JPH0587693B2 - - Google Patents
Info
- Publication number
- JPH0587693B2 JPH0587693B2 JP61300301A JP30030186A JPH0587693B2 JP H0587693 B2 JPH0587693 B2 JP H0587693B2 JP 61300301 A JP61300301 A JP 61300301A JP 30030186 A JP30030186 A JP 30030186A JP H0587693 B2 JPH0587693 B2 JP H0587693B2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- ball valve
- rotary disk
- ball
- center
- 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 - Lifetime
Links
Landscapes
- Check Valves (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Description
〈産業上の利用分野〉
本発明は、回転盤に装着される弁装置例えばク
ラツチピストンのブリードバルブに関するもので
ある。
〈従来技術〉
従来のクラツチピストンは、土工車両としての
ホイールローダなどに使用される。すなわちホイ
ールローダは一般にフルパワーシフトトランスミ
ツシヨンが採用されている。フルパワーシフトト
ランスミツシヨンとは歯車が常に噛み合つてお
り、その動力伝達機構は、第５図の如く、回転軸
２にハブギヤ１１が回転自在に外嵌され、該回転
軸２にクラツチドラム１２が溶接固定され、該ク
ラツチドラム１２に前記ハブギヤ１１を一体化す
るクラツチ１３および該クラツチ１３を押圧弛緩
するクラツチピストン（回転盤）１が内装され、
該クラツチピストン１を押圧弛緩させるための油
圧回路１４にブリードバルブ１５（弁装置）が取
付けられてなる。クラツチ１３は、前記クラツチ
ドラム１２と一体回転可能で前記回転軸２の軸方
向へ移動可能なアウタ１１３Ａと、前記ハブギヤ
１１に一体回転可能に外嵌され前記回転軸２の軸
方向へ移動可能なインナ１３Ｂとを備えている。
そして、ブリードバルブ１５は、第３図の球弁
子離座状態断面図、第４図の球弁子の着座状態断
面図の如く、回転盤１にその回転軸２の中心から
離れた位置で該回転軸２と平行に弁通路３が貫通
され、該弁通路３は、回転盤１に形成された圧力
流体入口４および円筒形弁室５と弁シート６に形
成された円筒形弁孔７とから構成され、前記弁室
５には鋼球製またはナイロン製の球弁子８が離着
座自在に収納され、前記弁孔７の径、球弁子８の
径および弁室５の径はそれぞれ順次大きく形成さ
れていた。
そして前記弁孔７の中心Ｃ１と弁室５の中心Ｃ
２とは一致して組立てられていた。
上記において圧力流体（圧油）の圧力Ｐが零の
状態では回転盤１が所定値以上に回転すれば、そ
の遠心力Ｗ２による開弁モーメントＭ２で球弁子
８は弁孔７の周縁の支点７ａに乗り上げて弁孔７
が開き、また圧力流体の圧力Ｐが所定値以上に大
きくなると、その閉弁力Ｗ１による閉弁モーメン
トＭ１が開弁モーメントＭ２より大きくなり球弁
子８が弁孔７を閉じる。
これを式により表示すると下記の如くである。
Ｍ１＝Ｗ１・Ｌ１
Ｍ２＝Ｗ２・Ｌ２
Ｗ１＝（P0＋Ｐ）Ａ
P0：ゲージ圧
Ｐ：遠心油圧
Ｐ＝ω2（r2 2−r1 2）γ／２ｇ
ω＝Ｎ×（2π／60）
Ｎ：回転数（rpm）
ω：角速度
γ：油比重量＝0.89ｇ／cm3
Ａ：φ3の積＝d2π／４
Ｗ２＝ｗ・r2・ω2／ｇ
ｗ：球弁子の重量
ｇ＝9.8×102cm／sec2
〈発明が解決しようとする問題点〉
しかし、上記従来の構造では、球弁子８を開弁
状態から閉弁状態に切替えるとき開弁モーメント
Ｍ２の値が大きいため、閉弁させ難い問題があつ
た。
そこで、本発明は、従来通りの加工性を維持す
るために、球弁子の材質や大きさ、弁孔の大きさ
や角度を変化させず、かつ、閉弁させ易い回転盤
に装着される弁装置、換言すればモジユレート性
能を向上できる回転盤に装着される弁装置の提供
を目的としている。
〈問題点を解決するための手段〉
本発明は、第１，２図の如く、回転盤１の回転
軸２の中心から離れた位置に弁通路３が貫通さ
れ、該弁通路３は、回転盤１に前記回転軸２と平
行に形成された圧力流体入口４および円筒形弁室
５と、弁シート６に前記回転軸２と平行に形成さ
れた円筒形弁孔７とから構成され、前記弁室５に
は球弁子８が離着座自在に収納され、前記弁孔７
の径、球弁子８の径および弁室５の径はそれぞれ
順次大きく形成され、前記円筒形弁孔７の弁室５
側端部に、開閉切換時に球弁子８の乗り上げ支点
７ａとなる角部が形成された弁装置において、前
記弁孔７は、その中心Ｃ１が弁室５の中心Ｃ２に
対して回転盤１の遠心方向Ｄ１へずれるよう偏心
Ｅされたものである。
〈作用〉
上記において、弁孔７の中心Ｃ１と弁室５の中
心Ｃ２とは偏心Ｅされているので、第１図の球弁
子８が支点７ａに乗り上げた開弁状態（離座状
態）での球弁子８の中心８ａと支点７ａとを結ぶ
線のなす角度（β1）は従来の角度（α1）より大
きくなり、球弁子８の中心８ａから座面６ｃまで
の高さ寸法Ｌ３は従来の寸法Ｌ２より小さくなる
ので、離座状態の球弁子８に作用する開弁モーメ
ントＭ２は小さくなる。このように離座状態で球
弁子８を着座（閉弁）させようとしたとき、遠心
力Ｗ２の影響が小さいので閉弁させ易い。
また球弁子８の着座（閉弁）状態での油圧Ｐに
よる閉弁モーメントＭ１は、球弁子８の重量、球
弁子８の中心８ａと弁孔７の周縁までの寸法Ｌ１
が従来のもの（第４図参照）と同一のため、開弁
し易さにおいて同一である。
〈実施例〉
以下、本発明弁装置を、クラツチピストンのブ
リードバルブに適用した実施例を第１図の球弁子
の離座（開弁）状態断面図、第２図の球弁子の着
座（閉弁）状態断面図により説明すると、回転盤
１にその回転軸の中心から離れた位置で該回転軸
と平行に弁通路３が貫通され、該弁通路３は、回
転盤１に形成された圧力流体入口４および円筒形
弁室５と弁シート６に形成された円筒形弁孔７と
から構成され、前記弁室５には鋼球製球弁子８が
離着座自在に収納され、前記弁孔７の径、球弁子
８の径および弁室５の径はそれぞれ順次大きく形
成されている。また、前記円筒形弁孔７の弁室５
側端部には、従来と同様に、開閉切換時に球弁子
８の乗り上げ支点７ａとなる角部が形成されてい
る。そして、前記弁孔７の中心Ｃ１と弁室５の中
心Ｃ２とは弁孔７が回転盤１の遠心方向Ｄ１へず
れるように僅かに偏心Ｅされ、これにより弁孔７
周縁から弁室５周面までの弁シート６の巾は遠心
側巾６ａが最小で求心側巾６ｂが最大とされ、球
弁子８の離座（開弁）状態ではその中心８ａから
弁シート６の座面６ｃまでの高さ寸法Ｌ３は従来
高さ寸法Ｌ２より小さくされている。
そして上記においては、圧力流体（圧油）の圧
力Ｐが零の状態では回転盤１が所定値以上に回転
すれば、その遠心力Ｗ２による開弁モーメントＭ
２で球弁子８は弁孔７周縁の支点７ａに乗り上げ
て弁孔７が開き、また圧力流体の圧力Ｐが所定値
以上に大きくなると、その閉弁力Ｗ１による閉弁
モーメントＭ１が開弁モーメントＭ２より大きく
なり球弁子８が弁孔７を閉じる。
また弁孔７の中心Ｃ１と弁室５の中心Ｃ２とは
偏心Ｅされているので、第１図の球弁子８が支点
７ａに乗り上げた開弁状態（離座状態）での球弁
子８の中心８ａと支点７ａとを結ぶ線のなす角度
（β1）は従来の角度（α1）より大きくなり、球弁
子８の中心８ａから座面６ｃまでの高さ寸法Ｌ３
は従来の寸法Ｌ２より小さくなるので、離座状態
の球弁子８に作用する開弁モーメントＭ２は小さ
くなる。このように離座状態で球弁子８を着座
（閉弁）させようとしたとき、遠心力Ｗ２の影響
が小さいので閉弁させ易い。
また球弁子８の着座（閉弁）状態での油圧Ｐに
よる閉弁モーメントＭ１は、球弁子８の重量、球
弁子８の中心８ａと弁孔７の周縁までの寸法Ｌ１
が従来のもの（第４図参照）と同一のため、開弁
し易さにおいて同一である。
なお、本発明は、上記実施例に限定されるもの
ではなく、本発明の範囲内で上記実施例に多くの
修正および変更を加え得ることは勿論である。
〈発明の効果〉
以上の説明から明らかな通り、本発明による
と、弁孔の中心と弁室の中心とは偏心されている
ので、球弁子が円筒形弁孔の乗り上げ支点に乗り
上げた開弁状態（離座状態）での球弁子の中心と
支点とを結ぶ線のなす角度は従来の角度より大き
くなり、球弁子の中心から座面までの高さ寸法は
従来の寸法より小さくなるので、離座状態の球弁
子に作用する開弁モーメントは小さくなる。この
ように離座状態で球弁子を着座（閉弁）させよう
としたとき、遠心力の影響が小さいので閉弁させ
易くなる。
また、球弁子の着座（閉弁）状態での油圧によ
る閉弁モーメントは、球弁子の重量、球弁子の中
心と弁孔の周縁までの寸法が従来のものと同一の
ため、開弁し易さにおいて同一である。
しかも、弁孔等をあくまで回転軸に平行に形成
することで、従来通りの穴加工のしやすさを保持
することを前提にしながら、ただ弁孔を僅かにず
らすだけで、球弁子の開弁モーメントを小さくで
きる。したがつて、従来と同様、加工作業が楽で
あり、高い加工性を有せしめることができるとい
つた優れた効果がある。
<Industrial Application Field> The present invention relates to a valve device mounted on a rotary disk, such as a bleed valve for a clutch piston. <Prior Art> Conventional clutch pistons are used in wheel loaders and the like as earthmoving vehicles. In other words, wheel loaders generally employ full power shift transmissions. A full power shift transmission has gears that are always in mesh with each other, and its power transmission mechanism includes a hub gear 11 rotatably fitted onto a rotating shaft 2, and a clutch drum 12 mounted on the rotating shaft 2, as shown in FIG. is fixed by welding, and a clutch 13 that integrates the hub gear 11 into the clutch drum 12 and a clutch piston (rotary disk) 1 that presses and releases the clutch 13 are installed inside the clutch drum 12.
A bleed valve 15 (valve device) is attached to a hydraulic circuit 14 for pressing and releasing the clutch piston 1. The clutch 13 includes an outer 113A that is rotatable integrally with the clutch drum 12 and movable in the axial direction of the rotary shaft 2, and an outer 113A that is fitted onto the hub gear 11 so as to be integrally rotatable and movable in the axial direction of the rotary shaft 2. It is equipped with an inner 13B. The bleed valve 15 is mounted on the rotary disk 1 at a position away from the center of the rotating shaft 2, as shown in the cross-sectional view of the ball valve in the unseated state in FIG. 3 and the cross-sectional view in the seated state of the ball valve in FIG. A valve passage 3 is passed through parallel to the rotation axis 2, and the valve passage 3 includes a pressure fluid inlet 4 formed in the rotary disk 1, a cylindrical valve chamber 5, and a cylindrical valve hole 7 formed in the valve seat 6. A ball valve 8 made of steel balls or nylon is housed in the valve chamber 5 so as to be able to be moved into and out of the valve chamber 5, and the diameter of the valve hole 7, the diameter of the ball valve 8, and the diameter of the valve chamber 5 are as follows. Each of them grew larger in turn. The center C1 of the valve hole 7 and the center C of the valve chamber 5
2 was assembled to match. In the above, when the pressure P of the pressure fluid (pressure oil) is zero, if the rotary disk 1 rotates above a predetermined value, the valve opening moment M2 due to the centrifugal force W2 causes the ball valve 8 to move to the fulcrum of the periphery of the valve hole 7. Climb onto 7a and open valve hole 7
opens, and when the pressure P of the pressure fluid increases to a predetermined value or more, the valve closing moment M1 due to the valve closing force W1 becomes larger than the valve opening moment M2, and the ball valve 8 closes the valve hole 7. This can be expressed using the following formula. M1=W1・L1 M2=W2・L2 W1=( P0 +P)A P0 : Gauge pressure P: Centrifugal oil pressure P=ω 2 (r 2 2 − r 1 2 ) γ/2g ω=N×(2π/ 60) N: Rotation speed (rpm) ω: Angular speed γ: Oil specific weight = 0.89g/cm 3 A: Product of φ3 = d 2 π/4 W2 = w・r 2・ω 2 /g w: Ball valve weight g=9.8×10 2 cm/sec 2 <Problem to be solved by the invention> However, in the above conventional structure, when switching the ball valve 8 from the open state to the closed state, the opening moment M2 Because the value was large, there was a problem that it was difficult to close the valve. Therefore, in order to maintain the conventional workability, the present invention has developed a valve that is mounted on a rotary disk that can be easily closed without changing the material and size of the ball valve and the size and angle of the valve hole. The purpose of this invention is to provide a device, in other words, a valve device mounted on a rotary disk that can improve modulation performance. <Means for Solving the Problems> In the present invention, as shown in FIGS. 1 and 2, a valve passage 3 is penetrated at a position away from the center of the rotating shaft 2 of the rotary disk 1, and the valve passage 3 is It is composed of a pressure fluid inlet 4 and a cylindrical valve chamber 5 formed in the plate 1 parallel to the rotation axis 2, and a cylindrical valve hole 7 formed in the valve seat 6 parallel to the rotation axis 2. A ball valve 8 is housed in the valve chamber 5 so as to be able to be moved into and out of the valve hole 7.
The diameter of the cylindrical valve hole 7, the diameter of the ball valve element 8, and the diameter of the valve chamber 5 are each sequentially increased.
In a valve device in which a corner is formed at the side end to serve as a fulcrum 7a for the ball valve 8 to ride on when switching between opening and closing, the center C1 of the valve hole 7 is located on the rotary disk 1 with respect to the center C2 of the valve chamber 5. The eccentricity E is shifted in the centrifugal direction D1. <Operation> In the above, since the center C1 of the valve hole 7 and the center C2 of the valve chamber 5 are eccentric E, the valve is in the open state (unseated state) in which the ball valve 8 in FIG. 1 rides on the fulcrum 7a. The angle (β1) formed by the line connecting the center 8a of the ball valve 8 and the fulcrum 7a is larger than the conventional angle (α1), and the height dimension L3 from the center 8a of the ball valve 8 to the seat surface 6c is is smaller than the conventional dimension L2, so the valve opening moment M2 acting on the ball valve 8 in the unseated state becomes smaller. When trying to seat (close the valve) the ball valve 8 in the unseated state as described above, the influence of the centrifugal force W2 is small, so it is easy to close the valve. In addition, the valve closing moment M1 due to the oil pressure P when the ball valve 8 is seated (valve closed) is determined by the weight of the ball valve 8 and the dimension L1 between the center 8a of the ball valve 8 and the periphery of the valve hole 7.
Since it is the same as the conventional one (see Fig. 4), the ease of opening the valve is the same. <Example> Hereinafter, an example in which the valve device of the present invention is applied to a bleed valve of a clutch piston is shown in Fig. 1, which is a sectional view of the ball valve in the unseated (opened) state, and Fig. 2, which is a sectional view of the ball valve in the seated state. (Valve closed) state To explain with a sectional view, a valve passage 3 is passed through the rotary disk 1 at a position away from the center of the rotation axis and parallel to the rotation axis, and the valve passage 3 is formed in the rotary disk 1. It is composed of a pressure fluid inlet 4, a cylindrical valve chamber 5, and a cylindrical valve hole 7 formed in a valve seat 6, and a ball valve 8 made of a steel ball is housed in the valve chamber 5 so as to be able to be moved into and out of the valve seat 6. The diameter of the valve hole 7, the diameter of the ball valve 8, and the diameter of the valve chamber 5 are each sequentially increased. Further, the valve chamber 5 of the cylindrical valve hole 7
As in the conventional case, a corner portion is formed at the side end portion to serve as a fulcrum 7a on which the ball valve 8 rests when switching between opening and closing. The center C1 of the valve hole 7 and the center C2 of the valve chamber 5 are slightly eccentric E so that the valve hole 7 is shifted in the centrifugal direction D1 of the rotary disk 1.
The width of the valve seat 6 from the periphery to the circumferential surface of the valve chamber 5 is such that the distal width 6a is the minimum and the centripetal width 6b is the maximum. The height L3 up to the seat surface 6c of No. 6 is smaller than the conventional height L2. In the above, when the pressure P of the pressure fluid (pressure oil) is zero, if the rotary disk 1 rotates above a predetermined value, the valve opening moment M due to the centrifugal force W2
At 2, the ball valve 8 rides on the fulcrum 7a on the periphery of the valve hole 7 and the valve hole 7 opens, and when the pressure P of the pressure fluid increases to a predetermined value or more, the valve closing moment M1 due to the valve closing force W1 causes the valve to open. The moment becomes larger than M2 and the ball valve element 8 closes the valve hole 7. Also, since the center C1 of the valve hole 7 and the center C2 of the valve chamber 5 are eccentric E, the ball valve 8 in the open state (unseated state) in which the ball valve 8 rides on the fulcrum 7a in FIG. The angle (β1) formed by the line connecting the center 8a of the ball valve 8 and the fulcrum 7a is larger than the conventional angle (α1), and the height dimension L3 from the center 8a of the ball valve 8 to the seat surface 6c is
is smaller than the conventional dimension L2, so the valve opening moment M2 acting on the ball valve 8 in the unseated state becomes smaller. When trying to seat (close the valve) the ball valve 8 in the unseated state as described above, the influence of the centrifugal force W2 is small, so it is easy to close the valve. In addition, the valve closing moment M1 due to the oil pressure P when the ball valve 8 is seated (valve closed) is determined by the weight of the ball valve 8 and the dimension L1 between the center 8a of the ball valve 8 and the periphery of the valve hole 7.
Since it is the same as the conventional one (see Fig. 4), the ease of opening the valve is the same. It should be noted that the present invention is not limited to the above embodiments, and it goes without saying that many modifications and changes can be made to the above embodiments within the scope of the present invention. <Effects of the Invention> As is clear from the above explanation, according to the present invention, the center of the valve hole and the center of the valve chamber are eccentric, so that when the ball valve runs onto the fulcrum of the cylindrical valve hole, the opening is prevented. The angle formed by the line connecting the center of the ball valve and the fulcrum in the valve state (unseated state) is larger than the conventional angle, and the height dimension from the center of the ball valve to the seat surface is smaller than the conventional dimension. Therefore, the valve opening moment acting on the ball valve in the unseated state becomes smaller. In this way, when attempting to seat (close) the ball valve in the unseated state, the effect of centrifugal force is small, making it easier to close the valve. In addition, the valve closing moment due to hydraulic pressure when the ball valve is seated (valve closed) is the same as the weight of the ball valve and the dimensions from the center of the ball valve to the periphery of the valve hole are the same as conventional ones. They are the same in terms of ease of speaking. Moreover, by forming the valve hole parallel to the rotation axis, the ball valve can be opened by simply shifting the valve hole slightly, while maintaining the ease of hole machining as before. Valve moment can be reduced. Therefore, similar to the conventional method, there are excellent effects such as ease of processing and high workability.
第１図は本発明弁装置をクラツチピストンのブ
リードバルブに適用した実施例の球弁子の離座
（開弁）状態断面図、第２図は同じく球弁子の着
座（閉弁）状態断面図、第３図は従来のクラツチ
ピストンのブリードバルブの球弁子離座状態断面
図、第４図は同じく球弁子の着座状態断面図、第
５図は同じく回転盤および回転軸の断面図であ
る。
１……回転盤、２……回転軸、３……弁通路、
４……圧力流体入口、５……弁室、６……弁シー
ト、７……弁孔、８……球弁子、８ａ……その中
心、Ｄ１……遠心方向、Ｅ……偏心量、６ａ……
遠心側巾、６ｂ……求心側巾、６ｃ……座面、Ｌ
３……高さ寸法。
Fig. 1 is a sectional view of a ball valve in an unseated (open) state, and Fig. 2 is a sectional view of a ball valve in a seated (closed) state, in an embodiment in which the valve device of the present invention is applied to a bleed valve of a clutch piston. Figure 3 is a cross-sectional view of the ball valve of a conventional clutch piston bleed valve in the unseated state, Figure 4 is a cross-sectional view of the ball valve in the seated state, and Figure 5 is a cross-sectional view of the rotary disk and rotating shaft. It is. 1... Rotating disk, 2... Rotating shaft, 3... Valve passage,
4... Pressure fluid inlet, 5... Valve chamber, 6... Valve seat, 7... Valve hole, 8... Ball valve, 8a... Center thereof, D1... Centrifugal direction, E... Eccentricity, 6a...
Distal side width, 6b... Centripetal side width, 6c... Seat surface, L
3... Height dimension.
Claims (1)
路が貫通され、該弁通路は、回転盤に前記回転軸
と平行に形成された圧力流体入口および円筒形弁
室と、弁シートに前記回転軸と平行に形成された
円筒形弁孔とから構成され、前記弁室には球弁子
が離着座自在に収納され、前記弁孔の径、球弁子
の径および弁室の径はそれぞれ順次大きく形成さ
れ、前記円筒形弁孔の弁室側端部に、開閉切換時
に球弁子の乗り上げ支点となる角部が形成された
弁装置において、前記弁孔は、その中心が弁室の
中心に対して回転盤の遠心方向へずれるよう偏心
されたことを特徴とする回転盤に装着される弁装
置。1. A valve passage is penetrated at a position away from the center of the rotation axis of the rotary disk, and the valve passage includes a pressure fluid inlet and a cylindrical valve chamber formed in the rotary disk parallel to the rotation axis, and a cylindrical valve chamber formed in the valve seat. It is composed of a cylindrical valve hole formed parallel to the rotation axis, and a ball valve is housed in the valve chamber so that it can be moved into and out of the valve chamber, and the diameter of the valve hole, the diameter of the ball valve, and the diameter of the valve chamber are In the valve device, each of the cylindrical valve holes is formed to be larger in size, and a corner portion is formed at the end of the valve chamber side of the cylindrical valve hole to serve as a fulcrum on which the ball valve rests when switching between opening and closing. A valve device mounted on a rotary disk, characterized in that the valve device is eccentrically offset from the center of the rotary disk in a centrifugal direction of the rotary disk.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61300301A JPS63152730A (en) | 1986-12-16 | 1986-12-16 | Valve device mounted to rotary disk |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61300301A JPS63152730A (en) | 1986-12-16 | 1986-12-16 | Valve device mounted to rotary disk |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS63152730A JPS63152730A (en) | 1988-06-25 |
| JPH0587693B2 true JPH0587693B2 (en) | 1993-12-17 |
Family
ID=17883135
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP61300301A Granted JPS63152730A (en) | 1986-12-16 | 1986-12-16 | Valve device mounted to rotary disk |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS63152730A (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2535379Y2 (en) * | 1990-08-08 | 1997-05-14 | 株式会社富士鉄工所 | Clutch piston |
| JP5501314B2 (en) * | 2011-09-06 | 2014-05-21 | 本田技研工業株式会社 | Lubricating structure of planetary gear mechanism |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60157520A (en) * | 1984-01-28 | 1985-08-17 | Mitsubishi Motors Corp | Hydraulic clutch device |
-
1986
- 1986-12-16 JP JP61300301A patent/JPS63152730A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS63152730A (en) | 1988-06-25 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4458797A (en) | Control for rotating clutch | |
| JPH01279136A (en) | Anti-spin differential | |
| US4184573A (en) | Double-acting disc brake having floating cylinder head | |
| US6183387B1 (en) | Variable pressure relief system for hydraulically actuated limited slip differentials | |
| JPS62216829A (en) | Changeover device for multidisk clutch for locking gear box differential gear in order to drive two axle for automobile | |
| US3905253A (en) | Transmission assembly | |
| JPH0587693B2 (en) | ||
| JPH01220728A (en) | Drive force transmission | |
| JPS6025663B2 (en) | Automatic transmission for vehicles | |
| US4493404A (en) | Hydraulic gerotor motor and parking brake for use therein | |
| JP6437037B2 (en) | Actuator and fluid pressure control circuit having the same | |
| JPS6231671B2 (en) | ||
| JPS6124753Y2 (en) | ||
| US3633595A (en) | Hydraulic governor | |
| JP3368185B2 (en) | Supply structure of pressure oil to clutch drum in transmission | |
| JPH0453461Y2 (en) | ||
| JP3427459B2 (en) | Transmission control device for friction wheel type continuously variable transmission | |
| JPH0717859Y2 (en) | Four-wheel drive transmission | |
| JPS5933052Y2 (en) | Fluid governor pressure generator | |
| JPH04314938A (en) | Exhaust brake valve | |
| JPS60157520A (en) | Hydraulic clutch device | |
| JP2815755B2 (en) | Hydraulic power transmission coupling | |
| JPH04125344A (en) | Automatic transmission | |
| JPS61290237A (en) | Viscous coupling device | |
| JPS61197843A (en) | Differential gears |