JPH0347423B2 - - Google Patents
Info
- Publication number
- JPH0347423B2 JPH0347423B2 JP58081641A JP8164183A JPH0347423B2 JP H0347423 B2 JPH0347423 B2 JP H0347423B2 JP 58081641 A JP58081641 A JP 58081641A JP 8164183 A JP8164183 A JP 8164183A JP H0347423 B2 JPH0347423 B2 JP H0347423B2
- Authority
- JP
- Japan
- Prior art keywords
- prime mover
- hydraulic pump
- rotation speed
- engine
- throttle lever
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D29/00—Controlling engines, such controlling being peculiar to the devices driven thereby, the devices being other than parts or accessories essential to engine operation, e.g. controlling of engines by signals external thereto
- F02D29/04—Controlling engines, such controlling being peculiar to the devices driven thereby, the devices being other than parts or accessories essential to engine operation, e.g. controlling of engines by signals external thereto peculiar to engines driving pumps
-
- 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
- E02F9/2246—Control of prime movers, e.g. depending on the hydraulic load of work tools
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Control Of Vehicle Engines Or Engines For Specific Uses (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Description
【発明の詳細な説明】
本発明は原動機の燃料噴射ポンプのガバナ作動
領域の設定の如何にかかわらず原動機の過回転を
防止する原動機のオーバーラン防止装置に関す
る。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an overrun prevention device for a prime mover that prevents overspeeding of the prime mover regardless of the setting of the governor operating range of the fuel injection pump of the prime mover.
従来、原動機で駆動される可変容量形油圧ポン
プを油圧アクチユエータと閉回路に接続する油圧
駆動回路システムが提案されている。この油圧回
路を、たとえば油圧シヨベルの駆動回路に適用す
ると、ブーム下げ時、旋回ブレーキ時あるいは坂
道の降坂時にはアクチユエータ側がポンプ作用を
行い、可変容量形油圧ポンプがモータ作用をして
原動機を駆動するため、所謂動力回収が行われ、
原動機の燃料消費率が著しく軽減され省エネルギ
の実現を図ることができる。 Conventionally, a hydraulic drive circuit system has been proposed in which a variable displacement hydraulic pump driven by a prime mover is connected to a hydraulic actuator in a closed circuit. When this hydraulic circuit is applied to the drive circuit of a hydraulic excavator, for example, when the boom is lowered, when the swing brake is applied, or when going down a slope, the actuator performs a pump action, and the variable displacement hydraulic pump performs a motor action to drive the prime mover. Therefore, so-called power recovery is performed,
The fuel consumption rate of the prime mover is significantly reduced, making it possible to achieve energy savings.
しかし、ブーム下げと旋回ブレーキが同時に行
われたり、急坂を降りる時には油圧ポンプのモー
タ作用のトルクが原動機の摩擦トルクより大きく
なる場合があり、このとき原動機の回転数はスロ
ツトルレバーで指令された燃料噴射ポンプのガバ
ナ作動領域の最大値をはるかに越えた高い回転数
になり、原動機で駆動される可変容量形油圧ポン
プの吐出量が回転数の上昇に伴ない増加するの
で、油圧アクチユエータの速度も増加し、油圧ア
クチユエータが所期のスピードより早く動くこと
になるため、操作性の悪化や思わぬ事故の発生の
原因となるばかりでなく、原動機の回転数が異常
に上昇して原動機およびこれに駆動される油圧ポ
ンプが破損を起こすこともある。 However, when the boom is lowered and the swing brake is applied at the same time, or when descending a steep slope, the torque of the hydraulic pump's motor may be greater than the friction torque of the prime mover, and in this case, the rotation speed of the prime mover is commanded by the throttle lever. The rotational speed of the fuel injection pump becomes high, far exceeding the maximum governor operating range, and the discharge amount of the variable displacement hydraulic pump driven by the prime mover increases as the rotational speed increases, so the speed of the hydraulic actuator increases. This causes the hydraulic actuator to move faster than the intended speed, which not only deteriorates operability and causes unexpected accidents, but also causes the prime mover's rotational speed to rise abnormally, causing damage to the prime mover and the hydraulic actuator. Damage may occur to the hydraulic pump driven by the
この原動機の過回転現象を原動機（エンジン）
軸出力特性を示す第１図のエンジン出力トルク
Te−エンジン回転数Ne線図によつて説明する。 This overspeeding phenomenon of the prime mover is detected by the prime mover (engine).
Engine output torque in Figure 1 showing shaft output characteristics
This will be explained using a T e -engine speed N e diagram.
図においてイはエンジンの回転数Neに対する
最大軸出力曲線であり、ロはエンジンの摩擦トル
ク曲線である。ハ，ニ，ホはそれぞれスロツトル
レバー低速、中速、高速設定時の燃料噴射ポンプ
のガバナ作動領域線であり、スロツトルレバーを
任意に設定すればガバナ作動領域線はハ〜ホの間
の一定の直線として表わすことができる。 In the figure, A is the maximum shaft output curve with respect to the engine rotational speed N e , and B is the engine friction torque curve. C, D, and Ho are the governor operating range lines of the fuel injection pump when the throttle lever is set at low, medium, and high speeds, respectively.If the throttle lever is set arbitrarily, the governor operating range line is between H and H. It can be expressed as a constant straight line.
今、たとえばスロツトルレバーを直線ニの中速
に設定し、急坂を降る時、エンジンで駆動される
可変容量形油圧ポンプがモータ作用をすると、エ
ンジン軸出力は直線ニに沿つて降下し、ついには
Ne軸（零）を越え、エンジン摩擦トルクをも油
圧ポンプのモータ作用トルクで補つてしまうので
Ｄ点に至る。このＤ点はスロツトルレバーで指令
されたガバナ作動領域でのエンジン最大回転数を
取る点であり、また燃料が無噴射になる点、すな
わち燃料消費率が最も良い点でもある。しかし、
モータ作用トルクがさらに働くと、エンジンはエ
ンジン摩擦トルク曲線ロに沿つて右方向にさらに
過回転させられ、エンジン回転数限界点Ｅを越え
てしまうことになる。 Now, for example, when the throttle lever is set to a medium speed in a straight line, and when descending a steep slope, the variable displacement hydraulic pump driven by the engine acts as a motor, the engine shaft output decreases along a straight line, and finally teeth
The N e axis (zero) is exceeded, and the engine friction torque is also compensated for by the hydraulic pump's motor action torque, resulting in point D. This point D is the point at which the engine reaches the maximum rotational speed in the governor operating range commanded by the throttle lever, and is also the point at which no fuel is injected, that is, the point at which the fuel consumption rate is the best. but,
If the motor acting torque acts further, the engine will be further over-revved to the right along the engine friction torque curve B, and the engine speed limit point E will be exceeded.
本発明は上述のような従来の問題点に鑑み成さ
れたもので、可変容量形油圧ポンプのモータ作用
によつて原動機が駆動されても、原動機の回転数
をガバナ作動領域を余り越えない範囲に制限し
て、原動機の過回転を防止する原動機のオーバー
ラン防止装置を提供することを目的とする。 The present invention has been made in view of the conventional problems as described above, and even when the prime mover is driven by the motor action of a variable displacement hydraulic pump, the rotational speed of the prime mover is controlled within a range that does not significantly exceed the governor operating range. It is an object of the present invention to provide an overrun prevention device for a prime mover that prevents over-rotation of the prime mover by limiting the number of rotations.
この目的を達成するため本発明は、原動機で駆
動される少くとも一つの可変容量形油圧ポンプ
と、原動機の燃料噴射ポンプのガバナ作動領域を
設定するスロツトルレバーと、スロツトルレバー
の作動量に応じた信号を出力するスロツトルレバ
ー信号出力手段と、原動機の回転数を検出して信
号を出力する回転数検出手段と、上記両信号の偏
差を演算する回転数偏差演算手段と、原動機で駆
動される上記可変容量形油圧ポンプを含む油圧ポ
ンプの少くとも一つの油圧ポンプの回路の圧力を
設定する圧力設定手段とを具備すると共に上記回
転数偏差が予め設定された値を越えるとき、その
回転数偏差に応じて上記圧力設定手段の設定値を
変えて上記回路圧力を上昇させるように制御する
圧力制御手段を備えたものである。 To achieve this object, the present invention provides at least one variable displacement hydraulic pump driven by the prime mover, a throttle lever that sets the governor operating range of the fuel injection pump of the prime mover, and a throttle lever that sets the operating range of the throttle lever. a throttle lever signal output means for outputting a corresponding signal; a rotation speed detection means for detecting the rotation speed of the prime mover and outputting a signal; and a rotation speed deviation calculation means for calculating the deviation between the two signals. pressure setting means for setting the pressure in the circuit of at least one of the hydraulic pumps including the variable displacement hydraulic pump, and when the rotational speed deviation exceeds a preset value, the rotational speed is increased. The pressure control means is provided for controlling the pressure setting means to increase the circuit pressure by changing the set value of the pressure setting means according to the number deviation.
以下本発明の一実施例を第１図乃至第４図によ
り説明する。 An embodiment of the present invention will be described below with reference to FIGS. 1 to 4.
第２図は原動機のオーバーラン防止装置の構成
を説明する図で、１はエンジン、２はエンジン１
の燃料噴射ポンプ、３，４はエンジン１に駆動さ
れる両傾転可変容量形油圧ポンプ、固定容量形油
圧ポンプ、５は燃料噴射ポンプ２のガバナ作動領
域を設定するスロツトルレバーである。６はスロ
ツトルレバー５の操作量を検出する検出器でポテ
ンシヨメータや差動トランスなどを使用する。７
はエンジン１の回転数を検出する回転数検出器、
８は油圧ポンプ４の回路に設けられた電磁比例形
リリーフ弁で、油圧ポンプ４の回路圧力を設定す
る圧力設定手段を構成している。９はプツシユブ
ルケーブルでスロツトルレバー５の操作量を燃料
噴射ポンプ２に伝達する。１０は作動油タンクで
ある。 Figure 2 is a diagram explaining the configuration of the overrun prevention device for the prime mover, where 1 is the engine, and 2 is the engine 1.
The fuel injection pumps 3 and 4 are double tilting variable displacement hydraulic pumps and fixed displacement hydraulic pumps driven by the engine 1, and the reference numeral 5 is a throttle lever for setting the governor operating range of the fuel injection pump 2. A detector 6 detects the amount of operation of the throttle lever 5, and uses a potentiometer, a differential transformer, or the like. 7
is a rotation speed detector that detects the rotation speed of the engine 1,
Reference numeral 8 denotes an electromagnetic proportional relief valve provided in the circuit of the hydraulic pump 4, which constitutes pressure setting means for setting the circuit pressure of the hydraulic pump 4. A pushable cable 9 transmits the operation amount of the throttle lever 5 to the fuel injection pump 2. 10 is a hydraulic oil tank.
１１は制御装置で第３図に示すように、スロツ
トルレバー検出器６の出力信号Tsおよび回転数
検出器７の出力信号Neを入力し、油圧ポンプ４
の回路圧力を設定する電磁比例形リリーフ弁８の
設定圧力を変化させる信号Cputを出力する。制御
装置１１は加算器１１ａ、関数発生器１１ｂ、増
幅器１１ｃより構成されている。加算器１１ａは
TsおよびNeから回転数偏差△ω＝Ne−Tsを演算
する。関数発生器１１ｂは、その出力特性の一例
を第４図に示すように、△ωに対して、△ωがａ
点に至るまでは出力信号out＝０で、ａ＜△ω≦
ｂでは△ωに比例した出力信号outを出し、ｂ＜
△ωでは出力信号outを所定の最大値に保持する。 11 is a control device which inputs the output signal T s of the throttle lever detector 6 and the output signal N e of the rotation speed detector 7, and controls the hydraulic pump 4 as shown in FIG.
outputs a signal Cput that changes the set pressure of the electromagnetic proportional relief valve 8 that sets the circuit pressure. The control device 11 includes an adder 11a, a function generator 11b, and an amplifier 11c. The adder 11a is
Calculate the rotation speed deviation △ω=N e −T s from T s and N e . As an example of the output characteristic of the function generator 11b is shown in FIG.
Until the point is reached, the output signal out = 0, and a<△ω≦
b outputs an output signal o out proportional to △ω, and b <
At Δω, the output signal out is held at a predetermined maximum value.
この出力特性を第１図に示したエンジンの出力
トルク特性と関連して説明すると、たとえば、ス
ロツトルレバー５を直線ニの中速に設定した場合
に、今、エンジン１の出力トルクが最大軸出力線
上にある場合には回転数はＡ点となり、Ａ点は第
４図の０点に相当する。すなわちＡ点は制御基準
点（最大燃料噴射点）である。次に、B′点をａ
点に、Ｃ点をｂ点になるように関数発生器１１ｂ
を設定する。B′点はエンジン１のエンジン摩擦
トルクは両傾転可変容量形油圧ポンプ３のモータ
作用によりすべて補われるＤ点（この時のエンジ
ン回転数はＢ点となる）に至る直前のエンジンの
回転数を表わす点であり、エンジン１のオーバー
ラン防止制御を開始する制御開始点である。Ｃ点
はエンジン１がＤ点を過ぎてさらに前記モータ作
用により上昇する回転数の限界を表わす制御限界
点であり、このときに関数発生器１１ｂのout信
号は最大値となる。 To explain this output characteristic in relation to the output torque characteristic of the engine shown in FIG. 1, for example, when the throttle lever 5 is set to a medium speed in a straight line, When it is on the output line, the rotational speed is at point A, and point A corresponds to point 0 in FIG. That is, point A is the control reference point (maximum fuel injection point). Next, set point B′ to a
function generator 11b so that point C becomes point b.
Set. Point B' is the engine rotational speed just before reaching point D (the engine rotational speed at this time is point B), where the engine friction torque of the engine 1 is completely compensated for by the motor action of the double tilting variable displacement hydraulic pump 3. , and is the control start point at which the overrun prevention control of the engine 1 is started. Point C is a control limit point representing the limit of the rotational speed of the engine 1 which exceeds point D and further increases due to the action of the motor, and at this time the output signal of the function generator 11b reaches its maximum value.
このように関数発生器１１ｂの出力特性を設定
すれば、エンジン１が両傾転可変容量形油圧ポン
プ３のモータ作用で駆動され、第１図に示す
B′点に到達すると、関数発生器１１ｂから零以
上のout信号が出力され、その信号は増幅器１１
ｃで増巾されて電磁比例リリーフ弁８を駆動し、
固定形油圧ポンプ４の回路圧力を上昇させる。回
路圧力が上昇すると固定形油圧ポンプ４の負荷が
増大し、この負荷がエンジン１に加わるため、エ
ンジン１の回転数の上昇を抑える。また、前述の
ようにエンジン回転数がB′点を越えて上昇すれ
ば、その上昇量に応じて関数発生器１１ｂから出
力されるout信号も増大するので、油圧ポンプ４
の負荷も増大する。 By setting the output characteristics of the function generator 11b in this way, the engine 1 is driven by the motor action of the double tilting variable displacement hydraulic pump 3, as shown in FIG.
When the point B' is reached, the function generator 11b outputs an output signal of zero or more, and the signal is sent to the amplifier 11.
c is amplified and drives the electromagnetic proportional relief valve 8,
The circuit pressure of the fixed hydraulic pump 4 is increased. When the circuit pressure increases, the load on the fixed hydraulic pump 4 increases, and this load is applied to the engine 1, thereby suppressing the increase in the rotational speed of the engine 1. Furthermore, as mentioned above, if the engine speed increases beyond point B', the out signal output from the function generator 11b also increases in accordance with the amount of increase, so the hydraulic pump 4
The load will also increase.
B′点は前述の燃料消費率の最も良いＢ点に近
い点に選定するのが好ましく、Ｃ点もなるべくＢ
点に接近させて選ぶのが良いが、B′点とＣ点の
間が余り近いと制御系がハンチングを起こす恐れ
があるため、実際には制御ハンチングを起さず且
つ動力回収を最も有効に行なえるようB′点およ
びＣ点を選定する。 It is preferable to select point B′ close to the above-mentioned point B with the best fuel consumption rate, and point C as well.
It is better to select points close to each other, but if points B' and C are too close together, there is a risk of hunting in the control system. Point B' and point C are selected so that this can be done.
第５図は本発明の他の実施例を示すもので、第
２図の実施例では回路圧力を設定する電磁比例リ
リーフ弁８を固定形油圧ポンプ４の回路中に設け
た例を示したが、第５図の実施例ではこの電磁比
例リリーフ弁８を両傾転可変容量形油圧ポンプ３
の途中に設けたもので、制御装置（第２図の制御
装置１１と同様なので省略）よりの信号により両
傾転可変容量形油圧ポンプの回路圧力を上昇する
ようにすれば、第２図の実施例と全く同様の作用
効果を奏することができる。 FIG. 5 shows another embodiment of the present invention, and the embodiment shown in FIG. 2 shows an example in which an electromagnetic proportional relief valve 8 for setting the circuit pressure is provided in the circuit of the fixed hydraulic pump 4. , in the embodiment shown in FIG.
If the circuit pressure of the double tilting variable displacement hydraulic pump is increased by a signal from the control device (not shown since it is the same as the control device 11 in FIG. 2), the circuit pressure of the double tilting variable displacement hydraulic pump can be increased. Exactly the same effects as in the embodiment can be achieved.
このように、電磁比例リリーフ弁８はエンジン
１に駆動される油圧ポンプの油圧回路中であれば
どこに設けても本発明の作用効果は達成される。 In this way, the effects of the present invention can be achieved even if the electromagnetic proportional relief valve 8 is installed anywhere in the hydraulic circuit of the hydraulic pump driven by the engine 1.
また、回路圧力設定手段として電磁比例リリー
フ弁８を示したが、代りに電磁比例流量制御弁等
の圧力制御弁を用いても良い。 Further, although the electromagnetic proportional relief valve 8 is shown as the circuit pressure setting means, a pressure control valve such as an electromagnetic proportional flow control valve may be used instead.
以上の実施例では制御装置１１をブロツク図を
用いて説明したが、これを実現する手段としてア
ナログ式の電子回路を用いてもデジタルコンピユ
ータを用いても良い。なお、制御装置１１の回転
数偏差を演算する装置として、スロツトルレバー
信号と回転数信号を検出して燃料噴射量を電気的
に制御するところの電子ガバナの出力信号を用い
ても良い。 In the above embodiments, the control device 11 has been explained using a block diagram, but an analog electronic circuit or a digital computer may be used as a means for realizing this. Note that as a device for calculating the rotational speed deviation of the control device 11, an output signal of an electronic governor that detects the throttle lever signal and the rotational speed signal and electrically controls the fuel injection amount may be used.
また、上述の実施例ではモータ作用をしてエン
ジンを駆動する可変容量形油圧ポンプとして両傾
転のものを示したが、片傾転のものであつても本
発明は全く同様の作用効果を奏することができ
る。 Further, in the above-described embodiment, a double tilting type variable displacement hydraulic pump that operates as a motor to drive an engine is shown, but even if it is a single tilting type, the present invention can achieve exactly the same effect. can play.
以上説明した本発明によれば、モータ作用をす
る可変容量形油圧ポンプによつて原動機が駆動さ
れ、原動機の回転数がスロツトルレバーによつて
設定されたガバナ領域から外れて上昇しようとす
ると、この原動機によつて駆動される油圧ポンプ
の回路圧力を上昇させて原動機の回転数上昇を阻
止するようにしたので、原動機の過回転を防止す
ることができ、アクチユエータが所期のスピード
より早く動くことがないので、操作性の向上が図
れると共に思わぬ事故の発生がなく且つ原動機お
よびこれに駆動される油圧ポンプの破損を起こす
ことがない。 According to the present invention described above, the prime mover is driven by the variable displacement hydraulic pump that acts as a motor, and when the rotational speed of the prime mover deviates from the governor range set by the throttle lever and attempts to rise, By increasing the circuit pressure of the hydraulic pump driven by this prime mover to prevent the prime mover from increasing its rotational speed, it is possible to prevent the prime mover from over-rotating, causing the actuator to move faster than the intended speed. As a result, operability is improved, unexpected accidents do not occur, and the prime mover and the hydraulic pump driven by the prime mover are not damaged.
第１図はエンジンの軸出力特性を示すと共に本
発明に係る関数発生器の関数設定条件を説明する
ための図、第２図は本発明の一実施例に係る原動
機のオーバーラン防止装置の構成を示す図、第３
図は本発明に係る関数発生器の詳細を示す図、第
４図は本発明に係る関数発生器に設定される関数
を示す図、第５図は本発明の他の実施例に係る原
動機のオーバーラン防止装置の構成の一部を示す
図である。
１…原動機（エンジン）、２…燃料噴射ポンプ、
３…可変容量形油圧ポンプ、４…固定容量形油圧
ポンプ、５…スロツトルレバー、６…スロツトル
レバー検出器、７…エンジン回転数検出器、８…
電磁比例リリーフ弁、１１…制御装置、１１ａ…
加算器、１１ｂ…関数発生器。
FIG. 1 is a diagram showing the shaft output characteristics of the engine and is a diagram for explaining the function setting conditions of the function generator according to the present invention, and FIG. 2 is a diagram showing the configuration of an overrun prevention device for a prime mover according to an embodiment of the present invention. Figure 3 showing
4 is a diagram showing the details of the function generator according to the present invention, FIG. 4 is a diagram showing the functions set in the function generator according to the present invention, and FIG. 5 is a diagram showing the function generator according to another embodiment of the present invention. FIG. 2 is a diagram showing part of the configuration of an overrun prevention device. 1... Prime mover (engine), 2... Fuel injection pump,
3... Variable displacement hydraulic pump, 4... Fixed displacement hydraulic pump, 5... Throttle lever, 6... Throttle lever detector, 7... Engine rotation speed detector, 8...
Electromagnetic proportional relief valve, 11...control device, 11a...
Adder, 11b...Function generator.
Claims (1)
形油圧ポンプと、原動機の燃料噴射ポンプのガバ
ナ作動領域を設定するスロツトルレバーと、スロ
ツトルレバーの作動量に応じた信号を出力するス
ロツトルレバー信号出力手段と、原動機の回転数
を検出して信号を出力する回転数検出手段と、上
記両信号の偏差を演算する回転数偏差演算手段
と、原動機で駆動される上記可変容量形油圧ポン
プを含む油圧ポンプの少くとも一つの油圧ポンプ
の回路圧力を設定する圧力設定手段とを具備する
と共に上記回転数偏差が予め設定された値を越え
るとき、その回転数偏差に応じて上記圧力設定手
段の設定値を変えて上記回路圧力を上昇させるよ
う制御する圧力制御手段を備えたことを特徴とす
る原動機のオーバーラン防止装置。1 At least one variable displacement hydraulic pump driven by the prime mover, a throttle lever that sets the governor operating range of the fuel injection pump of the prime mover, and a throttle lever that outputs a signal according to the operating amount of the throttle lever. a signal output means, a rotation speed detection means for detecting the rotation speed of the prime mover and outputting a signal, a rotation speed deviation calculation means for calculating the deviation between the two signals, and the variable displacement hydraulic pump driven by the prime mover. and pressure setting means for setting the circuit pressure of at least one of the hydraulic pumps, and when the rotation speed deviation exceeds a preset value, the pressure setting means is configured to set the circuit pressure of at least one of the hydraulic pumps, and when the rotation speed deviation exceeds a preset value, the pressure setting means An overrun prevention device for a prime mover, comprising a pressure control means for increasing the circuit pressure by changing a set value.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8164183A JPS59208140A (en) | 1983-05-12 | 1983-05-12 | Apparatus for preventing prime mover from over-run |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8164183A JPS59208140A (en) | 1983-05-12 | 1983-05-12 | Apparatus for preventing prime mover from over-run |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS59208140A JPS59208140A (en) | 1984-11-26 |
| JPH0347423B2 true JPH0347423B2 (en) | 1991-07-19 |
Family
ID=13751962
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8164183A Granted JPS59208140A (en) | 1983-05-12 | 1983-05-12 | Apparatus for preventing prime mover from over-run |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59208140A (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20130140104A (en) | 2011-01-21 | 2013-12-23 | 히다찌 겐끼 가부시키가이샤 | Work vehicle control apparatus and work vehicle |
| DE102015209377B4 (en) * | 2015-05-21 | 2017-05-11 | Mtu Friedrichshafen Gmbh | Injection system for an internal combustion engine and internal combustion engine with such an injection system |
| CN110439695B (en) * | 2019-08-15 | 2020-08-28 | 济宁医学院 | Engineering vehicle engine overspeed protection control system and control method thereof |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57171042A (en) * | 1981-04-15 | 1982-10-21 | Hitachi Constr Mach Co Ltd | Control system for series including internal-combustion engine and hydraulic pump |
-
1983
- 1983-05-12 JP JP8164183A patent/JPS59208140A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS59208140A (en) | 1984-11-26 |
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