JPH09126150A - Hydraulic pump control device for construction machine - Google Patents
Hydraulic pump control device for construction machineInfo
- Publication number
- JPH09126150A JPH09126150A JP7288948A JP28894895A JPH09126150A JP H09126150 A JPH09126150 A JP H09126150A JP 7288948 A JP7288948 A JP 7288948A JP 28894895 A JP28894895 A JP 28894895A JP H09126150 A JPH09126150 A JP H09126150A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- hydraulic pump
- reducing valve
- atmospheric pressure
- pressure reducing
- 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
Landscapes
- Fluid-Driven Valves (AREA)
- Fluid-Pressure Circuits (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Operation Control Of Excavators (AREA)
Abstract
Description
【0001】[0001]
【発明の属する技術分野】本発明は建設機械の油圧ポン
プ制御装置に関するものであり、特に、大気圧の変化に
対応した油圧ポンプ制御装置に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic pump control device for a construction machine, and more particularly to a hydraulic pump control device that responds to changes in atmospheric pressure.
【0002】[0002]
【従来の技術】油圧ショベル等の建設機械に於いて、油
圧ポンプの設定トルクをエンジンスピートセンシング制
御によって電気的に行うものが知られているが、高価な
装置が必要である。近年、電気的な制御を行わないで油
圧ポンプの設定トルクを調整する装置も使用されてい
る。2. Description of the Related Art There is known a construction machine such as a hydraulic excavator that electrically sets a torque of a hydraulic pump by engine speed sensing control, but requires an expensive device. In recent years, a device that adjusts the set torque of a hydraulic pump without performing electrical control has also been used.
【0003】そして、電気的な制御を行わない場合は、
油圧ポンプの応答遅れによる過負荷に対応させておくた
めに、エンジンの定格出力軸トルクに対して油圧ポンプ
の設定トルクを若干低めに設定する。When no electrical control is performed,
In order to deal with overload due to the response delay of the hydraulic pump, the set torque of the hydraulic pump is set slightly lower than the rated output shaft torque of the engine.
【0004】[0004]
【発明が解決しようとする課題】従来、此種建設機械の
油圧ポンプ制御装置は、エンジンの定格出力軸トルクに
対して油圧ポンプの設定トルクを低めにしているが、高
地等大気圧の低い場所ではエンジンの出力そのものが低
下してエンストし易くなるので、設定トルクを更に低め
に設定する必要がある。然し、油圧ポンプの設定トルク
をあまり低くし過ぎると、一般の平地での稼働効率が悪
化することになる。Conventionally, a hydraulic pump control device for a construction machine of this type has a low set torque of the hydraulic pump with respect to the rated output shaft torque of the engine, but it is used in places with low atmospheric pressure, such as in highlands. In this case, the output of the engine itself decreases and it is easy to stall, so it is necessary to set the set torque even lower. However, if the set torque of the hydraulic pump is set too low, the operating efficiency on general flat ground will deteriorate.
【0005】そこで、高価な電気的な制御を用いること
なく、安価な装置によって大気圧の変化に対応した油圧
ポンプの制御を行うために解決すべき技術的課題が生じ
てくるのであり、本発明はこの課題を解決することを目
的とする。Therefore, there arises a technical problem to be solved in order to control the hydraulic pump in response to the change in atmospheric pressure by an inexpensive device without using expensive electric control. Aims to solve this problem.
【0006】[0006]
【課題を解決するための手段】本発明は上記目的を達成
するために提案されたものであり、内部が1気圧で密閉
され、且つ大気圧の下で伸縮自在なベローズ状の密封容
器を設け、該密封容器の伸縮により減圧弁の2次圧を調
整可能に構成し、この減圧弁の2次圧を油圧ポンプのレ
ギュレータへ作用させた建設機械の油圧ポンプ制御装
置、及び、吐出圧が常時1気圧に調整された空気ポンプ
を設け、片ロッド形複動シリンダのボトム側ポートへ前
記空気ポンプの吐出圧を導入するとともに、該複動シリ
ンダのトップ側のポートへ大気圧を導入し、更に、該複
動シリンダ形のロッドの伸縮により減圧弁の2次圧を調
整可能に構成し、この減圧弁の2次圧を油圧ポンプのレ
ギュレータへ作用させた建設機械の油圧ポンプ制御装置
を提供するものである。DISCLOSURE OF THE INVENTION The present invention has been proposed in order to achieve the above object, and is provided with a bellows-shaped hermetically sealed container whose inside is hermetically sealed at 1 atm and is expandable and contractable under atmospheric pressure. The expansion pressure of the pressure reducing valve is adjustable by expansion and contraction of the hermetically sealed container, and the secondary pressure of the pressure reducing valve is applied to the regulator of the hydraulic pump. An air pump adjusted to 1 atm is provided, the discharge pressure of the air pump is introduced into the bottom port of the single rod double acting cylinder, and the atmospheric pressure is introduced into the top port of the double acting cylinder. Provided is a hydraulic pump control device for a construction machine in which the secondary pressure of a pressure reducing valve is adjustable by expansion and contraction of the double-acting cylinder type rod, and the secondary pressure of the pressure reducing valve is applied to a regulator of the hydraulic pump. Thing .
【0007】[0007]
【発明の実施の形態】以下、本発明の実施の形態を図面
に従って詳述する。図1は請求項1記載の発明の油圧ポ
ンプ制御装置を示し、油圧ポンプ10はレギュレータ1
1により傾転角度が変化し、該油圧ポンプ10から回路
へ供給される油の吐出量が制御される。前記レギュレー
タ11への信号圧は、油圧源12から減圧弁13を介し
て入力される。Embodiments of the present invention will be described below in detail with reference to the drawings. FIG. 1 shows a hydraulic pump control device according to a first aspect of the present invention, wherein the hydraulic pump 10 is a regulator 1.
The tilt angle is changed by 1 and the discharge amount of oil supplied from the hydraulic pump 10 to the circuit is controlled. The signal pressure to the regulator 11 is input from the hydraulic pressure source 12 via the pressure reducing valve 13.
【0008】一方、符号14はベローズ状の密封容器で
あり、その内部が1気圧で密閉され、且つ大気圧の下で
伸縮自在に形成されている。該密封容器14の一端14
aを固定するとともに、該密封容器14の他端14bを
前記減圧弁13の開放側13aへ当接する。On the other hand, reference numeral 14 is a bellows-shaped hermetic container, the inside of which is hermetically sealed at 1 atm and is expandable and contractable under atmospheric pressure. One end 14 of the sealed container 14
While fixing a, the other end 14b of the sealed container 14 is brought into contact with the open side 13a of the pressure reducing valve 13.
【0009】ここで、図2はエンジンの回転数と出力軸
トルクの関係を示したものであり、定格点Tにて出力軸
トルクが最大となる。通常は、油圧ポンプ10の応答遅
れによって過負荷が生じないように、油圧ポンプ10の
設定トルクが定格点Tよりやや低めのA点となるように
レギュレータ11を初期設定し、このときの減圧弁13
の状態を初期状態とする。Here, FIG. 2 shows the relationship between the engine speed and the output shaft torque, and the output shaft torque becomes maximum at the rated point T. Normally, in order to prevent overload due to the response delay of the hydraulic pump 10, the regulator 11 is initially set so that the set torque of the hydraulic pump 10 is a point A slightly lower than the rated point T, and the pressure reducing valve at this time is set. Thirteen
The state of is the initial state.
【0010】而して、油圧ポンプ10を稼働していると
きに、大気圧が1気圧であれば前記密封容器14は図1
に示したように収縮しており、減圧弁13が初期状態を
維持してレギュレータ11は変化せず、油圧ポンプ10
の設定トルクは前述したA点のままである。Thus, when the hydraulic pump 10 is operating and the atmospheric pressure is 1 atm, the sealed container 14 is shown in FIG.
, The pressure reducing valve 13 maintains the initial state, the regulator 11 does not change, and the hydraulic pump 10
The set torque of is the same as point A described above.
【0011】いま、高地等大気圧が1気圧より低い場所
では、前記密封容器14内の圧力により密封容器14が
膨張して伸長し、減圧弁13のスプールが開放側へ押圧
される。従って、密封容器14の伸長に伴って減圧弁1
3の開口面積が変化して2次圧が徐々に大きくなり、油
圧源12からレギュレータ11へ作用する信号圧が高く
なっていく。即ち、油圧ポンプ10の設定トルクは、図
2のグラフ上でA点より低いB点となり、気圧の低い場
所でのエンジンへの負荷を軽減してエンストを防止す
る。[0011] Now, in high altitudes where the atmospheric pressure is lower than 1 atm, the pressure inside the sealed container 14 causes the sealed container 14 to expand and expand, and the spool of the pressure reducing valve 13 is pressed to the open side. Therefore, as the sealed container 14 extends, the pressure reducing valve 1
The opening area of 3 changes, the secondary pressure gradually increases, and the signal pressure acting on the regulator 11 from the hydraulic power source 12 increases. That is, the set torque of the hydraulic pump 10 becomes a point B lower than the point A on the graph of FIG. 2, and the engine load is reduced and the engine stall is prevented in a place where the atmospheric pressure is low.
【0012】そして、大気圧が再び1気圧に戻ったとき
は、前記密封容器14周囲の圧力により、密封容器14
が押圧されて収縮し、減圧弁13が初期状態に復帰して
レギュレータ11は初期設定に戻る。即ち、油圧ポンプ
10の設定トルクが最初のA点に戻る。When the atmospheric pressure returns to 1 atm again, the pressure around the sealed container 14 causes the sealed container 14 to move.
Is pressed and contracted, the pressure reducing valve 13 returns to the initial state, and the regulator 11 returns to the initial setting. That is, the set torque of the hydraulic pump 10 returns to the first point A.
【0013】このように、油圧ポンプ10の設定トルク
が大気圧の変化に対応して上下するので、エンジンの定
格出力軸トルクに対して油圧ポンプの設定トルクを低く
し過ぎることがなく、平地での稼働効率の低下を防止で
きる。As described above, the set torque of the hydraulic pump 10 rises and falls according to the change of the atmospheric pressure, so that the set torque of the hydraulic pump does not become too low with respect to the rated output shaft torque of the engine, and it can be maintained on a level ground. It is possible to prevent a decrease in the operating efficiency of.
【0014】図3は請求項2記載の発明の油圧ポンプ制
御装置を示し、図1と同一構成部分には同一符号を付し
てその説明を省略する。同図にて符号15は空気ポンプ
であり、圧力制御弁16により吐出圧が常時1気圧にな
るように調整されている。FIG. 3 shows a hydraulic pump control device according to a second aspect of the present invention. The same components as those in FIG. In the figure, reference numeral 15 is an air pump, which is adjusted by a pressure control valve 16 so that the discharge pressure is always 1 atm.
【0015】また、17は片ロッド形の複動シリンダで
あり、該複動シリンダ17のボトム側のポート17aへ
前記空気ポンプ15の吐出圧を導入するとともに、該複
動シリンダ17のトップ側のポート17bへ大気圧を導
入する。該複動シリンダ17のロッド17cはバネ17
dによりボトム側へ付勢されており、更に、該ロッド1
7cの先端を前記減圧弁13の開放側13aへ当接す
る。Reference numeral 17 denotes a single rod type double acting cylinder, which introduces the discharge pressure of the air pump 15 into a port 17a on the bottom side of the double acting cylinder 17 and at the top side of the double acting cylinder 17. Atmospheric pressure is introduced into the port 17b. The rod 17c of the double-acting cylinder 17 is a spring 17
The rod 1 is urged toward the bottom by d.
The tip of 7c is brought into contact with the open side 13a of the pressure reducing valve 13.
【0016】而して、油圧ポンプ10を稼働していると
きに、大気圧が1気圧であれば前記複動シリンダ17の
ロッド17cは没入した状態であり、減圧弁13が初期
状態を維持してレギュレータ11は変化せず、油圧ポン
プ10の設定トルクは前述したA点のままである。When the hydraulic pump 10 is operating and the atmospheric pressure is 1 atm, the rod 17c of the double-acting cylinder 17 is in a depressed state, and the pressure reducing valve 13 maintains the initial state. As a result, the regulator 11 does not change, and the set torque of the hydraulic pump 10 remains at the point A described above.
【0017】いま、高地等大気圧が1気圧より低い場所
では、前記複動シリンダ17のボトム側のポート17a
がトップ側のポート17bより高圧となり、バネ17d
の押圧力に抗してロッド17cが突出し、減圧弁13の
スプールが開放側へ押圧される。従って、該ロッド17
cの突出に伴って減圧弁13の開口面積が変化して2次
圧が徐々に大きくなり、油圧源12からレギュレータ1
1へ作用する信号圧が高くなっていく。即ち、前述した
ように油圧ポンプ10の設定トルクは、図2のグラフ上
でA点より低いB点となり、気圧の低い場所でのエンジ
ンへの負荷を軽減してエンストを防止する。Now, in a place where atmospheric pressure such as high altitude is lower than 1 atm, the port 17a on the bottom side of the double-acting cylinder 17 is used.
Becomes higher than the port 17b on the top side, and the spring 17d
The rod 17c projects against the pressing force of, and the spool of the pressure reducing valve 13 is pressed toward the open side. Therefore, the rod 17
With the protrusion of c, the opening area of the pressure reducing valve 13 changes and the secondary pressure gradually increases.
The signal pressure acting on 1 increases. That is, as described above, the set torque of the hydraulic pump 10 becomes a point B lower than the point A on the graph of FIG. 2, and the engine load is reduced in a place where the atmospheric pressure is low to prevent engine stall.
【0018】そして、大気圧が再び1気圧に戻ったとき
は、前記複動シリンダ17のボトム側のポート17aが
トップ側のポート17bと同圧となり、バネ17dの付
勢によってロッド17cがボトム側へ押圧されて没入
し、減圧弁13が初期状態に復帰してレギュレータ11
は初期設定に戻る。即ち、油圧ポンプ10の設定トルク
が最初のA点に戻る。When the atmospheric pressure returns to 1 atm again, the bottom side port 17a of the double-acting cylinder 17 becomes the same pressure as the top side port 17b, and the rod 17c is urged by the spring 17d. The pressure reducing valve 13 is returned to its initial state by being pushed into the regulator 11
Returns to default settings. That is, the set torque of the hydraulic pump 10 returns to the first point A.
【0019】尚、図示は省略するが、前記複動シリンダ
17は片ロッド形に限定されるべきではなく、両ロッド
形を使用してもよい。而して、本発明は、本発明の精神
を逸脱しない限り種々の改変を為すことができ、そし
て、本発明が該改変されたものに及ぶことは当然であ
る。Although not shown in the drawings, the double-acting cylinder 17 should not be limited to a single rod type, but may be a double rod type. Therefore, the present invention can be variously modified without departing from the spirit of the present invention, and it is a matter of course that the present invention covers the modifications.
【0020】[0020]
【発明の効果】以上説明したように、本発明では大気圧
の変化に対応して減圧弁の2次圧を調整可能にし、油圧
ポンプのレギュレータを制御して設定トルクを上下する
ので、エンジンの定格出力軸トルクに対して油圧ポンプ
の設定トルクを低くし過ぎることがなく、平地での稼働
効率を良好にすることができる。As described above, according to the present invention, the secondary pressure of the pressure reducing valve can be adjusted according to the change of the atmospheric pressure, and the set torque is increased or decreased by controlling the regulator of the hydraulic pump. The set torque of the hydraulic pump is not made too low with respect to the rated output shaft torque, and the operating efficiency on a level ground can be improved.
【0021】また、高価な電気的な制御を用いることな
く、安価な装置によって大気圧の変化に対応した油圧ポ
ンプの制御を行うためコストダウンにも寄与できる。Further, the cost of the hydraulic pump can be reduced because the hydraulic pump is controlled in response to the change of the atmospheric pressure by the inexpensive device without using the expensive electric control.
【図1】請求項1記載の発明の実施の形態を示し、建設
機械の油圧ポンプ制御装置を示す回路図。FIG. 1 is a circuit diagram showing an embodiment of the invention according to claim 1 and showing a hydraulic pump control device for a construction machine.
【図2】エンジンの回転数と出力軸トルクの関係を示し
たグラフ。FIG. 2 is a graph showing the relationship between engine speed and output shaft torque.
【図3】請求項2記載の発明の実施の形態を示し、建設
機械の油圧ポンプ制御装置を示す回路図。FIG. 3 is a circuit diagram showing an embodiment of the invention according to claim 2 and showing a hydraulic pump control device for a construction machine.
10 油圧ポンプ 11 レギュレータ 12 油圧源 13 減圧弁 14 密封容器 15 空気ポンプ 16 圧力制御弁 17 複動シリンダ 17a ボトム側のポート 17b トップ側のポート 17c ロッド 17d バネ 10 Hydraulic Pump 11 Regulator 12 Hydraulic Source 13 Pressure Reducing Valve 14 Sealed Container 15 Air Pump 16 Pressure Control Valve 17 Double Acting Cylinder 17a Bottom Port 17b Top Port 17c Rod 17d Spring
Claims (2)
下で伸縮自在なベローズ状の密封容器を設け、該密封容
器の伸縮により減圧弁の2次圧を調整可能に構成し、こ
の減圧弁の2次圧を油圧ポンプのレギュレータへ作用さ
せたことを特徴とする建設機械の油圧ポンプ制御装置。1. A bellows-shaped sealed container whose inside is sealed at 1 atm and is expandable and contractable under atmospheric pressure, and the secondary pressure of a pressure reducing valve can be adjusted by expanding and contracting the sealed container. A hydraulic pump control device for a construction machine, wherein the secondary pressure of a pressure reducing valve is applied to a regulator of a hydraulic pump.
ンプを設け、片ロッド形複動シリンダのボトム側ポート
へ前記空気ポンプの吐出圧を導入するとともに、該複動
シリンダのトップ側のポートへ大気圧を導入し、更に、
該複動シリンダ形のロッドの伸縮により減圧弁の2次圧
を調整可能に構成し、この減圧弁の2次圧を油圧ポンプ
のレギュレータへ作用させたことを特徴とする建設機械
の油圧ポンプ制御装置。2. An air pump whose discharge pressure is constantly adjusted to 1 atm is provided, and the discharge pressure of the air pump is introduced into the bottom side port of the single rod type double acting cylinder, and the top side of the double acting cylinder is also provided. Introducing atmospheric pressure to the port,
A hydraulic pump control for a construction machine, characterized in that the secondary pressure of the pressure reducing valve can be adjusted by expanding and contracting the double-acting cylinder type rod, and the secondary pressure of the pressure reducing valve acts on the regulator of the hydraulic pump. apparatus.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP7288948A JPH09126150A (en) | 1995-11-07 | 1995-11-07 | Hydraulic pump control device for construction machine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP7288948A JPH09126150A (en) | 1995-11-07 | 1995-11-07 | Hydraulic pump control device for construction machine |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH09126150A true JPH09126150A (en) | 1997-05-13 |
Family
ID=17736887
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP7288948A Pending JPH09126150A (en) | 1995-11-07 | 1995-11-07 | Hydraulic pump control device for construction machine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH09126150A (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1533524A1 (en) * | 2002-08-26 | 2005-05-25 | Hitachi Construction Machinery Co., Ltd. | Signal processing device of construction machinery |
JP2006112288A (en) * | 2004-10-14 | 2006-04-27 | Komatsu Ltd | Construction machinery |
WO2007060948A1 (en) | 2005-11-25 | 2007-05-31 | Hitachi Construction Machinery Co., Ltd. | Pump torque controller of hydraulic working machine |
WO2007142012A1 (en) * | 2006-06-06 | 2007-12-13 | Hitachi Construction Machinery Co., Ltd | Drive system for electrically driven dump truck |
-
1995
- 1995-11-07 JP JP7288948A patent/JPH09126150A/en active Pending
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1533524A1 (en) * | 2002-08-26 | 2005-05-25 | Hitachi Construction Machinery Co., Ltd. | Signal processing device of construction machinery |
EP1533524A4 (en) * | 2002-08-26 | 2010-11-10 | Hitachi Construction Machinery | Signal processing device of construction machinery |
JP2006112288A (en) * | 2004-10-14 | 2006-04-27 | Komatsu Ltd | Construction machinery |
WO2007060948A1 (en) | 2005-11-25 | 2007-05-31 | Hitachi Construction Machinery Co., Ltd. | Pump torque controller of hydraulic working machine |
US8056331B2 (en) | 2005-11-25 | 2011-11-15 | Hitachi Construction Machinery Co., Ltd. | Pump torque controller of hydraulic working machine |
WO2007142012A1 (en) * | 2006-06-06 | 2007-12-13 | Hitachi Construction Machinery Co., Ltd | Drive system for electrically driven dump truck |
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