CN109611411B - High-speed heavy-load actuator - Google Patents
High-speed heavy-load actuator Download PDFInfo
- Publication number
- CN109611411B CN109611411B CN201811644013.7A CN201811644013A CN109611411B CN 109611411 B CN109611411 B CN 109611411B CN 201811644013 A CN201811644013 A CN 201811644013A CN 109611411 B CN109611411 B CN 109611411B
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- Prior art keywords
- oil
- piston
- cylinder barrel
- oil supply
- supply channel
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- 230000002706 hydrostatic effect Effects 0.000 claims abstract description 52
- 230000000149 penetrating effect Effects 0.000 claims abstract description 3
- 230000003068 static effect Effects 0.000 claims description 15
- 230000002093 peripheral effect Effects 0.000 claims description 6
- 238000007789 sealing Methods 0.000 claims description 3
- 239000007788 liquid Substances 0.000 claims 4
- 230000008878 coupling Effects 0.000 description 3
- 238000010168 coupling process Methods 0.000 description 3
- 238000005859 coupling reaction Methods 0.000 description 3
- 238000004088 simulation Methods 0.000 description 3
- 238000005461 lubrication Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
Classifications
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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
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
-
- 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
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1428—Cylinders
-
- 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
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1447—Pistons; Piston to piston rod assemblies
-
- 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
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1457—Piston rods
-
- 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
- F15B2215/00—Fluid-actuated devices for displacing a member from one position to another
- F15B2215/30—Constructional details thereof
Abstract
The invention discloses a high-speed heavy-load actuator, which relates to the technical field of hydraulic servo actuators and comprises a cylinder barrel and a piston rod, wherein two hydrostatic bearings are respectively embedded at two ends of an inner cavity of the cylinder barrel, the piston rod is arranged in the two hydrostatic bearings in a penetrating manner, an oil supply channel is arranged on a piston on the piston rod, and a first servo oil supply channel and a second servo oil supply channel are respectively arranged on the hydrostatic bearings, close to the two ends, of the side wall of the cylinder barrel; when the piston moves to the top of the inner cavity of the cylinder barrel, oil provided by the first servo oil supply channel enters the top of the piston through the oil supply channel on the piston; when the piston moves to the bottommost part of the inner cavity of the cylinder barrel, oil provided by the second servo oil supply channel enters the bottom of the piston through the oil supply channel on the piston. By arranging the oil supply channel on the piston, when the piston moves to the upper limit position and the lower limit position of the cylinder barrel, oil enters a gap between the end face of the piston and the cylinder barrel through the oil supply channel, so that the piston is convenient to start, and waveform distortion phenomena such as waveform peak clipping and the like caused by blockage of the piston and the servo oil supply channel are avoided.
Description
Technical Field
The invention relates to the technical field of hydraulic servo actuators, in particular to a high-speed heavy-load actuator which is used for a tire coupling vehicle road simulation test bed and needs to bear larger radial force.
Background
The high-speed heavy-load actuator is a key execution mechanism of a tire coupling vehicle road simulation test bed and mainly comprises an upper area double-head piston rod, a lower area double-head piston rod and a cylinder barrel with a static load balancing device at the bottom. The sliding pair of the double-head piston rod and the cylinder barrel adopts a hydrostatic bearing to reduce the friction resistance between the piston rod and the cylinder barrel, so that the high-speed heavy-load actuator has the characteristics of high speed, high frequency and low viscosity.
The prior actuator has the following technical defects:
1) The piston blocks the oil inlet hole on the side surface of the cylinder barrel at the starting position, so that the starting is slow or difficult to start, and waveform distortion phenomena such as waveform peak clipping and the like are generated when the piston and the oil supply channel are partially blocked when the piston moves to the upper limit position and the lower limit position.
2) The hydrostatic bearing between the sliding pair of the double-end piston rod and the cylinder barrel adopts pressure oil lubrication, the structure of the hydrostatic bearing adopts radial four-section pressure oil chambers, when radial force is applied, one side gap between the piston rod and the cylinder barrel is reduced, the other side gap is increased, the pressure of the pressure oil chamber on one side with the reduced gap is reduced, and the pressure on one side with the increased gap is reduced, so that a reverse hydraulic radial force is generated to be balanced with the applied radial force, but lubrication failure can be caused when the direction of the radial force is inconsistent with the direction of the pressure oil chamber.
Disclosure of Invention
The invention aims to provide a high-speed heavy-load actuator, which solves the problems of overlarge oil discharge amount of an actuator piston and static pressure sealing failure.
In order to achieve the above purpose, the present invention adopts the following technical scheme:
the high-speed heavy-load actuator comprises a cylinder barrel and a piston rod, wherein two hydrostatic bearings are respectively embedded at two ends of an inner cavity of the cylinder barrel, the piston rod penetrates through the two hydrostatic bearings, an oil supply channel is arranged on a piston on the piston rod, and a first servo oil supply channel and a second servo oil supply channel are respectively arranged on the hydrostatic bearings, close to the two ends, of the side wall of the cylinder barrel; when the piston moves to the top of the inner cavity of the cylinder barrel, oil provided by the first servo oil supply channel enters the top of the piston through the oil supply channel on the piston; when the piston moves to the bottommost part of the inner cavity of the cylinder barrel, oil provided by the second servo oil supply channel enters the bottom of the piston through the oil supply channel on the piston.
Further, the oil supply channel on the piston comprises a first annular oil groove, a second annular oil groove, an upper oil starting channel and a lower oil starting channel, wherein the annular oil grooves are distributed on the outer circumferential surface of the piston, the first annular oil groove is communicated with the upper end surface of the piston through the upper oil starting channel, and the second annular oil groove is communicated with the lower end surface of the piston through the lower oil starting channel.
Preferably, the first annular oil groove and the second annular oil groove are respectively communicated with 2 to 6 upper oil starting channels and lower oil starting channels, and the upper oil starting channels and the lower oil starting channels are respectively and uniformly distributed along the radial direction of the piston.
Further, the piston rod is a double-head piston rod.
Furthermore, eight sections of hydrostatic oil cavities are arranged on the inner peripheral surface of the hydrostatic bearing, an annular oil supply groove is arranged on the outer peripheral surface of the hydrostatic bearing, and each hydrostatic oil cavity is communicated with the annular oil supply groove through orifices corresponding to the hydrostatic oil cavities one by one.
Further, the eight sections of static pressure oil cavities are uniformly distributed along the radial direction of the static pressure bearing.
Further, the cylinder barrel is provided with two oil inlet holes and an oil supply channel communicated with the two oil inlet holes, and the two oil inlet holes are respectively communicated with annular oil supply grooves on the two hydrostatic bearings.
Further, the oil inlet hole and the oil supply channel on the cylinder barrel, and the annular oil supply groove and the throttling hole on the hydrostatic bearing form an oil supply channel of the hydrostatic bearing.
Further, the cylinder top be equipped with the upper end cover on sealed cylinder top, upper end cover butt is located the hydrostatic bearing of cylinder inner chamber upper end, the cylinder afterbody is equipped with the tail sleeve that supports the cylinder, tail sleeve butt is located the hydrostatic bearing of cylinder inner chamber lower extreme, tail sleeve inner chamber is the dead load cavity.
Further, the upper end cover be equipped with the third annular oil groove, third annular oil groove intercommunication and the terminal surface of the hydrostatic bearing of upper end cover butt, the tail sleeve be equipped with the fourth annular oil groove, the terminal surface of the hydrostatic bearing of fourth annular oil groove intercommunication and tail sleeve butt, the cylinder on be equipped with oil gallery and oil return channel, third annular oil groove and fourth annular oil groove communicate with the oil gallery through this oil return channel, third annular oil groove, fourth annular oil groove, oil gallery and oil return channel constitute hydrostatic bearing's oil return passageway.
Compared with the prior art, the invention has the following beneficial effects:
according to the invention, the oil supply channel is formed in the piston, so that when the piston moves to the upper limit position and the lower limit position of the cylinder barrel, oil enters a gap between the end face of the piston and the cylinder barrel through the oil supply channel, the piston is conveniently started, and waveform distortion phenomena such as waveform peak clipping and the like caused by blockage of the piston and the servo oil supply channel are avoided.
Drawings
FIG. 1 illustrates a cross-sectional view of a high speed, heavy duty actuator according to an embodiment of the present invention;
FIG. 2 is a cross-sectional view taken along line A-A of FIG. 1;
FIG. 3 is a cross-sectional view taken along B-B in FIG. 1;
FIG. 4 is a cross-sectional view taken along line C-C of FIG. 2;
FIG. 5 is a cross-sectional view taken along line D-D of FIG. 4;
FIG. 6 is an enlarged view of FIG. 1 at I;
fig. 7 is an enlarged view at ii in fig. 1.
Detailed Description
The high-speed heavy-load actuator is used for a tire coupling vehicle road simulation test bed and needs to bear larger radial force.
The action of the actuator is generated by supplying oil to the servo valve, so that the servo oil supply channel can only be arranged on the side surface of the cylinder barrel. Before the actuator is started, the piston is positioned at the bottommost part of the cylinder barrel. The existing actuator can completely block the servo oil supply channel due to the side surface of the piston, and oil can only enter the bottom of the piston from the gap between the piston and the cylinder barrel, so that the starting is slow and difficult. The invention can realize quick start by arranging the oil supply channel on the piston, and can also eliminate waveform distortion phenomena such as waveform peak clipping and the like generated when the piston and the servo oil supply channel on the cylinder block are blocked when the piston moves to the upper limit position and the lower limit position.
As shown in fig. 1, the high-speed heavy-load actuator comprises a cylinder 4 and a piston rod 1, wherein two hydrostatic bearings 3 are respectively embedded at two ends of an inner cavity of the cylinder 4, the piston rod 1 is arranged in the two hydrostatic bearings 3 in a penetrating manner, and the piston rod 1 is a double-head piston rod. The top of the cylinder barrel 4 is provided with an upper end cover 2 for sealing the top end of the cylinder barrel 4, and the upper end cover 2 is abutted against a hydrostatic bearing 3 positioned at the upper end of the inner cavity of the cylinder barrel 4. The tail of the cylinder barrel 4 is provided with a tail sleeve 6 for supporting the cylinder barrel 4, the tail sleeve 6 is abutted against a hydrostatic bearing 3 positioned at the lower end of the inner cavity of the cylinder barrel 4, and the inner cavity of the tail sleeve 6 is a static load cavity.
Referring to fig. 1 and 7, hydrostatic bearings 3 near both ends of the sidewall of the cylinder tube 4 are respectively provided with a first servo oil supply passage 41 and a second servo oil supply passage 42 communicating with a servo valve. An oil supply channel is arranged on a piston 5 on the piston rod 1. When the piston 5 moves to the top of the inner cavity of the cylinder barrel 4, oil provided by the first servo oil supply channel 41 enters the top of the piston 5 through the oil supply channel on the piston 5; when the piston 5 moves to the bottom of the inner cavity of the cylinder tube 4, the oil provided by the second servo oil supply channel 42 enters the bottom of the piston through the oil supply channel on the piston 5.
Referring to fig. 1, 2, 4 and 7, preferably, the oil supply passage on the piston 5 includes a first annular oil groove 52, a second annular oil groove 53, an upper oil starting passage 51 and a lower oil starting passage 54. Each annular oil groove is distributed on the outer circumferential surface of the piston 5, the first annular oil groove 52 is communicated with the upper end surface of the piston 5 through an upper oil starting channel 51, and the second annular oil groove 53 is communicated with the lower end surface of the piston 5 through a lower oil starting channel 54. Further preferably, the first annular oil groove 52 and the second annular oil groove 53 are respectively communicated with 2 to 6 upper oil starting passages 51 and lower oil starting passages 54, and the upper oil starting passages 51 and the lower oil starting passages 54 are respectively uniformly distributed along the radial direction of the piston 5.
When the piston 5 moves to the top of the inner cavity of the cylinder tube 4, the first servo oil supply channel 41 is communicated with the first annular oil groove 52 of the piston 5, and oil enters the top of the piston 5 through the first annular oil groove 52. When the piston 5 moves to the bottom of the inner cavity of the cylinder barrel 4, the second servo oil supply channel 42 is communicated with the second annular oil groove 53 of the piston 5, and oil enters the bottom of the piston 5 through the second annular oil groove 53.
As shown in fig. 5, eight sections of hydrostatic oil chambers 31 are provided on the inner peripheral surface of the hydrostatic bearing 3, and an annular oil supply groove 33 is provided on the outer peripheral surface of the hydrostatic bearing 3, and each hydrostatic oil chamber 31 communicates with the annular oil supply groove 33 through orifices 32 in one-to-one correspondence therewith. Preferably, eight sections of hydrostatic oil chambers 31 are radially distributed along the hydrostatic bearing 3.
Referring to fig. 4, 5 and 7, the cylinder 4 is provided with two oil inlet holes 43 and an oil supply channel 44 communicating the two oil inlet holes 43, and the two oil inlet holes 43 are respectively communicated with the annular oil supply grooves 33 on the two hydrostatic bearings 3. The oil inlet hole 43 and the oil supply passage 44 in the cylinder tube 4, and the annular oil supply groove 33 and the orifice 32 in the hydrostatic bearing 3 constitute an oil supply passage of the hydrostatic bearing 3.
As shown in fig. 1, the upper end cap 2 is provided with a third annular oil groove 21, and the third annular oil groove 21 communicates with an end surface of the hydrostatic bearing 3 that abuts against the upper end cap 2. The tail sleeve 6 is provided with a fourth annular oil groove 61, and the fourth annular oil groove 61 communicates with the end face of the hydrostatic bearing 3 abutting against the tail sleeve 6. The cylinder tube 4 is provided with an oil return hole 45 and an oil return channel 46, the third annular oil groove 21 and the fourth annular oil groove 61 are communicated with the oil return hole 45 through the oil return channel 46, and the third annular oil groove 21, the fourth annular oil groove 61, the oil return hole 45 and the oil return channel 46 form an oil return passage of the hydrostatic bearing 3.
The working principle of the hydrostatic bearing is that when the piston rod deflects under the action of radial load, a closed oil cavity is formed at one side of the clearance, so that oil leakage is reduced, and the pressure of the oil cavity is increased; the other side forms an open oil cavity due to the increase of the clearance, so that the oil leakage quantity is increased, and the pressure of the open oil cavity is rapidly reduced due to the throttling effect of the throttle hole. The opposite sides create a large pressure differential, thus creating a reverse radial pressure that balances the radially applied force. However, in the case of the four-stage oil chamber, when the direction of the applied radial force does not coincide with the direction of the hydrostatic chamber, it is difficult to form a closed oil chamber on the side where the clearance is small, and in order to balance the hydraulic pressure with the radial force, only the oil supply pressure and the oil supply flow rate are increased. The invention changes four sections into eight sections of the inner side static pressure oil chamber of the static pressure bearing, and can reduce the oil supply pressure and the oil supply flow, thereby greatly reducing the oil supply power.
The above description is illustrative of the embodiments using the present teachings, and is not intended to limit the scope of the present teachings to any particular modification or variation of the present teachings by those skilled in the art.
Claims (6)
1. The utility model provides a high-speed heavy load actuator which characterized in that: the hydraulic cylinder comprises a cylinder barrel (4) and a piston rod (1), wherein two hydrostatic bearings (3) are respectively embedded at two ends of an inner cavity of the cylinder barrel (4), the piston rod (1) is arranged in the two hydrostatic bearings (3) in a penetrating mode, an oil supply channel is arranged on a piston (5) on the piston rod (1), and a first servo oil supply channel (41) and a second servo oil supply channel (42) are respectively arranged on the hydrostatic bearings (3) on the side wall of the cylinder barrel (4) close to the two ends; when the piston (5) moves to the top of the inner cavity of the cylinder barrel (4), oil provided by the first servo oil supply channel (41) enters the top of the piston (5) through the oil supply channel on the piston; when the piston (5) moves to the bottommost part of the inner cavity of the cylinder barrel (4), oil provided by the second servo oil supply channel (42) enters the bottom part of the piston (5) through the oil supply channel on the piston;
the oil supply channel on the piston (5) comprises a first annular oil groove (52), a second annular oil groove (53), an upper oil starting channel (51) and a lower oil starting channel (54), wherein the annular oil grooves are distributed on the outer circumferential surface of the piston (5), the first annular oil groove (52) is communicated with the upper end surface of the piston (5) through the upper oil starting channel (51), and the second annular oil groove (53) is communicated with the lower end surface of the piston (5) through the lower oil starting channel (54);
eight sections of static pressure oil cavities (31) are formed in the inner peripheral surface of the static pressure bearing (3), annular oil supply grooves (33) are formed in the outer peripheral surface of the static pressure bearing (3), and each static pressure oil cavity (31) is communicated with each annular oil supply groove (33) through an orifice (32) corresponding to each static pressure oil cavity one by one;
the top of the cylinder barrel (4) is provided with an upper end cover (2) for sealing the top end of the cylinder barrel (4), the upper end cover (2) is abutted against a hydrostatic bearing (3) positioned at the upper end of the inner cavity of the cylinder barrel (4), the tail part of the cylinder barrel (4) is provided with a tail sleeve (6) for supporting the cylinder barrel (4), the tail sleeve (6) is abutted against the hydrostatic bearing (3) positioned at the lower end of the inner cavity of the cylinder barrel (4), and the inner cavity of the tail sleeve (6) is a static load cavity;
the upper end cover (2) be equipped with third annular oil groove (21), the terminal surface of third annular oil groove (21) intercommunication and hydrostatic bearing (3) of upper end cover (2) butt, tail sleeve (6) be equipped with fourth annular oil groove (61), the terminal surface of fourth annular oil groove (61) intercommunication and hydrostatic bearing (3) of tail sleeve (6) butt, cylinder (4) on be equipped with oil gallery (45) and oil return channel (46), third annular oil groove (21) and fourth annular oil groove (61) are through oil return channel (46) and oil gallery (45) intercommunication, third annular oil groove (21), fourth annular oil groove (61), oil gallery (45) and oil return channel (46) constitute the oil return passageway of hydrostatic bearing (3).
2. The high speed, heavy duty actuator of claim 1, wherein: the number of the upper oil liquid starting channels (51) and the lower oil liquid starting channels (54) is 2 to 6, and the upper oil liquid starting channels (51) and the lower oil liquid starting channels (54) are uniformly distributed along the radial direction of the piston (5) respectively.
3. The high speed, heavy duty actuator of claim 1, wherein: the piston rod is a double-head piston rod.
4. The high speed, heavy duty actuator of claim 1, wherein: the eight sections of static pressure oil cavities (31) are radially and uniformly distributed along the static pressure bearing (3).
5. The high speed, heavy duty actuator of claim 1, wherein: the cylinder barrel (4) is provided with two oil inlet holes (43) and an oil supply channel (44) communicated with the two oil inlet holes (43), and the two oil inlet holes (43) are respectively communicated with the annular oil supply grooves (33) on the two hydrostatic bearings (3).
6. The high-speed, heavy-duty actuator of claim 5, wherein: the oil inlet hole (43) and the oil supply channel (44) on the cylinder barrel (4) and the annular oil supply groove (33) and the throttle hole (32) on the hydrostatic bearing (3) form an oil supply channel of the hydrostatic bearing (3).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811644013.7A CN109611411B (en) | 2018-12-29 | 2018-12-29 | High-speed heavy-load actuator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811644013.7A CN109611411B (en) | 2018-12-29 | 2018-12-29 | High-speed heavy-load actuator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109611411A CN109611411A (en) | 2019-04-12 |
| CN109611411B true CN109611411B (en) | 2024-04-12 |
Family
ID=66017338
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811644013.7A Active CN109611411B (en) | 2018-12-29 | 2018-12-29 | High-speed heavy-load actuator |
Country Status (1)
| Country | Link |
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| CN (1) | CN109611411B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111207935B (en) * | 2020-03-13 | 2022-02-22 | 湖南科技大学 | Wide-band large-displacement vibration simulation vibration exciter suitable for road simulation of high-speed tracked vehicle |
Citations (7)
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|---|---|---|---|---|
| CN102042281A (en) * | 2011-01-11 | 2011-05-04 | 浙江大学 | Oil cylinder of static pressure vibration exciter |
| WO2012010032A1 (en) * | 2010-07-23 | 2012-01-26 | 湖南三一智能控制设备有限公司 | Hydraulic oil cylinder, correlative device thereof, hydraulic cushion system, excavator and concrete pump truck |
| CN102588382A (en) * | 2012-03-19 | 2012-07-18 | 北京航空航天大学 | Direct-drive electro-hydraulic actuator |
| KR20140121184A (en) * | 2013-04-05 | 2014-10-15 | 한국기계연구원 | Highly precision concentric and high responsiveness of a hydraulic servo actuator |
| CN105179362A (en) * | 2015-09-02 | 2015-12-23 | 张响芝 | Unbalance load-resisting servo oil cylinder |
| CN207598633U (en) * | 2017-09-20 | 2018-07-10 | 沈阳中之杰流体控制系统有限公司 | A kind of High-performance static hydraulic support servo actuator |
| CN209469643U (en) * | 2018-12-29 | 2019-10-08 | 厦门理工学院 | A kind of high-speed overload actuator |
-
2018
- 2018-12-29 CN CN201811644013.7A patent/CN109611411B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2012010032A1 (en) * | 2010-07-23 | 2012-01-26 | 湖南三一智能控制设备有限公司 | Hydraulic oil cylinder, correlative device thereof, hydraulic cushion system, excavator and concrete pump truck |
| CN102042281A (en) * | 2011-01-11 | 2011-05-04 | 浙江大学 | Oil cylinder of static pressure vibration exciter |
| CN102588382A (en) * | 2012-03-19 | 2012-07-18 | 北京航空航天大学 | Direct-drive electro-hydraulic actuator |
| KR20140121184A (en) * | 2013-04-05 | 2014-10-15 | 한국기계연구원 | Highly precision concentric and high responsiveness of a hydraulic servo actuator |
| CN105179362A (en) * | 2015-09-02 | 2015-12-23 | 张响芝 | Unbalance load-resisting servo oil cylinder |
| CN207598633U (en) * | 2017-09-20 | 2018-07-10 | 沈阳中之杰流体控制系统有限公司 | A kind of High-performance static hydraulic support servo actuator |
| CN209469643U (en) * | 2018-12-29 | 2019-10-08 | 厦门理工学院 | A kind of high-speed overload actuator |
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| CN109611411A (en) | 2019-04-12 |
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