JPH041183B2 - - Google Patents
Info
- Publication number
- JPH041183B2 JPH041183B2 JP12384284A JP12384284A JPH041183B2 JP H041183 B2 JPH041183 B2 JP H041183B2 JP 12384284 A JP12384284 A JP 12384284A JP 12384284 A JP12384284 A JP 12384284A JP H041183 B2 JPH041183 B2 JP H041183B2
- Authority
- JP
- Japan
- Prior art keywords
- signal
- prime mover
- rotational speed
- hydraulic pump
- rotation speed
- 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
Links
- 239000000446 fuel Substances 0.000 claims description 29
- 238000002347 injection Methods 0.000 claims description 15
- 239000007924 injection Substances 0.000 claims description 15
- 230000007423 decrease Effects 0.000 claims description 13
- 238000010586 diagram Methods 0.000 description 5
- 230000001276 controlling effect Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000011664 signaling Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/04—Introducing corrections for particular operating conditions
- F02D41/08—Introducing corrections for particular operating conditions for idling
- F02D41/083—Introducing corrections for particular operating conditions for idling taking into account engine load variation, e.g. air-conditionning
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (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】
〔発明の利用分野〕
本発明は原動機の目標回転数信号と出力回転数
信号との回転数偏差信号に基づいて原動機の燃料
噴射量と油圧ポンプの吐出量とを制御する原動機
と油圧ポンプとを含む系の制御装置に関する。[Detailed Description of the Invention] [Field of Application of the Invention] The present invention controls the fuel injection amount of a prime mover and the discharge amount of a hydraulic pump based on a rotation speed deviation signal between a target rotation speed signal of the prime mover and an output rotation speed signal. The present invention relates to a control device for a system including a prime mover and a hydraulic pump.
第６図は特開昭57−65822号公報に詳細に開示
されるような従来の原動機と油圧ポンプを含む系
の制御装置を示すブロツク図である。
FIG. 6 is a block diagram showing a conventional control device for a system including a prime mover and a hydraulic pump, as disclosed in detail in Japanese Patent Application Laid-Open No. 57-65822.
図において、１はデイーゼルエンジン等の原動
機を示し、２は電気的に原動機へ燃料噴射量を制
御する、所謂電子式燃料噴射ポンプである。３は
原動機１によつて駆動される可変容量形の油圧ポ
ンプ、４は油圧ポンプ３の斜板（もしくは斜軸）
の傾転角を電気信号によつて制御する、所謂電子
式ポンプレギユレータである。原動機１の指令回
転数信号Nso（この場合は目標回転数信号Noとな
る）は燃料スロツトルレバー５により運転者によ
つて設定され、一方原動機１の出力回転数信号Ｎ
は回転検出器６により検出出力されて、加算器７
は目標回転数信号Noと出力回転数Ｎとの回転数
偏差信号ΔNを演算出力する。燃料噴射ポンプ２
のラツク（図示せず）の変位がラツク位置検出器
（図示せず）によつて検出されたラツク位置信号
Ｌが出力される。加算器８はラツク目標位置信号
として与えられた回転数偏差信号ΔNとラツク位
置信号Ｌとの偏差信号Loに基いてラツク位置を
制御し、燃料噴射ポンプ２の燃料噴射量が決定さ
れる。 In the figure, 1 indicates a prime mover such as a diesel engine, and 2 is a so-called electronic fuel injection pump that electrically controls the amount of fuel injected into the prime mover. 3 is a variable displacement hydraulic pump driven by the prime mover 1; 4 is a swash plate (or slant shaft) of the hydraulic pump 3;
This is a so-called electronic pump regulator that controls the tilt angle of the pump by an electric signal. The command rotational speed signal Nso of the prime mover 1 (in this case, the target rotational speed signal No.) is set by the driver using the fuel throttle lever 5, while the output rotational speed signal Nso of the prime mover 1
is detected and outputted by the rotation detector 6, and the adder 7
calculates and outputs a rotational speed deviation signal ΔN between the target rotational speed signal No. and the output rotational speed N. fuel injection pump 2
A rack position signal L is output, in which the displacement of the rack (not shown) is detected by a rack position detector (not shown). The adder 8 controls the rack position based on the deviation signal Lo between the rotation speed deviation signal ΔN given as the rack target position signal and the rack position signal L, and the fuel injection amount of the fuel injection pump 2 is determined.
また、９はポンプ制御関数発生器で、油圧ポン
プ３の吐出管１０に設けられた圧力検出器１１か
らの圧力信号Ｐと加算器７よりの回転数偏差信号
ΔNを入力し、油圧ポンプ３のレギユレータ４に
吐出量を制御するためのポンプ傾転量信号Xqを
出力する。 Further, 9 is a pump control function generator which inputs the pressure signal P from the pressure detector 11 provided in the discharge pipe 10 of the hydraulic pump 3 and the rotation speed deviation signal ΔN from the adder 7. A pump tilt amount signal Xq for controlling the discharge amount is output to the regulator 4.
回転数偏差信号ΔNは油圧ポンプ３の負荷が大
きくなつて、出力回転数Ｎが低下して行くと大き
くなり、逆に油圧ポンプ３に負荷が軽くなつて、
出力回転数Ｎが上昇すると小さくなる。そこで
ΔNが大きくなるに伴つて電子式燃料噴射ポンプ
２はラツクク位置を燃料噴射量が増大する方向に
移動して原動機１の出力を増加させ、出力回転数
Ｎの低下を抑制し、またΔNが小さくなると燃料
噴射量を減少させて原動機１の出力回転数Ｎが過
回転になるのを防止している。 The rotational speed deviation signal ΔN increases as the load on the hydraulic pump 3 increases and the output rotational speed N decreases, and conversely, as the load on the hydraulic pump 3 becomes lighter,
As the output rotation speed N increases, it becomes smaller. Therefore, as ΔN increases, the electronic fuel injection pump 2 easily moves its position in the direction of increasing the fuel injection amount to increase the output of the prime mover 1, suppressing the decrease in the output rotation speed N, and increasing ΔN. When it becomes smaller, the fuel injection amount is reduced to prevent the output rotation speed N of the prime mover 1 from becoming overspeed.
油圧ポンプ３の入力トルクは斜板傾転量と吐出
圧力との積に比例する。したがつて、油圧ポンプ
３の負荷が増大（吐出圧力Ｐが上昇）し、原動機
１の出力回転数信号Ｎが低下し、回転数偏差信号
ΔNが増大すると、ポンプ制御関数発生器９は
ΔNの増加に伴つてポンプ傾転量信号Xqと吐出
圧力信号Ｐとの積を小さくし、油圧ポンプ３の入
力トルクが原動機１のスロツトレバー５により設
定された原動機１の出力トルク線に沿つて減少す
るように傾転量信号Xqを出力し、油圧ポンプ３
の吐出量を減少する。 The input torque of the hydraulic pump 3 is proportional to the product of the swash plate tilting amount and the discharge pressure. Therefore, when the load on the hydraulic pump 3 increases (discharge pressure P rises), the output rotational speed signal N of the prime mover 1 decreases, and the rotational speed deviation signal ΔN increases, the pump control function generator 9 changes the value of ΔN. The product of the pump tilting amount signal Xq and the discharge pressure signal P is made smaller as the pump tilting amount signal Outputs the tilting amount signal Xq to the hydraulic pump 3.
Reduce the discharge amount.
上記のように構成された従来の原動機と油圧ポ
ンプを含む系の制御装置では、原動機１の出力は
燃料スロツトルレバー５によつて指令された目標
回転信号No（＝Nso）によつて規制を受けるとい
う欠点がある。すなわち、スロツトレバー５によ
つて原動機１の最大目標回転数を指令すると、油
圧ポンプ３の負荷が小さいときにも原動機１が最
高回転数で駆動されて燃料消費率が悪化し、また
最大目標回転数に比して比較的低い目標回転数を
スロツトレバー５で指令すると、油圧ポンプ３の
負荷が大きくなつたときに原動機の出力を高い目
標回転数時の最大出力まで上げることが出来ず、
大きな負荷を駆動出来ない。したがつて、運転者
は油圧ポンプ３の負荷に応じて燃料スロツトレバ
ー５を常に操作しないと、上記問題に対処出来
ず、この操作は非常にわずらわしいのみならず熟
練を要することにより、また人間の操作感覚では
負荷の変動に完全に追従することは困難であつ
た。 In the conventional control device for a system including a prime mover and a hydraulic pump configured as described above, the output of the prime mover 1 is regulated by the target rotation signal No (=Nso) commanded by the fuel throttle lever 5. There is a drawback to receiving it. That is, if the maximum target rotation speed of the prime mover 1 is commanded by the slot lever 5, the prime mover 1 will be driven at the maximum rotation speed even when the load on the hydraulic pump 3 is small, resulting in a worsening of the fuel consumption rate. If a relatively low target rotation speed is commanded by the slot lever 5, when the load on the hydraulic pump 3 becomes large, the output of the prime mover cannot be increased to the maximum output at a high target rotation speed.
Cannot drive large loads. Therefore, the operator must constantly operate the fuel slot lever 5 according to the load of the hydraulic pump 3 in order to solve the above problem, and this operation is not only very troublesome but also requires skill and is difficult for human operators to operate. It was difficult to completely follow the load fluctuations by feeling.
本発明は上記従来の制御装置の欠点に鑑み成さ
れたもので、油圧ポンプに加わる負荷が小さいと
きには原動機を比較的回転が低く出力の比較的小
さい領域で使用し、負荷が大きくなると自動的に
回転数を上昇させて、原動機を回転数が高く出力
の大きい領域で使用し、燃料消費率と操作性の向
上を図ることが目的とする。
The present invention has been made in view of the above-mentioned drawbacks of the conventional control device, and when the load applied to the hydraulic pump is small, the prime mover is used in a region with relatively low rotation and relatively low output, and when the load becomes large, the motor is automatically activated. The purpose is to increase the rotational speed and use the prime mover in a high rotational speed and high output range to improve fuel consumption and operability.
この目的を達成するため本発明は、目標回転数
信号と出力回転数信号との差である回転数偏差信
号の増減に対応して設定された増加回転信号を燃
料スロツトルレバーの指令回転数信号に加算して
目標回転数信号とし、この目標回転数信号の基い
て燃料噴射量と油圧ポンプ吐出量を制御すること
により、油圧ポンプの負荷が軽いときには、スロ
ツトルレバーで指令された比較的低い目標回転数
信号に基いて原動機の出力回転数を制御し、油圧
ポンプの負荷が増加したときには、回転数偏差信
号の増大に応じて上昇した高い目標回転数信号に
基いて原動機の出力回転数を制御するものであ
る。
In order to achieve this object, the present invention uses an increased rotation signal set in response to an increase or decrease in a rotation speed deviation signal, which is the difference between a target rotation speed signal and an output rotation speed signal, as a command rotation speed signal of a fuel throttle lever. By adding it to the target rotation speed signal and controlling the fuel injection amount and hydraulic pump discharge amount based on this target rotation speed signal, when the load on the hydraulic pump is light, the relatively low speed commanded by the throttle lever is controlled. The output rotation speed of the prime mover is controlled based on the target rotation speed signal, and when the load on the hydraulic pump increases, the output rotation speed of the prime mover is controlled based on the high target rotation speed signal that increases in accordance with the increase in the rotation speed deviation signal. It is something to control.
以下本発明の一実施例を第１図ないし第３図を
参照して説明する。
An embodiment of the present invention will be described below with reference to FIGS. 1 to 3.
第１図は本発明の一実施例に係る原動機と油圧
ポンプを含む系の制御ブロツク図を示すもので、
第６図と同一部分には同符号を付している。 FIG. 1 shows a control block diagram of a system including a prime mover and a hydraulic pump according to an embodiment of the present invention.
The same parts as in FIG. 6 are given the same reference numerals.
１２は増加回転数関数発生器で加算器７より回
転数偏差信号ΔNを入力し、増加回転数信号Nn
を発生する。１３は燃料スロツトルレバー５と加
算器７との間に設けられた加算器で、燃料スロツ
トルレバー５の指令回転信号Nsoに増加回転数信
号Nnを加算して目標回転数信号Noとし、この
Noを加算器７に出力する。 12 is an increased rotational speed function generator which inputs the rotational speed deviation signal ΔN from the adder 7, and generates an increased rotational speed signal Nn.
occurs. 13 is an adder provided between the fuel throttle lever 5 and the adder 7, which adds an increased rotation speed signal Nn to the command rotation signal Nso of the fuel throttle lever 5 to obtain a target rotation speed signal No.
Output No to adder 7.
増加回転数関数発生器１２のΔN−Nnの関数
関係の例を第２図および第３図に示す。 Examples of the functional relationship of ΔN-Nn of the increased rotational speed function generator 12 are shown in FIGS. 2 and 3.
第２図は縦軸に増加回転数信号Nn、横軸に回
転数偏差信号ΔNを取つており、ΔNが設定値ａ
を越えるとNnがＯからNnmaxまでステツプ状に
増加するものである。 In Figure 2, the vertical axis is the increased rotational speed signal Nn, and the horizontal axis is the rotational speed deviation signal ΔN, where ΔN is the set value a.
When Nn exceeds 0, Nn increases stepwise from O to Nnmax.
第３図は縦軸、横軸は第２図と同じであり、
ΔNがａ点を越えるとΔNの大きさに比例してNn
が増加して、ｂ点でNn＝Nnmaxとなるものであ
る。 In Figure 3, the vertical axis and horizontal axis are the same as in Figure 2,
When ΔN exceeds point a, Nn increases in proportion to the size of ΔN.
increases, and Nn=Nnmax at point b.
作用について説明する。燃料スロツトルレバー
５によつて比較的低い回転数の指令回転数信号
Nsoを指令すると、油圧ポンプ３の負荷が小さい
ときには、原動機１の出力回転信号Ｎと指令回転
数信号Nsoとは接近した値であるので、Nsoが目
標回転数信号Noとなつて燃料噴射ポンプ２が燃
料噴射量および油圧ポンプ３の吐出量が制御され
る。 The effect will be explained. A relatively low rotational speed command signal is generated by the fuel throttle lever 5.
When Nso is commanded, when the load on the hydraulic pump 3 is small, the output rotation signal N of the prime mover 1 and the command rotation speed signal Nso are close values, so Nso becomes the target rotation speed signal No and the fuel injection pump 2 The fuel injection amount and the discharge amount of the hydraulic pump 3 are controlled.
この状態から油圧ポンプ３の負荷が大きくな
り、原動機１の出力回転数信号Ｎが低下すると、
回転数偏差信号ΔNが大きくなり、ΔNが設定値
ａを越えると増加回転数発生器１２より増加回転
数信号Nnが発生し、加算器１３で指令回転数信
号NsoにNnが加算されて目標回転数信号Noとな
る。したがつて、燃料噴射ポンプ２の燃料噴射量
および油圧ポンプの吐出量はスロツトレバー５に
よつて指令された指令回転数信号NsoにNnを加
算した高い目標回転数信号Noにより制御される
ことになる。 From this state, when the load on the hydraulic pump 3 increases and the output rotation speed signal N of the prime mover 1 decreases,
When the rotational speed deviation signal ΔN increases and ΔN exceeds the set value a, the increased rotational speed generator 12 generates an increased rotational speed signal Nn, and the adder 13 adds Nn to the commanded rotational speed signal Nso to reach the target rotation. The number signal becomes No. Therefore, the fuel injection amount of the fuel injection pump 2 and the discharge amount of the hydraulic pump are controlled by a high target rotation speed signal No, which is obtained by adding Nn to the command rotation speed signal Nso commanded by the slot lever 5. .
以上の実施例によれば次の効果を奏する。 According to the above embodiment, the following effects are achieved.
(1) 油圧ポンプ３の負荷が小さいときには、原動
機１を回転数が低く出力の小さい領域で使用
し、燃料消費率を向上し、且つ原動機の発生音
を低くして運転できる。(1) When the load on the hydraulic pump 3 is small, the prime mover 1 can be used in a low rotational speed and low output range to improve the fuel consumption rate and reduce the noise generated by the prime mover.
(2) 油圧ポンプ３の負荷が大きくなると自動的に
原動機１の目標回転数が上昇し、原動機１を回
転数が高く出力の大きい領域で運転することが
できる。(2) When the load on the hydraulic pump 3 increases, the target rotational speed of the prime mover 1 automatically increases, and the prime mover 1 can be operated in a region of high rotational speed and large output.
(3) 油圧ポンプ３の負荷の変化に応じて原動機１
の目標回転数を自動的に追従させ得るので、運
転者の操作のわずらわしさを省き操作性が向上
する。(3) The prime mover 1 responds to changes in the load on the hydraulic pump 3.
Since the target rotation speed can be automatically followed, the troublesome operation by the driver is eliminated and the operability is improved.
第４図および第５図は第１図の増加回転数発生
器１２のΔN−Nn関数にヒステリリシスを持た
せた例を示すものである。各図において第２図お
よび第３図と同一部分には同符号を付してある。 4 and 5 show an example in which the ΔN-Nn function of the increased rotational speed generator 12 shown in FIG. 1 is provided with hysteresis. In each figure, the same parts as in FIGS. 2 and 3 are given the same reference numerals.
第４図は油圧ポンプ３の負荷が次第に増大して
回転数偏差信号ΔNが設定値a1を越えるとNn＝
Nnmaxを出力し、この状態から負荷が減少して
ΔNが小さくなつて行くときにはΔNが設定値a2
（但しa2＜a1）に至るとNn＝０となる（この経路
を矢印で示す）ようなヒステリシスの関数を示
す。 Figure 4 shows that when the load on the hydraulic pump 3 gradually increases and the rotation speed deviation signal ΔN exceeds the set value a1 , Nn=
Nnmax is output, and when the load decreases from this state and ΔN becomes smaller, ΔN becomes the set value a 2
A hysteresis function is shown in which Nn=0 when a 2 <a 1 is reached (this path is indicated by an arrow).
第２図および第３図の例ではΔNに対してNn
が一義的に決まる値であるのでΔNの僅かの変化
でNnの値で頻繁に増減をくり返すため、運転者
に不快感を与えるが、上記のようにヒステリシス
を持つた関数で制御すればa2＜Nn＜a1の範囲で
は目標回転数Noに変化を生じないので運転者の
不快感をなくすことが出来る。 In the examples in Figures 2 and 3, Nn for ΔN
Since it is a uniquely determined value, the value of Nn will frequently increase or decrease due to a slight change in ΔN, causing discomfort to the driver, but if it is controlled using a function with hysteresis as described above, a 2 <Nn<a Since no change occurs in the target rotation speed No in the range of 1 , driver discomfort can be eliminated.
第５図は関数にヒステリシスを持たせた他の例
を示すもので、ΔNが増加して行きa1を越えると
ΔNに比例してNnが増加し、ΔNがb1でNn＝
Nnmaxとなり、それ以上のΔNでは一定値とな
る。この状態からΔNが減少して行くと、ΔNが
b2（b2＜b1）まではNn＝Nnmaxを保持し、b2＜
ΔN＜a2ではΔNに比例したNnの値で減少し、
ΔN＜a2ではNn＝０となる。また、ΔNに比例し
てNnが増加して行き、ΔNがb1に至る途中のC1
点でNn＝Nncから逆にΔNが減少した場合には、
C2＜ΔN＜C1間ではNn＝Nncを保持し、a2＜ΔN
＜C2間では予め設定された設定線（a2b2）のNn
の値を出力する。 Figure 5 shows another example in which the function has hysteresis. When ΔN increases and exceeds a1 , Nn increases in proportion to ΔN, and when ΔN is b 1 , Nn =
Nnmax, and becomes a constant value for ΔN above that. As ΔN decreases from this state, ΔN becomes
Nn=Nnmax is maintained until b 2 (b 2 < b 1 ), and b 2 <
When ΔN<a 2 , it decreases with the value of Nn proportional to ΔN,
When ΔN<a 2 , Nn=0. Also, Nn increases in proportion to ΔN, and C 1 on the way to ΔN reaching b 1
If ΔN decreases from Nn=Nnc at the point,
Nn=Nnc is maintained between C 2 < ΔN < C 1 , and a 2 < ΔN
<C between 2 and Nn of the preset setting line (a 2 b 2 )
Outputs the value of .
上記のようなヒステリシスを関数に持たせれ
ば、負荷の大きさに応じて原動機１の目標回転数
を連続的に設定することが出来ると共に、第４図
の例と同様に油圧ポンプ３の負荷の変動に伴う原
動機１と頻繁な回転数の増減を制御し、運転者の
不快感を回避することが出来る。 If the function has hysteresis as described above, it is possible to continuously set the target rotation speed of the prime mover 1 according to the magnitude of the load, and also to adjust the load of the hydraulic pump 3 as in the example shown in FIG. By controlling frequent increases and decreases in the rotational speed of the prime mover 1 due to fluctuations, it is possible to avoid driver discomfort.
以上説明した本発明によれば、原動機と油圧ポ
ンプとを含む系の制御装置において、油圧ポンプ
の負荷が小さいときには原動機を低出力領域で制
御し、油圧ポンプの負荷の大きいときには原動機
を出力の大きい領域で制御する原動機の回転数制
御を自動的に行うことが出来るので、燃料消費率
を向上させ得ると共に運転時の操作性を良好にす
ることが出来る。
According to the present invention described above, in a control device for a system including a prime mover and a hydraulic pump, when the load on the hydraulic pump is small, the prime mover is controlled in a low output range, and when the load on the hydraulic pump is large, the prime mover is controlled in a high output range. Since the rotational speed of the prime mover can be automatically controlled in the range, the fuel consumption rate can be improved and the operability during operation can be improved.
第１図は本発明に係る原動機と油圧ポンプを含
む系の制御ブロツク図、第２図は第１図の増加回
転数関数発生器に設定した関数をステツプ状にし
た例を示す図、第３図は増加回転数関数発生器に
設定した関数を比例関係にした例を示す図、第４
図は増加回転数関数発生器に設定した関数をステ
ツプ状で且つヒステリシスを持たせた例を示す
図、第５図は増加回転数発生器に設定した関数を
比例関係で且つヒステリシスを持たせた例を示す
図、第６図は従来の原動機と油圧ポンプを含む系
の制御ブロツク図である。
１……原動機、２……燃料噴射ポンプ、３……
油圧ポンプ、４……レギユレータ、５……燃料ス
ロツトルレバー、６……回転検出器、７，８，１
３……加算器、１１……ポンプ制御関数発生器、
１２……増加回転数関数発生器、Ｎ……出力回転
数信号、No……目標回転数信号、Nn……増加回
転数信号、Nso……指令回転数信号、ΔN……回
転数偏差信号。
Fig. 1 is a control block diagram of a system including a prime mover and a hydraulic pump according to the present invention, Fig. 2 is a diagram showing an example in which the function set in the increasing rotation speed function generator of Fig. 1 is set in a step shape, and Fig. 3 The figure shows an example in which the function set in the increased rotation speed function generator is in a proportional relationship.
The figure shows an example in which the function set in the increasing rotation speed function generator is in a step shape and has hysteresis. Figure 5 shows an example in which the function set in the increasing rotation speed generator is in a proportional relationship and has hysteresis. An example is shown in FIG. 6, which is a control block diagram of a conventional system including a prime mover and a hydraulic pump. 1... Prime mover, 2... Fuel injection pump, 3...
Hydraulic pump, 4... Regulator, 5... Fuel throttle lever, 6... Rotation detector, 7, 8, 1
3...Adder, 11...Pump control function generator,
12... Increased rotation speed function generator, N... Output rotation speed signal, No... Target rotation speed signal, Nn... Increased rotation speed signal, Nso... Commanded rotation speed signal, ΔN... Rotation speed deviation signal.
Claims (1)
プとを含み、且つ原動機の目標回転数信号と出力
回転信号との差である回転数偏差信号をもとめ、
この回転数偏差信号に基いて原動機の燃料噴射量
を制御すると共に油圧ポンプの吐出量を制御する
系において、回転数偏差信号の増域に対応して設
定された増加回転数信号を燃料スロツトルレバー
の指令回転数信号に加算して目標回転数信号とす
ることを特徴とする原動機と油圧ポンプを含む系
の制御装置。 ２ 増加回転数信号は、回転数偏差の第１の設定
値から増加し、回転数偏差の第２の設定値から減
少し、且つ第１の設定値を第２の設定値より大き
く設定したヒステリシスを持つ関数関係にあるこ
とを特徴とする特許請求の範囲第１項記載の原動
機と油圧ポンプを含む系の制御装置。 ３ 増加回転数信号は、回転数偏差に比例して増
減することを特徴とする特許請求の範囲第２項記
載の原動機と油圧ポンプを含む系の制御装置。[Claims] 1. A system comprising a prime mover and a hydraulic pump driven by the prime mover, and obtaining a rotation speed deviation signal that is the difference between a target rotation speed signal and an output rotation signal of the prime mover,
In a system that controls the fuel injection amount of the prime mover and the discharge amount of the hydraulic pump based on this rotational speed deviation signal, the increased rotational speed signal set corresponding to the increase range of the rotational speed deviation signal is applied to the fuel throttle. A control device for a system including a prime mover and a hydraulic pump, characterized in that the signal is added to a lever command rotation speed signal to obtain a target rotation speed signal. 2. The increased rotational speed signal increases from the first setting value of the rotational speed deviation, decreases from the second setting value of the rotational speed deviation, and has hysteresis in which the first setting value is set larger than the second setting value. A control device for a system including a prime mover and a hydraulic pump according to claim 1, characterized in that the functional relationship is as follows. 3. A control device for a system including a prime mover and a hydraulic pump according to claim 2, wherein the increased rotational speed signal increases or decreases in proportion to the rotational speed deviation.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12384284A JPS614847A (en) | 1984-06-18 | 1984-06-18 | Controller for system equipped with prime mover and hydraulic pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12384284A JPS614847A (en) | 1984-06-18 | 1984-06-18 | Controller for system equipped with prime mover and hydraulic pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS614847A JPS614847A (en) | 1986-01-10 |
| JPH041183B2 true JPH041183B2 (en) | 1992-01-10 |
Family
ID=14870736
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP12384284A Granted JPS614847A (en) | 1984-06-18 | 1984-06-18 | Controller for system equipped with prime mover and hydraulic pump |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS614847A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2004113704A1 (en) * | 2003-06-25 | 2004-12-29 | Hitachi Construction Machinery Co., Ltd. | Engine control device for construction machine |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3607089B2 (en) * | 1998-09-03 | 2005-01-05 | 日立建機株式会社 | Torque control device for hydraulic pump of hydraulic construction machinery |
-
1984
- 1984-06-18 JP JP12384284A patent/JPS614847A/en active Granted
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2004113704A1 (en) * | 2003-06-25 | 2004-12-29 | Hitachi Construction Machinery Co., Ltd. | Engine control device for construction machine |
| CN100410517C (en) * | 2003-06-25 | 2008-08-13 | 日立建机株式会社 | Engine control devices for construction machinery |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS614847A (en) | 1986-01-10 |
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