CN109268349B - Dual-redundancy hydraulic actuator with single-end mechanical lock - Google Patents
Dual-redundancy hydraulic actuator with single-end mechanical lock Download PDFInfo
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- CN109268349B CN109268349B CN201811410377.9A CN201811410377A CN109268349B CN 109268349 B CN109268349 B CN 109268349B CN 201811410377 A CN201811410377 A CN 201811410377A CN 109268349 B CN109268349 B CN 109268349B
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
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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
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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
- F15B15/1447—Pistons; Piston to piston rod assemblies
- F15B15/1452—Piston sealings
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/041—Removal or measurement of solid or liquid contamination, e.g. filtering
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Actuator (AREA)
Abstract
The invention discloses a dual-redundancy hydraulic actuator with a single-end mechanical lock, which comprises: the oil filter comprises a first power component, a second power component, a high-pressure safety valve, an oil filter, a pressurizing oil tank, a filling valve, a one-way valve, an electromagnetic directional valve, a first balance valve, a second balance valve, an actuating cylinder, a first micro switch, a second micro switch, a third micro switch and a fourth micro switch. The invention overcomes the defects of complex system composition, large risk of oil leakage of pipeline connection and low integration level of the traditional centralized energy hydraulic actuating system for retracting and releasing the landing gear of the airplane.
Description
Technical Field
The invention belongs to the technical field of servo actuation, and particularly relates to a dual-redundancy hydraulic actuator with a single-ended mechanical lock.
Background
With the continuous development of China in the field of aviation, the development types of large fixed-wing unmanned aerial vehicles are increasingly abundant, and the requirements are increasingly large. Relative manned aircraft of unmanned aerial vehicle, its characteristics are: light weight, low speed and convenient maintenance in long voyage. The traditional power telex actuation system of concentrated hydraulic energy type is adopted for retraction of the landing gear of the airplane, the system pipeline is complex, the risk of high-pressure oil leakage is increased, in addition, after the landing gear is retracted in place, an independent mechanical lock system is required to bear the gravity load of the landing gear, and therefore the structure of the retraction system of the landing gear is complex, and the occupied space is large.
Disclosure of Invention
The technical problem solved by the invention is as follows: the defects of the prior art are overcome, the dual-redundancy hydraulic actuator with the single-end mechanical lock is provided, and the defects that the system composition of the existing aircraft landing gear retraction centralized energy hydraulic actuating system is complex, the risk of oil leakage of pipeline connection is large, and the integration level is low are overcome.
The purpose of the invention is realized by the following technical scheme: a dual redundant hydraulic actuator with a single ended mechanical lock, comprising: the automatic oil filter comprises a first power component, a second power component, a high-pressure safety valve, an oil filter, a pressurizing oil tank, a filling valve, a one-way valve, an electromagnetic directional valve, a first balance valve, a second balance valve, an actuating cylinder, a first micro switch, a second micro switch, a third micro switch and a fourth micro switch; one end of the first power component is connected with one end of the second power component, and the other end of the first power component is connected with the other end of the second power component; one end of the first power component is respectively connected with the high-pressure safety valve and the oil filter; the other end of the first power component is respectively connected with the one-way valve and the electromagnetic reversing valve; one end of the second power component is respectively connected with the high-pressure safety valve and the oil filter; the other end of the second power component is respectively connected with the one-way valve and the electromagnetic reversing valve; the high-pressure safety valve is respectively connected with the oil filter, the pressurizing oil tank and the one-way valve; the oil filter is connected with the electromagnetic directional valve; the pressurizing oil tank is connected with the filling valve; the one-way valve is respectively connected with the pressurizing oil tank and the electromagnetic directional valve; the electromagnetic directional valve is respectively connected with the first balance valve and the second balance valve; the first balance valve is connected with the actuating cylinder, and the second balance valve is connected with the actuating cylinder; the actuating cylinder is respectively connected with the first microswitch, the second microswitch, the third microswitch and the fourth microswitch.
In the dual-redundancy hydraulic actuator with the single-ended mechanical lock, the first power part comprises a first motor, a first cam bearing structure and a first valve distribution pump; the first motor is connected with the first cam bearing structure, and the first cam bearing structure is connected with the first valve flow distribution pump.
In the dual-redundancy hydraulic actuator with the single-ended mechanical lock, the second power part comprises a second motor, a second cam bearing structure and a second valve distribution pump; the second motor is connected with the second cam bearing structure, and the second cam bearing structure is connected with the second valve flow distribution pump.
In the dual-redundancy hydraulic actuator with the single-ended mechanical lock, the actuating cylinder comprises a front support lug, a locking nut, a piston transition joint, an inner hexagon screw, a fixing screw, a clamping claw, a lock head, a piston rod, a baffle ring, an inner piston rod, a spring, a transition nut, a rear support lug, the actuating cylinder and an oil circuit block; the front lug is in threaded connection with the piston transition joint, and the front lug and the piston transition joint are locked by the locking nut; the piston transition joint is connected with the piston rod, and the piston transition joint and the piston rod are fastened by the inner hexagon screw; the clamping claw is connected with the piston transition joint and is fastened through a fixing screw; the lock head is in threaded connection with one end of the inner piston rod, and the outer circular surface of the lock head is in contact with the inner circular surface of the clamping claw; the piston rod is arranged in the actuating cylinder; the baffle ring is arranged between the piston rod and the inner piston rod; one end of the inner piston rod is connected with the locking thread, the middle of the inner piston rod is connected with the baffle ring through a spring, and the other end of the inner piston rod is connected with the oil path block through a transition nut; one end of the spring is connected with the baffle ring, and the other end of the spring is connected with the inner piston rod; the internal thread of the transition nut is connected with the inner piston rod; the rear lug is connected with the oil circuit block; the actuating cylinder is respectively connected with the oil circuit block and the piston rod; the internal thread of the locking nut is connected with the front lug, and one end face of the locking nut is connected with the transition joint; the oil circuit block is respectively connected with the actuating cylinder, the rear lug, the transition nut and the inner piston rod.
In the above-mentioned dual redundancy hydraulic actuator with single-ended mechanical lock, still include: a piston seal ring; wherein, the piston seal ring is arranged in the annular groove at one end of the piston rod.
In the above-mentioned dual redundancy hydraulic actuator with single-ended mechanical lock, still include: an end face seal ring of the actuating cylinder; the actuating cylinder end face seal ring is arranged between the actuating cylinder and the oil circuit block.
In the above-mentioned dual redundancy hydraulic actuator with single-ended mechanical lock, still include: an inner piston seal ring; wherein, the inner piston sealing ring is arranged between the baffle ring and the inner piston rod.
In the above-mentioned dual redundancy hydraulic actuator with single-ended mechanical lock, still include: a baffle ring sealing ring; wherein, keep off the ring seal and install between fender ring and piston rod.
In the above-mentioned dual redundancy hydraulic actuator with single-ended mechanical lock, still include: an actuator cylinder seal ring; wherein, the actuator cylinder sealing ring is arranged between the actuator cylinder and the piston rod.
In the above-mentioned dual redundancy hydraulic actuator with single-ended mechanical lock, still include: a piston transition joint seal ring; wherein, the piston transition joint sealing washer is installed between transition joint and the piston rod.
Compared with the prior art, the invention has the following beneficial effects:
(1) according to the invention, the two groups of valve flow distribution pump assemblies are designed in parallel, so that the effect of dual redundancy of energy sources is achieved, when one group of energy source assemblies has a problem, the work of the other group of energy source assemblies is not influenced, and the normal function of the system is ensured;
(2) according to the invention, through the parallel design of the two groups of micro switches, the dual-redundancy effect of the in-place detection of the piston rod is achieved, when the piston rod moves in place, the in-place detection is carried out through the two independent micro switches, so that the reliability of the detection is improved;
(3) the invention achieves the effect of saving the axial installation size of the actuating cylinder by the design of the area of the single-rod symmetrical piston in the actuating cylinder;
(4) the invention achieves the effect of arranging the actuating cylinder with in-place locking function under the requirement of compact space by the structural design of the retraction in-place mechanism in the actuating cylinder with the single-rod symmetrical piston area.
Drawings
Various other advantages and benefits will become apparent to those of ordinary skill in the art upon reading the following detailed description of the preferred embodiments. The drawings are only for purposes of illustrating the preferred embodiments and are not to be construed as limiting the invention. Also, like reference numerals are used to refer to like parts throughout the drawings. In the drawings:
FIG. 1 is a schematic diagram of a dual redundant hydraulic actuator with a single ended mechanical lock according to an embodiment of the present invention;
fig. 2 is a diagram illustrating a retracted and locked state of the actuator cylinder according to an embodiment of the present invention;
FIG. 3 is a cross-sectional view of an actuator according to an embodiment of the present invention in an extended state;
fig. 4 is a diagram of a grab configuration provided by an embodiment of the present invention.
Detailed Description
Exemplary embodiments of the present disclosure will be described in more detail below with reference to the accompanying drawings. While exemplary embodiments of the present disclosure are shown in the drawings, it should be understood that the present disclosure may be embodied in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art. It should be noted that the embodiments and features of the embodiments may be combined with each other without conflict. The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings.
FIG. 1 is a schematic diagram of a dual redundant hydraulic actuator with a single ended mechanical lock according to an embodiment of the present invention. As shown in fig. 1, the dual redundancy hydraulic actuator with single-ended mechanical lock includes: the device comprises a first power component, a second power component, a high-pressure safety valve 4, an oil filter 5, a pressurized oil tank 6, a filling valve 7, a one-way valve 8, an electromagnetic directional valve 9, a first balance valve 10_1, a second balance valve 10_2, an actuating cylinder 11, a first micro switch 12_1, a second micro switch 12_2, a third micro switch 12_3 and a fourth micro switch 12_ 4; wherein the content of the first and second substances,
one end of the first power component is connected with one end of the second power component, and the other end of the first power component is connected with the other end of the second power component; one end of the first power component is respectively connected with the high-pressure safety valve 4 and the oil filter 5; the other end of the first power component is respectively connected with a one-way valve 8 and an electromagnetic directional valve 9; one end of the second power component is respectively connected with the high-pressure safety valve 4 and the oil filter 5; the other end of the second power component is respectively connected with a one-way valve 8 and an electromagnetic directional valve 9; the high-pressure safety valve 4 is respectively connected with the oil filter 5, the booster oil tank 6 and the one-way valve 8; the oil filter 5 is connected with the electromagnetic directional valve 9; the pressurizing oil tank 6 is connected with the filling valve 7; the one-way valve 8 is respectively connected with the pressurizing oil tank 6 and the electromagnetic directional valve 9; the electromagnetic directional valve 9 is respectively connected with the first balance valve 10_1 and the second balance valve 10_ 2; the first balance valve 10_1 is connected with the actuating cylinder 11, and the second balance valve 10_2 is connected with the actuating cylinder 11; the actuator cylinder 11 is connected to a first microswitch 12_1, a second microswitch 12_2, a third microswitch 12_3 and a fourth microswitch 12_4 respectively.
The working principle is as follows: the first power component and the second power component form dual redundancy of energy sources to provide power energy sources for the system, and when one group of power components fails, the other group of power components can normally complete the provision of the power energy sources for the system under the condition that the power components do not need to be cut off. The oil outlet ends of the two groups of power energy sources provide high-pressure oil, the high-pressure oil enters one cavity of the actuating cylinder 11 through the oil filter 5, the electromagnetic valve 9 and the balance valve 10_1, and the high-pressure oil returns to the oil inlet ends of the two groups of power energy sources through the balance valve 10_2 and the electromagnetic valve 9 in the other cavity of the actuating cylinder. The electromagnetic valve 9 is used for switching high-pressure oil to enter different cavities of the actuating cylinder to realize the extending and retracting actions of a piston rod in the actuating cylinder. The balance valve 10 is used for avoiding large fluctuation of the movement of the piston rod when the piston rod is subjected to large impact load, the safety valve 4 is used for setting the highest working pressure of the system, the system is protected from damage to structural members caused by overhigh pressure, the booster oil tank 6 is used for supplementing oil leakage in the working process of a power assembly, the filling valve 7 is used for filling oil for a closed system, the check valve 8 is used for realizing oil return of the oil and enters the booster oil tank 6, when the piston rod of the actuating cylinder 11 moves to one end, the micro switches 12_1 and 12_2 are triggered to indicate that the piston rod moves in place, the micro switches 12_1 and 12_2 form a redundant design, the reliability of in-place detection is ensured, when the piston rod of the actuating cylinder 11 moves to the other end, the micro switches 12_3 and 12_4 are triggered to indicate that the piston rod moves in place, and the micro switches 12_1 and 12_2 form a, the reliability of in-place detection is ensured.
As shown in fig. 1, the first power component comprises a first motor 1_1, a first cam bearing structure 2_1 and a first valve distribution pump 3_ 1; the first motor 1_1 is connected with the first cam bearing structure 2_1, and the first cam bearing structure 2_1 is connected with the first valve fluid distribution pump 3_ 1.
The working principle is as follows: after the motor 1_1 is electrified, the cam bearing 2_1 is driven to rotate at a one-way constant speed, the outer contour surface of the cam bearing 2_1 pushes the piston of the valve flow distribution pump 3_1 to realize axial movement, and the spring is arranged at the bottom end of the piston of the valve flow distribution pump 3_1, so that under the combined action of the cam bearing and the spring, the piston of the valve flow distribution pump 3_1 realizes reciprocating linear movement, and oil inlet and high-pressure oil outlet of oil are realized by matching with two one-way valves.
As shown in fig. 1, the second power component includes a second motor 1-2, a second cam bearing structure 2-2 and a second valve distribution pump 3-2; the second motor 1-2 is connected with a second cam bearing structure 2-2, and the second cam bearing structure 2-2 is connected with a second valve distribution pump 3-2.
The working principle is as follows: after the motor 1_2 is electrified, the cam bearing 2_2 is driven to rotate at a one-way constant speed, the outer contour surface of the cam bearing 2_2 pushes the piston of the valve flow distribution pump 3_2 to realize axial movement, and the spring is arranged at the bottom end of the piston of the valve flow distribution pump 3_2, so that under the combined action of the cam bearing and the spring, the piston of the valve flow distribution pump 3_2 realizes reciprocating linear movement, and oil inlet and high-pressure oil outlet of oil are realized by matching with two one-way valves.
As shown in fig. 2 and 3, the ram 11 includes: the hydraulic cylinder comprises a front support lug 13, a lock nut 32, a piston transition joint 14, an inner hexagon screw 15, a fixing screw 16, a clamping claw 17 (shown in figure 4), a lock head 18, a piston rod 19, a baffle ring 20, an inner piston rod 21, a spring 22, a piston seal ring 23, a transition nut 24, a rear support lug 25, a cylinder end face seal ring 26, a cylinder 27, an inner piston seal ring 28, a baffle ring seal ring 29, a cylinder seal ring 30, a piston transition joint seal ring 31 and an oil circuit block 33; wherein the content of the first and second substances,
the front lug 13 is in threaded connection with the piston transition joint 14, and the front lug 13 and the piston transition joint 14 are locked by the locking nut 32; the piston transition joint 14 is connected with the piston rod 19, and the piston transition joint 14 and the piston rod 19 are fastened by the hexagon socket head cap screw 15; the piston transition joint 14 is provided with a piston transition joint sealing ring 31 which seals the piston transition joint 14 and the piston rod 19; the clamping claw 17 is connected with the piston transition joint 14 and is fastened through a fixing screw 16; the lock head 18 is connected with one end of the inner piston rod 21 in a threaded manner, and the outer circular surface of the lock head 18 is contacted with the inner circular surface of the clamping claw 17; the piston rod 19 is arranged in the actuating cylinder 27, and the sealing between the piston rod and the actuating cylinder is completed through the actuating cylinder sealing ring 30 and the piston rod sealing ring 23; the baffle ring 20 is arranged between the piston rod 19 and the inner piston rod 21, and the sealing between the piston rod 19 and the inner piston rod 21 is completed through a baffle ring sealing ring 29 and an inner piston rod sealing ring 28; one end of an inner piston rod 21 is in threaded connection with the locking device 18, the middle of the inner piston rod 21 is connected with a baffle ring 20 through a spring 22, and the other end of the inner piston rod 21 is connected with an oil path block 33 through a transition nut 24; one end of the spring 22 is connected with the baffle ring 20, and the other end is connected with the inner piston rod 21; the sealing ring 23 is arranged in an annular groove at one end of the piston rod 19; the internal thread of the transition nut 24 is connected with the inner piston rod 21; the rear lug 25 is connected with the oil circuit block 33; the actuator cylinder end face seal ring 26 is arranged between the actuator cylinder 27 and the oil circuit block 33; the actuating cylinder 27 is respectively connected with the oil circuit block 33 and the piston rod 19; the inner piston sealing ring 28 is arranged between the baffle ring 20 and the inner piston rod 21; the retaining ring sealing ring 29 is arranged between the retaining ring 20 and the piston rod 19; the actuator cylinder seal ring 30 is arranged between the actuator cylinder 27 and the piston rod 19; the piston transition joint sealing ring 31 is arranged between the transition joint 14 and the piston rod 19; the internal thread of the locking nut 32 is connected with the front lug 13, and one end face of the locking nut is connected with the transition joint 14; the oil path block 33 is connected to the actuator cylinder 27, the rear lug 25, the transition nut 24, and the inner piston rod 21, respectively.
The working principle is as follows: the clamping claw 17 is fixed on the transition joint 14 through a fixing screw 16, the lock head 18 is fixedly installed at the left end of the inner piston rod 21 through internal threads, the baffle ring 20 is installed between the inner side of the cavity of the piston rod 19 and the outer side of the inner piston rod 21, the baffle ring 20 is connected with the inner piston rod 21 through a spring 22, and the inner piston rod 21 is fixedly connected with the oil circuit block 33 through a transition nut 24. As shown in fig. 2, when the actuator is locked, the top end of the grasping piece of the catch 17 is protruded and clamped at the right end of the lock head 18, and the outer side of the catch 17 is blocked by the blocking ring 20, so that the grasping piece of the catch 17 is prevented from sliding out of the right end of the lock head 18 under the condition of external force disturbance, and the piston rod 19 is mechanically locked. When high-pressure hydraulic oil passes through the internal cavity of the inner piston rod 21 through the oil path block 33 and enters the piston rod 19, leftward thrust is generated on the piston rod 19, and meanwhile, the high-pressure hydraulic oil also acts on the left end face of the retaining ring 20 to push the retaining ring 20 to move rightward against the pre-tightening force of the spring 22, so that the retaining ring 20 leaves the outer side of the grasping piece of the clamping claw 17, the shielding disappears, the piston rod 19 drives the clamping claw 17 to move leftward under the action of the thrust, the grasping piece of the clamping claw 17 is forced to open outward under the action of the right end inclined face of the locking head 18, the clamping claw 17 is separated from the locking head 18, the piston rod 19 is unlocked, the piston rod 19 continues to move leftward under the action of the hydraulic oil, until the extension microswitch 12 is touched, the power assembly stops working, the actuator extends to the right position, and the extension state. When high-pressure hydraulic oil enters a containing cavity between the actuating cylinder 27 and the piston rod 19 through an oil path block 33 on the actuating cylinder 27, the piston rod 19 starts to retract, when a grabbing piece of the grab 17 touches an inclined plane at the left end of the lock head 18, the grabbing piece is opened under the guidance of the grabbing piece, the piston rod 19 continues to move leftwards, the end part of the grabbing piece pushes the retaining ring 20 to move rightwards against the pretightening force of the spring 22, when the end part of the grabbing piece is restored to the original state through the inclined plane at the right end of the lock head 18, the retaining ring 20 moves leftwards under the restoring force of the spring 22 and is shielded outside the grabbing piece of the grab 17, and the piston rod.
The design scheme of the single-rod symmetric cylinder type dual-redundancy electro-hydraulic actuator with the single-end-in-place mechanical locking function in the actuating cylinder is provided, the actuator adopts dual energy components to form dual redundancy, and the system is high in working reliability; the pistons in the actuating cylinders are symmetrically arranged by adopting a single-rod, so that the overall axial size of the actuating cylinders is more compact, and the requirement of small axial installation space is met; the actuator cylinder is internally integrated with the in-place mechanical lock, the structure is compact, the requirement of mechanical locking by retracting the piston rod is met, the unlocking depends on internal hydraulic oil, and the unlocking reliability is high.
The above-described embodiments are merely preferred embodiments of the present invention, and general changes and substitutions by those skilled in the art within the technical scope of the present invention are included in the protection scope of the present invention.
Claims (9)
1. A dual redundancy hydraulic actuator having a single ended mechanical lock, comprising: the hydraulic oil filter comprises a first power component, a second power component, a high-pressure safety valve (4), an oil filter (5), a pressurized oil tank (6), a filling valve (7), a one-way valve (8), an electromagnetic directional valve (9), a first balance valve (10_1), a second balance valve (10_2), an actuating cylinder (11), a first micro switch (12_1), a second micro switch (12_2), a third micro switch (12_3) and a fourth micro switch (12_ 4); wherein the content of the first and second substances,
one end of the first power component is connected with one end of the second power component, and the other end of the first power component is connected with the other end of the second power component;
one end of the first power component is respectively connected with the high-pressure safety valve (4) and the oil filter (5); the other end of the first power component is respectively connected with a one-way valve (8) and an electromagnetic directional valve (9);
one end of the second power component is respectively connected with the high-pressure safety valve (4) and the oil filter (5); the other end of the second power component is respectively connected with a one-way valve (8) and an electromagnetic directional valve (9);
the high-pressure safety valve (4) is respectively connected with the oil filter (5), the booster oil tank (6) and the one-way valve (8);
the oil filter (5) is connected with the electromagnetic directional valve (9); the pressurizing oil tank (6) is connected with the filling valve (7); the one-way valve (8) is respectively connected with the pressurizing oil tank (6) and the electromagnetic directional valve (9);
the electromagnetic directional valve (9) is respectively connected with the first balance valve (10_1) and the second balance valve (10_ 2);
a first balance valve (10_1) is connected with the actuating cylinder (11), and a second balance valve (10_2) is connected with the actuating cylinder (11);
the actuating cylinder (11) is respectively connected with a first microswitch (12_1), a second microswitch (12_2), a third microswitch (12_3) and a fourth microswitch (12_ 4);
the actuating cylinder (11) comprises a front support lug (13), a locking nut (32), a piston transition joint (14), an inner hexagon screw (15), a fixing screw (16), a clamping claw (17), a lock head (18), a piston rod (19), a baffle ring (20), an inner piston rod (21), a spring (22), a transition nut (24), a rear support lug (25), an actuating cylinder shell (27) and an oil circuit block (33); wherein the content of the first and second substances,
the front support lug (13) is in threaded connection with the piston transition joint (14), and the front support lug (13) and the piston transition joint (14) are locked by a locking nut (32);
the piston transition joint (14) is connected with the piston rod (19), and the piston transition joint (14) and the piston rod (19) are fastened by an inner hexagonal screw (15);
the clamping claw (17) is connected with the piston transition joint (14) and is fastened through a fixing screw (16);
the lock head (18) is in threaded connection with one end of the inner piston rod (21), and the outer circular surface of the lock head (18) is in contact with the inner circular surface of the clamping claw (17);
the piston rod (19) is arranged inside the actuating cylinder shell (27);
the baffle ring (20) is arranged between the piston rod (19) and the inner piston rod (21);
one end of an inner piston rod (21) is in threaded connection with the lock head (18), the middle of the inner piston rod (21) is connected with a baffle ring (20) through a spring (22), and the other end of the inner piston rod (21) is connected with an oil path block (33) through a transition nut (24);
one end of the spring (22) is connected with the baffle ring (20), and the other end is connected with the inner piston rod (21);
the internal thread of the transition nut (24) is connected with the inner piston rod (21);
the rear support lug (25) is connected with the oil circuit block (33);
the actuating cylinder shell (27) is respectively connected with the oil circuit block (33) and the piston rod (19);
the internal thread of the locking nut (32) is connected with the front lug (13), and one end face of the locking nut (32) is connected with the piston transition joint (14);
the oil circuit block (33) is respectively connected with the rear lug (25), the transition nut (24) and the inner piston rod (21).
2. The dual redundancy hydraulic actuator with single ended mechanical lock of claim 1, wherein: the first power component comprises a first motor (1_1), a first cam bearing structure (2_1) and a first valve distribution pump (3_ 1); the first motor (1_1) is connected with the first cam bearing structure (2_1), and the first cam bearing structure (2_1) is connected with the first valve distribution pump (3_ 1).
3. The dual redundancy hydraulic actuator with single ended mechanical lock of claim 1, wherein: the second power component comprises a second motor (1-2), a second cam bearing structure (2-2) and a second valve distribution pump (3-2); the second motor (1-2) is connected with the second cam bearing structure (2-2), and the second cam bearing structure (2-2) is connected with the second valve flow distribution pump (3-2).
4. The dual redundancy hydraulic actuator with single ended mechanical lock of claim 1, further comprising: a piston seal ring (23); wherein, the piston sealing ring (23) is arranged in an annular groove at one end of the piston rod (19).
5. The dual redundancy hydraulic actuator with single ended mechanical lock of claim 1, further comprising: an actuator cylinder end face seal ring (26); the actuator cylinder end face seal ring (26) is mounted between the actuator cylinder housing (27) and the oil passage block (33).
6. The dual redundancy hydraulic actuator with single ended mechanical lock of claim 1, further comprising: an inner piston seal ring (28); wherein, the inner piston sealing ring (28) is arranged between the baffle ring (20) and the inner piston rod (21).
7. The dual redundancy hydraulic actuator with single ended mechanical lock of claim 1, further comprising: a baffle ring sealing ring (29); wherein, the baffle ring sealing ring (29) is arranged between the baffle ring (20) and the piston rod (19).
8. The dual redundancy hydraulic actuator with single ended mechanical lock of claim 1, further comprising: a ram seal (30); wherein the actuator cylinder seal ring (30) is mounted between the actuator cylinder housing (27) and the piston rod (19).
9. The dual redundancy hydraulic actuator with single ended mechanical lock of claim 1, further comprising: a piston transition joint seal ring (31); wherein, the piston transition joint sealing ring (31) is arranged between the piston transition joint (14) and the piston rod (19).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811410377.9A CN109268349B (en) | 2018-11-23 | 2018-11-23 | Dual-redundancy hydraulic actuator with single-end mechanical lock |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811410377.9A CN109268349B (en) | 2018-11-23 | 2018-11-23 | Dual-redundancy hydraulic actuator with single-end mechanical lock |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109268349A CN109268349A (en) | 2019-01-25 |
| CN109268349B true CN109268349B (en) | 2020-09-18 |
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| CN110202608B (en) * | 2019-06-25 | 2020-12-18 | 北京精密机电控制设备研究所 | Electro-static pressure actuator for robot joint |
| CN112855657A (en) * | 2019-10-18 | 2021-05-28 | 廖富爱 | Large-diameter hydraulic oil cylinder and using method thereof |
| CN111071436B (en) * | 2019-12-12 | 2024-06-18 | 四川凌峰航空液压机械有限公司 | Mechanical-hydraulic aircraft front wheel turning anti-swing system |
| CN111075782B (en) * | 2019-12-25 | 2022-04-22 | 北京空间机电研究所 | Distributed modular dual-redundancy integrated electro-hydraulic servo driving system and method |
| CN111637104B (en) * | 2020-04-22 | 2022-07-05 | 北京精密机电控制设备研究所 | Coaxial modular design's three-redundancy electro-static pressure servo mechanism |
| CN112728193B (en) * | 2020-12-25 | 2022-07-05 | 兰州飞行控制有限责任公司 | Valve closing actuator |
| CN118182827A (en) * | 2024-05-14 | 2024-06-14 | 中航通飞研究院有限公司 | Aircraft brake and steering integrated control system and aircraft |
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