configuration that does not require a universal joint as the first transmission shaft is possible.
Further, the axis of the front wheel transmission shaft 21 as the output shaft core of the fourth transmission mechanism F and the axis of the front wheel intermediate shaft 22 as the input shaft core as the second transmission mechanism E are on the same axis. There is also a second transmission shaft that connects the front wheel transmission shaft 21 and the front wheel intermediate shaft 22 on the same axis. With such a configuration, a configuration that does not require a universal joint as the second transmission shaft is possible.
The main clutch case 2, the front transmission case 3, and the hydrostatic continuously variable transmission can be obtained by changing the first and second transmission shafts, the cover frame 7 made of sheet metal, which is easy to form, and the like to those having different lengths. 5 and the rear mission case 6 and the like can be made (produced) with different wheelbase models without much change.

前輪への伝動構造について説明する。図１及び図２に示すように、前輪出力軸２３の前方側に前車軸ケース２６を設け、前車軸ケース２６を前後に配置されたブラケット２７を介してエンジン支持フレーム２９にローリング自在に支持する。前後に配置されたブラケット２７のうちの後方側ブラケット２７に前輪増速装置２８を取り付け、この前輪増速装置２８に前輪出力軸２３を連係している。
尚、前車軸ケース２６と前輪増速装置２８は、静油圧式無段変速装置５を使用しないギヤ式変速機構を採用する機種にも兼用できるように構成する。 The transmission structure for the front wheels will be described. As shown in FIGS. 1 and 2, a front axle case 26 is provided on the front side of the front wheel output shaft 23, and the front axle case 26 is supported by an engine support frame 29 via a bracket 27 arranged at the front and rear sides so as to be able to roll. . A front wheel speed increasing device 28 is attached to the rear side bracket 27 of the brackets 27 arranged at the front and rear, and the front wheel speed increasing device 28 is linked to the front wheel output shaft 23.
It should be noted that the front axle case 26 and the front wheel speed increasing device 28 are configured so that they can also be used in a model that employs a gear type speed change mechanism that does not use the hydrostatic continuously variable transmission 5.

〔別実施形態〕
（１） 第１伝動機構Ｂから第４伝動機構Ｆまでの構成においては、使用するギヤや伝動軸の数は適宜選択すればよく、かつ、ギヤ伝動機構以外のチェーンやベルトの伝動構造も採用できる。
（２） 第１伝動軸、及び、第２伝動軸は、カップリングを介して複数の軸で構成したが、軸単体で構成してもよい。
（３） 上記した伝動構造は、農用トラクタ以外に田植機等の他の作業車に適用してもよい。 [Another embodiment]
(1) In the configuration from the first transmission mechanism B to the fourth transmission mechanism F, the number of gears and transmission shafts to be used may be appropriately selected, and a chain or belt transmission structure other than the gear transmission mechanism is also employed. it can.
(2) The first transmission shaft and the second transmission shaft are configured by a plurality of shafts via a coupling, but may be configured by a single shaft.
(3) The transmission structure described above may be applied to other work vehicles such as rice transplanters in addition to agricultural tractors.

全体側面図Overall side view 伝動構造を示す概略構成図Schematic configuration diagram showing transmission structure 前後ミッションケースの内部構造を示す縦断側面図Longitudinal side view showing the internal structure of the front and rear mission case 図３におけるＩＶ−ＩＶ線断面図IV-IV line sectional view in FIG. 図３におけるＶ−Ｖ線断面図VV line sectional view in FIG.

符号の説明Explanation of symbols

３ 前ミッションケース
５ 静油圧式無段変速装置
５Ａ 油圧ポンプ
５Ｂ 油圧モータ
６ 後ミッションケース
１０ 後輪出力部（出力軸）
１７ 後輪駆動軸
２３ 前輪出力部（前輪用伝動軸）
Ｂ 第１伝動機構
Ｃ 副変速機構（第３伝動機構）
Ｅ 前輪伝動機構（第２伝動機構）
Ｆ 第４伝動機構 3 Front mission case 5 Hydrostatic continuously variable transmission 5A Hydraulic pump 5B Hydraulic motor 6 Rear mission case 10 Rear wheel output section (output shaft)
17 Rear wheel drive shaft 23 Front wheel output section (front wheel transmission shaft)
B 1st transmission mechanism C Sub transmission mechanism (3rd transmission mechanism)
E Front wheel transmission mechanism (second transmission mechanism)
F 4th transmission mechanism

Claims (3)

エンジン動力を受ける前ミッションケースと、前記前ミッションケースの後方に配置される後ミッションケースと、前記後ミッションケースの前面に装着される静油圧式無段変速装置とを設け、
前記前ミッションケース内に、エンジン動力を後輪出力部に伝達する第１伝動機構と、前記後ミッションケースから戻される動力を受けて前輪出力部へ伝達する第２伝動機構とを設け、
前記後ミッションケース内に、前記静油圧式無段変速装置の油圧モータ軸からの動力伝達を受けて後輪駆動軸に動力伝達する第３伝動機構と、前記第３伝動機構に伝達された動力を前記前ミッションケースへ戻す第４伝動機構とを設け、
前記後輪出力部から前記静油圧式無段変速装置の油圧ポンプ軸に動力伝達する第1伝動軸と、前記第４伝動機構の動力を前記第２伝動機構に伝達する第２伝動軸とを、前記前後ミッションケースに亘って架設し、
前記後輪出力部の出力軸芯と、前記油圧ポンプ軸の入力軸芯と、前記第１伝動軸とを同一軸芯位置に配置し、前記第４伝動機構の出力軸芯と、前記第２伝動機構の入力軸芯と、前記第２伝動軸を同一軸芯位置に配置し、
エンジン動力を、前記第１伝動機構、前記後輪出力部、前記第１伝動軸を介して前記静油圧式無段変速装置の油圧モータ軸に伝達し、前記静油圧式無段変速装置の油圧モータに伝達された動力を、前記第３伝動機構を介して前記後輪駆動軸に伝達し、前記第３伝動機構に伝達された動力を、前記第２伝動軸を介して前記前輪出力部に伝達する乗用型作業車。 A front mission case for receiving engine power, a rear mission case disposed behind the front mission case, and a hydrostatic continuously variable transmission mounted on the front surface of the rear mission case;
In the front transmission case, a first transmission mechanism that transmits engine power to the rear wheel output unit and a second transmission mechanism that receives power returned from the rear transmission case and transmits the power to the front wheel output unit are provided.
In the rear transmission case, a third transmission mechanism that receives power transmitted from the hydraulic motor shaft of the hydrostatic continuously variable transmission and transmits power to the rear wheel drive shaft, and power transmitted to the third transmission mechanism. And a fourth transmission mechanism for returning to the previous mission case,
A first transmission shaft that transmits power from the rear wheel output portion to a hydraulic pump shaft of the hydrostatic continuously variable transmission, and a second transmission shaft that transmits power of the fourth transmission mechanism to the second transmission mechanism. , Built over the front and rear mission case,
The output shaft core of the rear wheel output unit, the input shaft core of the hydraulic pump shaft, and the first transmission shaft are arranged at the same axial center position, the output shaft core of the fourth transmission mechanism, and the second The input shaft core of the transmission mechanism and the second transmission shaft are arranged at the same axial center position,
Engine power is transmitted to the hydraulic motor shaft of the hydrostatic continuously variable transmission via the first transmission mechanism, the rear wheel output unit, and the first transmission shaft, and the hydraulic pressure of the hydrostatic continuously variable transmission. The power transmitted to the motor is transmitted to the rear wheel drive shaft via the third transmission mechanism, and the power transmitted to the third transmission mechanism is transmitted to the front wheel output section via the second transmission shaft. A passenger work vehicle that communicates. 前記後輪出力部を前記前ミッションケース内の下部に配置し、前記静油圧式無段変速装置の油圧ポンプ軸を油圧モータ軸より下方に配置し、
前記後輪出力部から前記油圧ポンプ軸に動力伝達する第１伝動軸と、前記第４伝動機構の動力を前記第２伝動機構に伝達する第２伝動軸とを、前記第２伝動軸が前記第１伝動軸よりも上方に位置する状態で前記前後ミッションケースに亘って架設してある請求項１記載の乗用型作業車。 The rear wheel output portion is disposed in a lower portion of the front mission case, the hydraulic pump shaft of the hydrostatic continuously variable transmission is disposed below the hydraulic motor shaft,
A first transmission shaft that transmits power from the rear wheel output portion to the hydraulic pump shaft, a second transmission shaft that transmits power of the fourth transmission mechanism to the second transmission mechanism, and the second transmission shaft The riding type work vehicle according to claim 1, wherein the work vehicle is installed over the front and rear transmission cases in a state of being positioned above the first transmission shaft. 前記第３伝動機構が副変速機構であり、前記第３伝動機構が、上方に位置する前記油圧モータ軸から下方に位置する前記後輪出力軸に動力伝達すべく構成してある請求項１又は２記載の乗用型作業車。   The third transmission mechanism is a subtransmission mechanism, and the third transmission mechanism is configured to transmit power from the hydraulic motor shaft positioned above to the rear wheel output shaft positioned below. 2. The passenger work vehicle according to 2.
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