CN101749299A - Integrating electro-hydraulic servo actuator - Google Patents
Integrating electro-hydraulic servo actuator Download PDFInfo
- Publication number
- CN101749299A CN101749299A CN200910248516A CN200910248516A CN101749299A CN 101749299 A CN101749299 A CN 101749299A CN 200910248516 A CN200910248516 A CN 200910248516A CN 200910248516 A CN200910248516 A CN 200910248516A CN 101749299 A CN101749299 A CN 101749299A
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- hydraulic
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- oil
- fluid port
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- 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
- F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
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- 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
- F15B15/18—Combined units comprising both motor and pump
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention provides an integrating electro-hydraulic servo actuator, and the problem to be solved is as follows: the existing technology is formed by connecting a plurality of devices through an oil pipeline, the system is large and complex; an oil tank is an opening type, the oil liquid is easy to be polluted; the installation direction of the actuator is definite, which leads the installation location of a valve or an air valve to be limited. The key points of the invention are as follows: two inlets which are provided with a hydraulic locking valve set for locking a hydraulic cylinder location are connected with two oil ports of a double-direction hydraulic pump, and two outlets are connected with two cylinder ports of a double-rod hydraulic cylinder, and two control ends are respectively connected with an oil-feeding pipe which can leads the control ends to be opened at reverse direction; a position sensor detects the displacement of a piston rod of the hydraulic cylinder; a speed-regulating electric motor drives the double-direction hydraulic pump; the above devices are integrated into one body. The benefits of the invention are as follows: the plurality of devices are integrated into one body, the oil tank has no opening, and the installation is not limited by direction; and the external impurities can not enter the system.
Description
Technical field
The present invention relates to drive also a kind of actuator of operations such as control valve, air door, said actuator is meant electro-hydraulic actuator, and said operation is meant the open and close or the maintenance of valve or air door.It is widely used in industries such as electric power, metallurgy, petrochemical industry, pipe.
Background technique
Present electro-hydraulic actuator hydraulic driving system mainly is to be connected to form by oil pipe line by unidirectional oil hydraulic pump, hydrovalve, fuel tank, oil hydraulic cylinder, AC motor drives oil hydraulic pump, and the positioning control of oil hydraulic cylinder is realized by the control loop that electrohydraulic control or electro-hydraulic proportional valve and position transducer etc. are formed.As seen this system is connected to form by oil pipe line by several equipment, the discrete existence of each equipment, and floor space is big, and system is big and complicated, and maintenance work is more; Secondly, fuel tank is an open type, and fuel tank communicates with atmosphere by pneumostome, and fluid is easy to be subjected to outside contamination, makes hydrovalve, servovalve, Proportional valve bite, causes actuator failures; At last, also because fuel tank is an open type, must vertically place, and the space that the installation of final controlling element needs is bigger, and the mounting point of valve or air door is restricted.
Summary of the invention
For solving the problems of the technologies described above, the object of the present invention is to provide a kind of integrating electro-hydraulic servo actuator.
The object of the present invention is achieved like this: two inlets with hydraulic locking valve group of locking Position of Hydraulic Cylinder are received two hydraulic fluid ports of bidirectional hydraulic pump, it (refers to hydraulic locking valve group, two cylinder mouths of dual-rod hydraulic cylinder are received in two outlets down together), and its two control ends are received the last oil pipe that can make its reverse opening respectively; Position transducer detects the displacement of hydraulic cylinder piston rod; Speed-adjustable motor drives the bidirectional hydraulic pump; Above-mentioned each equipment integration is an integral body.The said speed-adjustable motor of this paper is meant any in variable-frequency motor, actuating motor and the stepper motor.
Speed-adjustable motor just changes, drive the high pressure oil that the bidirectional hydraulic pump produces, through the cylinder mouth of hydraulic locking valve group to oil hydraulic cylinder, the driving hydraulic cylinder piston rod moves, the high pressure oil of going up simultaneously oil pipe triggers hydraulic locking valve group, hydraulic locking valve group reverse opening is connected oil circuit, and the hydraulic oil of another cylinder mouth of oil hydraulic cylinder is got back to another hydraulic fluid port of bidirectional hydraulic pump through hydraulic locking valve group.After sensor goes out the position of hydraulic cylinder piston rod, output to the control circuit of establishing in addition, shut down according to setting the control speed-adjustable motor by control circuit, the oil pressure of last oil pipe is lower than setting value, can not trigger hydraulic locking valve group, hydraulic locking valve group is closed the system oil return pipe, the position of locking oil hydraulic cylinder and piston rod, and hydraulic cylinder piston rod is realized accurately location; The motor counter-rotating, the working procedure of system and last symmetry.Pressure oil transmits energy in the loop of a sealing, make oil hydraulic cylinder to-and-fro motion or location.
Prior art is compared, and the invention has the beneficial effects as follows: it is with several equipment integration one, becomes locking system, imperforation formula fuel tank, install final controlling element not the recipient and then provide convenience for the installation of valve or air door to restriction; Secondly the impurity of outside can not enter system, does not need oil filter, and has avoided system the bite phenomenon to occur, has improved the reliability of system; Owing to used speed-adjustable motor and sensor, make the system accuracy height once more; Final system diminishes, take up an area of little, for the assembling and maintenance convenience is provided.
Description of drawings
Further specify the present invention below in conjunction with accompanying drawing.
Fig. 1 is the hydraulic system schematic representation of the present invention when using a kind of hydraulic locking valve group.
Fig. 2 is the structural representation of the present invention after integrated.
Fig. 3 is the hydraulic system schematic representation of the present invention when using another kind of hydraulic locking valve group.
Embodiment
Referring to Fig. 1, said hydraulic locking valve group with locking Position of Hydraulic Cylinder is made up of two equilibrium valve 8-1 and 8-2, the inlet of these two valves is received the A hydraulic fluid port and the B hydraulic fluid port of bidirectional hydraulic pump 3 respectively, the A cylinder mouth and the B cylinder mouth of dual-rod hydraulic cylinder 10 received in the outlet of these two valves respectively, the control end of these two valves is received the last oil pipe that can make its reverse opening respectively, be the B hydraulic fluid port that the control end of equilibrium valve 8-1 is received the bidirectional hydraulic pump, the control end of equilibrium valve 8-2 is received the A hydraulic fluid port of bidirectional hydraulic pump.Position transducer 4 is arranged on the housing 20, the hydraulic cylinder piston rod side, to detect the displacement of cylinder piston rod, an inductive head 101 is fixed in the end of piston rod, inductive head apart from the distance of induction switch less than the distance of piston rod, to detect the displacement of piston rod apart from induction switch.Speed-adjustable motor M drives the bidirectional hydraulic pump.
This system also is provided with the protection loop; specifically be; the A hydraulic fluid port and the B hydraulic fluid port of bidirectional hydraulic pump received in the outlet of two one-way valve 2-2 and 2-1 respectively; the inlet parallel connection of two one-way valve 2-1 and 2-2; form the return tube in protection loop; two imports of shuttle valve 7 are connected in the upper and lower oil pipe of system respectively, and the outlet of shuttle valve is received the return tube in protection loop by relief valve 5, and solenoid valve 6 is in parallel with relief valve.
Above-mentioned each equipment integration is an integral body (referring to Fig. 2)
Working procedure is: when speed-adjustable motor M is just changeing, the high pressure oil that bidirectional hydraulic pump 3 produces from the A hydraulic fluid port is through the A cylinder mouth of equilibrium valve 8-1 to oil hydraulic cylinder, simultaneously, this high pressure oil triggers the control end of equilibrium valve 8-2, when the difference of the oil pressure of this control end and oil hydraulic cylinder B cylinder oil pressure reaches setting value, equilibrium valve 8-2 reverse opening, the hydraulic oil of oil hydraulic cylinder B cylinder mouth is got back to bidirectional hydraulic pump B hydraulic fluid port through equilibrium valve 8-2, and this moment, hydraulic locking valve group produced reverse balance pressure.After sensor goes out the position of hydraulic cylinder piston rod, output to the control circuit of establishing in addition, shut down according to setting the control speed-adjustable motor by control circuit, the oil pressure of last oil pipe is lower than setting value, can not trigger hydraulic locking valve group, hydraulic locking valve group is closed the system oil return pipe, the position of locking oil hydraulic cylinder and piston rod, and hydraulic cylinder piston rod is realized accurately location; The motor counter-rotating, the working procedure of system and last symmetry.Pressure oil transmits energy in the loop of a sealing, make oil hydraulic cylinder to-and-fro motion or location.
When system overload, high pressure oil surpasses setting value, and shuttle valve is opened, and oil is through the return tube in shuttle valve, relief valve and protection loop; When system was unloaded, high pressure oil was through the return tube in shuttle valve, solenoid valve and protection loop, and be used at the beginning of the system start-up this moment.
Referring to Fig. 3, said hydraulic locking valve group is, two entrance and exits of valve group are the entrance and exits of two one-way valve 6-1 and 6-2, the inlet of these two one-way valves is received the A hydraulic fluid port and the B hydraulic fluid port of bidirectional hydraulic pump 3 respectively, the A cylinder mouth and the B cylinder mouth of dual-rod hydraulic cylinder 10 received in the outlet of these two valves respectively, two control ends that control end is two sequence valves of valve group, it is the B hydraulic fluid port that the control end of sequence valve 7-1 is received oil hydraulic pump, the control end of sequence valve 7-2 is received the A hydraulic fluid port of oil hydraulic pump, the loop of reverse opening is composed in series by said sequence valve and another one-way valve, after being sequence valve 7-1 and one-way valve 9-1 series connection, 6-1 is in parallel with one-way valve, after sequence valve 7-2 and the one-way valve 9-2 series connection, 6-2 is in parallel with one-way valve.Working procedure is: when speed-adjustable motor M is just changeing, the high pressure oil that bidirectional hydraulic pump 3 produces from the A hydraulic fluid port is through the A cylinder mouth of one-way valve 6-1 to oil hydraulic cylinder, the driving hydraulic cylinder piston moves down, simultaneously, the control end of this high pressure oil trigger sequence valve 7-2, when the difference of the oil pressure of control end and oil hydraulic cylinder B cylinder oil pressure reached predefined value, sequence valve 7-2 opened, and the hydraulic oil of oil hydraulic cylinder B cylinder mouth is got back to bidirectional hydraulic pump B hydraulic fluid port through sequence valve 7-2, one-way valve 9-2.During the motor counter-rotating, the B branch line high pressure oil that bidirectional hydraulic pump 3 produces from the B hydraulic fluid port is through the B cylinder mouth of one-way valve 6-2 to oil hydraulic cylinder, the driving hydraulic cylinder piston moves up, simultaneously, the control end of B branch line high pressure oil trigger sequence valve 7-1, when the difference of the oil pressure of this control end and oil hydraulic cylinder A cylinder oil pressure reached setting value, sequence valve 7-1 opened, and the hydraulic oil of oil hydraulic cylinder A cylinder mouth is got back to bidirectional hydraulic pump A hydraulic fluid port through sequence valve 7-1, one-way valve 9-1.
Present embodiment also is provided with the protection loop, specifically is that solenoid valve 6 is in parallel with oil hydraulic pump 3.When system was unloaded, high pressure oil was got back to oil hydraulic pump through solenoid valve, and be used at the beginning of the system start-up this moment.
Claims (5)
1. integrating electro-hydraulic servo actuator, it is characterized in that: two inlets with hydraulic locking valve group of locking Position of Hydraulic Cylinder are received two hydraulic fluid ports of bidirectional hydraulic pump, two cylinder mouths of dual-rod hydraulic cylinder are received in its two outlets, and its two control ends are received the last oil pipe that can make its reverse opening respectively; Position transducer detects the displacement of hydraulic cylinder piston rod; Speed-adjustable motor drives the bidirectional hydraulic pump; Above-mentioned each equipment integration is an integral body.
2. according to the described integrating electro-hydraulic actuator of claim 1, it is characterized in that: said hydraulic locking valve group is by two equilibrium valves and form, the inlet of these two valves is received the A hydraulic fluid port and the B hydraulic fluid port of bidirectional hydraulic pump respectively, the A cylinder mouth and the B cylinder mouth of dual-rod hydraulic cylinder received in the outlet of these two valves respectively, the control end of these two valves is received respectively on the last oil pipe that can make its reverse opening, be the B hydraulic fluid port that the control end of equilibrium valve is received the bidirectional hydraulic pump, the control end of another equilibrium valve is received the A hydraulic fluid port of bidirectional hydraulic pump.
3. according to the described integrating electro-hydraulic actuator of claim 1, it is characterized in that: said hydraulic locking valve group is, two entrance and exits of valve group are two one-way valves (6-1) and entrance and exit (6-2), the inlet of these two one-way valves is received the A hydraulic fluid port and the B hydraulic fluid port of bidirectional hydraulic pump (3) respectively, the A cylinder mouth and the B cylinder mouth of dual-rod hydraulic cylinder (10) received in the outlet of these two valves respectively, two control ends that control end is two sequence valves of valve group, it is the B hydraulic fluid port that the control end of sequence valve (7-1) is received oil hydraulic pump, the control end of sequence valve (7-2) is received the A hydraulic fluid port of oil hydraulic pump, the loop of reverse opening is composed in series by said sequence valve and another one-way valve, after being sequence valve (7-1) and one-way valve 9-1 series connection, (6-1) is in parallel with one-way valve, after sequence valve (7-2) and one-way valve (9-2) series connection, (6-2) is in parallel with one-way valve.
4. according to claim 1,2 or 3 described integrating electro-hydraulic actuators; it is characterized in that: it also is provided with the protection loop; specifically be; two one-way valves and outlet receive the A hydraulic fluid port and the B hydraulic fluid port of bidirectional hydraulic pump respectively; the inlet parallel connection of two one-way valves forms the return tube of protecting the loop, and two imports of shuttle valve are connected in the upper and lower oil pipe of system respectively; the outlet of shuttle valve is received the return tube in protection loop by relief valve, and solenoid valve is in parallel with relief valve.
5. according to claim 1 or 3 described integrating electro-hydraulic actuators, it is characterized in that: solenoid valve is in parallel with oil hydraulic pump.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910248516A CN101749299A (en) | 2009-12-18 | 2009-12-18 | Integrating electro-hydraulic servo actuator |
| PCT/CN2010/070803 WO2011072503A1 (en) | 2009-12-18 | 2010-03-01 | Integrated electro-hydraulic servo actuator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910248516A CN101749299A (en) | 2009-12-18 | 2009-12-18 | Integrating electro-hydraulic servo actuator |
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| CN101749299A true CN101749299A (en) | 2010-06-23 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN200910248516A Pending CN101749299A (en) | 2009-12-18 | 2009-12-18 | Integrating electro-hydraulic servo actuator |
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| CN (1) | CN101749299A (en) |
| WO (1) | WO2011072503A1 (en) |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101907108A (en) * | 2010-07-29 | 2010-12-08 | 南通航海机械集团有限公司 | Miniature power unit |
| WO2011072502A1 (en) * | 2009-12-18 | 2011-06-23 | 沈阳东北电力调节技术有限公司 | Integrated electro-hydraulic actuator |
| CN102913510A (en) * | 2012-11-06 | 2013-02-06 | 昆山北极光电子科技有限公司 | One-piece hydraulic linear driving device |
| CN103321981A (en) * | 2013-07-01 | 2013-09-25 | 武汉船用机械有限责任公司 | Pressure protection system for oil cylinder of shark pincers |
| CN104405711A (en) * | 2014-11-20 | 2015-03-11 | 沈阳东北电力调节技术有限公司 | Overload electrohydraulic executing mechanism drive valve system with compensation function |
| CN105020458A (en) * | 2015-07-27 | 2015-11-04 | 江苏大学 | Electro hydraulic actuator for butterfly valve |
| CN105402200A (en) * | 2015-12-29 | 2016-03-16 | 沈阳东北电力调节技术有限公司 | Integrated electro hydraulic control device |
| CN107605818A (en) * | 2017-10-19 | 2018-01-19 | 燕山大学 | A kind of electro-hydraulic driving swing mechanism |
| CN110345129A (en) * | 2019-07-19 | 2019-10-18 | 韩国昊 | Hydraulic cylinder |
| CN112360831A (en) * | 2020-12-02 | 2021-02-12 | 江苏新扬新材料股份有限公司 | Synchronous opening and closing control device for cabin door of auxiliary power system |
| CN112963560A (en) * | 2021-04-16 | 2021-06-15 | 江苏理工学院 | Electro-hydraulic drive gas gate valve with stress detection function and control system |
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| US5144801A (en) * | 1989-04-28 | 1992-09-08 | Parker Hannifin Corporation | Electro-hydraulic actuator system |
| FR2671144B1 (en) * | 1990-12-28 | 1994-10-21 | Faivre Duboz Denis | DEVICE FOR CONTROLLING A SELF-CONTAINED CYLINDER. |
| AT409521B (en) * | 2000-06-06 | 2002-09-25 | Hoerbiger Hydraulik | ACTUATING ARRANGEMENT FOR SWIVELING PARTS ON VEHICLES |
| WO2002004820A1 (en) * | 2000-07-10 | 2002-01-17 | Kobelco Construction Machinery Co., Ltd. | Hydraulic cylinder circuit |
| DE102004029409A1 (en) * | 2004-06-18 | 2006-01-05 | Jungheinrich Ag | Pressure-medium-actuated actuating device, in particular for a vehicle steering device |
| JP4820552B2 (en) * | 2005-01-19 | 2011-11-24 | カヤバ工業株式会社 | Hydraulic control device and hydraulic drive unit including the hydraulic control device |
| CN2823627Y (en) * | 2005-09-14 | 2006-10-04 | 刘建 | Electric manual dual-purpose hydraulic pushing rod |
| CN101749300A (en) * | 2009-12-18 | 2010-06-23 | 沈阳东北电力调节技术有限公司 | Integrating electro-hydraulic actuator |
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2009
- 2009-12-18 CN CN200910248516A patent/CN101749299A/en active Pending
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2010
- 2010-03-01 WO PCT/CN2010/070803 patent/WO2011072503A1/en active Application Filing
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011072502A1 (en) * | 2009-12-18 | 2011-06-23 | 沈阳东北电力调节技术有限公司 | Integrated electro-hydraulic actuator |
| CN101907108A (en) * | 2010-07-29 | 2010-12-08 | 南通航海机械集团有限公司 | Miniature power unit |
| CN102913510A (en) * | 2012-11-06 | 2013-02-06 | 昆山北极光电子科技有限公司 | One-piece hydraulic linear driving device |
| CN103321981A (en) * | 2013-07-01 | 2013-09-25 | 武汉船用机械有限责任公司 | Pressure protection system for oil cylinder of shark pincers |
| CN103321981B (en) * | 2013-07-01 | 2015-09-02 | 武汉船用机械有限责任公司 | Shark jaw oil cylinder working-pressure protective system |
| CN104405711B (en) * | 2014-11-20 | 2016-08-24 | 沈阳东北电力调节技术有限公司 | The heavily loaded electrohydraulic actuator that band compensates drives valve system |
| CN104405711A (en) * | 2014-11-20 | 2015-03-11 | 沈阳东北电力调节技术有限公司 | Overload electrohydraulic executing mechanism drive valve system with compensation function |
| CN105020458A (en) * | 2015-07-27 | 2015-11-04 | 江苏大学 | Electro hydraulic actuator for butterfly valve |
| CN105402200A (en) * | 2015-12-29 | 2016-03-16 | 沈阳东北电力调节技术有限公司 | Integrated electro hydraulic control device |
| CN107605818A (en) * | 2017-10-19 | 2018-01-19 | 燕山大学 | A kind of electro-hydraulic driving swing mechanism |
| CN110345129A (en) * | 2019-07-19 | 2019-10-18 | 韩国昊 | Hydraulic cylinder |
| CN110345129B (en) * | 2019-07-19 | 2020-09-11 | 浙江雷宸智能科技有限公司 | Hydraulic cylinder |
| CN112360831A (en) * | 2020-12-02 | 2021-02-12 | 江苏新扬新材料股份有限公司 | Synchronous opening and closing control device for cabin door of auxiliary power system |
| CN112963560A (en) * | 2021-04-16 | 2021-06-15 | 江苏理工学院 | Electro-hydraulic drive gas gate valve with stress detection function and control system |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2011072503A1 (en) | 2011-06-23 |
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Open date: 20100623 |