JPH02195074A - Hydraulic structure of vehicle - Google Patents
Hydraulic structure of vehicleInfo
- Publication number
- JPH02195074A JPH02195074A JP1367989A JP1367989A JPH02195074A JP H02195074 A JPH02195074 A JP H02195074A JP 1367989 A JP1367989 A JP 1367989A JP 1367989 A JP1367989 A JP 1367989A JP H02195074 A JPH02195074 A JP H02195074A
- Authority
- JP
- Japan
- Prior art keywords
- hydraulic
- oil
- hydraulic motor
- cam plate
- plate angle
- 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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/46—Automatic regulation in accordance with output requirements
- F16H61/478—Automatic regulation in accordance with output requirements for preventing overload, e.g. high pressure limitation
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2253—Controlling the travelling speed of vehicles, e.g. adjusting travelling speed according to implement loads, control of hydrostatic transmission
-
- 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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
- F16H61/423—Motor capacity control by fluid pressure control means
-
- 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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
- F16H61/433—Pump capacity control by fluid pressure control means
-
- 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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/46—Automatic regulation in accordance with output requirements
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Control Of Fluid Gearings (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は車輌の油圧構造に関し、詳しくは、可変容量型
の油圧ポンプと、この油圧ポンプか、ら供給される圧油
によって駆動される油圧モータとを備えて成る無段変速
装置の速度制御を行うための油圧構造に関するものであ
る。[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to a hydraulic structure for a vehicle, and more specifically, a variable displacement hydraulic pump and a hydraulic system driven by pressure oil supplied from the hydraulic pump. The present invention relates to a hydraulic structure for controlling the speed of a continuously variable transmission including a motor.
従来、上記の如く構成される無段変速装置の一例として
、静油圧式のものを挙げることができ、この静油圧式の
無段変速装置では実開昭６１１９１５８号公報等に示さ
れるように、角度変更自在な斜板を有する油圧ポンプと
、角度が固定された斜板を有する油圧モータとを備えて
構成され、その作動は、油圧ポンプの斜板を駆動回転す
ることにより、斜板によって操作される多数のピストン
からの圧油が油圧モータの多数のピストンに送り出され
、この結果、この油圧モータのピストンが一定の周期で
伸縮して油圧モータの斜板を回転させるよう構成され、
更に、油圧ポンプの斜板角の変更により油圧モータに取
出される回転速度を調節できるよう構成されている。Conventionally, as an example of a continuously variable transmission configured as described above, there is a hydrostatic type continuously variable transmission. It is composed of a hydraulic pump with a swash plate whose angle can be changed and a hydraulic motor with a swash plate whose angle is fixed.The swash plate is operated by driving and rotating the swash plate of the hydraulic pump. Pressure oil from a large number of pistons is delivered to a large number of pistons of a hydraulic motor, and as a result, the pistons of the hydraulic motor expand and contract at a constant cycle to rotate a swash plate of the hydraulic motor,
Furthermore, the rotational speed taken out by the hydraulic motor can be adjusted by changing the swash plate angle of the hydraulic pump.
ここで、前記静油圧式の無段変速装置を車輌の走行変速
系に用い、かつ、油圧モータの斜板角を高低二段に切換
えるものについて考えるに、この車輌を走行させている
状態において、油圧モータの斜板角を高速側から低速側
に切換えた場合には、以下のような不都合の発生が予想
される。Now, when considering a system in which the hydrostatic continuously variable transmission is used in a vehicle's traveling transmission system and the swash plate angle of the hydraulic motor is switched between high and low stages, when the vehicle is running, When the swash plate angle of the hydraulic motor is switched from the high speed side to the low speed side, the following problems are expected to occur.
即ち、前述のように斜板角を高速側から低速側に切換え
ると、この切換が行われたタイミングでの車輌の動慣性
力が、この油圧モータに作用することとなる。このこと
は斜板角を切換える直前の速度で油圧モータの出力軸を
回転させようとする力が走行系から作用することを意味
し、このように走行系からの作用で油圧モータの出力軸
が回転する際には、この回転数が許容回転数より増大し
、装置の破損に繋ることもある。That is, when the swash plate angle is switched from the high speed side to the low speed side as described above, the dynamic inertia of the vehicle at the timing when this switching is performed acts on the hydraulic motor. This means that the force that tries to rotate the output shaft of the hydraulic motor at the speed just before switching the swash plate angle is applied from the travel system, and in this way, the output shaft of the hydraulic motor is rotated by the action from the travel system. When rotating, the number of rotations may exceed the allowable number of rotations, which may lead to damage to the device.
詳述すると、前述のように外力によって油圧モータの出
力軸が増速方向に回転する場合においては、油圧モータ
が油圧ポンプのように機能して作動油を送り出すため、
油圧モータに連結する２つの油路の高圧側と低圧側とが
逆転するばかりで無く、２つの油路の間に設けられたリ
リーフ弁が開放する結果、乗用車におけるエンジンブレ
ーキの如き作用が期待できず、油圧ポンプが正常作動し
ていても、前述のように出力軸の増速を許してしまい、
装置の破損に繋ることも考えられていたのである。To be more specific, when the output shaft of the hydraulic motor is rotated in the speed increasing direction by an external force as described above, the hydraulic motor functions like a hydraulic pump and pumps out hydraulic oil.
Not only are the high-pressure side and low-pressure side of the two oil passages connected to the hydraulic motor reversed, but the relief valve installed between the two oil passages is opened, and as a result, an effect similar to engine braking in a passenger car can be expected. Even if the hydraulic pump is operating normally, it will allow the output shaft to speed up as described above.
It was thought that this could lead to damage to the equipment.
尚、油圧モータの許容回転数の上限は、単位時間内にお
けるピストンの作動ストローク量に基いて設定され、こ
の作動ストローク量が所定の値に達する際における回転
数が許容回転数に設定され、この許容回転数の上限は斜
板角を低速側に設定した場合と比較して、高速側に設定
した場合において大きい値となる。Note that the upper limit of the allowable rotation speed of the hydraulic motor is set based on the operating stroke amount of the piston within a unit time, and the rotation speed when this operating stroke amount reaches a predetermined value is set as the allowable rotation speed. The upper limit of the allowable rotation speed becomes a larger value when the swash plate angle is set on the high speed side compared to when the swash plate angle is set on the low speed side.
本発明の目的は、前記のように静油圧型に構成された無
段変速装置の油圧モー欠測の斜板角を高低二段に変更す
るための油圧操作系を合理的に構成すると共に、この操
作系による変速時に油圧モータに破損を生じ難い構造を
得る点にある。An object of the present invention is to rationally configure a hydraulic operation system for changing the swash plate angle of a hydraulic mode missing in a continuously variable transmission device configured as a hydrostatic type as described above into two stages, high and low. The object of the present invention is to obtain a structure in which damage to the hydraulic motor is less likely to occur when changing speeds using this operating system.
〔課題を解決するための手段］
本発明の特徴は可変容量型の油圧ポンプと、その斜板の
角度の変更によって駆動速度を高低二段に切換可能な油
圧モータとを備えて車輌の走行駆動系を構成すると共に
、圧油供給によって前記斜板の角度を高速側に設定し、
排油によって前記斜板の角度をバネの付勢力で低速側に
設定する油圧シリンダを備え、この油圧シリンダに対す
る油路に絞り機構を介装して成る点にあり、その作用、
及び、効果は次の通りである。[Means for Solving the Problems] The present invention is characterized in that it is equipped with a variable displacement hydraulic pump and a hydraulic motor whose drive speed can be switched between high and low speeds by changing the angle of its swash plate. configuring the system, and setting the angle of the swash plate to the high speed side by supplying pressure oil,
The present invention is comprised of a hydraulic cylinder that sets the angle of the swash plate to the low speed side by the biasing force of a spring using drained oil, and a throttling mechanism is interposed in the oil path for the hydraulic cylinder, and the operation thereof is as follows.
And the effects are as follows.
〔作 用］
上記特徴を例えば第１図に示すように構成すると、油圧
モータ（１７）の斜板角を高速側に設定して走行してい
る状態で、油圧モータ（１７）の斜板角を低速側に切換
えるため油圧シリンダ（２４）から排油を開始すると、
この排油が絞り機構（３６）によって抑制されるため、
油圧モータ（１７）の斜板はバネ（３４）の付勢により
、比較的低速で低速側に切換操作されることになり、車
輌が比較的高速で走行している状況下で、この切換操作
を行っても、この無段変速装置内の油路抵抗、あるいは
、走行伝動系の機械的抵抗の作用に起因する車速の減速
により、油圧モータ（１７）の出力軸（１７ａ）を許容
回転数より高めること無く、しかも、滑かに切換作動が
完了する。[Function] When the above characteristics are configured as shown in FIG. 1, for example, when the hydraulic motor (17) is traveling with the swash plate angle set to the high speed side, the swash plate angle of the hydraulic motor (17) When the oil starts draining from the hydraulic cylinder (24) in order to switch to the low speed side,
Since this drained oil is suppressed by the throttle mechanism (36),
The swash plate of the hydraulic motor (17) is operated to switch to the low speed side at a relatively low speed by the bias of the spring (34), and this switching operation is performed under the condition that the vehicle is traveling at a relatively high speed. Even if this is done, the output shaft (17a) of the hydraulic motor (17) will be rotated at the permissible rotation speed due to the deceleration of the vehicle speed due to the oil passage resistance in the continuously variable transmission or the mechanical resistance of the travel transmission system. The switching operation is completed smoothly without increasing the height.
従って、無段変速装置の油圧モータ側の斜板角を高低２
段に変更するための油圧操作系が合理的に構成されると
共に、車輌が比較的高速で走行している状況下で、この
油圧操作系によって変速を行っても油圧モータに破損を
生じ難い構造が得られたのである。Therefore, the swash plate angle on the hydraulic motor side of the continuously variable transmission is set to 2
The hydraulic operating system for changing gears is rationally constructed, and the hydraulic motor is unlikely to be damaged even if the hydraulic operating system is used to shift gears while the vehicle is running at relatively high speeds. was obtained.
尚、油圧モータの許容回転数の上限を斜板の角度に基い
て描くと、第２図のグラフのように表され、例えば、斜
板角を急速に高速位置（１１）から低速位置（Ｌ）に操
作すると、仮想線の矢印で示すように許容回転数の上限
を越える場合でも、破線の矢印で示すように許容回転数
以下に収めることが可能となる。If the upper limit of the permissible rotation speed of the hydraulic motor is drawn based on the angle of the swash plate, it will be expressed as shown in the graph in Figure 2. For example, the swash plate angle can be rapidly changed from the high speed position (11) to the low speed position (L ), even if the upper limit of the allowable rotational speed is exceeded as shown by the imaginary line arrow, it is possible to keep the rotational speed below the allowable rotational speed as shown by the broken line arrow.
〔実施例〕 以下、本発明の実施例を図面に基づいて説明する。〔Example〕 Embodiments of the present invention will be described below based on the drawings.
第３図に示すように、左右一対の駆動車輪（１）を有す
る前部車体（２）と、左右一対の駆動車輪（３）を有す
る後部車体（４）とを縦向き軸芯（Ｙ）周りで揺動自在
に連結し、前部、後部車体（２）。As shown in FIG. 3, a front body (2) having a pair of left and right drive wheels (1) and a rear body (4) having a pair of left and right drive wheels (3) are connected to a vertical axis (Y). The front and rear car bodies (2) are connected to each other so that they can swing freely.
（４）夫々の間にステアリングシリンダ（５）を設けて
走行車体を構成すると共に、前部車体（２）に、左右一
対のアーム（６）によって昇降自在に支持されるショベ
ル（７）、及び、これらを駆動するリフトシリンダ（８
）、チルトシリンダ（９）を設け、又、後部車体（４）
にエンジン（１０）、運転座席（１１）、ステアリング
ハンドル（１２）、前後の車輪（１） 、 （３）夫々
に動力を伝える駆動系を設けて車輌の一例としてのホイ
ールローダを構成する。(4) An excavator (7) which is supported by a pair of left and right arms (6) on the front body (2) so as to be movable up and down; , lift cylinders (8
), a tilt cylinder (9) is provided, and a rear body (4) is provided.
A wheel loader as an example of a vehicle is constructed by providing a drive system for transmitting power to an engine (10), a driver's seat (11), a steering handle (12), and front and rear wheels (1) and (3), respectively.
このホイールローダでは前記３種のシリンダ（５） 、
（８） 、 （９）夫々に対する油圧系、車輪（１）
、 （３）を駆動する油圧系が第１図のように構成さ
れている。In this wheel loader, the three types of cylinders (5),
(8), (9) Hydraulic system and wheels for each (1)
, (3) is constructed as shown in FIG.
つまり、この油圧系ではエンジン（１０）の動力で駆動
される可変容量の型の油圧ポンプ（１３）、作業ポンプ
（１４）、チャージポンプ（１５）を有し、可変容量型
の油圧ポンプ（１３）からの圧油は油路（１６） 、
（１６）を介して、斜板角を高低２段に切換え、かつ、
その出力軸（１７ａ）が走行系と連結する走行用の油圧
モータ（１７）に供給され、作業ポンプ（１４）からの
圧油は前記ステアリングシリンダ（５）に対する制御弁
（１８）、チルトシリンダ（９）に対する制御弁（１９
）、リフトシリンダ（８）、（８）に対する制御弁（２
０）夫々に供給され、チャージポンプ（１５）からの圧
油の一部は、可変容量型の油圧ポンプ（１３）の容量を
調節するサーボシリンダ（２１）に対する電磁弁（２２
）に送られ、又、走行駆動用の前記油路（１６） 、
（１６）に対してチャージ用として送られ、又、残りの
一部は、切換弁（２３）を介して前記油圧モータ（１７
）の斜板角を切換える油圧シリンダ（２４）、及び、走
行系に介装されたネガティブブレーキ（２５）夫々に供
給される。In other words, this hydraulic system includes a variable displacement hydraulic pump (13), a work pump (14), and a charge pump (15) driven by the power of the engine (10). ) from the oil passage (16),
(16), the swash plate angle is switched to two high and low steps, and
Its output shaft (17a) is supplied to a travel hydraulic motor (17) connected to the travel system, and pressure oil from the work pump (14) is supplied to the control valve (18) for the steering cylinder (5) and the tilt cylinder ( control valve (19) for
), control valves (2) for lift cylinders (8), (8)
0), and a part of the pressure oil from the charge pump (15) is supplied to the solenoid valve (22) for the servo cylinder (21) that adjusts the capacity of the variable displacement hydraulic pump (13).
), and the oil passage (16) for traveling drive;
(16) for charging, and the remaining part is sent to the hydraulic motor (17) via a switching valve (23).
) and a negative brake (25) installed in the travel system.
尚、このネガティブブレーキ（２５）はチャージポンプ
（１５）からの圧力が作用することで制動状態を解除す
るよう動作し、エンジン（１０）の停止時には必ず走行
系に制動力を作用させるように構成され、又、走行時に
はフートペダル（２６）の操作によっても制動できるよ
う独立した管路（２７）も形成されている。The negative brake (25) operates to release the braking state when pressure from the charge pump (15) is applied, and is configured to always apply braking force to the drive system when the engine (10) is stopped. Furthermore, an independent conduit (27) is also formed so that braking can be performed by operating a foot pedal (26) when the vehicle is running.
又、このホイールローダでは前記油圧ポンプ（１３）と
油圧モータ（１７）とで成る系を無段変速装置（Ａ）と
称し、前記ステアリングハンドル（１２）の側部に設け
たレバー型の操作具（２８）によって前後進いずれが一
方の走行方向を選択できるよう、この操作具（２８）と
連係するスイッチ（２９）からの信号が、前記電磁弁（
２２）を制御する制御装置（３０）に入力される。In addition, in this wheel loader, the system consisting of the hydraulic pump (13) and the hydraulic motor (17) is called a continuously variable transmission (A), and a lever-type operating tool is provided on the side of the steering handle (12). A signal from a switch (29) associated with this operating tool (28) is transmitted to the electromagnetic valve (
22) is input to a control device (30) that controls the control device (22).
尚、サーボシリンダ（２１）の作動量がエンジン（１０
）の回転数の増大に伴って大きくなるよう、チャージポ
ンプ（１５）からの圧油は、オリフィス（３１）によっ
て分圧した２系統の圧油路（３２） 、 （３２）を介
して電磁弁（２２）に送られ、エンジン（１０）の回転
数の変更による差圧の値と、サーボシリンダ（２１）に
内装された中立バネ（３３）とがバランスする位置まで
サーボシリンダ（２１）を作動させるようになっている
。It should be noted that the operating amount of the servo cylinder (21) is the same as that of the engine (10
) The pressure oil from the charge pump (15) is transferred to the solenoid valve via two pressure oil lines (32) and (32) divided by the orifice (31) so that the pressure increases as the rotation speed of the charge pump (15) increases. (22) and operates the servo cylinder (21) to a position where the value of the differential pressure caused by changing the rotation speed of the engine (10) and the neutral spring (33) built into the servo cylinder (21) are balanced. It is designed to let you do so.
更に、前記油圧シリンダ（２４）は圧油供給により油圧
モータ（１７）の斜板（図示せず）の角度を高速側に設
定し、排油時にはバネ（３４）の付勢力により斜板の角
度を低速側に設定するよう構成され、この油圧シリンダ
（２４）に対する油路（３５）には絞り機構（３６）が
介装され、斜板角の急峻な切換が抑制されるようになっ
ている。Further, the hydraulic cylinder (24) sets the angle of the swash plate (not shown) of the hydraulic motor (17) to the high speed side by supplying pressure oil, and when draining oil, the angle of the swash plate is adjusted by the biasing force of the spring (34). is configured to be set to a low speed side, and a throttle mechanism (36) is interposed in the oil passage (35) for this hydraulic cylinder (24) to suppress steep switching of the swash plate angle. .
因みに、前記切換弁（２３）は高速位置（Ｈ）、低速位
置（Ｌ）、駐車位置（Ｐ）の３位置に設定可能である。Incidentally, the switching valve (23) can be set to three positions: a high speed position (H), a low speed position (L), and a parking position (P).
本発明は上記実施例以外に例えば、切換弁の操作スプー
ルとランド部との間に狭小化した油路を形成して絞り機
構に用いることが可能であり、又、排油時にのみ絞り機
構が作用するよう絞り機構と並列してチエツク弁を介装
することも可能である。In addition to the embodiments described above, the present invention can also be used as a throttling mechanism by forming a narrowed oil passage between the operating spool and the land of a switching valve, and the throttling mechanism can be used only when draining oil. It is also possible to insert a check valve in parallel with the throttling mechanism for operation.
尚、特許請求の範囲の項に図面との対照を便利にする為
に符号を記すが、該記入により本発明は添付図面の構造
に限定されるものではない。Incidentally, although reference numerals are written in the claims section for convenient comparison with the drawings, the present invention is not limited to the structure shown in the accompanying drawings.
図面は本発明に係る車輌の油圧構造の実施例を示し、第
１図は該構造を表す油圧回路図、第２図は油圧モータの
許容回転数を表すグラフ、第３図はホイールローダの全
体側面図である。
（１３）・・・・・・油圧ポンプ、（１７）・・・・・
・油圧モータ、（２４）・・・・・・油圧シリンダ、（
３５）・・・・・・油路、（３６）・・・・・・絞り機
構。The drawings show an embodiment of the hydraulic structure of a vehicle according to the present invention, FIG. 1 is a hydraulic circuit diagram showing the structure, FIG. 2 is a graph showing the allowable rotation speed of the hydraulic motor, and FIG. 3 is an overall diagram of the wheel loader. FIG. (13)...Hydraulic pump, (17)...
・Hydraulic motor, (24)...Hydraulic cylinder, (
35)... Oil passage, (36)... Throttle mechanism.
Claims (1)
の変更によって駆動速度を高低二段に切換可能な油圧モ
ータ（１７）とを備えて車輌の走行駆動系を構成すると
共に、圧油供給によって前記斜板の角度を高速側に設定
し、排油によって前記斜板の角度をバネ（３４）の付勢
力で低速側に設定する油圧シリンダ（２４）を備え、こ
の油圧シリンダ（２４）に対する油路（３５）に絞り機
構（３６）を介装して成る車輌の油圧構造。The travel drive system of the vehicle is comprised of a variable displacement hydraulic pump (13) and a hydraulic motor (17) whose drive speed can be switched between high and low speeds by changing the angle of its swash plate. A hydraulic cylinder (24) is provided, which sets the angle of the swash plate to the high speed side by supplying oil, and sets the angle of the swash plate to the low speed side by the biasing force of a spring (34) by draining oil, the hydraulic cylinder (24) A vehicle hydraulic structure in which a throttle mechanism (36) is interposed in an oil passage (35) for a vehicle.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1367989A JPH02195074A (en) | 1989-01-23 | 1989-01-23 | Hydraulic structure of vehicle |
| CA 2008280 CA2008280C (en) | 1989-01-23 | 1990-01-22 | Hydraulic propelling apparatus for a vehicle |
| DE19904001888 DE4001888A1 (en) | 1989-01-23 | 1990-01-23 | Hydrostatic transmission for tractor - incorporates swash plate position switching mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1367989A JPH02195074A (en) | 1989-01-23 | 1989-01-23 | Hydraulic structure of vehicle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH02195074A true JPH02195074A (en) | 1990-08-01 |
Family
ID=11839873
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1367989A Pending JPH02195074A (en) | 1989-01-23 | 1989-01-23 | Hydraulic structure of vehicle |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPH02195074A (en) |
| CA (1) | CA2008280C (en) |
| DE (1) | DE4001888A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19620665C1 (en) | 1996-05-22 | 1997-06-12 | Brueninghaus Hydromatik Gmbh | Hydraulic control system for dredger slewing gear |
| DE19625393A1 (en) * | 1996-05-22 | 1998-01-02 | Brueninghaus Hydromatik Gmbh | Slewing gear control with double-sided braking |
| CN115324150B (en) * | 2022-08-25 | 2023-09-05 | 江苏徐工工程机械研究院有限公司 | Control method of backhoe loader and backhoe loader |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6245401B2 (en) * | 1982-01-28 | 1987-09-26 | Hideo Nakagawa | |
| JPS63235134A (en) * | 1987-03-23 | 1988-09-30 | Yutani Heavy Ind Ltd | Travelling speed changeover device of hydraulic travelling vehicle |
| JPS63235135A (en) * | 1987-03-23 | 1988-09-30 | Yutani Heavy Ind Ltd | Travelling speed changeover device of hydraulic travelling vehicle |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1528473B2 (en) * | 1966-02-11 | 1974-10-17 | Linde Ag, 6200 Wiesbaden | Setting device for an adjustable hydraulic motor |
| DE2422480A1 (en) * | 1974-05-09 | 1975-11-13 | Kloeckner Humboldt Deutz Ag | Hydrostatic vehicle transmission system - has control system damper throttle bypassed by valve at low pressure |
| JPS57107666U (en) * | 1980-12-24 | 1982-07-02 |
-
1989
- 1989-01-23 JP JP1367989A patent/JPH02195074A/en active Pending
-
1990
- 1990-01-22 CA CA 2008280 patent/CA2008280C/en not_active Expired - Fee Related
- 1990-01-23 DE DE19904001888 patent/DE4001888A1/en active Granted
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6245401B2 (en) * | 1982-01-28 | 1987-09-26 | Hideo Nakagawa | |
| JPS63235134A (en) * | 1987-03-23 | 1988-09-30 | Yutani Heavy Ind Ltd | Travelling speed changeover device of hydraulic travelling vehicle |
| JPS63235135A (en) * | 1987-03-23 | 1988-09-30 | Yutani Heavy Ind Ltd | Travelling speed changeover device of hydraulic travelling vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| CA2008280A1 (en) | 1990-07-23 |
| DE4001888C2 (en) | 1993-09-02 |
| DE4001888A1 (en) | 1990-08-02 |
| CA2008280C (en) | 1993-09-21 |
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