CN105805061A - Control method of electro-hydraulic proportion loop system with reasonable structure - Google Patents

Control method of electro-hydraulic proportion loop system with reasonable structure Download PDF

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Publication number
CN105805061A
CN105805061A CN201610163449.9A CN201610163449A CN105805061A CN 105805061 A CN105805061 A CN 105805061A CN 201610163449 A CN201610163449 A CN 201610163449A CN 105805061 A CN105805061 A CN 105805061A
Authority
CN
China
Prior art keywords
valve
plc
master cylinder
pump
rodless cavity
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN201610163449.9A
Other languages
Chinese (zh)
Inventor
郭成功
徐晓轶
周建智
朱张蓓
陆佳南
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.)
State Grid Corp of China SGCC
State Grid Jiangsu Electric Power Co Ltd
Nantong Power Supply Co of Jiangsu Electric Power Co Ltd
Original Assignee
State Grid Corp of China SGCC
State Grid Jiangsu Electric Power Co Ltd
Nantong Power Supply Co of Jiangsu Electric Power Co 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 State Grid Corp of China SGCC, State Grid Jiangsu Electric Power Co Ltd, Nantong Power Supply Co of Jiangsu Electric Power Co Ltd filed Critical State Grid Corp of China SGCC
Priority to CN201610163449.9A priority Critical patent/CN105805061A/en
Publication of CN105805061A publication Critical patent/CN105805061A/en
Pending 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/08—Servomotor systems incorporating electrically operated control 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/02—Servomotor systems with programme control derived from a store or timing device; Control devices therefor
    • 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
    • F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
    • F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
    • F15B9/08—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor
    • F15B9/09—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor with electrical control 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/28—Means for indicating the position, e.g. end of stroke
    • F15B15/2815—Position sensing, i.e. means for continuous measurement of position, e.g. LVDT
    • F15B15/2869—Position sensing, i.e. means for continuous measurement of position, e.g. LVDT using electromagnetic radiation, e.g. radar or microwaves
    • F15B15/2876—Position sensing, i.e. means for continuous measurement of position, e.g. LVDT using electromagnetic radiation, e.g. radar or microwaves using optical means, e.g. laser
    • 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
    • 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
    • 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
    • F15B2211/65—Methods of control of the load sensing pressure
    • F15B2211/651—Methods of control of the load sensing pressure characterised by the way the load pressure is communicated to the load sensing circuit
    • 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
    • F15B2211/6656—Closed loop control, i.e. control using feedback

Abstract

The invention discloses a control method of an electro-hydraulic proportion loop system with a reasonable structure. The electro-hydraulic proportion loop system is characterized in that a pump is connected with a secondary combination valve composed of a cartridge valve and a reversing valve controlled by a PLC; the secondary combination valve communicates with a rodless cavity of a master cylinder; a rod cavity of the master cylinder communicates with a tertiary combination valve composed of an overflow valve, a reversing valve and a cartridge valve; the tertiary combination valve communicates with an oil tank; pressure sensors are arranged on the rodless cavity and the rod cavity of the master cylinder; a grating ruler used for sensing the position of a piston of the master cylinder is additionally arranged; the pressure sensors and the grating ruler are connected with the PLC; the PLC is connected with a driver controlling a synchronous servo motor to operate; the rodless cavity of the master cylinder is connected with an oil supplementation tank through a pilot operated check valve; and the reversing valve controlled by the PLC in the secondary combination valve is a high-speed reversing valve. According to the electro-hydraulic proportion loop system, the structure is reasonable, and the pressing effect can be effectively improved.

Description

The control method of electric-hydraulic proportion circuit system rational in infrastructure
The application is application number: 201410341288.9, the applying date: 2014.7.18, title " electric-hydraulic proportion circuit system " divisional application.
Technical field
The present invention relates to a kind of electric-hydraulic proportion circuit system.
Background technology
In the process of the compacted products of hydraulic test, the overshoot of position and pressure is to cause one of principal element that goods precision is inadequate.Overshoot is often because of the response lag of detecting element (such as pressure transducer, displacement transducer), reversal valve etc., reaching to exist between setting value and fuel cut-off interval, hydraulic pump has unnecessary hydraulic oil to flow out, unnecessary hydraulic oil enters master cylinder, inevitable build-up of pressure overshoot or position overshoot.And piston rod deadweight is very big, it is difficult to stop immediately under effect of inertia, is also one of factor causing overshoot.
The hydraulic system used at power equipment there is also pressure controlled problem.
Summary of the invention
It is an object of the invention to provide a kind of rational in infrastructure, the electric-hydraulic proportion circuit system of suppression performance can be effectively improved.
The technical solution of the present invention is:
A kind of electric-hydraulic proportion circuit system, including fuel tank, pump, it is characterized in that: pump adopts the dosing pump that synchronous servo motor controls, the secondary groups that pump forms with the reversal valve by inserted valve with by PLC control is closed valve and is connected, secondary groups is closed valve and is communicated with the rodless cavity of master cylinder, the rod chamber of master cylinder communicates with the three grades of combination valves being made up of overflow valve, reversal valve, inserted valve, and three grades of combination valves communicate with fuel tank；Being respectively provided with pressure transducer on the rodless cavity of master cylinder, rod chamber, be additionally provided with the grating scale of perception master cylinder piston position signalling, described pressure transducer, grating scale are all connected with PLC, and PLC is connected with the driver controlling synchronous servo motor work；The rodless cavity of master cylinder is connected with oil feeding reservoir by hydraulic control one-way valve, described servomotor, dosing pump and driver composition speed change energy driver；Flow system flow entirety is controlled by speed change energy driver, and the secondary groups containing high speed reversal valve is closed valve and flow system flow is accurately controlled, and system pressure is accurately controlled by three grades of combination valves containing proportional pressure control valve.
The reversal valve by PLC control that secondary groups is closed in valve is common reversal valve or high speed reversal valve.
Overflow valve in three grades of combination valves is common overflow valve or proportional pressure control valve.
Present configuration is reasonable, can be effectively improved suppression performance, good working effect.It is applicable to and includes the various hydraulic test of power system.
Accompanying drawing explanation
Fig. 1 is the structural representation of one embodiment of the invention.
Figure includes: servomotor 3, dosing pump 4, oil filter 5, fuel tank 6, reversal valve 7,13,14,19, overflow valve 8,15, inserted valve 9,10,16,17, master cylinder 21, oil-supplementing system 20(oil feeding reservoir and hydraulic control one-way valve), pressure transducer 22, grating scale 23, PLC 1 and driver 2 etc..
Detailed description of the invention
Embodiment 1:
A kind of electric-hydraulic proportion circuit system, including fuel tank 6, pump 4, pump adopts the gear quantitative pump that synchronous servo motor controls, the secondary groups that pump forms with the reversal valve 19 by inserted valve 17 with by PLC control is closed valve and is connected, secondary groups is closed valve and is communicated with the rodless cavity of master cylinder 21, the rod chamber of master cylinder communicates with the three grades of combination valves being made up of overflow valve 8, reversal valve 7, inserted valve 9, and three grades of combination valves communicate with fuel tank 6；The rodless cavity of master cylinder, rod chamber are respectively provided with pressure transducer 22, it is additionally provided with the grating scale 23 of perception master cylinder piston position signalling, described pressure transducer, grating scale are all connected with PLC 1, and PLC is connected with the driver 2 controlling synchronous servo motor work；The rodless cavity of master cylinder is connected with oil feeding reservoir by hydraulic control one-way valve, described servomotor, dosing pump and driver composition speed change energy driver；Flow system flow entirety is controlled by speed change energy driver, and the secondary groups containing high speed reversal valve is closed valve and flow system flow is accurately controlled, and system pressure is accurately controlled by three grades of combination valves containing proportional pressure control valve.
The reversal valve by PLC control that secondary groups is closed in valve is common reversal valve or high speed reversal valve.
Overflow valve in three grades of combination valves is common overflow valve or proportional pressure control valve.
When fast downlink, speed change energy source device (the gear quantitative pump that synchronous servo motor controls) output flow opens inserted valve 17 by common reversal valve 19 so that pressure oil enters the rodless cavity of master cylinder 21, descent of piston.When rod chamber pressure is more than overflow valve 8 setting value, overflow valve 8 is opened, and unnecessary fluid returns to fuel tank through inserted valve 9.When descending at a slow speed, grating scale 23 gathers the position signalling of piston rod in real time, and sends PLC 1 to, then is made corresponding action accordingly by driver 2.The downstream position of piston is set desired value, when piston continue descending reach precalculated position time, PLC 1 sends the rotating speed referring to that the present changes servomotor 3, so that the output flow of pump diminishes, realization is descending at a slow speed.The common overflow valve 8 of fluctuation that changes in flow rate causes can not smoothly pressure release.When pressurize, according to the position signalling that the feedback signal of pressure transducer 22 and grating scale 23 are fed back, PLC 1 sends signal immediately makes reversal valve 19 act accordingly.Meanwhile, PLC 1 sends signal and makes servomotor stop operating.System response lag and the overshoot that causes can pass through overflow valve 8 pressure release.When wanting quick return, PLC 1 sends instruction, and master cylinder is in backhaul state.
Native system uses grating scale 23 Real-time Feedback piston rod position, compares the general travel switch just used of other powder forming special hydraulic press, has response speed faster.Wherein variable speed energy source device according to the demand automatic adjustment system flow of load, can reach the reasonable disposition of flow.
Figure also has reducer 11,18, valve 12.

Claims (1)

1. the control method of electric-hydraulic proportion circuit system one kind rational in infrastructure, it is characterized in that: described electric-hydraulic proportion circuit system includes fuel tank, pump, pump adopts the dosing pump that synchronous servo motor controls, the secondary groups that pump forms with the first reversal valve by the first inserted valve with by PLC control is closed valve and is connected, secondary groups is closed valve and is communicated with the rodless cavity of master cylinder, the rod chamber of master cylinder communicates with the three grades of combination valves being made up of overflow valve, the second reversal valve, the second inserted valve, and three grades of combination valves communicate with fuel tank；Being respectively provided with pressure transducer on the rodless cavity of master cylinder, rod chamber, be additionally provided with the grating scale of perception master cylinder piston position signalling, described pressure transducer, grating scale are all connected with PLC, and PLC is connected with the driver controlling synchronous servo motor work；The rodless cavity of master cylinder is connected with oil feeding reservoir by hydraulic control one-way valve, described servomotor, dosing pump and driver composition speed change energy driver；
When fast downlink, speed change energy source device output flow opens the first inserted valve (17) by the first reversal valve 19 controlled by PLC so that pressure oil enters the rodless cavity of master cylinder (21), descent of piston；When rod chamber pressure is more than overflow valve (8) setting value, overflow valve (8) is opened, and unnecessary fluid returns to fuel tank through the second inserted valve (9)；When descending at a slow speed, grating scale (23) gathers the position signalling of piston rod in real time, and sends PLC (1) to, then is made corresponding action accordingly by driver (2)；The downstream position of piston is set desired value, when piston continue descending reach precalculated position time, PLC (1) sends the rotating speed referring to that the present changes servomotor 3, so that the output flow of pump diminishes, realization is descending at a slow speed；The fluctuation overflow valve (8) that changes in flow rate causes can not smoothly pressure release；When pressurize, according to the position signalling that the feedback signal of pressure transducer (22) and grating scale (23) are fed back, PLC (1) sends signal immediately makes the first reversal valve (19) act accordingly；Meanwhile, PLC (1) sends signal and makes servomotor stop operating；System response lag and the overshoot that causes are by overflow valve (8) pressure release；When wanting quick return, PLC (1) sends instruction, and master cylinder is in backhaul state；
The reversal valve by PLC control that secondary groups is closed in valve is high speed reversal valve.
CN201610163449.9A 2014-07-18 2014-07-18 Control method of electro-hydraulic proportion loop system with reasonable structure Pending CN105805061A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201610163449.9A CN105805061A (en) 2014-07-18 2014-07-18 Control method of electro-hydraulic proportion loop system with reasonable structure

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Application Number Priority Date Filing Date Title
CN201410341288.9A CN104121255B (en) 2014-07-18 2014-07-18 Electric-hydraulic proportion circuit system
CN201610163449.9A CN105805061A (en) 2014-07-18 2014-07-18 Control method of electro-hydraulic proportion loop system with reasonable structure

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CN201610163447.XA Pending CN105697472A (en) 2014-07-18 2014-07-18 Control method of electro-hydraulic proportional loop system capable of improving pressing performance effectively
CN201410341288.9A Active CN104121255B (en) 2014-07-18 2014-07-18 Electric-hydraulic proportion circuit system
CN201610163446.5A Pending CN105697471A (en) 2014-07-18 2014-07-18 Control method of electro-hydraulic proportional loop system with good working effect
CN201610163451.6A Pending CN105697462A (en) 2014-07-18 2014-07-18 Electro-hydraulic proportional loop system with good working effect
CN201610163449.9A Pending CN105805061A (en) 2014-07-18 2014-07-18 Control method of electro-hydraulic proportion loop system with reasonable structure
CN201610163454.XA Pending CN105697473A (en) 2014-07-18 2014-07-18 Electro-hydraulic proportional loop system with reasonable structure

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CN201610163447.XA Pending CN105697472A (en) 2014-07-18 2014-07-18 Control method of electro-hydraulic proportional loop system capable of improving pressing performance effectively
CN201410341288.9A Active CN104121255B (en) 2014-07-18 2014-07-18 Electric-hydraulic proportion circuit system
CN201610163446.5A Pending CN105697471A (en) 2014-07-18 2014-07-18 Control method of electro-hydraulic proportional loop system with good working effect
CN201610163451.6A Pending CN105697462A (en) 2014-07-18 2014-07-18 Electro-hydraulic proportional loop system with good working effect

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CN107642511B (en) * 2017-10-20 2024-01-19 河南科技大学 Direct-drive electrohydraulic servo die forging hammer control system
CN109931314A (en) * 2019-03-22 2019-06-25 中国铁建重工集团有限公司 Hydraulic system
CN110332180A (en) * 2019-08-16 2019-10-15 中冶赛迪工程技术股份有限公司 A kind of energy-saving type blast furnace hot-blast stove hydraulic control system and method
CN113864274A (en) * 2021-10-18 2021-12-31 山东泰丰智能控制股份有限公司 Lifting hydraulic control system

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CN104121255A (en) 2014-10-29
CN105697472A (en) 2016-06-22
CN104121255B (en) 2016-08-17
CN105697471A (en) 2016-06-22
CN105697462A (en) 2016-06-22
CN105697473A (en) 2016-06-22

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Application publication date: 20160727