CN101749300A - Integrating electro-hydraulic actuator - Google Patents
Integrating electro-hydraulic actuator Download PDFInfo
- Publication number
- CN101749300A CN101749300A CN200910248517A CN200910248517A CN101749300A CN 101749300 A CN101749300 A CN 101749300A CN 200910248517 A CN200910248517 A CN 200910248517A CN 200910248517 A CN200910248517 A CN 200910248517A CN 101749300 A CN101749300 A CN 101749300A
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- Prior art keywords
- hydraulic
- valve
- oil
- received
- fluid port
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- 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.)
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
-
- 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
- F15B2211/20507—Type of prime mover
- F15B2211/20515—Electric motor
-
- 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
- F15B2211/2053—Type of pump
- F15B2211/20561—Type of pump reversible
-
- 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
- F15B2211/27—Directional control by means of the pressure source
-
- 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
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30505—Non-return valves, i.e. check valves
- F15B2211/3051—Cross-check 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
- F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
- F15B2211/50527—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves using cross-pressure relief valves
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/61—Secondary circuits
- F15B2211/611—Diverting circuits, e.g. for cooling or filtering
-
- 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
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
-
- 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
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7051—Linear output members
- F15B2211/7053—Double-acting output members
- F15B2211/7054—Having equal piston areas
Landscapes
- 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 actuator, the problems to be solved are 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 of an opening type, the oil liquid is easy to pollute; and the installation direction of the actuator is fixed. 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, an electric motor drives the double-direction hydraulic pump, and the above devices are integrated into one body. The benefits of the invention are as follows: a 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, pipeline.
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 actuator.
The object of the present invention is achieved like this: two inlets with hydraulic locking valve group of locking Position of Hydraulic Cylinder dock with two hydraulic fluid ports of bidirectional hydraulic pump, two outlets of hydraulic locking valve group are docked with two cylinder mouths of dual-rod hydraulic cylinder, two control ends of hydraulic locking valve group are received respectively on the last oil pipeline that can make its reverse opening, motor driving bidirectional hydraulic pump, above-mentioned each equipment integration is an integral body.
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 pipeline 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.When the termination of pumping of external command oil hydraulic pump (such as to the motor outage), the oil pressure of last oil pipeline is lower than setting value, can not trigger hydraulic locking valve group, and hydraulic locking valve group is closed the system oil return pipeline, accurately location is realized in the position of locking oil hydraulic cylinder and piston rod, hydraulic cylinder piston rod; The motor counter-rotating, the working procedure of system and last symmetry.Pressure oil transmits energy in the loop of a sealing.
Compared with prior art, the invention has the beneficial effects as follows: it is with several equipment integration one integral body, becomes locking system, and imperforation formula fuel tank is installed not the recipient to restriction, and then provides convenience for the installation of valve or air door; 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 hydraulic locking valve group, provide the system reverse equilibrant once more, made the system accuracy height; 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 underground schematic representation of the present invention when using first kind of hydraulic locking valve group.
Fig. 2 is a structural representation of the present invention.
Fig. 3 is the underground schematic representation of the present invention when using second 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 respectively on the last oil pipeline that can make its reverse opening, 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.
When oil hydraulic cylinder (valve) does not need to keep midway, system establishes position limit switch, make oil hydraulic cylinder (valve) on the position of Kai Heguan, realize keeping automatically, said position limit switch is, two electromagnetic induction switch 13-1,13-2 are arranged on the housing 20, these two electromagnetic induction switch are located at the corresponding position, two stroke ends up and down with hydraulic cylinder piston rod respectively, 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 apart from induction switch, be used to trigger induction switch, to detect the position of piston rod.
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 oil return pipeline in protection loop; two imports of shuttle valve 7 are connected in the upper and lower oil pipeline of system respectively, and the outlet of shuttle valve is received the oil return pipeline in protection loop by relief valve 5, and solenoid valve 6 is in parallel with relief valve.
Above-mentioned each equipment integration is assembled into one (referring to Fig. 2).
Working procedure is: when motor M is just being changeed, 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.When hydraulic cylinder piston is moved downward to the stroke end, inductive head triggers corresponding induction switch 13-1, this switch sends signal, output to the control circuit of establishing in addition, this control circuit cuts off the power supply to motor M, on this moment on the oil pipeline hydraulic pressure be lower than setting value, can not trigger the control end of equilibrium valve 8-2, equilibrium valve 8-2 closes the system oil return pipeline, the position of locking oil hydraulic cylinder and piston rod, and valve is realized opening or closing reliably; The control circuit that other establishes send electricity to motor M and makes its counter-rotating, the working procedure of system and last symmetry.
When system overload, high pressure oil surpasses setting value, and shuttle valve is opened, and oil is through the oil return pipeline in shuttle valve, relief valve and protection loop; When system was unloaded, high pressure oil was through the oil return pipeline 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 A branch line 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 is provided with position limit switch, and the position of setting is identical with a last embodiment with working procedure.
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 (6)
1. integrating electro-hydraulic 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 two outlets of hydraulic locking valve group, motor driving 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 have the hydraulic locking valve group of locking Position of Hydraulic Cylinder by two equilibrium valves with 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 pipeline 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: two electromagnetic induction switch are arranged on the housing, these two electromagnetic induction switch are located at the corresponding position, two stroke ends up and down with hydraulic cylinder piston rod respectively, an inductive head is fixed in the end of piston rod, inductive head apart from the distance of induction switch less than the distance of piston rod apart from induction switch.
5. according to claim 1 or 2 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 oil return pipeline of protecting the loop, and two imports of shuttle valve are connected in the upper and lower oil pipeline of system respectively; the outlet of shuttle valve is received the oil return pipeline in protection loop by relief valve, and solenoid valve is in parallel with relief valve.
6. 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 |
|---|---|---|---|
| CN200910248517A CN101749300A (en) | 2009-12-18 | 2009-12-18 | Integrating electro-hydraulic actuator |
| PCT/CN2010/070802 WO2011072502A1 (en) | 2009-12-18 | 2010-03-01 | Integrated electro-hydraulic actuator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910248517A CN101749300A (en) | 2009-12-18 | 2009-12-18 | Integrating electro-hydraulic actuator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101749300A true CN101749300A (en) | 2010-06-23 |
Family
ID=42476770
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200910248517A Pending CN101749300A (en) | 2009-12-18 | 2009-12-18 | Integrating electro-hydraulic actuator |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN101749300A (en) |
| WO (1) | WO2011072502A1 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011072503A1 (en) * | 2009-12-18 | 2011-06-23 | 沈阳东北电力调节技术有限公司 | Integrated electro-hydraulic servo actuator |
| 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 |
| CN105422971A (en) * | 2015-12-29 | 2016-03-23 | 沈阳东北电力调节技术有限公司 | Integrated electric-hydraulic adjustment device |
| CN113944678A (en) * | 2021-10-28 | 2022-01-18 | 杭州华鼎新能源有限公司 | Double-rod linkage type hydraulic drive control system |
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| CN102606800B (en) * | 2012-03-31 | 2013-09-11 | 绍兴文理学院 | Detection restorative method of hydraulic valve jamming and chucking faults |
| MX2016011024A (en) | 2014-02-28 | 2017-03-15 | Project Phoenix Llc | Pump integrated with two independently driven prime movers. |
| WO2015148662A1 (en) | 2014-03-25 | 2015-10-01 | Afshari Thomas | System to pump fluid and control thereof |
| EP3134648B1 (en) | 2014-04-22 | 2023-06-14 | Project Phoenix, LLC | Fluid delivery system with a shaft having a through-passage |
| CN104044004B (en) * | 2014-05-23 | 2016-05-18 | 宁波大红鹰学院 | Machine slide case reciprocation cycle transmission device and method of work thereof |
| WO2015187681A1 (en) | 2014-06-02 | 2015-12-10 | Afshari Thomas | Hydrostatic transmission assembly and system |
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| US10072676B2 (en) | 2014-09-23 | 2018-09-11 | Project Phoenix, LLC | System to pump fluid and control thereof |
| EP3204647B1 (en) | 2014-10-06 | 2021-05-26 | Project Phoenix LLC | Linear actuator assembly and system |
| WO2016064569A1 (en) | 2014-10-20 | 2016-04-28 | Afshari Thomas | Hydrostatic transmission assembly and system |
| EP3344853B1 (en) | 2015-09-02 | 2020-11-04 | Project Phoenix LLC | System to pump fluid and control thereof |
| EP3344874B1 (en) | 2015-09-02 | 2021-01-20 | Project Phoenix LLC | System to pump fluid and control thereof |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN101749299A (en) * | 2009-12-18 | 2010-06-23 | 沈阳东北电力调节技术有限公司 | Integrating electro-hydraulic servo actuator |
-
2009
- 2009-12-18 CN CN200910248517A patent/CN101749300A/en active Pending
-
2010
- 2010-03-01 WO PCT/CN2010/070802 patent/WO2011072502A1/en active Application Filing
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011072503A1 (en) * | 2009-12-18 | 2011-06-23 | 沈阳东北电力调节技术有限公司 | Integrated electro-hydraulic servo actuator |
| 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 |
| CN105422971A (en) * | 2015-12-29 | 2016-03-23 | 沈阳东北电力调节技术有限公司 | Integrated electric-hydraulic adjustment device |
| CN113944678A (en) * | 2021-10-28 | 2022-01-18 | 杭州华鼎新能源有限公司 | Double-rod linkage type hydraulic drive control system |
| CN113944678B (en) * | 2021-10-28 | 2024-05-31 | 杭州华鼎新能源有限公司 | Double-rod linkage type hydraulic driving control system |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2011072502A1 (en) | 2011-06-23 |
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