JPH0258482B2 - - Google Patents

Info

Publication number
JPH0258482B2
JPH0258482B2 JP54136618A JP13661879A JPH0258482B2 JP H0258482 B2 JPH0258482 B2 JP H0258482B2 JP 54136618 A JP54136618 A JP 54136618A JP 13661879 A JP13661879 A JP 13661879A JP H0258482 B2 JPH0258482 B2 JP H0258482B2
Authority
JP
Japan
Prior art keywords
amount
variable displacement
pump
oil
loaded
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
Application number
JP54136618A
Other languages
Japanese (ja)
Other versions
JPS5659005A (en
Inventor
Akira Asari
Tatsuhiko Noyori
Kyoshi Gotoda
Masaru Takeda
Munenori Soejima
Masayuki Ekuma
Yasuhiro Nakajima
Masanobu Aoki
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kobe Steel Ltd
Original Assignee
Kobe Steel Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Kobe Steel Ltd filed Critical Kobe Steel Ltd
Priority to JP13661879A priority Critical patent/JPS5659005A/en
Priority to EP19800303741 priority patent/EP0027743B1/en
Priority to DE8080303741T priority patent/DE3070650D1/en
Publication of JPS5659005A publication Critical patent/JPS5659005A/en
Publication of JPH0258482B2 publication Critical patent/JPH0258482B2/ja
Granted legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/30575—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve in a Wheatstone Bridge arrangement (also half bridges)
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5153—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/615—Filtering means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6653—Pressure control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7052—Single-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7107—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being mechanically linked
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7114—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators
    • F15B2211/7128—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators the chambers being connected in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/88—Control measures for saving energy

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Presses (AREA)
  • Press Drives And Press Lines (AREA)

Description

【発明の詳細な説明】 本発明は、並列に接続された複数台の可変容量
形ポンプの圧油によつて金属押出しプレスを作動
させる金属押出しプレスの作動方法に関するもの
である。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a method for operating a metal extrusion press in which the metal extrusion press is operated by pressure oil from a plurality of variable displacement pumps connected in parallel.

この種の金属押出しプレスでは、一行程中に、
無負荷前進、アプセツト、押出し、後退、等の数
多くの動作があり、これら各動作に応じてステム
の作動速度すなわちポンプからプレスのシリンダ
に対する供給油量が制御されるのが通例である。
たとえば第７図に示すように、プレスの一行程に
おいて、まず、ステムを仕様最高速度の100％の
作動速度で無負荷前進させた後、アプセツトのた
めに同30％の作動速度で前進させ、次いで、押出
し行程で、押出し初期に付属設備による製品ハン
ドリング等のために同15％の作動速度で前進させ
た後、押出し中期で同40％の作動速度で前進させ
て製品を押出し、押出し終期に慣性力低減のため
に同10％の作動速度で前進させた後、停止させ、
然る後、同60％の作動速度で後退させる。このよ
うに金属押出しプレスが仕様値の最高速度（必要
油量が全ポンプの最大吐出量の合計）で使用され
ることは少ない。とくに、この金属押出しプレス
では、一行程中における押出し行程（押出し初
期、中期、終期）の占める時間的割合が大きく、
しかも、この押出し行程では、作動速度が仕様最
高速度の40％前後で運転される。従つて、この押
出し行程でのポンプ効率の向上は、非常に重要な
要素であることがわかる。 In this type of metal extrusion press, during one stroke,
There are many operations such as no-load advance, upset, extrusion, and retraction, and it is customary to control the operating speed of the stem, that is, the amount of oil supplied from the pump to the cylinder of the press, depending on each of these operations.
For example, as shown in Fig. 7, in one stroke of the press, the stem is first advanced without load at an operating speed of 100% of the maximum specification speed, and then advanced at an operating speed of 30% of the maximum specification speed for upset. Next, in the extrusion process, the product is advanced at 15% of the operating speed in the early stage of extrusion for handling of the product by attached equipment, and then the product is advanced at 40% of the same operating speed in the middle of extrusion, and the product is extruded at the end of extrusion. In order to reduce inertia, it is moved forward at the same 10% operating speed, then stopped,
After that, it is moved backward at 60% of the operating speed. In this way, metal extrusion presses are rarely used at the maximum specified speed (the amount of oil required is the sum of the maximum discharge volumes of all pumps). In particular, in this metal extrusion press, the extrusion process (initial, middle, and final stages of extrusion) occupies a large proportion of time in one process.
Moreover, in this extrusion process, the operating speed is approximately 40% of the maximum specification speed. Therefore, it can be seen that improving pump efficiency in this extrusion process is a very important factor.

このような金属押出しプレスにおいて、従来で
は、一般に全ポンプを一斉にオンロードした状態
で、ステムの作動速度設定値に基いて、全ポンプ
の傾転角を常に均等に制御しながら、全ポンプか
ら前記シリンダにそれぞれ均等量の圧油を供給し
て必要油量を満たすようにしていた。すなわち、
たとえば４台の可変容量形ポンプを並列に備えた
金属押し出しプレスにおいて、仕様最高速度の50
％の作動速度で該プレスを運転する場合、従来で
は４台全部のポンプを一斉にオンロードさせた状
態で、４台のポンプの吐出量がすべて50％になる
ように均等に制御していた。 Conventionally, in such metal extrusion presses, all pumps are generally on-loaded at the same time, and the tilting angles of all pumps are always controlled equally based on the operating speed setting of the stem. An equal amount of pressure oil was supplied to each cylinder to satisfy the required amount of oil. That is,
For example, in a metal extrusion press equipped with four variable displacement pumps in parallel, the specified maximum speed of 50
When operating the press at an operating speed of 50%, conventionally all four pumps were on-loaded at the same time, and the discharge volume of all four pumps was controlled equally so that it was 50%. .

しかしながら、可変容量形ポンプは、一般的に
第９図および第１０図に示すように、その容積効
率および全体効率がポンプの傾転角αすなわち吐
出量によつて異なり、ポンプ仕様値の最大吐出量
（最大傾転角）で使用した場合に容積効率および
全体効率が最大となり、それ以外（中間および小
傾転角）では容積効率および全体効率が低下する
という特性がある。 However, as shown in Figures 9 and 10, variable displacement pumps generally have a volumetric efficiency and an overall efficiency that vary depending on the pump's tilt angle α, that is, the discharge volume, and the maximum discharge of the pump specification value is It has a characteristic that the volumetric efficiency and overall efficiency are maximum when used at a large amount (maximum tilt angle), and the volumetric efficiency and overall efficiency decrease at other times (intermediate and small tilt angles).

このため、従来のように、全ポンプを常に一斉
にオンロードして中間吐出状態で運転する方式で
あると、全ポンプが容積効率ならびに全体効率が
悪い状態で運転されることになり、電力すなわち
エネルギーが無駄に消費される。とくに、金属押
出しプレスは、金属を押出すという性質上、極め
て大力量を必要とするので、大容量の可変容量形
ポンプが使用され、そのポンプを駆動する電動機
も大容量のものが使用されている。従つて、前記
のように効率の悪い状態で運転した場合、エネル
ギー損失は非常に大きなものとなる。 For this reason, if all the pumps are always on-loaded at the same time and operated in an intermediate discharge state as in the past, all the pumps will be operated with poor volumetric efficiency and overall efficiency, and the electric power Energy is wasted. In particular, metal extrusion presses require extremely large amounts of force due to the nature of extruding metal, so large-capacity variable displacement pumps are used, and the electric motors that drive the pumps are also large-capacity. There is. Therefore, when operating under inefficient conditions as described above, energy loss becomes extremely large.

また、プランジヤ型の可変容量形ポンプの吐出
量を制御する場合、吐出量が小さい範囲では制御
精度が悪く、たとえば最大吐出量でヒステリシス
が１％の精度であつても、1/10の吐出量では10％
のヒステリシスになる。このため、従来のよう
に、全ポンプをその制御精度が悪い低吐出量域で
使用した場合、各ポンプの制御精度の誤差が相乗
され、金属押出しプレスの速度制御に大きな誤差
が生じ、正確な制御ができない。 In addition, when controlling the discharge rate of a plunger type variable displacement pump, the control accuracy is poor in a small discharge rate range.For example, even if the hysteresis is 1% accuracy at the maximum discharge rate, the discharge rate is 1/10. Then 10%
becomes hysteresis. For this reason, if all the pumps are used in the low discharge volume range where their control accuracy is poor, as in the past, the errors in the control accuracy of each pump will be compounded, resulting in a large error in the speed control of the metal extrusion press, and it will not be possible to accurately control the speed of the metal extrusion press. I can't control it.

本発明は、このような問題を解決するためのも
のであり、その第１の目的は、金属容量形ポンプ
を常に効率よく作動させ、エネルギー損失を極力
少なくしていわゆる省エネルギー効果を高めるこ
とができる金属押出しプレスの作動方法を提供す
ることにある。また、第２の目的は、省エネルギ
ー効果を高めながら、とくに、金属押出しプレス
の作動速度を連続的に変化させる場合に、各可変
容量形ポンプを連係させて、制御精度の誤差の影
響の少ない状態で、速度制御を円滑にできる金属
押出しプレスの作動方法を提供することにある。 The present invention is intended to solve such problems, and its first purpose is to constantly operate a metal displacement pump efficiently and to minimize energy loss, thereby increasing the so-called energy saving effect. An object of the present invention is to provide a method for operating a metal extrusion press. The second objective is to increase the energy-saving effect while also making it possible to achieve a state where the influence of errors in control accuracy is reduced by linking each variable displacement pump, especially when the operating speed of a metal extrusion press is continuously changed. An object of the present invention is to provide a method for operating a metal extrusion press that allows smooth speed control.

そして、上記第１の目的を達成するために、第
１の発明の方法は、並列に接続された複数台の可
変容量形ポンプから金属押出しプレスに圧油を供
給して金属押出しプレスを作動させる方法におい
て、該プレスにおけるステムの作動速度設定器に
設定された設定値に基いて、該プレスの必要油量
を求め、必要油量が可変容量形ポンプ１台分の最
大吐出量以下のときは、可変容量形ポンプ１台を
オンロードして同ポンプからの吐出油によつて必
要油量を満たすように流量制御すると共に、残り
の可変容量形ポンプをアンロードさせ、必要油量
が可変容量形ポンプ１乃至数台分の最大吐出量よ
り多いときは、最大吐出状態でオンロードした１
乃至数台の可変容量形ポンプからの吐出油と、そ
の不足分を補うように可変吐出状態でオンロード
した１台の可変容量形ポンプからの吐出油とによ
つて必要油量を満たすように流量制御すると共
に、残りの可変容量形ポンプをアンロードするよ
うにしている。 In order to achieve the first object, the method of the first invention operates the metal extrusion press by supplying pressure oil to the metal extrusion press from a plurality of variable displacement pumps connected in parallel. In the method, the amount of oil required for the press is determined based on the setting value set in the operating speed setting device of the stem in the press, and if the amount of oil required is less than the maximum discharge amount for one variable displacement pump, , one variable displacement pump is on-loaded and the flow rate is controlled so that the required oil amount is met by the oil discharged from the same pump, and the remaining variable displacement pumps are unloaded, so that the required oil amount is changed to variable displacement. If the discharge amount is greater than the maximum discharge amount for one or several pumps, the pump
The required amount of oil is met by the oil discharged from several variable displacement pumps and the oil discharged from one variable displacement pump that is on-loaded in a variable discharge state to make up for the shortage. In addition to controlling the flow rate, the remaining variable displacement pumps are unloaded.

この構成により、プレスの必要油量に応じて必
要最少台数のポンプだけがオンロードされ、残り
のポンプがアンロードされる。しかも、オンロー
ドされるポンプのうち、１台のみが中間吐出状態
で、他のポンプが最大吐出状態となり、オンロー
ドされるポンプの総効率が高められ、プレスが常
に効率よく作動される。また、必要以外のポンプ
をアンロードすることによつて省エネルギー効果
が高められる。 With this configuration, only the minimum number of pumps required are on-loaded depending on the amount of oil required for the press, and the remaining pumps are unloaded. Furthermore, only one of the on-loaded pumps is in the intermediate discharge state and the other pumps are in the maximum discharge state, so that the total efficiency of the on-loaded pumps is increased and the press is always operated efficiently. Furthermore, the energy saving effect can be enhanced by unloading pumps that are not needed.

また、第２の目的達成のために、第２の発明の
方法は、上記第１の方法に加えて、さらに、必要
油量が連続的に変化するときは、前記可変容量形
ポンプを順次オンロードして必要油量を連続的に
満たし、かつ、そのつなぎの部分で、先にオンロ
ードした可変容量形ポンプが最大吐出状態になる
以前に次の可変容量形ポンプをオンロードすると
共に、必要油量の変化量に応じて先にオンロード
した可変容量形ポンプの吐出量と、新たにオンロ
ードした可変容量形ポンプの吐出量とを同時に可
変制御して必要油量を連続的に満たすようによう
にしている。 Furthermore, in order to achieve the second objective, the method of the second invention, in addition to the first method, further includes the step of sequentially turning on the variable displacement pump when the required amount of oil changes continuously. At the same time, the next variable displacement pump is loaded before the previously loaded variable displacement pump reaches its maximum discharge state, and the required oil amount is continuously filled. Depending on the amount of change in oil volume, the discharge volume of the previously loaded variable displacement pump and the discharge volume of the newly loaded variable displacement pump are simultaneously controlled to continuously satisfy the required oil volume. I'm trying to do that.

この構成により、前記つなぎの部分において、
先にオンロードされて最大吐出量付近になつてい
る可変容量形ポンプの効率のよい流量制御によつ
て、新たにオンロードされる低吐出量域の可変容
量形ポンプの精度誤差の影響が半減され、必要油
量の変化量を新たにオンロードした可変容量形ポ
ンプのみで制御する場合に比べて、制御精度が向
上され、金属押出しプレスの速度制御が円滑に遂
行される。 With this configuration, in the connecting part,
By efficiently controlling the flow rate of the variable displacement pump that has been on-loaded first and is near the maximum discharge rate, the influence of accuracy errors of the variable displacement pump that is newly on-loaded and has a low discharge rate is halved. Compared to the case where changes in the amount of required oil are controlled only by a newly loaded variable displacement pump, the control accuracy is improved and the speed control of the metal extrusion press is performed smoothly.

以下、本発明の実施例を図面によつて説明す
る。 Embodiments of the present invention will be described below with reference to the drawings.

第１図は金属押出しプレスの油圧回路を示すも
のであり、同図において、１１，１２，１３，１
４は可変容量形ポンプで、それぞれポンプ駆動用
モータ２１，２２，２３，２４によつて駆動され
る。３１，３２，３３，３４は各ポンプに具備さ
れたレギユレータ等の吐出量制御器で、各ポンプ
の傾転角を変更するためのたとえばシリンダ装置
が内蔵され、その作動用油圧源として、パイロツ
トポンプ７１から常に一定の一次圧力Paが負荷
されている。 Figure 1 shows the hydraulic circuit of a metal extrusion press.
Reference numeral 4 denotes a variable displacement pump, which is driven by pump drive motors 21, 22, 23, and 24, respectively. Reference numerals 31, 32, 33, and 34 are discharge amount controllers such as regulators provided in each pump, and include a built-in cylinder device for changing the tilting angle of each pump. A constant primary pressure Pa is always applied from 71.

前記各可変容量形ポンプ１１，１２，１３，１
４の吐出回路には各ポンプをオンロードまたはア
ンロードさせるためのロード切換用電磁弁４１，
４２，４３，４４と、リリーフ弁４５，４６，４
７，４８が接続されている。また、各ポンプの吐
出回路は互いに合流するように並列に接続され、
方向切換用電磁弁５１，５２，５３，５４，５５
によつて金属押出しプレス６０の主シリンダ６１
とサイドシリンダ６２，６３に対して切換自在に
接続されている。５７は満油弁で、主シリンダ６
１と油槽との間に設けられ、そのパイロツト回路
に方向切換用電磁弁５６を介してパイロツトポン
プ７２から開弁用一次圧力が切換自在に導かれ
る。５８，５９はリリーフ弁、６４は金属押出し
プレスのステムを示す。 Each of the variable displacement pumps 11, 12, 13, 1
The discharge circuit No. 4 includes a load switching solenoid valve 41 for on-loading or unloading each pump.
42, 43, 44 and relief valves 45, 46, 4
7 and 48 are connected. In addition, the discharge circuits of each pump are connected in parallel so that they merge with each other.
Directional switching solenoid valves 51, 52, 53, 54, 55
Main cylinder 61 of metal extrusion press 60 by
and the side cylinders 62 and 63 in a freely switchable manner. 57 is a full oil valve, main cylinder 6
1 and an oil tank, and the primary pressure for valve opening is guided to the pilot circuit from a pilot pump 72 via a direction switching solenoid valve 56 in a switchable manner. 58 and 59 are relief valves, and 64 is a stem of a metal extrusion press.

前記各可変容量形ポンプ１１，１２，１３，１
４のロード切換用電磁弁４１，４２，４３，４４
および吐出量制御器３１，３２，３３，３４は第
２図に示す制御回路によつて制御される。すなわ
ち、第２図において、８０はステム６４の作動速
度設定器で、予め設定されたプログラム（たとえ
ばタイムスケジユール等）に基いてステム６４の
必要作動速度が設定されている。この設定値は、
当該プレス６の仕様最高速度を100％（必要油量
は全ポンプの最大吐出量の合計）とし、この仕様
最高速度に対して実際の作動速度が何％であるか
を設定したものであり、その設定値を検出子８１
により検出して演算器８２に送り、この演算器８
２で必要油量を演算し、ACまたはDC信号に変換
して吐出量制御信号C1，C2，C3，C4を出力し、
この信号を各ポンプ１１，１２，１３，１４の吐
出量制御器３１，３２，３３，３４に送り、前記
プログラムに基づくステム６４の作動開始信号と
突合せて信号C1′，C2′，C3′，C4′を出力し、その
信号をロード切換用電磁弁４１，４２，４３，４
４に送る。 Each of the variable displacement pumps 11, 12, 13, 1
4 load switching solenoid valves 41, 42, 43, 44
The discharge amount controllers 31, 32, 33, and 34 are controlled by a control circuit shown in FIG. That is, in FIG. 2, 80 is an operating speed setting device for the stem 64, and the required operating speed of the stem 64 is set based on a preset program (eg, time schedule, etc.). This setting value is
The specified maximum speed of the press 6 is set as 100% (the required oil amount is the sum of the maximum discharge volumes of all pumps), and the actual operating speed is set as a percentage of this specified maximum speed. The setting value is detected by the detector 81.
is detected by the calculator 82 and sent to the calculator 82.
Calculate the required oil amount in step 2, convert it to an AC or DC signal, and output the discharge amount control signals C 1 , C 2 , C 3 , C 4 ,
This signal is sent to the discharge amount controllers 31, 32, 33, and 34 of each pump 11, 12, 13, and 14, and compared with the operation start signal of the stem 64 based on the program, the signals C 1 ′, C 2 ′, C 3 ', C4 ' and send the signal to the load switching solenoid valves 41, 42, 43, 4.
Send to 4.

そして、予め設定されたステム作動速度に応じ
てすなわち各シリンダ６１，６２，６３の必要油
量に応じて各電磁弁４１，４２，４３，４４を第
３図に示す如くON−OFF制御し、各ポンプ１
１，１２，１３，１４をオンロードまたはアンロ
ードさせると共に、各吐出量制御器３１，３２，
３３，３４により各ポンプ１１，１２，１３，１
４の傾転角を第４図に示す如く制御してその吐出
量を制御する。 Then, each solenoid valve 41, 42, 43, 44 is controlled ON-OFF as shown in FIG. Each pump 1
1, 12, 13, and 14, and each discharge amount controller 31, 32,
33, 34 for each pump 11, 12, 13, 1
The inclination angle of No. 4 is controlled as shown in FIG. 4 to control the discharge amount.

また、図外の制御盤等から前記プログラムに基
いて、各電磁弁５１，５２，５３，５４，５５，
５６に電気信号を送り、これら電磁弁のうち１乃
至数個を作動させ、各シリンダ６１，６２，６３
とポンプまたは油槽との回路を連通させ、作動さ
せるシリンダおよびその作動方向を制御する。 Also, each solenoid valve 51, 52, 53, 54, 55,
56 to operate one or several of these solenoid valves, each cylinder 61, 62, 63
The circuit between the cylinder and the pump or oil tank is connected to control the cylinder to be operated and the direction of its operation.

さらに詳述すると、ステム作動速度が仕様最高
速度の０〜25％の範囲、換言すればシリンダの必
要油量が各ポンプ１１，１２，１３，１４の最大
吐出量（仕様最大流量）の合計の０〜25％の範囲
では、電磁弁４１を励磁して１台のポンプ１１の
みをオンロードし、かつ、吐出量制御器３１によ
り同ポンプ１１の傾転角を制御してその吐出量を
０〜100％の範囲で可変制御し、該ポンプ１１の
みからシリンダに必要油量を供給してステム６４
を作動させる。このとき、他の電磁弁４２，４
３，４４は消磁し、他のポンプ１２，１３，１４
をアンロードさせて無負荷回転状態に保持する。 More specifically, if the stem operating speed is in the range of 0 to 25% of the maximum specification speed, in other words, the required oil amount of the cylinder is the sum of the maximum discharge volume (specified maximum flow rate) of each pump 11, 12, 13, and 14. In the range of 0 to 25%, the solenoid valve 41 is excited to load only one pump 11, and the discharge amount controller 31 controls the tilt angle of the pump 11 to reduce the discharge amount to 0. -100%, and supply the necessary amount of oil to the cylinder only from the pump 11 to supply the required amount of oil to the cylinder.
Activate. At this time, the other solenoid valves 42, 4
3 and 44 are demagnetized, and the other pumps 12, 13, 14
is unloaded and kept in a no-load rotation state.

また、前記作動速度が仕様最高速度の25〜50％
の範囲、換言すればシリンダの必要油量がポンプ
最大吐出量の合計の25〜50％の範囲では、電磁弁
４１，４２を励磁して２台のポンプ１１，１２を
オンロードし、かつ、吐出量制御器３１によりそ
の１台のポンプ１１の傾転角を最大（100％）に
して同ポンプ１１の吐出量を100％にすると共に、
吐出量制御器３２によりもう１台のポンプ１２の
傾転角を制御してその吐出量を０〜100％の範囲
で可変制御する。そして、100％吐出のポンプ１
１と、その不足分を補う吐出量のポンプ１２とか
らシリンダに必要油量を供給してステム６４を作
動させる。この場合は電磁弁４３，４４は消磁
し、残り２台のポンプ１３，１４をアンロードさ
せて無負荷回転状態に保持する。 In addition, the operating speed is 25 to 50% of the maximum specification speed.
In other words, in a range where the required oil amount of the cylinder is 25 to 50% of the total pump maximum discharge amount, the solenoid valves 41 and 42 are energized to on-load the two pumps 11 and 12, and The displacement controller 31 sets the tilting angle of that one pump 11 to the maximum (100%) to make the discharge rate of the same pump 11 100%, and
The displacement controller 32 controls the tilt angle of the other pump 12 to variably control its discharge rate within a range of 0 to 100%. And pump 1 with 100% discharge
The stem 64 is operated by supplying the necessary amount of oil to the cylinder from the pump 12 and the pump 12 with a discharge amount that makes up for the shortage. In this case, the solenoid valves 43 and 44 are demagnetized, and the remaining two pumps 13 and 14 are unloaded and maintained in a no-load rotation state.

以下同様にして前記作動速度が仕様最高速度の
50〜75％の範囲では、吐出量を100％の状態でオ
ンロードした２台のポンプ１１，１２と、その不
足分を補うように吐出量を０〜100％の範囲で制
御される可変吐出状態でオンロードした１台のポ
ンプ１３とからシリンダに必要油量を供給し、残
り１台のポンプ１４をアンロードさせる。また、
前記作動速度が仕様最高速度の75〜100％の範囲
では、吐出量を100％の状態でオンロードした３
台のポンプ１１，１２，１３と、その不足分を補
うように吐出量を０〜100％の範囲で制御される
可変吐出状態でオンロードした１台のポンプ１４
とからシリンダに必要油量を供給する。 Similarly, the operating speed is set to the maximum specified speed.
In the range of 50 to 75%, the two pumps 11 and 12 are on-loaded with the discharge volume at 100%, and the variable discharge volume is controlled in the range of 0 to 100% to compensate for the shortage. In this state, the required amount of oil is supplied to the cylinder from one pump 13 that is on-loaded, and the remaining one pump 14 is unloaded. Also,
When the operating speed is in the range of 75 to 100% of the maximum specification speed, on-load with the discharge amount at 100%3
pumps 11, 12, 13, and one pump 14 on-load in a variable discharge state where the discharge amount is controlled in the range of 0 to 100% to compensate for the shortage.
Supply the required amount of oil to the cylinder.

こうして必要油量が増大するに伴つて各ポンプ
１１，１２，１３，１４を順次オンロードさせ
（減少の場合は逆）、必要油量に対して、吐出量が
100％のポンプ何台かと不足分を補う１台の中間
負荷状態のポンプとによつて必要油量を満たし、
他のポンプは吐出量を０にして無負荷回転状態に
保つように制御する。このように必要油量に応じ
て最小台数のポンプだけをオンロードし、残りの
ポンプをアンロードさせ、かつ、オンロードさせ
たポンプのうち１台のポンプのみを中間吐出量で
運転するだけで、他のポンプは100％吐出量で運
転することにより、ポンプを効率よく作動させ、
省エネルギー効果を高めることができる。 In this way, as the required oil amount increases, each pump 11, 12, 13, 14 is sequentially on-loaded (in the case of a decrease, the opposite is applied), and the discharge amount is adjusted to the required oil amount.
The required amount of oil is met by several 100% pumps and one medium-load pump that makes up for the shortage.
The other pumps are controlled so that their discharge amounts are set to 0 and maintained in a no-load rotation state. In this way, only the minimum number of pumps are on-loaded depending on the required oil amount, the remaining pumps are unloaded, and only one of the on-loaded pumps is operated at an intermediate discharge amount. , other pumps operate at 100% discharge volume to ensure efficient pump operation.
Energy saving effects can be enhanced.

ここで、ポンプ総効率を考察すると第５図の通
りである。すなわち第５図は、必要油量を満たす
ポンプ総吐出量と、ポンプ総効率との関係を示す
ものであり、線は従来の方法で全ポンプを一斉
にオンロードした状態で全ポンプの吐出量を均等
に制御した場合を示し、線は本発明の方法によ
り、４台のポンプを必要油量が25％、50％、75％
のときに次のポンプを順次オンロードさせ、か
つ、それ以前にオンロードしたポンプを100％吐
出量で使用するように制御した場合を示してい
る。第５図で明らかなように、ポンプ総吐出量が
少ない領域において、従来では、全ポンプが低吐
出量でポンプ効率が悪い状態で使用されるため
に、ポンプ総効率が悪くなつているのに対し、本
発明によれば、オンロードしたポンプを効率のよ
い状態で使用しているので、従来に比べてポンプ
総効率を斜線分だけアツプできる。これに伴つて
消費電力量を節減でき、省エネルギー効果を高め
ることができる。 Here, when considering the pump total efficiency, it is as shown in Fig. 5. In other words, Figure 5 shows the relationship between the total pump discharge amount that satisfies the required oil amount and the total pump efficiency. The line shows the case where the required oil amount is 25%, 50%, and 75% by using the method of the present invention.
The figure shows the case where the next pump is sequentially turned on and the previously loaded pump is controlled to be used at 100% discharge rate. As is clear from Figure 5, in the area where the total pump discharge volume is small, conventionally all pumps are used with low discharge volume and poor pump efficiency, so the total pump efficiency deteriorates. On the other hand, according to the present invention, since the on-loaded pump is used in an efficient state, the total efficiency of the pump can be increased by the shaded area compared to the conventional system. Accordingly, power consumption can be reduced and energy saving effects can be enhanced.

因みに、今、たとえば４台の可変容量形ポンプ
を用い、押出し行程における作動速度を仕様最高
速度の25％と50％の場合を想定して省エネルギー
効果を考察すると、従来の全ポンプ均等制御方式
では、全ポンプをその吐出量を25％および50％に
制御してオンロードするのに対し、本発明では作
動速度が仕様最高速度の25％の場合は１台のポン
プのみを100％吐出量でオンロードして他の３台
のポンプをアンロードさせ、作動速度が仕様最高
速度の50％の場合は２台のポンプを100％吐出量
でオンロードして他の２台のポンプをアンロード
させることにより、第６図に示すような省エネル
ギー効果が得られる。第６図は上記各場合におけ
る従来方式による消費電力量を100として、本発
明による各場合の消費電力量の割合をそれぞれの
押出し圧力の場合で試算したものであり、線イは
作動速度が仕様最高速度の25％の場合の消費電力
量の割合を示し、線ロは作動速度が仕様最高速度
の50％の場合の消費電力量の割合を示している。
これによれば、従来に比べて、消費電力量をイの
場合で20〜40％、ロの場合で８〜18％節約でき、
押出し圧力（とくに50Kg／cm2以下の場合は顕著）
が低い程、作動速度が遅い程、消費電力量を節約
でき、省エネルギー効果が大きいことがわかる。 By the way, if we consider the energy saving effect by assuming that, for example, four variable displacement pumps are used and the operating speed during the extrusion stroke is 25% and 50% of the maximum specification speed, the conventional all-pump uniform control method , all pumps are on-loaded with their discharge volumes controlled at 25% and 50%, whereas in the present invention, when the operating speed is 25% of the maximum specification speed, only one pump is controlled at 100% discharge volume. Onload and unload the other three pumps, and if the operating speed is 50% of the maximum specification speed, onload two pumps at 100% discharge rate and unload the other two pumps. By doing so, an energy saving effect as shown in FIG. 6 can be obtained. Figure 6 shows the ratio of power consumption in each case according to the present invention calculated for each extrusion pressure, with the power consumption by the conventional method in each of the above cases set as 100, and line A indicates the operating speed specified. The percentage of power consumption is shown when the operating speed is 25% of the maximum speed, and the line (circle) shows the percentage of power consumption when the operating speed is 50% of the specified maximum speed.
According to this, compared to conventional methods, power consumption can be reduced by 20 to 40% in case A and 8 to 18% in case B.
Extrusion pressure (especially noticeable when it is less than 50Kg/ cm2 )
It can be seen that the lower the value and the slower the operating speed, the more power consumption can be saved and the energy saving effect is greater.

さらに、上記制御時において、アンロードして
いるポンプにおいては油圧回路のアンロードだけ
でなく、その駆動用モータ２１，２２，２３，２
４自身を停止させれば省エネルギー効果はさらに
大きくなることはいうまでもない。この場合、自
由シーケンスによつてモータの駆動、停止の制御
も同時に容易に行い得るものである。 Furthermore, during the above control, in the unloading pump, not only the hydraulic circuit is unloaded, but also the drive motors 21, 22, 23, 2
It goes without saying that the energy saving effect will be even greater if 4 itself is stopped. In this case, the drive and stop of the motor can be easily controlled at the same time using the free sequence.

ところで、上記実施例では、先にオンロードし
たポンプが100％傾転後に、次のポンプが傾転を
開始する場合について説明したが、第８図に示す
ように、たとえば押出し域で、ステム６４の作動
速度を連続的に変化させる必要がある場合には、
次のように制御する。すなわち、この種の可変容
量形ポンプで吐出量を制御する場合、吐出量が小
さい範囲では制御精度が悪いため、前記作動速度
の変化に対応して各ポンプを順次オンロードする
と共に、先にオンロードしたポンプ１１の吐出量
が最大になる前たとえば90％になつたときに、次
のポンプ１２をオンロードし、かつ、そのつなぎ
の部分で、先にオンロードしたポンプ１１の吐出
量と、新たにオンロードしたポンプ１２の吐出量
とを同時に可変制御する。これにより、必要油量
の変化を、吐出量精度の良い領域にある先のポン
プ１１と、吐出量精度の悪い領域にある次のポン
プ１２とによつて満たし、新たにオンロードした
ポンプ１２の精度誤差を、先にオンロードしたポ
ンプ１１によつて補うことができ、速度変化のつ
なぎの部分で設定速度に対する実速度の誤差を小
さくでき、金属押出しプレスの速度制御が円滑に
行われる。 By the way, in the above embodiment, the case where the next pump starts tilting after the first on-loaded pump has tilted 100% has been explained, but as shown in FIG. If it is necessary to continuously change the operating speed of
Control as follows. In other words, when controlling the discharge amount with this type of variable displacement pump, the control accuracy is poor in a range where the discharge amount is small. Before the discharge amount of the loaded pump 11 reaches the maximum, for example, when it reaches 90%, the next pump 12 is on-loaded, and at the transition point, the discharge amount of the previously on-loaded pump 11 is changed, At the same time, the discharge amount of the newly loaded pump 12 is variably controlled. As a result, changes in the required oil amount are satisfied by the previous pump 11 in the area with good discharge rate accuracy and the next pump 12 in the area with poor discharge rate accuracy, and the newly on-loaded pump 12. Accuracy errors can be compensated for by the pump 11 that was previously on-loaded, and the error between the actual speed and the set speed can be reduced at the transition between speed changes, and the speed control of the metal extrusion press can be performed smoothly.

以上説明したように、本発明は、金属押出しプ
レスの予め設定された作動速度に基いて、該プレ
スの仕様最高速度に対する割合から必要油量を求
め、その必要油量に応じて最小台数の可変容量形
ポンプだけをオンロードし、残りの可変容量形ポ
ンプをアンロードさせ、しかも、オンロードさせ
た可変容量形ポンプのうち１台のポンプのみを可
変吐出状態で運転するだけで、他のポンプは100
％吐出状態つまり最大効率で運転することによ
り、可変容量形ポンプの総効率を大幅にアツプで
き、従来のように常に全ポンプが一斉にオンロー
ドする方式に比べて、消費電力量が少なくなり、
省エネルギー効果を大幅に高めることができる。 As explained above, the present invention calculates the required amount of oil from the ratio of the specified maximum speed of the press based on the preset operating speed of the metal extrusion press, and changes the minimum number of units according to the required amount of oil. By on-loading only the displacement pump and unloading the remaining variable-displacement pumps, you can operate only one of the variable-displacement pumps that was on-loaded in a variable discharge state, and the other pumps can be is 100
% discharge state, that is, operating at maximum efficiency, the total efficiency of the variable displacement pump can be greatly increased, and compared to the conventional method where all pumps are always on-load at the same time, power consumption is reduced.
The energy saving effect can be greatly increased.

また、前記作動速度が連続的に変化する場合、
その速度変化に応じて各可変容量形ポンプを順次
オンロードすると共に、先にオンロードしている
ポンプが100％傾転する前に、次のポンプをオン
ロードし、かつ、そのつなぎの部分で、先にオン
ロードしているポンプの吐出量と、新たにオンロ
ードしたポンプの吐出量とを、必要油量の変化に
対応して同時に可変制御することにより、新たに
オンロードしたポンプの傾転初期の精度誤差の影
響を緩和でき、速度変化のつなぎを滑かにでき、
金属押出しプレスを極めて円滑に作動させること
ができる。 Further, when the operating speed changes continuously,
Each variable displacement pump is sequentially on-loaded according to the speed change, and the next pump is on-loaded before the previously on-loaded pump reaches 100% rotation, and at the transition point. , by simultaneously variable controlling the discharge amount of the previously on-loaded pump and the discharge amount of the newly on-loaded pump in response to changes in the required oil amount, the inclination of the newly on-loaded pump can be adjusted. The effect of accuracy errors at the beginning of rotation can be alleviated, and the transition between speed changes can be made smoother.
The metal extrusion press can operate extremely smoothly.

【図面の簡単な説明】[Brief explanation of the drawing]

第１図は本発明の方法を実施する金属押出しプ
レスの油圧回路図、第２図はその制御信号を取出
すための制御装置の一例を示す概略電気回路図、
第３図はプレス作動速度と可変容量形ポンプのオ
ンロードとの関係を示す説明図、第４図はプレス
作動速度とポンプ傾転角との関係を示す説明図、
第５図は可変容量形ポンプの総吐出量と総効率と
の関係を示す説明図、第６図は本発明による省エ
ネルギー効果を示す説明図、第７図はプレスの作
動行程と作動速度との関係を示す説明図、第８図
は作動速度が連続的に変化する場合の作動行程説
明図、第９図は可変容量形ポンプの容積効率を示
す特性図、第１０図は可変容量形ポンプの全体効
率を示す特性図である。 １１，１２，１３，１４……可変容量形ポン
プ、３１，３２，３３，３４……吐出量制御器、
４１，４２，４３，４４……ロード切換用電磁
弁、６０……金属押出しプレス、８０……速度設
定器、８１……検出子、８２……演算器、C1，
C2，C3，C4……吐出量制御用電気信号、C1′，
C2′，C3′，C4′……ロード切換制御用電気信号。 FIG. 1 is a hydraulic circuit diagram of a metal extrusion press that implements the method of the present invention, and FIG. 2 is a schematic electrical circuit diagram showing an example of a control device for extracting control signals.
FIG. 3 is an explanatory diagram showing the relationship between the press operating speed and the on-load of the variable displacement pump, and FIG. 4 is an explanatory diagram showing the relationship between the press operating speed and the pump tilting angle.
Fig. 5 is an explanatory diagram showing the relationship between the total discharge amount and total efficiency of a variable displacement pump, Fig. 6 is an explanatory diagram showing the energy saving effect of the present invention, and Fig. 7 is an explanatory diagram showing the relationship between the operating stroke and operating speed of the press. An explanatory diagram showing the relationship, Fig. 8 is an explanatory diagram of the operating stroke when the operating speed changes continuously, Fig. 9 is a characteristic diagram showing the volumetric efficiency of the variable displacement pump, and Fig. 10 is an explanatory diagram of the volumetric efficiency of the variable displacement pump. FIG. 3 is a characteristic diagram showing overall efficiency. 11, 12, 13, 14... variable displacement pump, 31, 32, 33, 34... discharge amount controller,
41, 42, 43, 44... Solenoid valve for load switching, 60... Metal extrusion press, 80... Speed setter, 81... Detector, 82... Arithmetic unit, C 1 ,
C 2 , C 3 , C 4 ...Electric signal for controlling discharge amount, C 1 ′,
C 2 ′, C 3 ′, C 4 ′...Electrical signals for load switching control.

Claims (1)

【特許請求の範囲】 １ 並列に接続された複数台の可変容量形ポンプ
から金属押出しプレスに圧油を供給して金属押出
しプレスを作動させる方法において、 該プレスにおけるステムの作動速度設定器に設
定された設定値に基いて該プレスの必要油量を求
め、 その必要油量が可変容量形ポンプ１台分の最大
吐出量以下のときは、可変容量形ポンプ１台をオ
ンロードして同ポンプからの吐出油によつて必要
油量を満たすように流量制御すると共に、残りの
可変容量形ポンプをアンロードさせ、 必要油量が可変容量形ポンプ１乃至数台分の最
大吐出量より多いときは、最大吐出状態でオンロ
ードした１乃至数台の可変容量形ポンプからの吐
出油と、その不足分を補うように可変吐出状態で
オンロードした１台の可変容量形ポンプからの吐
出油とによつて必要油量を満たすように流量制御
すると共に、残りの可変容量形ポンプをアンロー
ドすることを特徴とする金属押出しプレスの作動
方法。 ２ 並列に接続された複数台の可変容量形ポンプ
から金属押出しプレスに圧油を供給して金属押出
しプレスを作動させる方法において、 該プレスにおけるステムの作動速度設定器に設
定された設定値に基いて、該プレスの必要油量を
求め、 その必要油量が可変容量形ポンプ１台分の最大
吐出量以下のときは、可変容量形ポンプ１台をオ
ンロードして同ポンプからの吐出油によつて必要
油量を満たすように流量制御すると共に、残りの
可変容量形ポンプをアンロードさせ、 必要油量が可変容量形ポンプ１乃至数台分の最
大吐出量より多いときは、最大吐出状態もしくは
それに近い状態でオンロードした１乃至数台の可
変容量形ポンプからの吐出油と、その不足分を補
うように可変吐出状態でオンロードした１台の可
変容量形ポンプからの吐出油とによつて必要油量
を満たすように流量制御すると共に、残りの可変
容量形ポンプをアンロードさせ、 さらに、必要油量が連続的に変化するときは、
前記可変容量形ポンプを順次オンロードして必要
油量を連続的に満たし、かつ、そのつなぎの部分
で、先にオンロードした可変容量形ポンプが最大
吐出状態になる以前に次の可変容量形ポンプをオ
ンロードすると共に、必要油量の変化量に応じて
先にオンロードした可変容量形ポンプの吐出量
と、新たにオンロードした可変容量形ポンプの吐
出量とを同時に可変制御して必要油量を連続的に
満たすようにしたことを特徴とする金属押出しプ
レスの作動方法。[Claims] 1. A method for operating a metal extrusion press by supplying pressure oil to the metal extrusion press from a plurality of variable displacement pumps connected in parallel, comprising: setting an operating speed setting device of a stem in the press; The amount of oil required for the press is determined based on the set value, and if the amount of oil required is less than the maximum discharge amount for one variable displacement pump, one variable displacement pump is on-loaded and the same pump is The flow rate is controlled so that the required oil amount is met by the oil discharged from the pump, and the remaining variable displacement pumps are unloaded. When the required oil amount is greater than the maximum discharge amount for one or several variable displacement pumps. is the discharge oil from one or several variable displacement pumps that are on-loaded in the maximum discharge state, and the discharge oil from one variable-displacement pump that is on-loaded in the variable discharge state to make up for the shortage. 1. A method for operating a metal extrusion press, which comprises controlling the flow rate to meet the required amount of oil by using a variable displacement pump, and unloading the remaining variable displacement pump. 2. In a method of operating a metal extrusion press by supplying pressure oil to the metal extrusion press from multiple variable displacement pumps connected in parallel, If the required oil amount is less than the maximum discharge amount for one variable displacement pump, one variable displacement pump is on-loaded to absorb the oil discharged from the same pump. Therefore, the flow rate is controlled to meet the required oil amount, and the remaining variable displacement pumps are unloaded, and when the required oil amount is greater than the maximum discharge amount for one or several variable displacement pumps, the system returns to the maximum discharge state. Or the oil discharged from one or several variable displacement pumps that are on-loaded in a similar state, and the oil discharged from one variable-displacement pump that is loaded on-loaded in a variable discharge state to make up for the shortage. Therefore, the flow rate is controlled to meet the required oil amount, and the remaining variable displacement pump is unloaded.Furthermore, when the required oil amount changes continuously,
The variable displacement pumps are sequentially loaded to meet the required oil amount, and at the junction, the next variable displacement pump is turned on before the previously loaded variable displacement pump reaches its maximum discharge state. At the same time as the pump is on-loaded, the discharge amount of the variable displacement pump that was previously on-loaded and the discharge amount of the variable-displacement pump that was newly on-loaded are simultaneously controlled in accordance with the amount of change in the required oil amount. A method of operating a metal extrusion press characterized by continuously filling the amount of oil.
JP13661879A 1979-10-22 1979-10-22 Controller for hydraulic circuit including plural variable-capacity pumps in parallel Granted JPS5659005A (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP13661879A JPS5659005A (en) 1979-10-22 1979-10-22 Controller for hydraulic circuit including plural variable-capacity pumps in parallel
EP19800303741 EP0027743B1 (en) 1979-10-22 1980-10-22 Control system for a hydraulic circuit including a plurality of parallel variable-delivery pumps
DE8080303741T DE3070650D1 (en) 1979-10-22 1980-10-22 Control system for a hydraulic circuit including a plurality of parallel variable-delivery pumps

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP13661879A JPS5659005A (en) 1979-10-22 1979-10-22 Controller for hydraulic circuit including plural variable-capacity pumps in parallel

Publications (2)

Publication Number Publication Date
JPS5659005A JPS5659005A (en) 1981-05-22
JPH0258482B2 true JPH0258482B2 (en) 1990-12-07

Family

ID=15179505

Family Applications (1)

Application Number Title Priority Date Filing Date
JP13661879A Granted JPS5659005A (en) 1979-10-22 1979-10-22 Controller for hydraulic circuit including plural variable-capacity pumps in parallel

Country Status (3)

Country Link
EP (1) EP0027743B1 (en)
JP (1) JPS5659005A (en)
DE (1) DE3070650D1 (en)

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Also Published As

Publication number Publication date
EP0027743A1 (en) 1981-04-29
JPS5659005A (en) 1981-05-22
EP0027743B1 (en) 1985-05-15
DE3070650D1 (en) 1985-06-20

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