CN101865184A - Direct-drive redundant hydraulic system for servomotor - Google Patents
Direct-drive redundant hydraulic system for servomotor Download PDFInfo
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- CN101865184A CN101865184A CN200910049255A CN200910049255A CN101865184A CN 101865184 A CN101865184 A CN 101865184A CN 200910049255 A CN200910049255 A CN 200910049255A CN 200910049255 A CN200910049255 A CN 200910049255A CN 101865184 A CN101865184 A CN 101865184A
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- 239000012530 fluid Substances 0.000 claims description 17
- 239000002828 fuel tank Substances 0.000 claims description 12
- 238000009825 accumulation Methods 0.000 claims description 3
- 239000003921 oil Substances 0.000 description 88
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 4
- 238000001816 cooling Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
- 230000001105 regulatory effect Effects 0.000 description 3
- 238000011109 contamination Methods 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 230000035945 sensitivity Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000000052 comparative effect Effects 0.000 description 1
- 230000002950 deficient Effects 0.000 description 1
- 238000001914 filtration Methods 0.000 description 1
- 239000012467 final product Substances 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
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Abstract
The invention discloses a direct-drive redundant hydraulic system for a servomotor, relates to the technical field of hydraulic control, and solves the problem that the conventional low-cost system has low response speed and low control reliability. The system comprises a piston-type servomotor, a control unit and an oil tank, and is characterized in that: the control unit consists of two direct-drive volume control loops in parallel connection; each direct-drive volume control loop comprises an oil pump, an AC servo motor, an accumulator and an electromagnetic directional valve; an oil port of the oil pump is connected with a working cavity and the accumulator through a hydraulic control one-way valve and the electromagnetic directional valve respectively; the other oil port of the oil pump is connected with the other working cavity through the hydraulic control one-way valve; the accumulator is connected with the two working cavities of the servomotor through two high-speed on-off solenoid valves respectively; and the two oil ports of the oil pump are connected with the oil tank though the hydraulic control one-way valve respectively. The system has the advantages of low cost, high control reliability, and high response speed.
Description
Technical field
The present invention relates to the technology of hydraulic control, particularly relate to a kind of technology that is used for the direct-drive redundant hydraulic system for servomotor of small steam turbine (feed water pump) regulating system.
Background technique
Oil engine (oil hydraulic cylinder) is the power unit of steam turbine (feed water pump) adjusting and security system, and its major function is to change its piston action of control in real time by hydraulic pressure, and then the aperture of control steam turbine valve.
Traditional steam turbine (feed water pump) regulating system all adopts valve control oil engine electrohydraulic servo system, this system (referring to Fig. 2) adopts the electrohydraulic control Hs by outside fuel feeding, the oil inlet P of electrohydraulic control Hs is connected outside oil sources respectively with oil return inlet T, and two control ports connect two active chambers of piston type oil engine U2 respectively; Transfer valve bit instruction signal during operation, the valve position feedback signal LVDT of oil engine U2 after transferring electrical signal to, demodulator TD is compared with valve position command signal C, and according to comparative result control electrohydraulic control Hs action, and then the piston stroke of control oil engine U2.Because electrohydraulic control has speed of response faster, therefore this system can satisfy the requirement of the regulating system of steam turbine (feed water pump) to quick response well.But because the intrinsic structural feature of electrohydraulic control itself, make this system have following shortcoming: 1) requirement on machining accuracy of electrohydraulic control is higher, and its price is very expensive; 2) because the electro-hydraulic servo valve arrangement is tiny and valve body is fragile, therefore responsive especially to oil contamination, its spool is caused malfunctioning easily by the wearing and tearing of the impurity in the fluid, therefore must be equipped with the very high filtration system of filter precision; 3) because electrohydraulic control is responsive to temperature variation, and the energy loss of valve control oil engine electrohydraulic servo system is very serious, and its throttling heating is bigger, therefore must be equipped with more perfect cooling system; 4), thereby the volume and the complexity of entire system have been increased because electrohydraulic control by outside fuel feeding, therefore needs a cover pumping station system that constant pressure oil source is provided; 5) be in inoperative during the cycle (pressurize operating mode and idle running operating mode) when system, system still locates running state, has increased operating cost.Above-mentioned shortcoming makes that the cost of valve control oil engine electrohydraulic servo system is higher.
In order to overcome the shortcoming of valve control oil engine electrohydraulic servo system, a kind of directly driven volume controlled electro-hydraulic servo system (DDVC system) has appearred, the hydraulic main circuit of this system (referring to Fig. 3) adopts closed oil circuit, two hydraulic fluid ports of its oil pump D3 connect two active chambers of piston type oil engine U3 respectively, also are provided with Fill valve (two Pilot operated check valve H31, H32) that is used for balance sysmte oil mass difference in volume of positive and negative when operation and the locking-valve (two Pilot operated check valve H33, H34) that is used to pin piston rod in system; Control the output flow of oil pump D3 and the flow direction of hydraulic oil by AC servo motor M3 during operation, and then the piston stroke of control oil engine U3.This system has the following advantages: 1) because hydraulic main circuit is a closed circuit, therefore system with oil mass seldom and be subjected to the outside contamination chance less only needs little fuel tank (oil tank) get final product, and does not have sensing element in the system, so also do not need to be equipped with filtrating equipment; 2) owing to do not have throttle element in the directly driven volume controlled electro-hydraulic servo system, pressure loss is very little, so the heat that oil pump when work produces seldom, and system can not need to be equipped with cooling system from heat radiation; When 3) system only work in actuator, just start AC servo motor, when system is in inoperative (the pressurize operating mode and the operating mode that dallies) consumed energy hardly during the cycle, its operating cost is very low.Therefore directly driven volume controlled electro-hydraulic servo system relative valve control oil engine electrohydraulic servo system cost is lower, but because the sensitivity of AC servo motor and oil pump combination will be lower than the sensitivity of electrohydraulic control, therefore the speed of response of this system is slower, can't be applied to the large steam turbine higher to the quick closing valve functional requirement.
In addition, because valve control oil engine electrohydraulic servo system and directly driven volume controlled electro-hydraulic servo system all adopt single control oil channel, so its control reliability is relatively poor, and is accidents caused because of the control oil channel fault easily.
Summary of the invention
At the defective that exists in the above-mentioned prior art, technical problem to be solved by this invention provide a kind of with low cost, control reliability is high, and has the direct-drive redundant hydraulic system for servomotor of rapid response speed.
In order to solve the problems of the technologies described above, a kind of direct-drive redundant hydraulic system for servomotor provided by the present invention, comprise piston type oil engine, control unit and fuel tank, it is characterized in that: described control unit is formed in parallel by two direct drive type volume control loops, and each direct drive type volume control loop comprises an oil pump, an AC servo motor, an accumulator and a solenoid directional control valve; Described oil engine comprises first active chamber and second active chamber, described oil pump comprises first hydraulic fluid port and second hydraulic fluid port, first hydraulic fluid port of described oil pump is through a Pilot operated check valve, solenoid directional control valve connects first active chamber and the accumulator of oil engine respectively, it is first oil circuit, second hydraulic fluid port of described oil pump connects second active chamber of oil engine through a Pilot operated check valve, it is second oil circuit, described accumulator connects two active chambers of oil engine respectively through two snap switch solenoid valves, Pilot operated check valve in described first oil circuit and second oil circuit is used to lock the piston rod of oil engine, each connects fuel tank through a Pilot operated check valve two hydraulic fluid ports of described oil pump, be used for the repairing of oil circuit oil mass difference in volume when oil pump is positive and negative to be moved, described AC servo motor connects oil pump, be used to control the oil pump operation, described accumulator is provided with pressure switch, be used to control the accumulator accumulation of energy, second active chamber of described oil engine connects fuel tank through a snap switch solenoid valve.
Direct-drive redundant hydraulic system for servomotor provided by the invention has following beneficial effect: 1) owing to adopted the double pump redundancy scheme, its control unit is formed in parallel by two direct drive type volume control loops, thereby has improved the control reliability of system; 2) owing to adopt the direct drive type volume control loop, therefore do not need to be equipped with separately constant pressure oil source, filtrating equipment and cooling unit, thereby its cost is lower; 3) in the direct drive type volume control loop, added accumulator, can make quick response to control signal, cooperated AC servo motor to realize the quick closing valve of system again by accumulator.
Description of drawings
Fig. 1 is the schematic diagram of the direct-drive redundant hydraulic system for servomotor of the embodiment of the invention;
Fig. 2 is the schematic diagram of existing valve control oil engine electrohydraulic servo system;
Fig. 3 is the schematic diagram of existing directly driven volume controlled electro-hydraulic servo system.
Embodiment
Below in conjunction with description of drawings embodiments of the invention are described in further detail, but present embodiment is not limited to the present invention, every employing analog structure of the present invention and similar variation thereof all should be listed protection scope of the present invention in.
As shown in Figure 1, a kind of direct-drive redundant hydraulic system for servomotor that the embodiment of the invention provided, comprise piston type oil engine U1, control unit and fuel tank X1, X2, X3, it is characterized in that: described control unit is formed in parallel by two direct drive type volume control loops, and each direct drive type volume control loop comprises an oil pump D1 (D2), an AC servo motor M1 (M2), an accumulator N1 (N2) and a solenoid directional control valve H11 (H21); Described oil engine U1 comprises first active chamber and second active chamber, described oil pump D1 (D2) comprises first hydraulic fluid port and second hydraulic fluid port, first hydraulic fluid port of described oil pump D1 (D2) is through a Pilot operated check valve H14 (H24), solenoid directional control valve H11 (H21) connects first active chamber and the accumulator N1 (N2) of oil engine U1, it is first oil circuit, second hydraulic fluid port of described oil pump D1 (D2) connects second active chamber of oil engine U1 through a Pilot operated check valve H15 (H25), it is second oil circuit, described accumulator N1 (N2) is respectively through two snap switch solenoid valve H12, H13 (H22, H23) two active chambers of connection oil engine U1, Pilot operated check valve H14 in described first oil circuit and second oil circuit, H15 (H24, H25) be used to lock the piston rod of oil engine U1, two hydraulic fluid ports of described oil pump D1 (D2) are respectively through a Pilot operated check valve H16, H17 (H26, H27) connect fuel tank X1 (X2), the repairing of oil circuit oil mass difference in volume when being used for the positive and negative operation of oil pump D1 (D2), described AC servo motor M1 (M2) connects oil pump D1 (D2), be used to control oil pump D1 (D2) operation, described accumulator N1 (N2) is provided with pressure switch K1 (K2), be used to control accumulator N1 (N2) accumulation of energy, second active chamber of described oil engine U1 connects fuel tank X3 through a snap switch solenoid valve H18.
Described fuel tank X1, X2, X3 communicate with each other.
The workflow of the direct-drive redundant hydraulic system for servomotor of the embodiment of the invention is as follows:
When utilizing oil pump D1 control oil engine U1, start AC servo motor M1 earlier and drive oil pump D1 operation, snap switch solenoid valve H12, H13, H18 energising are ended, and second load port of connecting solenoid directional control valve H11 is oil-filled to accumulator N1, after the oil pressure of accumulator N1 reaches predetermined pressure, switch to first load port, make system enter readiness for operation by pressure switch K1 control solenoid directional control valve H11;
When needing oil engine U1 action, send control signal and give AC servo motor M1, AC servo motor M1 is according to the traffic direction of control signal control oil pump D1, thereby the piston rod of control oil engine U1 acts accordingly;
When needing quick control, control signal control AC servo motor M1 connects corresponding snap switch solenoid valve H12 or H13 outage in the time of operation, oil among the accumulator N1 is released in the oil circuit through corresponding snap switch solenoid valve H12 or H13, thereby control oil engine U1 makes quick response action; When snap switch solenoid valve H12 outage is connected, snap switch solenoid valve H18 outage is connected, make oil engine U1 can make response action faster;
During system maintenance, snap switch solenoid valve H13, the H18 connection of cutting off the power supply, oil is released among the fuel tank X3 among the accumulator N1 thereby make;
Utilize workflow and the oil pump D1 of oil pump D2 control oil engine U1 similar.
The direct-drive redundant hydraulic system for servomotor of the embodiment of the invention can adopt single pump control when moving, also can adopt double pump control.
Claims (1)
1. direct-drive redundant hydraulic system for servomotor, comprise piston type oil engine, control unit and fuel tank, it is characterized in that: described control unit is formed in parallel by two direct drive type volume control loops, and each direct drive type volume control loop comprises an oil pump, an AC servo motor, an accumulator and a solenoid directional control valve; Described oil engine comprises first active chamber and second active chamber, described oil pump comprises first hydraulic fluid port and second hydraulic fluid port, first hydraulic fluid port of described oil pump is through a Pilot operated check valve, solenoid directional control valve connects first active chamber and the accumulator of oil engine respectively, it is first oil circuit, second hydraulic fluid port of described oil pump connects second active chamber of oil engine through a Pilot operated check valve, it is second oil circuit, described accumulator connects two active chambers of oil engine respectively through two snap switch solenoid valves, Pilot operated check valve in described first oil circuit and second oil circuit is used to lock the piston rod of oil engine, each connects fuel tank through a Pilot operated check valve two hydraulic fluid ports of described oil pump, be used for the repairing of oil circuit oil mass difference in volume when oil pump is positive and negative to be moved, described AC servo motor connects oil pump, be used to control the oil pump operation, described accumulator is provided with pressure switch, be used to control the accumulator accumulation of energy, second active chamber of described oil engine connects fuel tank through a snap switch solenoid valve.
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| Application Number | Priority Date | Filing Date | Title |
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| CN200910049255A CN101865184A (en) | 2009-04-14 | 2009-04-14 | Direct-drive redundant hydraulic system for servomotor |
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| Application Number | Priority Date | Filing Date | Title |
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| CN200910049255A CN101865184A (en) | 2009-04-14 | 2009-04-14 | Direct-drive redundant hydraulic system for servomotor |
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| CN101865184A true CN101865184A (en) | 2010-10-20 |
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Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102408075A (en) * | 2011-11-09 | 2012-04-11 | 三一集团有限公司 | Energy-saving type crane |
| CN102513413A (en) * | 2011-12-03 | 2012-06-27 | 南京埃尔法电液技术有限公司 | Hydraulic control system for novel servo pump control bending machine |
| CN103075393A (en) * | 2011-10-26 | 2013-05-01 | 北京精密机电控制设备研究所 | Novel multi-redundancy electromechanical hydrostatic servo mechanism |
| CN104540769A (en) * | 2012-06-08 | 2015-04-22 | 西马格特宝有限责任公司 | Disk brake system |
| CN105020207A (en) * | 2015-06-16 | 2015-11-04 | 中国海洋石油总公司 | Dual-redundancy pressure adjusting device having emergent pressure relief |
| CN105156368A (en) * | 2015-08-19 | 2015-12-16 | 江苏大学 | Hydraulic driving actuator system |
| CN105443248A (en) * | 2015-11-03 | 2016-03-30 | 北京航科发动机控制系统科技有限公司 | Standby system with electro-hydraulic conversion components of different structures |
| CN105715597A (en) * | 2016-03-18 | 2016-06-29 | 中冶赛迪工程技术股份有限公司 | Constant-backpressure direct drive type electro hydraulic servo system and control method thereof |
| CN108591137A (en) * | 2018-07-12 | 2018-09-28 | 西南交通大学 | A kind of novel robot hydraulic knuckle drive system |
| CN113090596A (en) * | 2021-03-15 | 2021-07-09 | 中国科学院工程热物理研究所 | Servomotor system with thermal redundancy backup oil supply and control method thereof |
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Patent Citations (6)
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| EP1223345A2 (en) * | 2001-01-12 | 2002-07-17 | Hoerbiger Hydraulik GmbH | Actuation arrangement for parts of vehicles pivotable about an axis |
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Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103075393A (en) * | 2011-10-26 | 2013-05-01 | 北京精密机电控制设备研究所 | Novel multi-redundancy electromechanical hydrostatic servo mechanism |
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| CN102513413A (en) * | 2011-12-03 | 2012-06-27 | 南京埃尔法电液技术有限公司 | Hydraulic control system for novel servo pump control bending machine |
| CN102513413B (en) * | 2011-12-03 | 2013-11-06 | 南京埃尔法电液技术有限公司 | Hydraulic control system for novel servo pump control bending machine |
| US9656648B2 (en) | 2012-06-08 | 2017-05-23 | Siemag Tecberg Gmbh | Disk brake system |
| CN104540769A (en) * | 2012-06-08 | 2015-04-22 | 西马格特宝有限责任公司 | Disk brake system |
| CN105020207A (en) * | 2015-06-16 | 2015-11-04 | 中国海洋石油总公司 | Dual-redundancy pressure adjusting device having emergent pressure relief |
| CN105156368A (en) * | 2015-08-19 | 2015-12-16 | 江苏大学 | Hydraulic driving actuator system |
| CN105443248A (en) * | 2015-11-03 | 2016-03-30 | 北京航科发动机控制系统科技有限公司 | Standby system with electro-hydraulic conversion components of different structures |
| CN105715597A (en) * | 2016-03-18 | 2016-06-29 | 中冶赛迪工程技术股份有限公司 | Constant-backpressure direct drive type electro hydraulic servo system and control method thereof |
| CN105715597B (en) * | 2016-03-18 | 2018-07-20 | 中冶赛迪工程技术股份有限公司 | Constant backpressure Direct Drive Electro-hydraulic Servo System and its control method |
| CN108591137A (en) * | 2018-07-12 | 2018-09-28 | 西南交通大学 | A kind of novel robot hydraulic knuckle drive system |
| CN113090596A (en) * | 2021-03-15 | 2021-07-09 | 中国科学院工程热物理研究所 | Servomotor system with thermal redundancy backup oil supply and control method thereof |
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Application publication date: 20101020 |