EP0231735B1 - Gleichlaufregeleinrichtung für einen hydraulischen Mehrzylinderantrieb - Google Patents

Gleichlaufregeleinrichtung für einen hydraulischen Mehrzylinderantrieb Download PDF

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Publication number
EP0231735B1
EP0231735B1 EP19860890350 EP86890350A EP0231735B1 EP 0231735 B1 EP0231735 B1 EP 0231735B1 EP 19860890350 EP19860890350 EP 19860890350 EP 86890350 A EP86890350 A EP 86890350A EP 0231735 B1 EP0231735 B1 EP 0231735B1
Authority
EP
European Patent Office
Prior art keywords
cylinder
hydraulic
control
pressure
working
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
EP19860890350
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German (de)
English (en)
French (fr)
Other versions
EP0231735A1 (de
Inventor
Bernd Walter
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.)
Hoerbiger Hydraulik GmbH
Original Assignee
Hoerbiger Hydraulik GmbH
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Filing date
Publication date
Application filed by Hoerbiger Hydraulik GmbH filed Critical Hoerbiger Hydraulik GmbH
Publication of EP0231735A1 publication Critical patent/EP0231735A1/de
Application granted granted Critical
Publication of EP0231735B1 publication Critical patent/EP0231735B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/22—Synchronisation of the movement of two or more servomotors
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/24—Control arrangements for fluid-driven presses controlling the movement of a plurality of actuating members to maintain parallel movement of the platen or press beam

Definitions

  • the invention relates to a synchronous control device for a hydraulic multi-cylinder drive, in particular for a die bending machine, each with a displacement transducer assigned to each working cylinder and connected to a common electronic control unit, and each with a control valve acted upon with pressure medium and connected to the control unit via control lines for each working cylinder, with all control valves are connected to a common drive station for supplying the working cylinders with pressure medium.
  • the object of the present invention is to improve a synchronization control device of the type mentioned at the outset in such a way that the structural outlay for the device can be further reduced while maintaining the high achievable parallelism or synchronization accuracy.
  • This is achieved in accordance with the present invention in that both sides of each working cylinder are connected via a shuttle valve to a three-way pressure compensator common to all working cylinders.
  • the use of the three-way pressure compensator which is already known per se in connection with the known electronic-hydraulic synchronous control device mentioned at the beginning, enables a low power loss in the dynamic state of the multi-cylinder drive, since this means that the unnecessary amount of pressure medium under the currently existing system pressure is via these three-way - Pressure compensator can be routed to the tank and does not have to be routed through the maximum pressure relief valve, which would mean a higher heat dissipation. Furthermore, this three-way pressure compensator ensures a constant pressure drop across the individual channels of the proportional directional control valves.
  • the upper beam 1 of the die bending machine which is not shown in further detail, is equipped with a hydraulic at its two outer ends 2, 3
  • the cylinder / piston arrangement 4 is provided, in each case the piston 5 with the upper beam 1 itself and the cylinder 6 in a manner not shown in connection with the machine frame in connection.
  • the lower beam 7 is rigidly connected to the machine frame in a manner also not shown, with which a relative movement between the upper beam 1 and the lower beam 7 can be brought about via the cylinder / piston arrangements 4, which bending work on corresponding, usually interchangeable die tools, between the upper beam 1 and the lower beam 7 workpieces located.
  • displacement transducers 8 are arranged, for example according to the principle of the reflection light barrier, in an inductive manner, or by using another known principle, either in an analog or incremental or digital manner Provide the actual signal between the actual distance between the upper beam 1 and lower beam 7 or send it to a common electronic control unit 10 via signal lines 9.
  • the drive station 17 connected to the annular spaces 11 of the cylinder / piston arrangements 4 via lines 12 to 16 essentially consists of a motor 18, the hydraulic pump 19 coupled to it and any filters not shown here, and is for both cylinder / piston arrangements 4 together.
  • control valves designed as proportional directional control valves 20 are switched on, which can be actuated directly from the control unit 10 via proportional magnets 21 and corresponding control lines 22, and depending on their switching position enable a more or less large amount of pressure on the annular spaces 11 - or alternatively via the lines 23, 23 'also the cylinder spaces 24 - and at the same time also the backflow of the hydraulic medium from the cylinder spaces 24 or annular spaces 11 via lines 25, Release or shut off 26, 27 in the tank 28 accordingly.
  • the outlet of the shuttle valve 37 at which, according to the design of all three shuttle valves, the highest system pressure is always present, is connected via a line 38 to a three-way pressure compensator 39, which, in the exemplary embodiment shown, is designed as a slide element, the input of line 38 from the superordinate shuttle valve 37 opposite slide chamber of the pressure compensator 39 is connected via a line 40 to the line 12 from the pressure side of the hydraulic pump 19;
  • the annular space 42 which is shut off in the illustrated position of the slide 41 of the pressure compensator 39 is relieved via the line 27 to the tank 28.
  • a pressure control valve is located between the line 12 adjoining the pressure side of the hydraulic pump 19 and the line 27 leading to the tank 28. 43 switched on via lines 44, 45, which, for example, is also electrically proportional and is operated from the control unit 10 in a manner not shown here to limit or ensure the necessary bending pressure, which is either programmable via the electronics in the control unit 10 or from the control unit 10 the various process parameters is calculated, can be influenced.
  • the upper beam 1 will begin to move relative to the lower beam 7 in the direction of the axes of the working cylinders 4, the direction of movement depending on which of the lines 15, 23 or 16, 23 'is activated.
  • the transducers 8 the current position of the two outer ends 2, 3 of the upper beam 1 relative to the lower beam 7 is continuously transmitted to the control unit 10 via the signal lines 9, where a target / actual comparison is carried out electronically.
  • the shuttle valves 33, 34 and 37 are designed or arranged so that the excess amount of hydraulic medium not required in this state via the line 40 in the then opened ring space 42 of the pressure compensator 39 or the line 27 is shut off, so that the pressure control valve 43, at which greater heating and thus greater power loss occurs, only opens at the bending point or at the adjustable maximum pressure.
  • the device shown and described manages with only one drive station and a pressure compensator regardless of the number of working cylinders, the design effort for the nevertheless very precise synchronization control is significantly reduced, which is also reflected in a reduced assembly and maintenance effort.
  • the arrangement or its functioning is independent of whether symmetrical or asymmetrical pistons are used for the proportional directional control valves, which allows a wide variety of cylinder transmission ratios of the working cylinders to be taken into account. Furthermore, to improve the control accuracy via the proportional directional control valves, the position of the pistons of these valves, not shown here, can be provided directly, which correspond to the control unit 10 via their own signal lines and a SoIVlst control of these valves and thus a further increased accuracy of the synchronous control device enable.
EP19860890350 1985-12-30 1986-12-19 Gleichlaufregeleinrichtung für einen hydraulischen Mehrzylinderantrieb Expired - Lifetime EP0231735B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT3773/85 1985-12-30
AT377385A AT385466B (de) 1985-12-30 1985-12-30 Gleichlaufregeleinrichtung fuer einen hydraulischen mehrzylinderantrieb

Publications (2)

Publication Number Publication Date
EP0231735A1 EP0231735A1 (de) 1987-08-12
EP0231735B1 true EP0231735B1 (de) 1990-01-24

Family

ID=3555231

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19860890350 Expired - Lifetime EP0231735B1 (de) 1985-12-30 1986-12-19 Gleichlaufregeleinrichtung für einen hydraulischen Mehrzylinderantrieb

Country Status (5)

Country Link
EP (1) EP0231735B1 (zh)
JP (1) JPS62230426A (zh)
CN (1) CN1007371B (zh)
AT (1) AT385466B (zh)
DE (1) DE3668433D1 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104540666A (zh) * 2012-04-17 2015-04-22 贺尔碧格自动化技术控股股份有限公司 压床

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2655907B1 (fr) * 1989-12-19 1993-07-30 Plazenet Jean Presse plieuse hydraulique a tablier inferieur mobile.
JPH087934Y2 (ja) * 1990-03-28 1996-03-06 株式会社小松製作所 プレスブレーキの油圧回路
CH683162A5 (fr) * 1990-04-25 1994-01-31 Bobst Sa Procédé d'asservissement du parallélisme des deux sommiers d'une presse à découper des éléments en forme de feuille ou bande en vue de la production d'emballages.
FR2676041B1 (fr) * 1991-05-03 1997-10-03 Freyssinet Procede de levage multipoint controle de structures importantes relativement souples, et systemes correspondant.
IT1264249B1 (it) * 1993-10-22 1996-09-23 Ravaglioli Spa "sollevatore elettroidraulico"
SE517223C2 (sv) * 2000-09-20 2002-05-14 Morphic Technologies Ab Hydraulanordning för synkronisering av åtminstone två samverkande hydraulkolvar
CN1325803C (zh) * 2004-11-03 2007-07-11 北京中水长固液分离技术有限公司 一种多缸同步加压压紧装置及控制方法
CN101975202B (zh) * 2010-10-15 2013-07-24 马鞍山钢铁股份有限公司 一种液压缸同步控制系统的控制方法
CN102943789B (zh) * 2012-11-09 2015-12-09 昆明中铁大型养路机械集团有限公司 一种可调压力和流量的缓冲液压缸、控制方法及液压系统
CN102996580A (zh) * 2012-11-27 2013-03-27 齐齐哈尔轨道交通装备有限责任公司 旁承油缸控制系统
CN103089750B (zh) * 2012-12-10 2015-11-18 天水锻压机床(集团)有限公司 用可编程控制器进行多组油缸控制的控制器及其控制方法
CN103640248A (zh) * 2013-11-16 2014-03-19 苏州蓝王机床工具科技有限公司 龙门液压机双液压缸同步控制系统
CN103671334B (zh) * 2013-12-12 2016-01-27 中联重科股份有限公司 一种油气悬挂油缸同步升降的液压控制系统及工程车辆
CN103775418B (zh) * 2014-01-06 2014-10-29 华中科技大学 一种液压机双缸同步装置
DE102014005352B4 (de) * 2014-04-11 2016-03-10 Hoerbiger Automatisierungstechnik Holding Gmbh Maschinenpresse
CN105458251B (zh) * 2014-09-02 2018-02-06 天津市天锻压力机有限公司 基于Delta控制器的粉末液压机精确定位系统
CN105465074A (zh) * 2014-09-02 2016-04-06 天津市天锻压力机有限公司 基于Delta控制器的粉末液压机过程同步运动系统
CN104340905A (zh) * 2014-11-12 2015-02-11 南京中船绿洲机器有限公司镇江船舶辅机厂 双吊点收放装置同步检测电路及同步控制方法
CN104747516B (zh) * 2015-01-30 2017-03-22 四川南骏汽车集团有限公司 一种液压缸同步升降控制系统
CN104743470A (zh) * 2015-03-31 2015-07-01 苏州艾沃意特机械设备制造有限公司 可视化自调平双柱式举升机
CN105020192A (zh) * 2015-07-30 2015-11-04 中国重型机械研究院股份公司 一种新型钢包升降同步控制系统
CN105818417A (zh) * 2016-05-24 2016-08-03 郭文坤 一种压力自平衡冲床
CN106438520A (zh) * 2016-12-17 2017-02-22 中国重型机械研究院股份公司 一种冷床升降液压同步控制装置
CN112387335A (zh) * 2020-11-05 2021-02-23 混楚(上海)环保设备制造有限公司 一种废混凝土智能静压破碎装置

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2029287C3 (de) * 1970-06-13 1978-07-13 Vereinigte Flugtechnische Werke- Fokker Gmbh, 2800 Bremen Anordnung zur Überwachung und Anpassung von mehreren auf einen gemeinsamen Ausgang wirkenden elektrohydraulischen Stellantrieben
US4145958A (en) * 1977-12-02 1979-03-27 Borg-Warner Corporation Fluid control system with automatically actuated motor port lock-out valves
DD204460A1 (de) * 1982-03-24 1983-11-30 Bauakademie Ddr Hydraulische einrichtung zur synchronen bewegung von lasten
JPH0677879B2 (ja) * 1985-07-06 1994-10-05 株式会社アマダ 加工機械の電気液圧サ−ボ装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104540666A (zh) * 2012-04-17 2015-04-22 贺尔碧格自动化技术控股股份有限公司 压床
CN104540666B (zh) * 2012-04-17 2017-05-17 贺尔碧格自动化技术控股股份有限公司 压床

Also Published As

Publication number Publication date
AT385466B (de) 1988-04-11
CN86108883A (zh) 1987-08-12
ATA377385A (de) 1987-09-15
EP0231735A1 (de) 1987-08-12
DE3668433D1 (de) 1990-03-01
JPS62230426A (ja) 1987-10-09
CN1007371B (zh) 1990-03-28

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