JPS60256629A - Hydraulic clutch cylinder control device - Google Patents
Hydraulic clutch cylinder control deviceInfo
- Publication number
- JPS60256629A JPS60256629A JP59112812A JP11281284A JPS60256629A JP S60256629 A JPS60256629 A JP S60256629A JP 59112812 A JP59112812 A JP 59112812A JP 11281284 A JP11281284 A JP 11281284A JP S60256629 A JPS60256629 A JP S60256629A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- clutch
- relief valve
- valve
- electromagnetic proportional
- 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
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
- F16D48/00—External control of clutches
- F16D48/06—Control by electric or electronic means, e.g. of fluid pressure
- F16D48/066—Control of fluid pressure, e.g. using an accumulator
-
- 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
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/30—Signal inputs
- F16D2500/306—Signal inputs from the engine
- F16D2500/3067—Speed of the engine
-
- 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
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/30—Signal inputs
- F16D2500/31—Signal inputs from the vehicle
- F16D2500/3108—Vehicle speed
-
- 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
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/50—Problem to be solved by the control system
- F16D2500/502—Relating the clutch
- F16D2500/50236—Adaptations of the clutch characteristics, e.g. curve clutch capacity torque - clutch actuator displacement
-
- 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
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/50—Problem to be solved by the control system
- F16D2500/502—Relating the clutch
- F16D2500/50239—Soft clutch engagement
-
- 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
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/70—Details about the implementation of the control system
- F16D2500/702—Look-up tables
- F16D2500/70205—Clutch actuator
- F16D2500/70217—Pressure
-
- 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
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/70—Details about the implementation of the control system
- F16D2500/704—Output parameters from the control unit; Target parameters to be controlled
- F16D2500/70402—Actuator parameters
- F16D2500/70406—Pressure
-
- 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
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/70—Details about the implementation of the control system
- F16D2500/704—Output parameters from the control unit; Target parameters to be controlled
- F16D2500/70402—Actuator parameters
- F16D2500/7041—Position
-
- 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
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/70—Details about the implementation of the control system
- F16D2500/706—Strategy of control
- F16D2500/70663—State analysis; Analysing potential states of the machine and developing control strategies at each state
Landscapes
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は主に車両のパワーシフト方式のトランスミッシ
ョンの変速用液圧クラッチを制御す。DETAILED DESCRIPTION OF THE INVENTION The present invention mainly controls a hydraulic clutch for shifting of a power shift type transmission of a vehicle.
る液圧制御装置に関するものである。This invention relates to a hydraulic pressure control device.
この種の従来装置は、例えば第1図に示すように圧力制
御機構(1)で圧力を制限されたポンプ(2)からの圧
液をうける方向切換弁(3)により、トランスミツ7ヨ
ンの複数個の歯車列に設けられた液圧クラッチ(4)、
(5)l (6)のうち、例えばクラッチオフのクラ
ッチ(4)のクラッチシリンダ(力にポンプ圧液を導く
と共に1クラツチオンのクラッチ(6)のクラッチシリ
ンダ(8)をタンク(9)に連通ずる。これによシフラ
ッチ(4ンはクラッチシリンダ(7)に充填された圧液
によってクラッチオンとなり、クラッチ(6)はクラッ
チシリンダ(8)の圧力が第2図に破線で示す如く低下
することによシクラッチオ7となる。For example, as shown in Fig. 1, this type of conventional device uses a directional control valve (3) that receives pressurized liquid from a pump (2) whose pressure is limited by a pressure control mechanism (1) to control the transmission. a hydraulic clutch (4) provided in a plurality of gear trains;
(5) l Among (6), for example, the pump pressure fluid is introduced into the clutch cylinder (force) of the clutch (4) when the clutch is off, and the clutch cylinder (8) of the clutch (6) when the clutch is on is connected to the tank (9). As a result, the shift latch (4) is turned on by the pressure fluid filled in the clutch cylinder (7), and the pressure in the clutch cylinder (8) of the clutch (6) decreases as shown by the broken line in Figure 2. It becomes Yosikura Chio 7.
前記圧力制御機構(1)はリリーフ弁(l■とその設定
圧を定めるばねaυのばね力を調整するシリンダQ2+
とチェック弁付き絞り+131からなり、次のように作
動する。空のクラッチシリンダ、例えばクラッチシリン
ダ(7)への圧液充填時においては、供給液圧がクラッ
チシリンダ(力への圧液充填抵抗に応じた低い圧力とな
るため、シリンダ(12)のヘッド室(14)の圧液は
ばね(1つ、 (lυに押されてチェック弁(161を
通シ流路αηへ排出され、リリーフ弁(IIの設定圧は
伸張したばねαυにょシ低下する。クラッチシリンダ(
力への圧液充填が終ると、クラッチ(4)は第2図に示
すようにクラッチ接続開始となり、供給圧液はごく少量
で足多るため、ポンプ(2)よりの圧液の大部分はリリ
ーフ弁(10)ヲ通ってトルクコンバータα9、クーラ
(イ)、潤滑液分配器C91)を経てタンク(9)へ還
流する。このため供給液圧はIJ IJ−7弁00)で
設定される圧力となるが、これと同時に圧液の一部は絞
りa81を経てヘッド室a41へ流入しばねαυを圧縮
していきリリーフ弁QO)の設定圧は漸増する。これに
より供給液圧は上昇しクラッチ(4)を接続した後もさ
らに上昇してヘッド室04)が最大容量に達するとヘッ
ド室0/Dへの圧液流人は停止してIJ IJ−フ弁(
10)は最大設定圧となる。The pressure control mechanism (1) includes a relief valve (l) and a cylinder Q2+ that adjusts the spring force of a spring aυ that determines its set pressure.
It consists of a throttle with a check valve +131, and operates as follows. When an empty clutch cylinder, for example, the clutch cylinder (7), is filled with pressure fluid, the supply fluid pressure becomes a low pressure corresponding to the pressure fluid filling resistance to the clutch cylinder (force), so the head chamber of the cylinder (12) The pressure fluid in (14) is pushed by the spring (lυ) and is discharged through the check valve (161) to the flow path αη, and the set pressure of the relief valve (II is lowered by the extended spring αυ. Cylinder(
When the filling of pressure fluid to the pump is completed, the clutch (4) starts to engage as shown in Figure 2, and since the supply pressure fluid is very small and there is a lot, most of the pressure fluid from the pump (2) is used. It passes through the relief valve (10), the torque converter α9, the cooler (a), and the lubricant distributor C91), and then flows back to the tank (9). Therefore, the supply liquid pressure becomes the pressure set by the IJ IJ-7 valve 00), but at the same time, a part of the pressure liquid flows into the head chamber a41 through the throttle a81 and compresses the spring αυ, causing the relief valve to flow into the head chamber a41. The set pressure of QO) gradually increases. As a result, the supply fluid pressure rises, and even after the clutch (4) is connected, it further rises and when the head chamber 04) reaches its maximum capacity, the flow of pressure fluid to the head chambers 0/D is stopped and the IJ valve(
10) is the maximum set pressure.
同、(2つはトルクコンバータa9への流入圧を制限す
る低圧IJ IJ−)弁である。Similarly, there are two low pressure IJ and IJ- valves that limit the inflow pressure to the torque converter a9.
前記するような従来装置では、クラッチシリ、 ′ダ″
17)EE液充填完了がらj5’/f接続完了までの間
(以下クラッチ接続時という)のクラッチシリンダ液圧
の昇圧力ーブは、この液圧制御装置の液圧回路の構造か
ら一義的に決まシ、例えば第2図に1点鎖線で示すよう
な昇圧力ーブとなる。ところが、昇圧力ーブの最適カー
ブは各速度段のクラッチ容量の違い、クラッチのシフト
アップとシフトダウンによる違い、車両速度及びトラン
スミッションを駆動するエンジンの回転速度の違い等に
よって異なるため、常傾最適昇圧力ーブを得ることが困
難となり、変速に時間がかかるとか、変速時に運転者に
ショックを与えるといった不具合が生じる。In the conventional device as mentioned above, the clutch cylinder, 'da'
17) The increasing force curve of the clutch cylinder hydraulic pressure from the completion of EE fluid filling to the completion of j5'/f connection (hereinafter referred to as clutch connection) is uniquely determined by the structure of the hydraulic pressure circuit of this hydraulic pressure control device. For example, the boost pressure curve will be as shown by the dashed line in FIG. 2. However, the optimal curve for the boost pressure curve differs depending on factors such as differences in clutch capacity for each speed stage, differences in clutch upshifts and downshifts, and differences in vehicle speed and rotational speed of the engine that drives the transmission. It becomes difficult to obtain a boost pressure curve, resulting in problems such as a time-consuming shift and a shock to the driver when shifting.
本発明は比較的簡潔な手段によりスムーズに且つ速やか
に変速し得る液圧クラッチシリンダ制御装置を提供する
ことを目的としている。SUMMARY OF THE INVENTION An object of the present invention is to provide a hydraulic clutch cylinder control device that can smoothly and quickly change gears using relatively simple means.
本発明に係る液圧クラッチ7リング制御装置は、前記目
的を達成するために、複数個のクラッチ/リンダをポン
プ及びタンクに選択的に接続する方向切換弁とポンプと
の間に、車両の運転状態よりクラッチ接続時におけるク
ラソチシ1)71−よ工。□7エ、−7,□。オ6、。In order to achieve the above object, the hydraulic clutch 7-ring control device according to the present invention provides a control device for driving a vehicle between a directional control valve that selectively connects a plurality of clutches/cylinders to a pump and a tank, and a pump. Based on the condition, the clamping force when the clutch is connected is 1) 71-Yo. □7E, -7, □. O6.
)・1□電気制御器とこの電気制御器からの指令信号
により設定圧を制御される電磁リリーフ弁からなる圧力
制御機構を配設するものである。)・1□ A pressure control mechanism consisting of an electric controller and an electromagnetic relief valve whose set pressure is controlled by a command signal from the electric controller is provided.
以下本発明を図面に示す実施例に基いて説明する。第6
図において、方向切換弁(3)はクラッチ(4)、 (
5)、 +6)のクラッチ/リンダ(力、 (2L ’
(8)をポンプ(2)とタンク(9)に選択的に接続せ
しめるものであり、余剰液は圧力制御機構(25+から
トルクコンバータα1、クーラ(至)、潤滑液分配器0
1)を経てタンク(9)へ還流させている。以上の構成
は第1図に示す従来装置と同じである。The present invention will be explained below based on embodiments shown in the drawings. 6th
In the figure, the directional control valve (3) is connected to the clutch (4), (
5), +6) clutch/linda (force, (2L'
(8) is selectively connected to the pump (2) and tank (9), and the excess liquid is transferred to the pressure control mechanism (from 25+ to torque converter α1, cooler (to), lubricating liquid distributor 0
1) and is refluxed to the tank (9). The above configuration is the same as the conventional device shown in FIG.
本発明においては、ポンプ液圧を制限する圧力制御機構
(25)は電磁比例リリーフ弁(26)と電気制御器0
7)とで構成している。In the present invention, the pressure control mechanism (25) that limits the pump hydraulic pressure includes an electromagnetic proportional relief valve (26) and an electric controller 0.
7).
電磁比例IJ IJ−フ弁G61の設定圧は電気制御器
(27)からの指令信号によシ設定される。電気制御器
(27)は車両速度、トランスミッションをlE動fる
エンジンの回転数、方向切換弁(3)の/7ト位置等を
検出するセンサよシの信号をうけて車両の運転状態を演
算し、この車両運転状態よりめたクラッチ接続時におけ
るクラッチシリンダ液圧の最適昇圧力ーブを電磁比例リ
リーフ弁に出力するもので、第4図に示すように車両運
転状態に応じて種々の最適昇圧力ーブI、n、 m・・
・が得られる。The set pressure of the electromagnetic proportional IJ IJ valve G61 is set by a command signal from the electric controller (27). The electric controller (27) calculates the operating state of the vehicle by receiving signals from a sensor that detects the vehicle speed, the rotational speed of the engine that operates the transmission, the /7 position of the directional control valve (3), etc. The optimum increase force curve for the clutch cylinder hydraulic pressure when the clutch is engaged is determined based on the vehicle operating condition and is output to the electromagnetic proportional relief valve. Boost force curve I, n, m...
・is obtained.
前記するような構成において、例えば液圧クラッチ(4
)、 +5)のクラッチ/リンダ(力、(2秒がタンク
(9)と連通し、液圧クラッチ(6)のクラッチシリン
ダ(8)がポンプ(2)と連通している状態から、方向
切換弁(3)を切換えて液圧クラッチ(4)のクラッチ
シリンダ(力をポンプ(2)に連通し液圧クラッチ(6
)のクラッチ/リンダ(8)をタンク(9)に連通した
とすれば、液圧クラッチ(6)はクラッチオフとなシ、
いままで空であったクラッチシリンダ(力にポンプ(2
)からの圧液が流入する。この場合、方向切換弁(3)
の/フト位置を検出するセンサよシの変速切換信号をう
けた電気制御器(27)は電磁比例リリーフ弁(26)
をクラッチ/す/ダ(力への圧液充填抵抗に応じた低い
圧力に設定する。In the configuration described above, for example, a hydraulic clutch (4
), +5) clutch/cylinder (force, (2 seconds) is in communication with the tank (9) and the clutch cylinder (8) of the hydraulic clutch (6) is in communication with the pump (2), then the direction change By switching the valve (3), the clutch cylinder (force) of the hydraulic clutch (4) is communicated to the pump (2) and the hydraulic clutch (6
)'s clutch/cylinder (8) is connected to the tank (9), the hydraulic clutch (6) will not be clutch-off,
Until now, the empty clutch cylinder (pump (2)
) flows in. In this case, the directional valve (3)
The electric controller (27) that receives the shift change signal from the sensor that detects the /foot position is an electromagnetic proportional relief valve (26).
Set the pressure to low according to the pressure fluid filling resistance to the clutch/su/da (force).
クラッチシリンダ(7)への圧液充填が終るとクラッチ
接続にはいb1クラッチシリンダ(力への圧液供給量は
ごく少量で足りるので、余剰液は電磁比例リリーフ弁(
26)からトルクコンバータa傷、クーラ(20)、潤
滑液分配器Cυを経てタンク(9)へ還流する。このク
ラッチ接続時においては、電気制御器(2′7)は車両
運転状態よ如求めたクラッチ接続時の最適昇圧力ーブに
より電磁比例リリーフ弁(26)の設定圧を制御するよ
うにしているので、電磁比例リリーフ弁(ハ)により制
限されたクラッチシリンダ液圧は車両運転状態に適した
昇圧となってクラッチを接続する。When the clutch cylinder (7) is filled with pressure fluid, the clutch is connected to the b1 clutch cylinder (a very small amount of pressure fluid is sufficient for the force), so excess fluid is removed by the electromagnetic proportional relief valve (
26), flows back to the tank (9) via the torque converter a, cooler (20), and lubricant distributor Cυ. When the clutch is connected, the electric controller (2'7) controls the set pressure of the electromagnetic proportional relief valve (26) based on the optimum boost pressure curve when the clutch is connected, which is determined based on the vehicle operating condition. Therefore, the clutch cylinder hydraulic pressure, which is limited by the electromagnetic proportional relief valve (c), increases to a pressure suitable for the vehicle operating condition and connects the clutch.
クラッチの接続が終ると、電磁比例IJ IJ−フ弁(
26)は最高設定圧まで昇圧してクラッチ接続を維持し
、余剰液は電磁比例IJ IJ−フ弁(26)を通シト
ルクコンバータ(ILクーラ(イ)、潤滑液分配器Qυ
を経てタンク(9)へ還流する。When the clutch is connected, the electromagnetic proportional IJ IJ valve (
26) is boosted to the maximum setting pressure to maintain clutch connection, and excess fluid is passed through the electromagnetic proportional IJ valve (26) to the torque converter (IL cooler (A), lubricating fluid distributor Qυ
The water is refluxed to the tank (9).
同、本実施例ではクラッチ切換時の液圧制御のタイミン
グは方向切換弁(3)のシフト位置を検出するセンサよ
シの変速切換信号をうけた電気9 制御器ア演算し、い
、ヵ1、方向切換弁(3)とし、例えば電磁切換弁の如
く電気指令信号によって作動するものを使用した場合に
は上記センサよりの信号の代りにこの電気指令信号を電
気制御器でうけるようにしてもよい。Similarly, in this embodiment, the timing of hydraulic pressure control at the time of clutch switching is calculated by the electric controller 9 which receives the gear shift signal from the sensor that detects the shift position of the directional control valve (3). If a directional switching valve (3) is used that is operated by an electrical command signal, such as an electromagnetic switching valve, the electrical command signal may be received by an electric controller instead of the signal from the sensor. good.
以上説明したように本発明においては、電磁比例リリー
フ弁と電気制御器からなる圧力制御機構によりクラッチ
接続時におけるクラッチシリングへの供給液圧を車両運
転状態に最適の昇圧力ーブで昇圧させるようにしている
ので、簡潔な構成により変速操作をスムーズに且つ速や
かに行うことができる。As explained above, in the present invention, the pressure control mechanism consisting of the electromagnetic proportional relief valve and the electric controller is used to increase the fluid pressure supplied to the clutch cylinder when the clutch is engaged using a boost pressure curve that is optimal for the vehicle operating condition. Therefore, the gear shifting operation can be performed smoothly and quickly with a simple configuration.
第1図は従来装置の液圧回路図、第2図は従来装置にお
けるポンプ液圧及びクラッチ/リンダ液圧の圧力変化を
示す図表、第6図は本発明の実施例を示す液圧回路図、
第4図は本発明装置におけるクラッチ接続時のクラッチ
/リンダ液圧の昇圧状態を示す図表である。
2 g y 7’・6”°方向切換弁・4・ 5・ 6
−bj′液圧クラッチ、7,8.28・・・クラッチシ
リン ′□ダ、25・・圧力制御機構、26・・・電磁
比例+717−7弁、27・・・電気制御器。
第1図
2
第2図
吟間t
第3図
第4図
特開 tFig. 1 is a hydraulic circuit diagram of a conventional device, Fig. 2 is a chart showing pressure changes of pump hydraulic pressure and clutch/cylinder hydraulic pressure in a conventional device, and Fig. 6 is a hydraulic circuit diagram showing an embodiment of the present invention. ,
FIG. 4 is a chart showing the increased state of the clutch/cylinder fluid pressure when the clutch is connected in the device of the present invention. 2 g y 7'/6" degree directional control valve/4/5/6
-bj'hydraulic clutch, 7,8.28...clutch cylinder '□da, 25...pressure control mechanism, 26...electromagnetic proportional +717-7 valve, 27...electric controller. Fig. 1 2 Fig. 2 Ginma t Fig. 3 Fig. 4 JP-A t
Claims (1)
に接続する方向切換弁とポンプとの間に、車両の運転状
態よりクラッチ接続時におけるり°ラッチシリンダ液圧
の昇圧力ーブを演算するための電気制御器とこの電気制
御器からの指令信号により設定圧を制御される・電磁比
例リリーフ弁からなる圧力制御機構を配設したことを特
徴とする液圧クラッチシリンダ制御装置。Between the pump and the directional control valve that selectively connects the plurality of clutch cylinders to the pump and the tank, there is a valve for calculating the increase pressure curve of the latch cylinder fluid pressure when the clutch is connected based on the driving condition of the vehicle. A hydraulic clutch cylinder control device comprising a pressure control mechanism consisting of an electric controller and an electromagnetic proportional relief valve whose set pressure is controlled by a command signal from the electric controller.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP59112812A JPS60256629A (en) | 1984-05-31 | 1984-05-31 | Hydraulic clutch cylinder control device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP59112812A JPS60256629A (en) | 1984-05-31 | 1984-05-31 | Hydraulic clutch cylinder control device |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS60256629A true JPS60256629A (en) | 1985-12-18 |
Family
ID=14596147
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP59112812A Pending JPS60256629A (en) | 1984-05-31 | 1984-05-31 | Hydraulic clutch cylinder control device |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS60256629A (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61136044A (en) * | 1984-12-04 | 1986-06-23 | Kubota Ltd | Method of operating hydraulic clutch in hydraulically operated speed change gear unit |
DE4337401C1 (en) * | 1993-10-26 | 1995-05-04 | Mannesmann Ag | Trolling device for a ship drive unit |
WO2001072586A1 (en) * | 2000-03-27 | 2001-10-04 | Reintjes Gmbh | Marine gear and a method for preventing a drop in motor speed when engaging a multi-plate clutch |
US6761600B2 (en) | 2000-03-27 | 2004-07-13 | Reintjes Gmbh | Marine gear and a method for preventing a drop in motor speed when engaging a multi-plate clutch |
-
1984
- 1984-05-31 JP JP59112812A patent/JPS60256629A/en active Pending
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61136044A (en) * | 1984-12-04 | 1986-06-23 | Kubota Ltd | Method of operating hydraulic clutch in hydraulically operated speed change gear unit |
DE4337401C1 (en) * | 1993-10-26 | 1995-05-04 | Mannesmann Ag | Trolling device for a ship drive unit |
WO2001072586A1 (en) * | 2000-03-27 | 2001-10-04 | Reintjes Gmbh | Marine gear and a method for preventing a drop in motor speed when engaging a multi-plate clutch |
US6761600B2 (en) | 2000-03-27 | 2004-07-13 | Reintjes Gmbh | Marine gear and a method for preventing a drop in motor speed when engaging a multi-plate clutch |
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