JPS60211137A - Hydraulic clutch with brake - Google Patents

Hydraulic clutch with brake

Info

Publication number
JPS60211137A
JPS60211137A JP59068739A JP6873984A JPS60211137A JP S60211137 A JPS60211137 A JP S60211137A JP 59068739 A JP59068739 A JP 59068739A JP 6873984 A JP6873984 A JP 6873984A JP S60211137 A JPS60211137 A JP S60211137A
Authority
JP
Japan
Prior art keywords
clutch
brake
output shaft
hydraulic
piston
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
Application number
JP59068739A
Other languages
Japanese (ja)
Inventor
Hideki Miura
三浦　秀喜
Mitsuyoshi Mori
森　光善
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Exedy Corp
Original Assignee
Daikin Manufacturing Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Daikin Manufacturing Co Ltd filed Critical Daikin Manufacturing Co Ltd
Priority to JP59068739A priority Critical patent/JPS60211137A/en
Publication of JPS60211137A publication Critical patent/JPS60211137A/en
Pending legal-status Critical Current

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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D67/00—Combinations of couplings and brakes; Combinations of clutches and brakes
    • F16D67/02—Clutch-brake combinations
    • F16D67/04—Clutch-brake combinations fluid actuated

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Braking Arrangements (AREA)

Abstract

PURPOSE:To keep off any operation of farm working machinery or the like due to drag torque, by installing an inertia brake alongside in a hydraulic clutch, while connecting a hydraulic line for energizing a clutch piston, to a braking hydraulic line. CONSTITUTION:A brake 30 operating in time of clutch disengagement is installed along-side in a clutch output shaft 2, while a hydraulic line for energizing a clutch piston 12 is connected to a power releasing hydraulic line of the brake 30. With this constitution, even in case of drag torque being transmitted to the output shaft 2, the output shaft 2 is in no case rotated so that the starting of a car or operation of farm working machinery due to the drag torque is surely preventable from occurring. In addition, the clutch and the brake 30 both are interlockable with certainty whereby operation of the brake 30 in time of clutch engagement and rotation of the output shaft 2 in time of clutch disengagement are surely preventable from occurring.

Description

【発明の詳細な説明】 （産業上の利用分野） 本発明は農用トラクター等に使用される油圧（湿式多板
）クラッチに関する。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a hydraulic (wet multi-disc) clutch used in agricultural tractors and the like.

（従来技術） 一般に湿式多板クラッチではディスク（摩擦板）の枚数
が多いことや、湿式であること等から、クラッチ遮断状
態において、少なくとも０．１〜０．２ｋｇｍのドラッ
グトルクが発生する。そして農用トラクターの様にクラ
ツヂ軸以降の変速比が大きい車両にその様なりラッチを
使用すると、ドラッグトルクが小さくても、走行用クラ
ッチの場合は車両が動き、ＰＴＯクラッｔの場合は作業
機が回る可能性がある。(Prior Art) In general, a wet type multi-disc clutch has a large number of discs (friction plates) and is a wet type, so a drag torque of at least 0.1 to 0.2 kgm is generated in the clutch disengaged state. If such a latch is used on a vehicle such as an agricultural tractor that has a large gear ratio after the clutch shaft, even if the drag torque is small, the vehicle will move if the drive clutch is used, and the work equipment will move if the PTO clutch is used. There is a possibility that it will turn.

（発明の目的） 本発明は上記不具合を解決するために、油圧クラッチに
イナーシ１１ブレーキを併設するとともに、該ブレーキ
の構造に改良を施すことを目的としている。(Object of the Invention) In order to solve the above problems, the present invention aims to provide an inertia 11 brake to a hydraulic clutch and to improve the structure of the brake.

（発明の構成） 本発明はトルク入力部と、トルク出力部と、両者を連結
するだめの複数の摩擦板と、摩擦板を押圧するためのク
ラッチピストンと、該ピストンを付勢するための油圧シ
リンダー機構とを備えた油圧クラッチにブレーキを併設
し、該ブレーキの被制動部を上記出力部に連結するとと
もに、ブレーキに制動力解除用の油圧シリンダー機構を
設け、該解除用シリンダー機構の油圧ラインを上記クラ
ッチピストン付勢用の油圧シリンダー機構の油圧ライン
と接続したことを特徴としている。(Structure of the Invention) The present invention includes a torque input section, a torque output section, a plurality of friction plates connecting the two, a clutch piston for pressing the friction plates, and a hydraulic pressure for urging the piston. A brake is attached to a hydraulic clutch having a cylinder mechanism, and the braked part of the brake is connected to the output part, and the brake is provided with a hydraulic cylinder mechanism for releasing the braking force, and a hydraulic line of the releasing cylinder mechanism is provided. is connected to the hydraulic line of the hydraulic cylinder mechanism for biasing the clutch piston.

（実施例） 縦断面図である第１図において、クラッチは筒状の入力
軸１（トルク入力部）と筒状の出力軸２゛（トルク出力
部）を向応に備えている。入力軸１の一端部外周にはギ
ヤ３が取付けてあり、このギヤ３は図示されていないエ
ンジン側の出力ギヤに噛合っている。入力軸１は他端部
に外向きフランジ４を備え、フランジ４の外周から多数
のラグ５がギヤ３と反対側に向かって突出している。ラ
グ５は入力軸１の円周方向に間隔を隔てて全体が筒状に
設けである。ラグ５は出力軸２の周囲に位置しており、
両者（２，５）の間に複数の入力側摩擦板６及び出力側
摩擦板７が配置しである。摩擦板６．７はいずれも環状
で、交互に配置しである。(Embodiment) In FIG. 1, which is a longitudinal sectional view, the clutch is equipped with a cylindrical input shaft 1 (torque input section) and a cylindrical output shaft 2' (torque output section). A gear 3 is attached to the outer periphery of one end of the input shaft 1, and this gear 3 meshes with an output gear on the engine side (not shown). The input shaft 1 has an outward flange 4 at its other end, and a number of lugs 5 protrude from the outer periphery of the flange 4 toward the side opposite to the gear 3. The lugs 5 are provided in a cylindrical shape as a whole at intervals in the circumferential direction of the input shaft 1. The lug 5 is located around the output shaft 2,
A plurality of input-side friction plates 6 and output-side friction plates 7 are arranged between the two (2, 5). The friction plates 6.7 are both annular and arranged alternately.

各摩擦板６は外周の突起がラグ５の間の溝に軸方向（入
力軸１、出力軸２の中心線Ｏ−Ｏと平行な方向）に摺動
自在に嵌合している。摩擦板７は内周の突起が出力軸２
の外周のスプライン８に軸方向に摺動自在に嵌合してい
る。摩擦板６．７群は出力軸２の端部外周に固定したバ
ックプレート１０によりフランジ４側から支持されてお
り、反対側から環状プレート１１を介してピストン１２
の押圧部１３により押圧されるようになっている。Each friction plate 6 has a protrusion on its outer periphery that is fitted into a groove between the lugs 5 so as to be slidable in the axial direction (in a direction parallel to the center line OO of the input shaft 1 and the output shaft 2). The protrusion on the inner circumference of the friction plate 7 corresponds to the output shaft 2.
It is fitted into a spline 8 on the outer periphery so as to be slidable in the axial direction. The friction plates 6 and 7 groups are supported from the flange 4 side by a back plate 10 fixed to the outer periphery of the end of the output shaft 2, and are connected to the piston 12 from the opposite side via an annular plate 11.
It is pressed by the pressing part 13 of.

なお両摩擦板６．７の内、摩擦ライニングは出力側摩擦
板７（被駆動側プレート）だけに張付りである。又出力
軸２は入力軸１と反対側の端部に内歯スプライン９を備
え、このスプライン９により図示されていない別の軸に
連結している。Of the two friction plates 6.7, the friction lining is attached only to the output side friction plate 7 (driven side plate). Further, the output shaft 2 is provided with an internal spline 9 at the end opposite to the input shaft 1, and is connected to another shaft (not shown) by this spline 9.

ピストン１２全体は上記押圧部１３を一端部に有づ゛る
筒状体で、０リング１４を介して出力軸２の外周に摺動
自在に嵌合する筒状部１５を中間部に備え、′油圧室２
０に面するフランジ状のピストン本体２１を他端部に備
えている。０リング１４にりも摩擦板７側において筒状
部１５の内周には段部１６が設けてあり、段部１６と出
力軸２の外周段部１７の間にリターンスプリング１８（
圧縮コイルスプリング）が入れである。ピストン本体２
１の外周側及び筒状部１５と反対側には環状のシリンダ
ー２５が設けである。シリンダー２５は油圧室２０を挟
んでピストン本体２１に対向する環状端壁２６と、油圧
室２０の外周を囲む筒状の外周壁２７と、出力軸２の外
周に焼嵌め等により固定される筒状の内周壁２８とを備
えている。ピストン本体２１の外周はシールリング２９
を介して外周壁２７の内周に摺動自在に嵌合している。The entire piston 12 is a cylindrical body having the above-mentioned pressing part 13 at one end, and has a cylindrical part 15 in the middle part which is slidably fitted to the outer periphery of the output shaft 2 via an O-ring 14. 'Hydraulic chamber 2
A flange-shaped piston body 21 facing 0 is provided at the other end. A step 16 is provided on the inner periphery of the cylindrical portion 15 on the friction plate 7 side of the O-ring 14, and a return spring 18 (
A compression coil spring) is inserted. Piston body 2
An annular cylinder 25 is provided on the outer peripheral side of the cylinder 1 and on the opposite side from the cylindrical part 15. The cylinder 25 includes an annular end wall 26 facing the piston body 21 with the hydraulic chamber 20 in between, a cylindrical outer peripheral wall 27 surrounding the outer periphery of the hydraulic chamber 20, and a cylinder fixed to the outer periphery of the output shaft 2 by shrink fitting or the like. The inner circumferential wall 28 has a shape. The outer circumference of the piston body 21 is a seal ring 29
It is slidably fitted to the inner periphery of the outer circumferential wall 27 via.

シリンダー２５はイナーシャブレーキ３０の被制動部を
兼ねている。ブレーキ３０の環状ピストン３１は端壁２
６を挟んでピストン本体２１と反対側に位置しており、
内周がＯリング２４を介して内周壁２８に）３動自在に
嵌合しでいる。端壁２６とピストン３１は両者の対向面
に設けた環状の凸部３２と四部３３により嵌合しており
、中心線Ｏ−Ｏと平行なピン３５をピストン３１の孔に
挿入して凸部３２に固定することにより、シリンダー２
５とピストン３１は相対回転不能に連結されている。凸
部３２の内周と凹部３３の間にはＯリング３４が介装さ
れている。The cylinder 25 also serves as a braked part of the inertia brake 30. The annular piston 31 of the brake 30 is attached to the end wall 2
It is located on the opposite side of the piston body 21 across 6,
The inner circumference is fitted into the inner circumferential wall 28 via an O-ring 24 so as to be movable. The end wall 26 and the piston 31 are fitted by an annular convex portion 32 and a fourth portion 33 provided on their opposing surfaces, and a pin 35 parallel to the center line O-O is inserted into the hole of the piston 31 to remove the convex portion. By fixing to 32, cylinder 2
5 and the piston 31 are connected so that they cannot rotate relative to each other. An O-ring 34 is interposed between the inner periphery of the convex portion 32 and the concave portion 33.

凸部３２の外周側においてシリンダー２５とピストン３
１の間秤はブレーキディスク３６か配置しである。ブレ
ーキディスク３６はコアプレート３７（芯板）の両面に
ブレーキライニングを張付けて構成されており、コアプ
レート３７外周の張出部３８がクラッチケース３９等の
静止部材に軸方向に摺動自在に嵌合されている。なおブ
レーキディスク３６の形状は第１図のＩＩ−Ｉ［矢視部
分図である第２図に明瞭に示されている。第１図の如く
内周壁２８の先端に隣接した位置において、出力軸２の
外周にはスナップリング４ｏによりストッパリング４１
が固定されており、ストッパリング４１とピストン３１
の間にピストン３１をブレーキディスク３６側へ（Ｊ勢
するためのコーンスプリング４２が配置しである。Cylinder 25 and piston 3 on the outer peripheral side of convex portion 32
1, the brake disc 36 is located. The brake disc 36 is constructed by pasting brake linings on both sides of a core plate 37 (core plate), and a protruding portion 38 on the outer periphery of the core plate 37 is slidably fitted in a stationary member such as a clutch case 39 in the axial direction. are combined. The shape of the brake disc 36 is clearly shown in FIG. 2, which is a partial view taken along line II--I in FIG. As shown in FIG. 1, a stopper ring 41 is attached to the outer periphery of the output shaft 2 by a snap ring 4o at a position adjacent to the tip of the inner peripheral wall 28.
is fixed, and the stopper ring 41 and piston 31
A cone spring 42 is arranged to force the piston 31 toward the brake disc 36 during this period.

ブレーキ３０には制動力解除用の油圧シリンダー機構４
５が設けである。油圧シリンダー機構４５のシリンダー
はクラッチピストン１２用のシリンダー２５に兼用され
ている。油圧シリンダー機構４５の油圧室４６は凸部３
２と内周壁２８の間かつピストン３１の内周部と端壁２
６の間に形成されている。端壁２６には油圧室２０と油
圧室４６をつなぐ油孔５０が設けである。油圧室２０は
筒状部１５内周の環状溝４７、出力軸２の油孔４８を経
て出力軸２内の油圧供給油路４９（制御通路）に接続し
ている。The brake 30 includes a hydraulic cylinder mechanism 4 for releasing braking force.
5 is a provision. The cylinder of the hydraulic cylinder mechanism 45 is also used as the cylinder 25 for the clutch piston 12. The hydraulic chamber 46 of the hydraulic cylinder mechanism 45 has a convex portion 3
2 and the inner peripheral wall 28 and between the inner peripheral part of the piston 31 and the end wall 2
It is formed between 6. The end wall 26 is provided with an oil hole 50 that connects the hydraulic chamber 20 and the hydraulic chamber 46. The hydraulic chamber 20 is connected to a hydraulic pressure supply oil passage 49 (control passage) in the output shaft 2 via an annular groove 47 on the inner periphery of the cylindrical portion 15 and an oil hole 48 in the output shaft 2 .

（作用） エンジン運転中はギヤ３を介して入力軸１に回転力が伝
わり、入ツノ軸１及び摩擦板６は常に回転している。こ
の状態で油路４９から油圧室２０に油圧を導入すると、
油圧によりピストン１２が付勢されて摩擦板６．７を互
いに圧接させる。これによりクラッチは接続され、入力
軸１から摩擦板６．７を経て出力軸２に回転力が伝達さ
れて出力軸２が回転する。このクラッチ接続状態では油
圧室２０から油孔５０を経て油圧室４６にも油圧が導入
されているので、油圧室４６内の油圧によりピストン３
１はスプリング４２の弾力に抗して押戻され、ブレーキ
ディスク３６に対するピストン３１の押圧力は解放され
る。従ってブレーキ３０は作動せず、ブレーキディスク
３６からシリンダー２５ならびに出力軸２に制動力が加
わることはない。(Function) During engine operation, rotational force is transmitted to the input shaft 1 via the gear 3, and the input horn shaft 1 and the friction plate 6 are constantly rotating. When hydraulic pressure is introduced into the hydraulic chamber 20 from the oil passage 49 in this state,
The piston 12 is urged by hydraulic pressure to press the friction plates 6.7 together. As a result, the clutch is connected, and rotational force is transmitted from the input shaft 1 to the output shaft 2 via the friction plates 6.7, causing the output shaft 2 to rotate. In this clutch connected state, oil pressure is introduced from the oil pressure chamber 20 to the oil pressure chamber 46 via the oil hole 50, so the oil pressure in the oil pressure chamber 46 causes the piston to
1 is pushed back against the elasticity of the spring 42, and the pressing force of the piston 31 against the brake disc 36 is released. Therefore, the brake 30 does not operate, and no braking force is applied from the brake disc 36 to the cylinder 25 or output shaft 2.

次に油圧室２０に対する油圧を解放すると、ピストン１
２はスプリング１８の弾力により押戻されて摩擦板６．
７に対する押圧力を解放し、クラッチは遮断される。こ
のようにして摩擦板６．７間の圧接力を解放した状態で
も、摩擦板６．７が互いに接触し、入力軸１から出力軸
２ヘトラツグトルクが伝達されることがある。ところが
このクラッチ遮断状態では、油圧室２０の油圧とともに
油圧室４６の油圧も解放されるので、ピストン３１はス
プリング４２の弾力を受【プてブレーキディスク３６を
シリンダー２５に圧接させる。従ってブレーキディスク
３６からシリンダー２５を経て出力軸２に制動力が伝わ
り、上記ドラッグトルクにより出力軸２が回転さぜられ
ることはない。Next, when the hydraulic pressure to the hydraulic chamber 20 is released, the piston 1
2 is pushed back by the elasticity of the spring 18 and the friction plate 6.
7 is released, and the clutch is disengaged. Even when the pressing force between the friction plates 6.7 is released in this manner, the friction plates 6.7 may come into contact with each other, and torque may be transmitted from the input shaft 1 to the output shaft 2. However, in this clutch disengaged state, the hydraulic pressure in the hydraulic chamber 46 as well as the hydraulic pressure in the hydraulic chamber 20 is released, so the piston 31 receives the elastic force of the spring 42 and presses the brake disc 36 against the cylinder 25. Therefore, the braking force is transmitted from the brake disc 36 to the output shaft 2 via the cylinder 25, and the output shaft 2 is not rotated by the drag torque.

（発明の効果） 以上説明したように本発明によると、クラッチ遮断時に
作動するブレーキ３０をクラッチ出力軸２に併設したの
で、出力軸２にドラッグトルクが伝わった場合でも出力
軸２が回転することはない。(Effects of the Invention) As explained above, according to the present invention, the brake 30 that operates when the clutch is disengaged is attached to the clutch output shaft 2, so that even when drag torque is transmitted to the output shaft 2, the output shaft 2 does not rotate. There isn't.

従ってドラッグトルクによる車両の発車や作業機の作動
を確実に防止することができる。しかもクラッチピスト
ン１２を付勢するための油圧ラインをブレーキ３０の制
動力解除用の油圧ラインと接続したので、クラッチとブ
レーキ３０を確実に連動させることができ、クラッチ接
続時のブレーキ°３０の作動ならびにクラッチ遮断時の
出力軸２の回転を確実に防止することができる。特に図
示の実施例の如く油圧室２０用のシリンダー２５を油圧
室４６用のシリンダーに兼用し、シリンダー２５の油孔
５０により油圧室２０と油圧室４６をつなぐようにする
と、シリンダー構造や油路構造を極めて簡単化すること
ができる。又図示の如くシリンダー２５をブレーキ３０
の被制動部として利用すると、構造を更に簡単化するこ
とができる。Therefore, it is possible to reliably prevent the vehicle from starting or the work equipment from operating due to drag torque. Moreover, since the hydraulic line for energizing the clutch piston 12 is connected to the hydraulic line for releasing the braking force of the brake 30, the clutch and the brake 30 can be reliably linked, and the brake 30 is activated when the clutch is connected. Furthermore, rotation of the output shaft 2 when the clutch is disengaged can be reliably prevented. In particular, if the cylinder 25 for the hydraulic chamber 20 is also used as the cylinder for the hydraulic chamber 46 as in the illustrated embodiment, and the hydraulic chamber 20 and the hydraulic chamber 46 are connected through the oil hole 50 of the cylinder 25, the cylinder structure and oil path The structure can be extremely simplified. Also, as shown in the figure, the cylinder 25 is connected to the brake 30.
When used as a braked part, the structure can be further simplified.

【図面の簡単な説明】[Brief explanation of the drawing]

第１図は実施例の縦断面図、第２図は第１図のＩＩ−Ｉ
矢視部分図である。１・・・入力軸（入力部）、２・・
・出力軸（出力部）、６．７・・・摩擦板、１２・・・
ピストン、２５・・・シリンダー、３０・・・ブレーキ
、４５・・・油圧シリンダー機構Figure 1 is a longitudinal cross-sectional view of the embodiment, Figure 2 is II-I in Figure 1.
FIG. 1...Input shaft (input section), 2...
・Output shaft (output part), 6.7...Friction plate, 12...
Piston, 25...Cylinder, 30...Brake, 45...Hydraulic cylinder mechanism

Claims (1)

【特許請求の範囲】[Claims] トルク入力部と、トルク出力部と、両者を連結するため
の複数の摩擦板と、摩擦板を押圧するためのクラッチピ
ストンと、該ピストンを付勢するための油圧シリンダー
機構とを備えた油圧クラッチにブレーキを併設し、該ブ
レーキの被制動部を上記出力部に連結するとともに、ブ
レーキに制動力解除用の油圧シリンダー機構を設け、該
解除用シリンダー機構の油圧ラインを上記クラッチピス
トン付勢用の油圧シリンダー機構の油圧ラインと接続し
たことを特徴とするブレーキ付き油圧クラッチ。A hydraulic clutch comprising a torque input section, a torque output section, a plurality of friction plates for connecting the two, a clutch piston for pressing the friction plates, and a hydraulic cylinder mechanism for urging the piston. A brake is attached to the brake, and the braked part of the brake is connected to the output part, and the brake is provided with a hydraulic cylinder mechanism for releasing the braking force, and the hydraulic line of the releasing cylinder mechanism is connected to the hydraulic line for biasing the clutch piston. A hydraulic clutch with a brake characterized by being connected to the hydraulic line of a hydraulic cylinder mechanism.
JP59068739A 1984-04-05 1984-04-05 Hydraulic clutch with brake Pending JPS60211137A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP59068739A JPS60211137A (en) 1984-04-05 1984-04-05 Hydraulic clutch with brake

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP59068739A JPS60211137A (en) 1984-04-05 1984-04-05 Hydraulic clutch with brake

Publications (1)

Publication Number Publication Date
JPS60211137A true JPS60211137A (en) 1985-10-23

Family

ID=13382453

Family Applications (1)

Application Number Title Priority Date Filing Date
JP59068739A Pending JPS60211137A (en) 1984-04-05 1984-04-05 Hydraulic clutch with brake

Country Status (1)

Country Link
JP (1) JPS60211137A (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2019157999A (en) * 2018-03-13 2019-09-19 ヤンマー株式会社 Work vehicle
KR20210119694A (en) * 2020-03-25 2021-10-06 박동훈 Power transmission device

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2019157999A (en) * 2018-03-13 2019-09-19 ヤンマー株式会社 Work vehicle
KR20210119694A (en) * 2020-03-25 2021-10-06 박동훈 Power transmission device

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