JPH0968245A - Operating machine - Google Patents
Operating machineInfo
- Publication number
- JPH0968245A JPH0968245A JP22387795A JP22387795A JPH0968245A JP H0968245 A JPH0968245 A JP H0968245A JP 22387795 A JP22387795 A JP 22387795A JP 22387795 A JP22387795 A JP 22387795A JP H0968245 A JPH0968245 A JP H0968245A
- Authority
- JP
- Japan
- Prior art keywords
- braking
- clutch
- shaft
- clutch mechanism
- friction plate
- 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.)
- Pending
Links
Landscapes
- Braking Arrangements (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、作業装置に動力を
伝える出力軸系にクラッチ機構を介装すると共に、この
クラッチ機構の切り操作時に出力軸の遊転を阻止する制
動機構を備えた作業機に関し、詳しくは、制動機構の改
良に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a work provided with a clutch mechanism in an output shaft system for transmitting power to a work device and a braking mechanism for preventing idling of the output shaft when the clutch mechanism is disengaged. The present invention relates to a machine, more specifically, to improvement of a braking mechanism.
【０００２】[0002]
【従来の技術】従来、上記のように構成された作業機と
して特開平６‐１３７３４９号公報に示されるものが存
在し、この従来例では、クラッチ機構から出力軸に動力
を伝えるギヤ系をはすば歯車に構成し、クラッチ機構の
切り操作時に出力軸の慣性力に起因する力ではすば歯車
をスラスト方向に変位させ、該歯車の側面とブレーキシ
ューとの接触で出力軸の回転を阻止するよう構成されて
いる。2. Description of the Related Art Conventionally, there is a work machine constructed as described above as disclosed in Japanese Patent Laid-Open No. 6-137349. In this conventional example, a gear system for transmitting power from a clutch mechanism to an output shaft is provided. Configured as a helical gear, the force due to the inertial force of the output shaft displaces the helical gear in the thrust direction when the clutch mechanism is disengaged, and the rotation of the output shaft is blocked by the contact between the side of the gear and the brake shoe. Is configured to.
【０００３】[0003]
【発明が解決しようとする課題】しかし、従来例のよう
に、歯車のスラスト方向への変位で制動力を作用させる
ものでは、クラッチ機構の切り操作と連動して出力軸に
制動力を作用させ、短時間のうちに出力軸の回転を阻止
するという良好な面を有する反面、制動力を作用させる
面積をあまり大きくできず、例えば、ブレードを有した
モーアへの伝動系に該クラッチ機構系を介装した場合に
は、クラッチ機構の切り操作時にはブレードの回転に起
因して大きい慣性力が発生すると共に、この慣性力に比
例した過大な圧力が制動面に作用してブレーキシューの
傷みを促進しブレーキシューの寿命を短縮することもあ
った。However, in the case where the braking force is applied by the displacement of the gear in the thrust direction as in the conventional example, the braking force is applied to the output shaft in conjunction with the disengagement operation of the clutch mechanism. Although it has a good surface that prevents the rotation of the output shaft in a short time, the area for applying the braking force cannot be increased so much, for example, that the clutch mechanism system is added to the transmission system to the mower having a blade. When installed, a large inertial force is generated due to the rotation of the blade when the clutch mechanism is disengaged, and excessive pressure proportional to this inertial force acts on the braking surface to promote damage to the brake shoes. However, it sometimes shortened the life of the brake shoes.
【０００４】又、このようにクラッチ機構の切り作動と
連係して出力軸に制動力を作用させる制動機構を有する
ものでは、作動する部材が多く、この制動機構を簡便な
操作で容易に組立得ることが望まれる。In addition, in the device having the braking mechanism for applying the braking force to the output shaft in cooperation with the disengagement operation of the clutch mechanism, there are many members to be operated, and the braking mechanism can be easily assembled by a simple operation. Is desired.
【０００５】本発明の目的は、出力軸から動力を伝える
作業装置が高い慣性のものであっても制動系を傷めるこ
と少なくクラッチ機構の切り操作と連動して確実な制動
力を出力軸に作用させる作業機を合理的に構成する点に
ある。An object of the present invention is to apply a reliable braking force to the output shaft in cooperation with the disengagement operation of the clutch mechanism without damaging the braking system even if the working device for transmitting power from the output shaft has a high inertia. The point is to reasonably configure the working machine.
【０００６】[0006]
【課題を解決するための手段】本発明の第１の特徴は冒
頭に記したように、作業装置に動力を伝える出力軸系に
クラッチ機構を介装すると共に、このクラッチ機構の切
り操作時に出力軸の遊転を阻止する制動機構を備えた作
業機において、前記クラッチ機構を、圧油が給排される
油圧ピストンと、油圧ピストンへの圧油の供給時に該油
圧ピストンで圧接操作される伝動用の摩擦部材と、油圧
ピストンからの排油時に摩擦部材を離間操作するバネと
をクラッチケースに内装して構成し、前記制動機構を、
クラッチケースの回転軸芯と平行する姿勢で静止系に備
えた軸体に係合支持された摩擦板と、この摩擦板を挟み
込む位置に配置され、かつ、前記出力軸と連係する制動
部材とを備えると共に、前記クラッチ機構の切り操作時
には該クラッチ機構のバネの付勢力でクラッチケースの
外方に突出作動して摩擦板、制動部材夫々を押圧する押
圧部材とで構成してある点にあり、その作用は次の通り
である。As described at the beginning, the first feature of the present invention is that an output shaft system for transmitting power to a working device is provided with a clutch mechanism, and the clutch mechanism outputs an output when the clutch mechanism is disengaged. In a working machine provided with a braking mechanism for preventing idle rotation of a shaft, the clutch mechanism is a hydraulic piston to which pressure oil is supplied and discharged, and a transmission which is pressure-contacted by the hydraulic piston when the pressure oil is supplied to the hydraulic piston. Friction member and a spring for operating the friction member to separate from each other when oil is discharged from the hydraulic piston, the clutch case being internally configured, and the braking mechanism,
A friction plate engaged with and supported by a shaft body provided in a stationary system in a posture parallel to the rotation axis of the clutch case, and a braking member arranged at a position sandwiching the friction plate and linked with the output shaft. In addition to the above, when the clutch mechanism is disengaged, it is constituted by a pressing member that presses the friction plate and the braking member by projecting to the outside of the clutch case by the urging force of the spring of the clutch mechanism, The operation is as follows.
【０００７】又、本発明の第２の特徴は、前記クラッチ
機構をミッションケースの伝動軸に外嵌支持すると共
に、この伝動軸に対して前記制動機構の摩擦板と制動部
材とを備え、この伝動軸と一体的にクラッチ機構と制動
機構の一部とをミッションケースに対して着脱自在に構
成してある点にあり、その作用は次の通りである。A second feature of the present invention is that the clutch mechanism is externally fitted and supported on a transmission shaft of a transmission case, and a friction plate and a braking member of the braking mechanism are provided on the transmission shaft. The clutch mechanism and a part of the braking mechanism are configured to be detachable from the transmission case integrally with the transmission shaft, and the operation thereof is as follows.
【０００８】〔作用〕上記第１の特徴によると、クラッ
チ機構の切り操作時にはバネの付勢力で押圧部材が突出
作動して摩擦板と制動部材とを圧接操作することにな
り、この圧接によって摩擦板と制動部材との相対回転が
阻止され、出力軸に制動力を作用させるものとなる。つ
まり、本発明では制動機構の制動力を得るためにクラッ
チ機構に備えたバネを用いることで、クラッチ機構の切
り操作と連動した迅速な制動を可能にすると共に、クラ
ッチケースあるいはクラッチ機構に連係するギヤ等の径
に制約を受けない大きい制動面を摩擦板、制動部材を形
成して制動系の耐久性の向上を可能にし、又、クラッチ
ケースの軸芯から離間した位置に軸体を配置して摩擦板
の回転を確実に阻止して強力な制動力を得ることも可能
になる。[Operation] According to the first feature described above, when the clutch mechanism is disengaged, the pressing member projects due to the urging force of the spring to press-contact the friction plate and the braking member, and this press-contact causes friction. The relative rotation between the plate and the braking member is blocked, and the braking force acts on the output shaft. That is, in the present invention, the spring provided in the clutch mechanism is used to obtain the braking force of the braking mechanism, which enables quick braking in conjunction with the disengagement operation of the clutch mechanism and is linked to the clutch case or the clutch mechanism. A large braking surface that is not restricted by the diameter of the gear etc. is formed with a friction plate and a braking member to improve the durability of the braking system, and the shaft body is arranged at a position separated from the clutch case axis. It is also possible to reliably block the rotation of the friction plate and obtain a strong braking force.
【０００９】又、上記第２の特徴によると、ミッション
ケースの組立時にはクラッチ機構と制動機構とを伝動軸
と一体的にミッションケース内に備えることで済み、点
検、修理等、クラッチ機構、制動機構を分解する必要の
ある場合にも、これらを伝動軸と一体的にミッションケ
スから取外し、ミッションケース外の開放された空間で
作業を行えるものとなる。Further, according to the second feature, when the mission case is assembled, the clutch mechanism and the braking mechanism may be provided in the mission case integrally with the transmission shaft, and the clutch mechanism and the braking mechanism may be inspected or repaired. Even when it is necessary to disassemble the parts, they can be removed from the mission case integrally with the transmission shaft, and work can be performed in the open space outside the mission case.
【００１０】[0010]
【発明の実施の形態】以下、本発明の実施の形態を図面
に基づいて説明する。Embodiments of the present invention will be described below with reference to the drawings.
【００１１】図１及び図２に示すように、操向操作され
ない前車輪１、操向操作される後車輪２夫々を備えた機
体３の中央部に運転座席４を配置すると共に、該機体３
の後部にエンジン５を搭載し、中央部に静油圧式の無段
変速装置６、及び、ミッションケース７を配置し、又、
該機体３の前端位置に作業装置としてのモーア８を備え
て作業機の一例として乗用型の芝刈機を構成する。As shown in FIGS. 1 and 2, a driver's seat 4 is arranged at the center of an airframe 3 having front wheels 1 that are not steered and rear wheels 2 that are not steered.
The engine 5 is mounted on the rear part, and the hydrostatic continuously variable transmission 6 and the transmission case 7 are arranged in the central part.
A mower 8 as a working device is provided at the front end position of the machine body 3 to form a riding lawn mower as an example of the working machine.
【００１２】この芝刈機では無段変速装置６で変速され
た動力をミッションケース７を介して前車輪１、及び、
後車輪２に伝える伝動系を備えると共に、モーア８に連
結するリンク９をリフトアーム１０を介して昇降操作す
る油圧シリンダ１１をミッションケース７の上部に配置
してあり、このモーア８に対してはミッションケース７
の前面に突設した外部動力取出し軸１２（出力軸の一
例）から中間軸１３を介して動力が伝えられる。尚、モ
ーア８は縦軸芯周りで回転する３つのブレードをケース
に内装して構成されている。In this lawnmower, the power transmitted by the continuously variable transmission 6 is transmitted through the transmission case 7 to the front wheels 1 and
A hydraulic system 11 is provided on the upper part of the transmission case 7, which is provided with a transmission system for transmitting to the rear wheels 2 and which raises and lowers a link 9 connected to the mower 8 via a lift arm 10. Mission case 7
Power is transmitted from an external power take-out shaft 12 (an example of an output shaft) provided on the front surface of the vehicle through an intermediate shaft 13. In addition, the mower 8 is configured by housing three blades that rotate around the axis of the vertical axis in a case.
【００１３】図２乃至図４に示すように、前記無段変速
装置６はエンジン５からの動力が伝えられる可変容量型
の油圧ポンプ６Ａと、この油圧ポンプ６Ａからの作動油
の供給で駆動される油圧モータ６Ｂとを油路が形成され
たバルブブロック６Ｃの一側面に配置して成り、油圧モ
ータ６Ｂの出力軸１４からの動力はミッションケース内
の副変速装置Ｓ、及び、ベベルピニオン軸１５を介して
前車輪用の差動装置１Ａに伝えられ、又、このベベルピ
ニオン軸１５に形成したギヤ１６からの動力は外部動力
取出し用の伝動軸１７にニードルベアリングを介して遊
転支承した中間ギヤ１８、これに咬合するギヤ１９を有
した中間伝動軸２０、デュアルワンウエイクラッチ２
１、シャフト２２夫々を介して後車輪２の差動装置２Ａ
に伝えられる。As shown in FIGS. 2 to 4, the continuously variable transmission 6 is driven by a variable displacement hydraulic pump 6A to which the power from the engine 5 is transmitted, and the supply of hydraulic oil from the hydraulic pump 6A. And a hydraulic motor 6B that is arranged on one side surface of a valve block 6C in which an oil passage is formed. Power from the output shaft 14 of the hydraulic motor 6B is generated by the auxiliary transmission S in the transmission case and the bevel pinion shaft 15 The power from the gear 16 formed on the bevel pinion shaft 15 is transmitted to the front wheel differential gear 1A via the intermediate shaft which is idle-supported on the transmission shaft 17 for extracting the external power via the needle bearing. Gear 18, intermediate transmission shaft 20 having gear 19 meshing with gear 18, dual one-way clutch 2
1, the differential device 2A of the rear wheel 2 via the shaft 22 respectively
Conveyed to.
【００１４】又、油圧ポンプ６Ａの側面には油圧ポンプ
６Ａからの作動油の吐出量を調節するトラニオン軸６Ｄ
を備え、このトラニオン軸６Ｄと運転座席５の前方位置
の変速ペダル２３とを機械式に連係してある（操作構造
は詳述せず）。図３及び図４に示すように、前記副変速
装置Ｓは油圧モータ６Ｂの前記出力軸１４からの動力が
ギヤ伝動機構２４を介して伝えられ、ベベルピニオン軸
１５と平行姿勢のカウンタ軸２５に備えた高速用、低速
用のギヤとに選択的に咬合するようベベルピニオン軸１
５にスプライン嵌合したシフトギヤ２６を備えて成り、
このシフトギヤ２６は運転座席５の近傍の副変速レバー
２７と機械的に連係している（操作構造は詳述せず）。A trunnion shaft 6D is provided on the side surface of the hydraulic pump 6A for adjusting the amount of hydraulic oil discharged from the hydraulic pump 6A.
The trunnion shaft 6D and the speed change pedal 23 at the front position of the driver's seat 5 are mechanically linked (the operating structure is not described in detail). As shown in FIGS. 3 and 4, in the auxiliary transmission S, the power from the output shaft 14 of the hydraulic motor 6B is transmitted through the gear transmission mechanism 24, and is transmitted to the counter shaft 25 in a posture parallel to the bevel pinion shaft 15. Bevel pinion shaft 1 for selectively engaging with the gears for high speed and low speed
5 is equipped with a shift gear 26 spline-fitted,
The shift gear 26 is mechanically linked to an auxiliary transmission lever 27 near the driver's seat 5 (the operating structure is not described in detail).
【００１５】図３乃至図４に示すように、無段変速装置
６の油圧ポンプ６Ａを貫通するライブ軸２８に連結した
出力ギヤ２９と咬合する入力ギヤ３０を外部動力取出し
用の前記伝動軸１７にベアリング３１を介して遊転支承
し、この入力ギヤ３０と該伝動軸１７との間に油圧式の
クラッチ機構Ｃを備えると共に、このクラッチ機構Ｃと
隣接して制動機構Ｂを備えている、又、この伝動軸１７
と外部動力取出し軸１２とを同軸芯上に配置し、カップ
リング３２で連結することで、エンジン５からのライブ
動力をクラッチ機構Ｃを介して外部動力取出し軸１２に
伝える伝動系が形成され、次にクラッチ機構Ｃと制動機
構Ｂとの詳細を説明する。As shown in FIGS. 3 to 4, an input gear 30 meshing with an output gear 29 connected to a live shaft 28 penetrating the hydraulic pump 6A of the continuously variable transmission 6 is connected to the transmission shaft 17 for taking out external power. And a hydraulic clutch mechanism C between the input gear 30 and the transmission shaft 17, and a braking mechanism B adjacent to the clutch mechanism C. Also, this transmission shaft 17
The external power take-off shaft 12 and the external power take-off shaft 12 are arranged coaxially and connected by the coupling 32 to form a transmission system for transmitting live power from the engine 5 to the external power take-off shaft 12 via the clutch mechanism C. Next, details of the clutch mechanism C and the braking mechanism B will be described.
【００１６】クラッチ機構Ｃは入力ギヤ３０、及び、伝
動軸１７に支持されたクラッチケース３３夫々に備えた
複数の摩擦板３４（摩擦部材の一例）を有すると共に、
これらの摩擦板３４を圧接操作するピストン３５と、ピ
ストン３５を戻し操作する圧縮バネ３６とを有し、これ
ら摩擦板３４、ピストン３５、圧縮バネ３６を伝動軸１
７に一体回転状態に外嵌支持されたクラッチケース３３
に内装して成り、伝動軸１７にはピストン３５に対する
作動油の給排を行う油路１７Ｒが穿設されると共に、こ
の油路１７Ｒに連通する油路６Ｒが無段変速装置６のバ
ルブブロック６Ｃに形成され、この油路６Ｒに対しては
デュアルワンウエイクラッチ２１のケーシング２１Ａの
上部位置に内装したバルブ３７からの作動油が供給され
る。又、バルブ３７は図５に示すように、ケーシング２
１Ａに穿設した油路２１Ｒを遮る位置に配置され、この
油路２１Ｒと直交する軸芯周りで回動自在に構成され、
このバルブ３７を回動操作することにより、図６に示す
如く、バルブ３７の送油路３７Ａを介してクラッチ機構
Ｃに圧油を供給する状態と、図５に示す如く、バルブ３
７の排油路３７Ｂを介してクラッチ機構Ｃから油を排出
する状態とを現出するように構成されている。尚、この
バルブ３７は運転座席４の近傍に配置したクラッチレバ
ー３８で操作される（操作構造は詳述せず）。The clutch mechanism C includes an input gear 30 and a plurality of friction plates 34 (an example of friction members) provided in each of the clutch cases 33 supported by the transmission shaft 17, and
The friction plate 34 is provided with a piston 35 for pressure contact operation, and a compression spring 36 for returning the piston 35. The friction plate 34, the piston 35, and the compression spring 36 are connected to the transmission shaft 1.
7, a clutch case 33 that is externally fitted and supported so as to be integrally rotated.
The transmission shaft 17 is provided with an oil passage 17R for supplying and discharging hydraulic oil to and from the piston 35, and the oil passage 6R communicating with the oil passage 17R is formed in the valve block of the continuously variable transmission 6. 6C, the hydraulic oil is supplied to the oil passage 6R from a valve 37 installed in an upper position of the casing 21A of the dual one-way clutch 21. Further, the valve 37 is, as shown in FIG.
It is arranged at a position that intercepts the oil passage 21R formed in 1A, and is configured to be rotatable around an axis perpendicular to the oil passage 21R,
By rotating this valve 37, as shown in FIG. 6, a state in which pressure oil is supplied to the clutch mechanism C via the oil supply passage 37A of the valve 37, and as shown in FIG.
7 is configured to expose the state in which oil is discharged from the clutch mechanism C via the oil discharge passage 37B. The valve 37 is operated by a clutch lever 38 arranged near the driver's seat 4 (the operating structure is not described in detail).
【００１７】図５乃至図７に示すように、制動機構Ｂは
クラッチケース３３の回転軸芯（伝動軸１７の軸芯と一
致する）と平行する姿勢でミッションケース内に備えた
２本の軸体３９に係合支持された単一のつ摩擦板４０
と、この摩擦板４０を挟み込む位置に配置され、かつ、
クラッチケース３３が伝動軸１７を囲繞する筒状部３３
Ａにトルク伝動自在に係合した一対のプレート状の制動
部材４１とを備えると共に、クラッチ機構Ｃの切り操作
時にはピストン３５と一体的にクラッチケース３３の開
口部を介して制動機構Ｂの側に突出する複数の押圧部材
４２とで構成され、図５に示す如く、油圧クラッチＣの
切り操作時には前記圧縮バネ３６の付勢力で押圧部材４
２が軸芯方向に突出作動することで摩擦板４０を制動部
材４１で挟み込んでクラッチケース３３とともに伝動軸
１７に制動力を作用させるよう構成されている。尚、摩
擦板４０は軸体１７に対して、その長手方向に移動自在
に支持され、制動部材４１はクラッチケース３３の筒状
部３３Ａに対して軸芯方向に移動自在に支持されること
で押圧部材４２の突出作動によって互いに圧接できるよ
う構成されでいる。As shown in FIGS. 5 to 7, the braking mechanism B has two shafts provided in the mission case in a posture parallel to the rotation axis of the clutch case 33 (which coincides with the axis of the transmission shaft 17). Single friction plate 40 engaged with and supported by the body 39
And the friction plate 40 is sandwiched between the positions, and
A cylindrical portion 33 in which the clutch case 33 surrounds the transmission shaft 17.
A pair of plate-shaped braking members 41 engaged with A for torque transmission are provided, and when the clutch mechanism C is disengaged, it is integrated with the piston 35 to the side of the braking mechanism B through the opening of the clutch case 33. A plurality of projecting pressing members 42 are provided. As shown in FIG. 5, the pressing member 4 is pressed by the urging force of the compression spring 36 when the hydraulic clutch C is disengaged.
The friction plate 40 is sandwiched between the braking members 41 by the protruding operation of the shaft 2 in the axial direction, and the braking force acts on the transmission shaft 17 together with the clutch case 33. The friction plate 40 is movably supported in the longitudinal direction of the shaft body 17, and the braking member 41 is movably supported in the axial direction of the tubular portion 33A of the clutch case 33. The pressing members 42 are configured to be pressed against each other by the projecting operation.
【００１８】又、入力ギヤ３０、クラッチ機構Ｃを構成
する全ての部材、及び、軸体３９を除いた制動機構Ｂを
構成する部材は伝動軸１７に支持され、クラッチ機構
Ｃ、制動機構Ｂをミッションケース７に組込む場合には
伝動軸１７上でクラッチ機構Ｃ、制動機構Ｂを予め組立
て得るようになっている。更に、伝動軸１７の無段変速
装置６側の端部はバルブブロック６Ｃに凹状の形成した
部位に係合保持したボールベアリング４３に支持されて
いる。Further, the input gear 30, all members constituting the clutch mechanism C, and members constituting the braking mechanism B excluding the shaft 39 are supported by the transmission shaft 17, and the clutch mechanism C and the braking mechanism B are connected. When assembled in the mission case 7, the clutch mechanism C and the braking mechanism B can be preassembled on the transmission shaft 17. Further, the end portion of the transmission shaft 17 on the continuously variable transmission 6 side is supported by a ball bearing 43 which is engaged and held in a concave portion of the valve block 6C.
【００１９】このように本発明では、クラッチ機構Ｃの
操作でモーア８の駆動と停止とを行えるものであり、更
に、クラッチ機構Ｃの切り操作時には、この切り操作と
機械的に連動して制動機構Ｂが制動力を作用させるので
モーア８のブレードの回転は短時間のうちに停止するも
のとなっている。更に、このクラッチ機構Ｃ、制動機構
Ｂは伝動軸１７に備えられているので、ミッションケー
ス７内にクラッチ機構Ｃ、制動機構Ｂを組込む際にも、
これらを予め組立て、調整しておき簡便な操作で済み、
逆に分解する際にもクラッチ機構Ｃ、制動機構Ｂを容易
にミッションケース外に取出せるものとなっている。As described above, according to the present invention, the mower 8 can be driven and stopped by operating the clutch mechanism C. Further, when the clutch mechanism C is disengaged, the braking operation is mechanically linked with the disengagement operation. Since the mechanism B applies the braking force, the rotation of the blade of the mower 8 is stopped within a short time. Further, since the clutch mechanism C and the braking mechanism B are provided on the transmission shaft 17, even when the clutch mechanism C and the braking mechanism B are assembled in the mission case 7,
Assembling and adjusting these in advance, simple operation is enough,
Conversely, even when disassembling, the clutch mechanism C and the braking mechanism B can be easily taken out of the mission case.
【００２０】[0020]
【発明の効果】従って、出力軸から動力を伝える作業装
置が高い慣性のものであっても制動系を傷めること少な
くクラッチ機構の切り操作と連動して確実な制動力を出
力軸に作用させる作業機が合理的に構成されたのである
（請求項１）。又、簡便な操作でクラッチ機構、制動機
構を容易に組立、分解できるものが得られた（請求項
２）。Therefore, even if the work device for transmitting the power from the output shaft has a high inertia, the work for applying a reliable braking force to the output shaft in cooperation with the disengagement operation of the clutch mechanism without damaging the braking system. The machine was reasonably constructed (Claim 1). Moreover, a clutch mechanism and a braking mechanism which can be easily assembled and disassembled by a simple operation were obtained (claim 2).
【００２１】尚、特許請求の範囲の項に図面との対照を
便利にするために符号を記すが、該記入により本発明は
添付図面の構成に限定されるものではない。It should be noted that reference numerals are given in the claims for convenience of comparison with the drawings, but the present invention is not limited to the configurations of the accompanying drawings by the entry.
【図１】芝刈機の全体側面図FIG. 1 is an overall side view of a lawn mower.
【図２】芝刈機の伝動系の側面図[Fig. 2] Side view of the transmission system of the lawn mower
【図３】無段変速装置及びミッションケースにおける伝
動系の線図FIG. 3 is a diagram of a transmission system in a continuously variable transmission and a mission case.
【図４】ミッションケース内部の一部切欠き側面図[Fig. 4] Side view of the transmission case with some cutaways
【図５】切り状態のクラッチ機構の縦断側面図FIG. 5 is a vertical sectional side view of the clutch mechanism in a disengaged state.
【図６】入り状態のクラッチ機構の縦断側面図FIG. 6 is a vertical sectional side view of the clutch mechanism in an engaged state.
【図７】制動機構の縦断正面図FIG. 7 is a vertical sectional front view of the braking mechanism.
７ ミッションケース ８ 作業装置 １２ 出力軸 １７ 伝動軸 ３３ クラッチケース ３４ 摩擦部材 ３５ 油圧ピストン ３６ バネ ３９ 軸体 ４０ 摩擦板 ４１ 制動部材 ４２ 押圧部材 Ｂ 制動機構 Ｃ クラッチ機構 7 mission case 8 working device 12 output shaft 17 transmission shaft 33 clutch case 34 friction member 35 hydraulic piston 36 spring 39 shaft body 40 friction plate 41 braking member 42 pressing member B braking mechanism C clutch mechanism
───────────────────────────────────────────────────── フロントページの続き (72)発明者 藤原 修身 大阪府堺市石津北町64番地 株式会社クボ タ堺製造所内 (72)発明者 島村 輝郎 大阪府堺市石津北町64番地 株式会社クボ タ堺製造所内 (72)発明者 松井 昭男 大阪府堺市石津北町64番地 株式会社クボ タ堺製造所内 (72)発明者 梅本 英哉 大阪府堺市石津北町64番地 株式会社クボ タ堺製造所内 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Shuji Fujiwara 64 Ishizukitamachi, Sakai City, Osaka Prefecture Kubota Sakai Factory Co., Ltd. (72) Inventor Teruo Shimamura 64, Ishizukitamachi, Sakai City, Osaka Manufacturing Kubota Sakai Co., Ltd. (72) Inventor Akio Matsui 64, Ishizukita-machi, Sakai City, Osaka Prefecture Kubota Sakai Manufacturing Co., Ltd. (72) Inventor, Hideya Umemoto 64, Ishizukita-machi, Sakai City, Osaka Kubota Sakai Manufacturing Co., Ltd.
Claims (2)
にクラッチ機構（Ｃ）を介装すると共に、このクラッチ
機構（Ｃ）の切り操作時に出力軸（１２）の遊転を阻止
する制動機構（Ｂ）を備えた作業機であって、 前記クラッチ機構（Ｃ）を、圧油が給排される油圧ピス
トン（３５）と、油圧ピストン（３５）への圧油の供給
時に該油圧ピストン（３５）で圧接操作される伝動用の
摩擦部材（３４）と、油圧ピストン（３５）からの排油
時に摩擦部材（３４）を離間操作するバネ（３６）とを
クラッチケース（３３）に内装して構成し、前記制動機
構（Ｂ）を、クラッチケース（３３）の回転軸芯と平行
する姿勢で静止系に備えた軸体（３９）に係合支持され
た摩擦板（４０）と、この摩擦板（４０）を挟み込む位
置に配置され、かつ、前記出力軸（１２）と連係する制
動部材（４１）とを備えると共に、前記クラッチ機構
（Ｃ）の切り操作時には該クラッチ機構（Ｃ）のバネ
（３６）の付勢力でクラッチケース（３３）の外方に突
出作動して摩擦板（４０）、制動部材（４１）夫々を押
圧する押圧部材（４２）とで構成してある作業機。1. A clutch mechanism (C) is provided in an output shaft system for transmitting power to a work device (8), and idling of the output shaft (12) is prevented when the clutch mechanism (C) is disengaged. A working machine equipped with a braking mechanism (B), wherein the clutch mechanism (C) is provided with a hydraulic piston (35) for supplying and discharging pressure oil, and the hydraulic pressure when the pressure oil is supplied to the hydraulic piston (35). A transmission friction member (34) that is pressed into contact with the piston (35) and a spring (36) that operates to separate the friction member (34) during oil discharge from the hydraulic piston (35) are provided in the clutch case (33). A friction plate (40), which is configured as an internal component, and in which the braking mechanism (B) is engaged and supported by a shaft body (39) provided in a stationary system in a posture parallel to the rotation axis of the clutch case (33); Is arranged at a position where the friction plate (40) is sandwiched, and A braking member (41) linked to the force shaft (12) is provided, and when the clutch mechanism (C) is disengaged, the spring force (36) of the clutch mechanism (C) urges the outside of the clutch case (33). A working machine constituted by a pressing member (42) for pressing each of the friction plate (40) and the braking member (41) by projecting in one direction.
ース（７）の伝動軸（１７）に外嵌支持すると共に、こ
の伝動軸（１７）に対して前記制動機構（Ｂ）の摩擦板
（４０）と制動部材（４１）とを備え、この伝動軸（１
７）と一体的にクラッチ機構（Ｃ）と制動機構（Ｂ）の
一部とをミッションケース（７）に対して着脱自在に構
成してある請求項１記載の作業機。2. The clutch mechanism (C) is externally fitted and supported on a transmission shaft (17) of a transmission case (7), and the friction plate (40) of the braking mechanism (B) is supported on the transmission shaft (17). ) And a braking member (41), and the transmission shaft (1
The working machine according to claim 1, wherein the clutch mechanism (C) and a part of the braking mechanism (B) are integrally formed with the transmission case (7) so as to be detachable from the mission case (7).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22387795A JPH0968245A (en) | 1995-08-31 | 1995-08-31 | Operating machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22387795A JPH0968245A (en) | 1995-08-31 | 1995-08-31 | Operating machine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0968245A true JPH0968245A (en) | 1997-03-11 |
Family
ID=16805117
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP22387795A Pending JPH0968245A (en) | 1995-08-31 | 1995-08-31 | Operating machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0968245A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2336640B (en) * | 1998-04-21 | 2003-02-19 | Agco Gmbh & Co | Auxiliary drive for utility vehicle & method of operation thereof |
| CN108506360A (en) * | 2018-04-25 | 2018-09-07 | 福建省威诺数控有限公司 | A kind of static pressure support gear clutch |
| CN113108000A (en) * | 2021-04-13 | 2021-07-13 | 山推工程机械股份有限公司 | Main clutch system of mechanical bulldozer |
-
1995
- 1995-08-31 JP JP22387795A patent/JPH0968245A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2336640B (en) * | 1998-04-21 | 2003-02-19 | Agco Gmbh & Co | Auxiliary drive for utility vehicle & method of operation thereof |
| CN108506360A (en) * | 2018-04-25 | 2018-09-07 | 福建省威诺数控有限公司 | A kind of static pressure support gear clutch |
| CN113108000A (en) * | 2021-04-13 | 2021-07-13 | 山推工程机械股份有限公司 | Main clutch system of mechanical bulldozer |
| CN113108000B (en) * | 2021-04-13 | 2023-08-04 | 山推工程机械股份有限公司 | Main clutch system of mechanical bulldozer |
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