CN102155445A - Hydraulic control system with double-feedback active proportional servo cartridge valve for CNC (Computer Numerical Control) bending machine - Google Patents
Hydraulic control system with double-feedback active proportional servo cartridge valve for CNC (Computer Numerical Control) bending machine Download PDFInfo
- Publication number
- CN102155445A CN102155445A CN2011100465611A CN201110046561A CN102155445A CN 102155445 A CN102155445 A CN 102155445A CN 2011100465611 A CN2011100465611 A CN 2011100465611A CN 201110046561 A CN201110046561 A CN 201110046561A CN 102155445 A CN102155445 A CN 102155445A
- Authority
- CN
- China
- Prior art keywords
- valve
- communicated
- control
- master cylinder
- way
- 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.)
- Granted
Links
Images
Landscapes
- Control Of Presses (AREA)
- Bending Of Plates, Rods, And Pipes (AREA)
Abstract
The invention relates to a hydraulic control system with a double-feedback active proportional servo cartridge valve for a CNC (Computer Numerical Control) bending machine, in particular to hydraulic control system equipment with the double-feedback active proportional servo cartridge valve for the CNC bending machine, wherein the hydraulic control system is synchronized actively and has adjustable speed servo. The hydraulic control system consists of two main cylinder control valve banks, an oil inlet control valve bank and a workbench compensating oil cylinder, wherein the two main cylinder control valve banks are arranged separately; two double-active servo cartridge valve units, a safety control unit and a pressure regulating unit are arranged in each valve bank; the two main cylinder control valve banks are used for driving corresponding main cylinders respectively to ensure the synchronous position accuracy of each main cylinder; and the oil inlet control valve bank is used for controlling the inlet and outlet of oil and the proportional regulation of the system pressure and supplying pilot control oil to the double-active servo cartridge valve. The hydraulic control system has the advantages of simple structure, accuracy and simplicity and convenience for operation control due to the adoption of the cartridge valve, stability and reliability for work, no leakage, high efficiency, reduced energy consumption, reduced equipment manufacturing cost and high integration degree, and is widely applied to the hydraulic control equipment of the CNC bending machine.
Description
Technical field:
The present invention relates to the active proportional servo cartridge valve numerical control bender hydraulic control system of a kind of two feedbacks, particularly have active synchronization, the active proportional servo cartridge valve numerical control bender hydraulic control system equipment of two feedbacks that speed servo is adjustable.
Background technique:
At present, numerical control bender is mainly used in sheetmetal working, can reduce operation easier according to angle automatic computing engine tool position, increases work efficiency.The main sliding valve style hydraulic control system equipment that adopts the development fifties in the numerical control bender system, its guiding valve hydraulic control system performance parameter is low, when running into bigger offset loading force in the bender working stroke, can produce bigger unbalance loading moment to equipment, can not guarantee the displacement accuracy of oil cylinder, main frame mechanism is deformed, cause the bender precision low, while control section complex structure, rate of fault height, leak serious, action is unstable, impacts greatly, descends speed unadjustable soon, it is bigger to take up room, and maintenance is inconvenient.
Summary of the invention:
Purpose of the present invention provides the active proportional servo cartridge valve numerical control bender hydraulic control system of a kind of two feedbacks, and it is to adopt cartridge valve to combine with the integrated hydraulic control system, the control system of control numerical control bender, it is low to solve the bender precision, complex structure, rate of fault height, leak serious, action is unstable, impacts greatly, descends speed unadjustable soon, it is bigger to take up room, the problem that maintenance is inconvenient.
The active proportional servo cartridge valve numerical control bender hydraulic control system of the two feedbacks of the present invention takes following technological scheme to realize: it is to be made of two master cylinder control valve groups, an oil-feed control valve group and a worktable compensating cylinder, two master cylinder control valve groups are provided with separately, be provided with two two initiatively servo cartridge valve unit and security control unit and pressure regulation unit in each valve group, drive corresponding master cylinder respectively, guarantee the sync bit precision of each master cylinder; The turnover of oil-feed control valve group control fluid and the ratio of system pressure are regulated and are provided two initiatively guides of servo cartridge valve to control oil; The worktable that the worktable compensating cylinder is used for before the bending is regulated, by pump, the two-position four-way solenoid directional control valve, proportional servo valve, Solenoid ball valve, direct-acting overflow valve, cartridge valve, two aggressive valve, electromagnetic relief valve, one-way valve, reduction valve, proportional pressure control valve, accumulator and control valve group constitute, it is the number one pump, No. three pump, the oil outlet of No. four pump is connected with oil-feed control valve group, No. second pump connects high pressure filter one end, the high pressure filter the other end is connected with oil-feed control valve group, electromagnetic relief valve one end is communicated with high pressure filter, the electromagnetic relief valve the other end is communicated with oiling valve group return opening, No. second one-way valve one end is communicated with high pressure filter, No. second the one-way valve the other end is communicated with reduction valve, the reduction valve the other end is communicated with No. three two-position four-way solenoid valve, No. three two-position four-way solenoid valve the other end is by liquid-filling valve control mouth and number one liquid-filling valve, No. second liquid-filling valve is communicated with, direct-acting overflow valve one end is communicated with No. second one-way valve, the direct-acting overflow valve the other end is communicated with oiling valve group return opening, accumulator is communicated with No. second one-way valve, accumulator is communicated with number one master cylinder control valve group and No. second master cylinder control valve group by number one flange mouth and proportional servo valve filler opening, number one one-way valve one end is communicated with the number one pump, the number one one-way valve the other end is communicated with No. second cartridge valve, No. three one-way valve one end is communicated with No. four pump, No. three the one-way valve the other end is communicated with No. second plug-in mounting pressure valve, No. four one-way valve one end is communicated with No. three pump, No. four the one-way valve the other end is communicated with No. second plug-in mounting pressure valve, No. second the plug-in mounting pressure valve the other end is communicated with oiling valve group return opening, proportional pressure control valve one end is communicated with No. second plug-in mounting pressure valve and No. four one-way valve, the proportional pressure control valve the other end is communicated with oiling valve group return opening, No. second plug-in mounting pressure valve one end is communicated with number one master cylinder control valve group and No. second master cylinder control valve group by No. second flange mouth, No. second plug-in mounting pressure valve one end is communicated with the threeway proportional pressure-reducing valve by No. three flange mouth, and the other end of threeway proportional pressure-reducing valve is connected with the worktable compensating cylinder; Master cylinder control valve group filler opening is communicated with No. second two aggressive valve one ends, the other end of No. second two aggressive valve is communicated with the plug chamber of No. second liquid-filling valve and No. second master cylinder, the control oil of No. second two aggressive valve is communicated with No. second proportional servo valve, No. second proportional servo valve is communicated with proportional servo valve filler opening and proportional servo valve return opening, No. second cartridge valve one end is communicated with main valve group filler opening, No. second the cartridge valve the other end is communicated with the two aggressive valve of number one plug-in mounting pressure valve and number one cartridge valve and number one, connect No. second two-position four-way solenoid valve on No. second cartridge valve, connect Solenoid ball valve on the number one cartridge valve, the number one two-position four-way solenoid valve is communicated with number one plug-in mounting pressure valve, the number one plug-in mounting pressure valve the other end is communicated with main valve group return opening, the two aggressive valve the other ends of number one are communicated with main valve group return opening, the control oil of the two aggressive valve of number one is communicated with the number one proportional servo valve, the number one proportional servo valve is communicated with proportional servo valve filler opening and proportional servo valve return opening, the number one cartridge valve the other end connects the bar chamber of master cylinder, one end of safety valve connects the bar chamber of master cylinder, the other end of safety valve is communicated with main valve group return opening, and the grating chi is installed in the master cylinder side.
The effect of the active proportional servo cartridge valve numerical control bender hydraulic control system of the two feedbacks of the present invention is simple in structure, adopt cartridge valve, the external form volume is little, operation control is accurately easy, and working stability is reliable, does not have and reveals, have high efficiency and energy efficient, reduce equipment manufacturing cost, the level of integration height is widely used on the numerical control bender machine hydraulic-pressure control apparatus.
Description of drawings:
The active proportional servo cartridge valve numerical control bender hydraulic control system of the two feedbacks of the present invention will describe in further detail in conjunction with the accompanying drawings.
Fig. 1 is the hydraulic structure schematic representation of the active proportional servo cartridge valve numerical control bender hydraulic control system of the two feedbacks of the present invention.
Fig. 2 is the hydraulic structure schematic representation of master cylinder control valve group of the present invention.
Fig. 3 is the hydraulic structure schematic representation of oiling valve group of the present invention.
1—— 2—— 3—— 4—— 5—— 6—— 7—— 8—— 9—— 10—— 11—— 12—— 13—— 14——15—— 16—— 17—— 18—— 19—— 20—— 21—— 22—— 23—— 24—— 25—— 26—— 27—— 28—— 29—— 30—— 31—— 32—— 33—— 34—— 35—— 36—— 37——38—— 39—— 40—— 41—— 42—— 43—— 44——45—— 46—— 47——
Embodiment:
With reference to Fig. 1,2,3, the active proportional servo cartridge valve numerical control bender hydraulic control system of the two feedbacks of the present invention, it is to be made of two master cylinder control valve groups, an oil-feed control valve group and a worktable compensating cylinder 13, two master cylinder control valve groups are provided with separately, be provided with two two initiatively servo cartridge valve unit and security control unit and pressure regulation unit in each valve group, drive corresponding master cylinder respectively, guarantee the sync bit precision of each master cylinder; The turnover of oil-feed control valve group control fluid and the ratio of system pressure are regulated and are provided two initiatively guides of servo cartridge valve to control oil; The worktable that worktable compensating cylinder 13 is used for before the bending is regulated; By pump, the two-position four-way solenoid directional control valve, proportional servo valve, Solenoid ball valve, direct-acting overflow valve, cartridge valve, two aggressive valve, electromagnetic relief valve, one-way valve, reduction valve, proportional pressure control valve, accumulator and control valve group constitute, it is a number one pump 1, No. three pump 14, the oil outlet of No. four pump 15 is connected with oil-feed control valve group 3, No. second pump 2 connects high pressure filter 31 1 ends, high pressure filter 31 the other ends are connected with oil-feed control valve group 3, electromagnetic relief valve 32 1 ends are communicated with high pressure filter 31, electromagnetic relief valve 32 the other ends are communicated with oiling valve group return opening 47, No. second one-way valve 34 1 ends are communicated with high pressure filter 31, No. second one-way valve 34 the other ends are communicated with reduction valve 35, reduction valve 35 the other ends are communicated with No. three two-position four-way solenoid valve 36, No. three two-position four-way solenoid valve 36 the other ends are by liquid-filling valve control mouth 37 and number one liquid-filling valve 7, No. second liquid-filling valve 8 is communicated with, direct-acting overflow valve 40 1 ends are communicated with No. second one-way valve 34, direct-acting overflow valve 40 the other ends are communicated with oiling valve group return opening 47, accumulator 38 is communicated with No. second one-way valve 34, accumulator 38 is communicated with number one master cylinder control valve group 4 and No. second master cylinder control valve group 11 by number one flange mouth 39 and proportional servo valve filler opening 19, number one one-way valve 33 1 ends are communicated with number one pump 1, number one one-way valve 33 the other ends are communicated with No. second cartridge valve 43, No. three one-way valve 45 1 ends are communicated with No. four pump 15, No. three one-way valve 45 the other ends are communicated with No. second plug-in mounting pressure valve 43, No. four one-way valve 46 1 ends are communicated with No. three pump 14, No. four one-way valve 46 the other ends are communicated with No. second plug-in mounting pressure valve 43, No. second plug-in mounting pressure valve 43 the other ends are communicated with oiling valve group return opening 47, proportional pressure control valve 44 1 ends are communicated with No. second plug-in mounting pressure valve 43 and No. four one-way valve 46, proportional pressure control valve 44 the other ends are communicated with oiling valve group return opening 47, No. second plug-in mounting pressure valve 43 1 ends are communicated with number one master cylinder control valve group 4 and No. second master cylinder control valve group 11 by No. second flange mouth 41, No. second plug-in mounting pressure valve 43 1 ends are communicated with threeway proportional pressure-reducing valve 12 by No. three flange mouth 42, and the other end of threeway proportional pressure-reducing valve 12 is connected with worktable compensating cylinder 13; Master cylinder control valve group filler opening 29 is communicated with No. second two aggressive valve 27 1 ends, the other end of No. second two aggressive valve 27 is communicated with the plug chamber of No. second liquid-filling valve 8 and No. second master cylinder 9, the control oil of No. second two aggressive valve 27 is communicated with No. second proportional servo valve 28, No. second proportional servo valve 28 is communicated with proportional servo valve filler opening 19 and proportional servo valve return opening 18, No. second cartridge valve 26 1 ends are communicated with main valve group filler opening 29, No. second cartridge valve 26 the other ends are communicated with the two aggressive valve 21 of number one plug-in mounting pressure valve 30 and number one cartridge valve 23 and number one, connect No. second two-position four-way solenoid valve 25 on No. second cartridge valve 26, connect Solenoid ball valve 24 on the number one cartridge valve 23, number one two-position four-way solenoid valve 16 is communicated with number one plug-in mounting pressure valve 30, number one plug-in mounting pressure valve 30 the other ends are communicated with main valve group return opening 17, two aggressive valve 21 the other ends of number one are communicated with main valve group return opening 17, the control oil of the two aggressive valve 21 of number one is communicated with number one proportional servo valve 20, number one proportional servo valve 20 is communicated with proportional servo valve filler opening 19 and proportional servo valve return opening 18, number one cartridge valve 23 the other ends connect the bar chamber of No. second master cylinder 9, one end of safety valve 22 connects the bar chamber of second master cylinder 9, the other end of safety valve 22 is communicated with main valve group return opening 17, number one grating chi 5 is installed in the side of number one master cylinder 6, and No. second grating chi 10 is installed in the side of No. second master cylinder 9.
The embodiment of the active proportional servo cartridge valve numerical control bender hydraulic control system of the two feedbacks of the present invention, it is to be made of two master cylinder control valve groups, an oil-feed control valve group and a worktable compensating cylinder 13, two master cylinder control valve groups are provided with separately, be provided with two two initiatively servo cartridge valve unit and security control unit and pressure regulation unit in each valve group, drive corresponding master cylinder respectively, guarantee the sync bit precision of each master cylinder; The turnover of oil-feed control valve group control fluid and the ratio of system pressure are regulated and are provided two initiatively guides of servo cartridge valve to control oil; The worktable that worktable compensating cylinder 13 is used for before the bending is regulated; Constitute by pump, two-position four-way solenoid directional control valve, proportional servo valve, Solenoid ball valve, direct-acting overflow valve, cartridge valve, two aggressive valve, electromagnetic relief valve, one-way valve, reduction valve, proportional pressure control valve, accumulator and control valve group, realize bender fast down, the workflow of compacting, release, four operations of backhaul is as follows:
Fast operation down, number one pump 1, No. second pump 2, No. three pump 14, after No. four pump 15 is opened, electromagnet YV1, YV5, the YV8 energising, give proportion electro-magnet Y1 according to rate request, Y3, Y4, Y5, the corresponding scaling signal of Y6, electromagnetic relief valve 32 cuts out, No. second plug-in mounting pressure valve 43 is closed, this moment, the system pressure valve was a high pressure, make that system pressure oil can not oil return, system pressure oil is by number one one-way valve 33, No. three one-way valve 45, No. four one-way valve 46 enters number one master cylinder 6 with two aggressive valve, the plug chamber of No. second master cylinder 9, part oil enters accumulator 38 by No. second one-way valve 34 simultaneously, fluid by the topping up case through number one liquid-filling valve 7, No. second liquid-filling valve 8 enters number one master cylinder 6, No. second master cylinder 9, moved cross beam descends fast, can be by regulating proportion electro-magnet Y3, Y4, Y5, speed under the corresponding scaling signal size of Y6 changes soon.
Suppression process, when moved cross beam during soon near workpiece, electromagnet YV1, YV5, the YV8 energising, give proportion electro-magnet Y1 according to rate request, Y3, Y4, Y5, the corresponding scaling signal of Y6, this moment proportion electro-magnet Y4, the signal of Y6 reduces, the opening of corresponding proportional servo valve reduces, downstream rate is slack-off, system changes the worker into and advances, No. second master cylinder 9 begins pressurization, when the position of the position of No. second master cylinder 9 and No. second grating chi 10 and number one master cylinder 6 and number one grating chi 5 during not at same horizontal position, and the signal magnitude of change proportion electro-magnet Y6 after the grating chi feedback signal, the opening amount of corresponding proportional servo valve changes, make the displacement of No. second master cylinder 9 tracking number one master cylinders 6, the motion of two oil cylinders is kept synchronously, behind contact workpiece, system boosts, and realizes suppression process.
The release operation, be after compacting is finished, electromagnet YV1, YV2 energising, reduce the signal of proportion electro-magnet Y1, this moment, the system pressure valve was a low pressure, system pressure oil enters liquid-filling valve control mouthful by No. three two-position four-way solenoid valve 36, and number one liquid-filling valve 7, No. second liquid-filling valve 8 are realized pre-pressure release power.
The backhaul operation, electromagnet YV1, YV4, YV7 energising, this moment, the system pressure valve was a high pressure, make that system pressure oil can not oil return, system pressure oil enters the bar chamber of number one master cylinder 6, No. second master cylinder 9 by number one one-way valve 33, No. three one-way valve 45, No. four one-way valve 46 and cartridge valve, the fluid in number one master cylinder 6, No. second master cylinder 9 plug chambeies is got back to the topping up case by number one liquid-filling valve 7, No. second liquid-filling valve 8, realizes returning operation.
When needing to adjust worktable, give the corresponding scaling signal of proportion electro-magnet Y2 as requested, threeway proportional pressure-reducing valve 12 just by corresponding flow, moves worktable compensating cylinder 13.
Claims (1)
1. one kind pair is fed back active proportional servo cartridge valve numerical control bender hydraulic control system, it is by two master cylinder control valve groups, an oil-feed control valve group and a worktable compensating cylinder (13) constitute, it is characterized in that two master cylinder control valve groups are provided with separately, be provided with two two initiatively servo cartridge valve unit and security control unit and pressure regulation unit in each valve group, drive corresponding master cylinder respectively, it is number one pump (1), No. three pump (14), the oil outlet of No. four pump (15) is connected with oil-feed control valve group (3), No. second pump (2) connects high pressure filter (31) one ends, high pressure filter (31) the other end is connected with oil-feed control valve group (3), electromagnetic relief valve (32) one ends are communicated with high pressure filter (31), electromagnetic relief valve (32) the other end is communicated with oiling valve group return opening (47), No. second one-way valve (34) one ends are communicated with high pressure filter (31), No. second one-way valve (34) the other end is communicated with reduction valve (35), reduction valve (35) the other end is communicated with No. three two-position four-way solenoid valve (36), No. three two-position four-way solenoid valve (36) the other end is by liquid-filling valve control mouthful (37) and number one liquid-filling valve (7), No. second liquid-filling valve (8) is communicated with, direct-acting overflow valve (40) one ends are communicated with No. second one-way valve (34), direct-acting overflow valve (40) the other end is communicated with oiling valve group return opening (47), accumulator (38) is communicated with No. second one-way valve (34), accumulator (38) is communicated with number one master cylinder control valve group (4) and No. second master cylinder control valve group (11) by number one flange mouth (39) and proportional servo valve filler opening (19), number one one-way valve (33) one ends are communicated with number one pump (1), number one one-way valve (33) the other end is communicated with No. second cartridge valve (43), No. three one-way valve (45) one ends are communicated with No. four pump (15), No. three one-way valve (45) the other end is communicated with No. second plug-in mounting pressure valve (43), No. four one-way valve (46) one ends are communicated with No. three pump (14), No. four one-way valve (46) the other end is communicated with No. second plug-in mounting pressure valve (43), No. second plug-in mounting pressure valve (43) the other end is communicated with oiling valve group return opening (47), proportional pressure control valve (44) one ends are communicated with No. second plug-in mounting pressure valve (43) and No. four one-way valve (46), proportional pressure control valve (44) the other end is communicated with oiling valve group return opening (47), No. second plug-in mounting pressure valve (43) one ends are communicated with number one master cylinder control valve group (4) and No. second master cylinder control valve group (11) by No. second flange mouth (41), No. second plug-in mounting pressure valve (43) one ends are communicated with threeway proportional pressure-reducing valve (12) by No. three flange mouth (42), and the other end of threeway proportional pressure-reducing valve (12) is connected with worktable compensating cylinder (13); Master cylinder control valve group filler opening (29) is communicated with No. second two aggressive valve (27) one ends, the other end of No. second two aggressive valve (27) is communicated with the plug chamber of No. second liquid-filling valve (8) and No. second master cylinder (9), the control oil of No. second two aggressive valve (27) is communicated with No. second proportional servo valve (28), No. second proportional servo valve (28) is communicated with proportional servo valve filler opening (19) and proportional servo valve return opening (18), (260 1 ends are communicated with main valve group filler opening (29) to No. second cartridge valve, No. second cartridge valve (26) the other end is communicated with the two aggressive valve (21) of number one plug-in mounting pressure valve (30) and number one cartridge valve (23) and number one, No. second cartridge valve (26) gone up and connected No. second two-position four-way solenoid valve (25), number one cartridge valve (23) is gone up and is connected Solenoid ball valve (24), number one two-position four-way solenoid valve (16) is communicated with number one plug-in mounting pressure valve (30), number one plug-in mounting pressure valve (30) the other end is communicated with main valve group return opening (17), two aggressive valve (21) the other ends of number one are communicated with main valve group return opening (17), the control oil of the two aggressive valve (21) of number one is communicated with number one proportional servo valve (20), number one proportional servo valve (20) is communicated with proportional servo valve filler opening (19) and proportional servo valve return opening (18), number one cartridge valve (23) the other end connects the bar chamber of No. second master cylinder (9), one end of safety valve (22) connects the bar chamber of second master cylinder (9), the other end of safety valve (22) is communicated with main valve group return opening (17), number one grating chi (5) is installed in the side of number one master cylinder (6), and No. second grating chi (10) is installed in the side of No. second master cylinder (9).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201110046561 CN102155445B (en) | 2011-02-22 | 2011-02-22 | Hydraulic control system with double-feedback active proportional servo cartridge valve for CNC (Computer Numerical Control) bending machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201110046561 CN102155445B (en) | 2011-02-22 | 2011-02-22 | Hydraulic control system with double-feedback active proportional servo cartridge valve for CNC (Computer Numerical Control) bending machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102155445A true CN102155445A (en) | 2011-08-17 |
| CN102155445B CN102155445B (en) | 2013-07-03 |
Family
ID=44437068
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201110046561 Active CN102155445B (en) | 2011-02-22 | 2011-02-22 | Hydraulic control system with double-feedback active proportional servo cartridge valve for CNC (Computer Numerical Control) bending machine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN102155445B (en) |
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102410272A (en) * | 2011-12-03 | 2012-04-11 | 南京埃尔法电液技术有限公司 | Electrohydraulic servo bending machine hydraulic system |
| CN102691681A (en) * | 2012-06-26 | 2012-09-26 | 重庆键英液压机电有限公司 | Novel three-point type bending machine hydraulic system with quick energy conservation |
| CN103089721A (en) * | 2013-03-01 | 2013-05-08 | 山东泰丰液压股份有限公司 | High-flow electric-hydraulic proportional cartridge valve hydraulic control system for differential speed regulation |
| CN104763697A (en) * | 2015-04-14 | 2015-07-08 | 阜阳强松机械制造有限公司 | Hydraulic system for underdrive bending machine |
| CN105782154A (en) * | 2016-05-27 | 2016-07-20 | 桥弘数控科技（上海）有限公司 | Hydraulic machining machine, hydraulic system thereof and control method of hydraulic system |
| CN105909575A (en) * | 2016-06-28 | 2016-08-31 | 安徽东海机床制造有限公司 | Bending method of efficient bending machine |
| CN106194867A (en) * | 2016-08-31 | 2016-12-07 | 湖南华强电气股份有限公司 | A kind of hydraulic system and mould |
| CN106762892A (en) * | 2017-02-14 | 2017-05-31 | 南京麦克菲自动控制有限公司 | A kind of numerical control bending machine hydraulic system of use BID SVP hybrid powers control |
| CN109114075A (en) * | 2018-09-26 | 2019-01-01 | 河南科技大学 | A kind of stereo garage electro-hydraulic proportional control system |
| CN108150468B (en) * | 2017-12-05 | 2019-12-20 | 西安交通大学 | Hydraulic press hydraulic system capable of quickly and stably realizing local loading |
| CN111207121A (en) * | 2020-02-27 | 2020-05-29 | 桥弘数控科技（上海）有限公司 | Servo hydraulic device and servo hydraulic bending machine |
| CN112483491A (en) * | 2020-11-25 | 2021-03-12 | 山东海洋工程装备研究院有限公司 | Active and passive compensation system and method with energy recycling function |
| CN114030221A (en) * | 2021-11-24 | 2022-02-11 | 天水锻压机床(集团)有限公司 | Double-cylinder accurate constant-pressure fixed-stroke hydraulic variable-frequency servo control device |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB749571A (en) * | 1951-07-05 | 1956-05-30 | Fielding & Platt Ltd | Improvements in or relating to hydraulic apparatus and methods of operation thereof |
| JP3775982B2 (en) * | 2000-11-08 | 2006-05-17 | 太陽鉄工株式会社 | Fluid pressure cylinder device |
| CN201008887Y (en) * | 2007-01-09 | 2008-01-23 | 东北大学 | Constant tension control hydraulic system of single machine rack vertical pulling type cold rolling experimental machine |
| CN101132882A (en) * | 2005-03-24 | 2008-02-27 | 小松产业机械股份有限公司 | Hydraulic processing machine, hydraulic press brake, and method of controlling the same |
| CN101835601A (en) * | 2007-09-12 | 2010-09-15 | 特鲁普机械奥地利有限公司及两合公司 | Drive device for a bending press |
-
2011
- 2011-02-22 CN CN 201110046561 patent/CN102155445B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB749571A (en) * | 1951-07-05 | 1956-05-30 | Fielding & Platt Ltd | Improvements in or relating to hydraulic apparatus and methods of operation thereof |
| JP3775982B2 (en) * | 2000-11-08 | 2006-05-17 | 太陽鉄工株式会社 | Fluid pressure cylinder device |
| CN101132882A (en) * | 2005-03-24 | 2008-02-27 | 小松产业机械股份有限公司 | Hydraulic processing machine, hydraulic press brake, and method of controlling the same |
| CN201008887Y (en) * | 2007-01-09 | 2008-01-23 | 东北大学 | Constant tension control hydraulic system of single machine rack vertical pulling type cold rolling experimental machine |
| CN101835601A (en) * | 2007-09-12 | 2010-09-15 | 特鲁普机械奥地利有限公司及两合公司 | Drive device for a bending press |
Cited By (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102410272A (en) * | 2011-12-03 | 2012-04-11 | 南京埃尔法电液技术有限公司 | Electrohydraulic servo bending machine hydraulic system |
| CN102691681A (en) * | 2012-06-26 | 2012-09-26 | 重庆键英液压机电有限公司 | Novel three-point type bending machine hydraulic system with quick energy conservation |
| CN102691681B (en) * | 2012-06-26 | 2015-03-25 | 重庆键英液压机电有限公司 | Three-point type bending machine hydraulic system with quick energy conservation |
| CN103089721A (en) * | 2013-03-01 | 2013-05-08 | 山东泰丰液压股份有限公司 | High-flow electric-hydraulic proportional cartridge valve hydraulic control system for differential speed regulation |
| CN103089721B (en) * | 2013-03-01 | 2015-03-11 | 山东泰丰液压股份有限公司 | High-flow electric-hydraulic proportional cartridge valve hydraulic control system for differential speed regulation |
| CN104763697A (en) * | 2015-04-14 | 2015-07-08 | 阜阳强松机械制造有限公司 | Hydraulic system for underdrive bending machine |
| CN105782154A (en) * | 2016-05-27 | 2016-07-20 | 桥弘数控科技（上海）有限公司 | Hydraulic machining machine, hydraulic system thereof and control method of hydraulic system |
| WO2018001388A1 (en) * | 2016-06-28 | 2018-01-04 | 安徽东海机床制造有限公司 | High-efficiency bending machine bending method |
| CN105909575A (en) * | 2016-06-28 | 2016-08-31 | 安徽东海机床制造有限公司 | Bending method of efficient bending machine |
| CN106194867A (en) * | 2016-08-31 | 2016-12-07 | 湖南华强电气股份有限公司 | A kind of hydraulic system and mould |
| CN106762892A (en) * | 2017-02-14 | 2017-05-31 | 南京麦克菲自动控制有限公司 | A kind of numerical control bending machine hydraulic system of use BID SVP hybrid powers control |
| CN108150468B (en) * | 2017-12-05 | 2019-12-20 | 西安交通大学 | Hydraulic press hydraulic system capable of quickly and stably realizing local loading |
| CN109114075A (en) * | 2018-09-26 | 2019-01-01 | 河南科技大学 | A kind of stereo garage electro-hydraulic proportional control system |
| CN111207121A (en) * | 2020-02-27 | 2020-05-29 | 桥弘数控科技（上海）有限公司 | Servo hydraulic device and servo hydraulic bending machine |
| CN112483491A (en) * | 2020-11-25 | 2021-03-12 | 山东海洋工程装备研究院有限公司 | Active and passive compensation system and method with energy recycling function |
| CN112483491B (en) * | 2020-11-25 | 2022-07-08 | 山东海洋工程装备研究院有限公司 | Active and passive compensation system and method with energy recycling function |
| CN114030221A (en) * | 2021-11-24 | 2022-02-11 | 天水锻压机床(集团)有限公司 | Double-cylinder accurate constant-pressure fixed-stroke hydraulic variable-frequency servo control device |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102155445B (en) | 2013-07-03 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102155445B (en) | Hydraulic control system with double-feedback active proportional servo cartridge valve for CNC (Computer Numerical Control) bending machine | |
| CN103615436B (en) | Steel tube straightening machine numerical control electrohydraulic ratio system | |
| CN103552276B (en) | Slide block control system of hydraulic machine | |
| CN201855997U (en) | Plate shearing machine with shearing angle adjusting function | |
| CN105221497A (en) | High speed pre-shaping hydraulic press hydraulic control system | |
| CN102183918A (en) | Control system for servo numerical control bending machine | |
| CN103807239A (en) | Dual output shaft motor based shear plate synchronous control hydraulic system | |
| CN202579384U (en) | Hydraulic synchronous driving system for adjusting eccentric loads based on proportional valve -controlled energy accumulators | |
| CN103334971A (en) | Hydraulic control system for electric-hydraulic proportional numerical control bending machine | |
| CN202290768U (en) | Full-hydraulic screwdown servo control apparatus | |
| CN105697471A (en) | Control method of electro-hydraulic proportional loop system with good working effect | |
| CN211116877U (en) | Integrated bidirectional pump-controlled high-speed double-cylinder synchronous hydraulic control system | |
| CN205136185U (en) | Synchronous initiative hydraulic control system of many hydro -cylinders rigidity | |
| CN103775411B (en) | A kind of servovalve based on speed difference dynamic pressure feedback fluid-control pilot stage | |
| CN204003680U (en) | Novel master cylinder hydraulic circuit system | |
| CN203685776U (en) | Numerical control electric-hydraulic proportional system of steel pipe straightening machine | |
| CN102275331A (en) | Hydraulic leveling technique for presses | |
| CN203649108U (en) | Punch press | |
| CN102275332B (en) | A kind of hydraulic leveling technology being applicable to large, medium and small swaging machine | |
| CN102836942A (en) | High-response hydraulic synchronizing circuit for compensating dead zone of hydraulic valve | |
| CN103722063B (en) | A kind of punch press and workpiece blanking method | |
| CN102155446A (en) | Segmental control integration-type electro-hydraulic digital valve | |
| CN105003474A (en) | Hydraulic system of hydraulic drawing press | |
| CN203362665U (en) | Electric-hydraulic proportional hydraulic control device of numerical control bending machine | |
| CN103291675A (en) | Numerically-controlled bending machine hydraulic control system capable of achieving valve core position electrical monitoring |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CP01 | Change in the name or title of a patent holder |
Address after: 272025, triumph Road, Jining hi tech Development Zone, Shandong, 66 Patentee after: Shandong Taifeng intelligent control Limited by Share Ltd Address before: 272025, triumph Road, Jining hi tech Development Zone, Shandong, 66 Patentee before: Shandong Taifeng Hydraulic Co., Ltd. |
|
| CP01 | Change in the name or title of a patent holder |