CN110953202B - Hydraulic system redundancy conversion device and method - Google Patents

Hydraulic system redundancy conversion device and method Download PDF

Info

Publication number
CN110953202B
CN110953202B CN201911229093.4A CN201911229093A CN110953202B CN 110953202 B CN110953202 B CN 110953202B CN 201911229093 A CN201911229093 A CN 201911229093A CN 110953202 B CN110953202 B CN 110953202B
Authority
CN
China
Prior art keywords
port
valve
hydraulic system
pressure
valve core
Prior art date
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.)
Active
Application number
CN201911229093.4A
Other languages
Chinese (zh)
Other versions
CN110953202A (en
Inventor
张学雷
谭伦
徐峰
黄胜
刘瑞杰
徐折贵
栾相鹏
熊莉
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
China Helicopter Research and Development Institute
Original Assignee
China Helicopter Research and Development Institute
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by China Helicopter Research and Development Institute filed Critical China Helicopter Research and Development Institute
Priority to CN201911229093.4A priority Critical patent/CN110953202B/en
Publication of CN110953202A publication Critical patent/CN110953202A/en
Application granted granted Critical
Publication of CN110953202B publication Critical patent/CN110953202B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B64—AIRCRAFT; AVIATION; COSMONAUTICS
    • B64C—AEROPLANES; HELICOPTERS
    • B64C13/00—Control systems or transmitting systems for actuating flying-control surfaces, lift-increasing flaps, air brakes, or spoilers
    • B64C13/24—Transmitting means
    • B64C13/38—Transmitting means with power amplification
    • B64C13/40—Transmitting means with power amplification using fluid pressure
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/875—Control measures for coping with failures
    • F15B2211/8757—Control measures for coping with failures using redundant components or assemblies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T50/00—Aeronautics or air transport
    • Y02T50/40—Weight reduction

Landscapes

  • 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)
  • Automation & Control Theory (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Power Steering Mechanism (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The invention belongs to the technical field of airborne hydraulic systems, and discloses a hydraulic system redundancy conversion device and method, which comprises the following steps: the device comprises a shell, a first throttle valve, a second throttle valve, a main reversing valve and a linkage reversing valve; a plurality of channels for flowing hydraulic oil are arranged on the shell, and the first throttling valve and the second throttling valve are embedded into the channels of the shell in an interference fit manner; the main reversing valve and the linkage reversing valve are respectively installed in a shell flow passage through clearance fit, and when 1 set of hydraulic system fails, the backup hydraulic system can automatically replace the failed system through back-up nuts, so that hydraulic energy is provided for a steering engine of the control system.

Description

Redundancy conversion device and method for hydraulic system
Technical Field
The invention belongs to the technical field of airborne hydraulic systems, and particularly relates to a redundancy conversion device and method for a hydraulic system.
Background
Both fixed wing aircraft and helicopters rely on hydraulic systems to provide driving force for their control systems, and because the reliability of hydraulic systems directly influences flight safety, the reliability of hydraulic systems is often improved through redundancy design, namely 2 sets or 3 sets of independent hydraulic systems are provided on the aircraft or the helicopter. When 1 set of hydraulic system among them breaks down, the hydraulic system of other redundancies still can provide the driving force for the operating system, but many sets of independent hydraulic systems need manual control to carry out interconversion.
Disclosure of Invention
In view of the above problems, an object of the present invention is to provide a redundancy switching apparatus and method for hydraulic systems, wherein when 1 set of hydraulic systems fails, a backup hydraulic system can automatically replace the failed system, so as to provide hydraulic energy for a steering engine of an operating system.
In order to achieve the purpose, the invention adopts the following technical scheme to realize the purpose:
the first technical scheme is as follows:
a hydraulic system redundancy conversion apparatus, the apparatus comprising: a housing 23, a first throttle valve 24, a second throttle valve 25, a main directional control valve and a linkage directional control valve;
a plurality of channels for flowing hydraulic oil are arranged on the shell, and the first throttling valve and the second throttling valve are embedded into the channels of the shell in an interference fit manner; the main reversing valve and the linkage reversing valve are respectively installed in the shell flow channel through clearance fit and are fixed through a back nut.
The first technical scheme of the invention has the characteristics and further improvements that:
1. the main reversing valve comprises a first valve sleeve 1, a first valve core 2, a first sealing ring 3, a first protection ring 4, a second valve sleeve 5, a second valve core 6, a first spring seat 7, a first spring 8, a first back-up nut 9, a second sealing ring 10 and a second protection ring 11;
the first valve sleeve 1 is arranged in a flow channel of the shell, and the second valve sleeve 5 compresses the first valve sleeve 1 and is coaxially arranged with the first valve sleeve 1;
gaps between the first valve sleeve 1 and the second valve sleeve 5 and the shell are sealed through a first sealing ring 3 and a first protection ring 4 respectively;
the first valve core 2 is arranged in the first valve sleeve 1 through clearance fit, and the first valve core 2 can move axially along the first valve sleeve 1; the second valve core 6 is arranged in the second valve sleeve 5 through clearance fit, and the second valve core 6 presses the first valve core 2 and moves along the axial direction of the first valve sleeve 1 along with the first valve core 2;
first spring holder 7 is installed at 6 right-hand members of second valve core, and first spring 8 is installed between first spring holder 7 and first back nut 9, and first back nut 9 is fixed first valve barrel 1 and second valve barrel 5 in the runner, seals through second sealing washer 10 and second guard circle 11 between first back nut 9 and the casing.
2. The linkage slide valve comprises a third valve sleeve 12, a third valve core 13, a third sealing ring 14, a third guard ring 15, a fourth valve core 16, a fourth valve sleeve 17, a fourth sealing ring 18, a fourth guard ring 19, a second spring seat 20, a second spring 21 and a second back nut 22;
the third valve sleeve 12 is arranged in a flow passage of the shell, and the fourth valve sleeve 17 compresses the third valve sleeve 1 and is coaxially arranged with the third valve sleeve 12;
gaps between the third valve sleeve 12 and the fourth valve sleeve 17 and the shell are respectively sealed through a third sealing ring 14 and a third protective ring 15;
the third valve core 13 is arranged in the third valve sleeve 12 in a clearance fit manner, and the third valve core 13 can axially move along the third valve sleeve 12; the fourth valve core 16 is arranged in the fourth valve sleeve 17 through clearance fit, and the fourth valve core 16 compresses the third valve core 13 and moves along the fourth valve sleeve 17 along with the third valve core 13;
the second spring seat 20 is installed at the right end of the fourth spool 16, the second spring 21 is installed between the second spring seat 20 and the second back-tightening nut 22, the second back-tightening nut 22 fixes the third valve sleeve 12 and the fourth valve sleeve 17 in the flow passage, and the second back-tightening nut 22 is sealed with the casing through the fourth sealing ring 18 and the fourth protection ring 19.
3. The port A is defined as the left end of the first valve core 2 of the main reversing valve, the ports B and L are oil return ports of a #2 hydraulic system, the ports C and G are oil return ports of a steering engine, the ports D and K are pressure supply ports of the #2 hydraulic system, the port K is communicated with the left side of the third valve core 13 of the linkage slide valve, the port E is a pressure supply port of the steering engine, the ports F, I and N are pressure supply ports of the #1 hydraulic system, the port I is communicated with the right end of the second valve core 6, the port N is communicated with the right end of the fourth valve core 16, and the ports H and M are oil return ports of the #1 hydraulic system.
4. The redundancy conversion device is simultaneously connected with the #1 hydraulic system and the #2 hydraulic system, and when the pressures of the #1 hydraulic system and the #2 hydraulic system are normal, the #1 hydraulic system supplies pressure to the steering engine through the redundancy conversion device; when the pressure of the #1 hydraulic system is reduced to a set value, the redundancy conversion device automatically isolates the #1 hydraulic system and switches to supply pressure to the steering engine from the #2 hydraulic system.
5. The port A is communicated with pressure oil of a #2 hydraulic system, the port B is communicated with return oil of the #2 hydraulic system, pressure is supplied to a steering engine through a port E of a redundancy conversion device, the port C is communicated with the port G through a shell oil way, return oil of the steering engine returns to the redundancy conversion device through the port C and the port G, the port F is communicated with the pressure oil of the #1 hydraulic system, and the port H is communicated with the return oil of the #1 hydraulic system; the port A, the port D and the port K are communicated through a shell oil way, the port B and the port L are communicated through a shell oil way, the port F, the port I and the port N are communicated through a shell oil way, and the port H and the port M are communicated through a shell oil way.
The second technical scheme is as follows:
when the pressure of a #1 hydraulic system is normal, the taste of the left end A of a first valve core 2 of a main reversing valve is subjected to the pressure of the #2 hydraulic system, the pressure of the #1 hydraulic system is sensed by an I port at the right end of a second valve core 6, and the force area of the right end of the second valve core 6 is larger than that of the left end of the first valve core 2;
the taste of K on the left side of the third valve core 13 of the linkage slide valve is under the pressure of a #2 hydraulic system, N ports on the right end of the fourth valve core 16 sense the pressure of a #1 hydraulic system, and the stress area of the right end of the fourth valve core 16 is larger than that of the left end of the third valve core 13;
pressure oil of a #1 hydraulic system enters the redundancy conversion device through an F port, then pressure is supplied to the steering engine through an E port, return oil of the steering engine enters the redundancy conversion device through a G port, and then returns to the #1 hydraulic system through an H port;
pressure oil of a #2 hydraulic system is communicated with a port D, and the port D is sealed by the first valve core 2 and the first valve sleeve 1; the port C and the port B are sealed and isolated by the first valve core 2 and the first valve sleeve 1, so that return oil of the steering engine cannot enter a #2 hydraulic system;
the pressure oil of the No. 2 hydraulic system enters the third valve core 13 through the K port, passes through a throttling port on the third valve core 13 and the third valve sleeve 12, and returns to the No. 2 hydraulic system through the L port; the orifice on the third spool 13 allows the #2 hydraulic system to build pressure, with high pressure before the orifice and low pressure after the orifice, and the operating state of the redundancy switching device is determined by monitoring the pressure after the orifice.
The second technical scheme of the invention has the characteristics and further improvements that:
when the pressure of the #1 hydraulic system is reduced, the third valve spool 13 and the fourth valve spool 16 firstly move rightwards under the action of the pressure difference of the #1 hydraulic system and the #2 hydraulic system, the throttling hole in the third valve spool 13 is not communicated with the L port, the pressure is converted from low pressure to high pressure after the throttling hole, and the monitoring of the pressure at the position can indicate that the redundancy conversion device works in a conversion state;
the M port on the shell is communicated with a throttle valve 25 through a third valve sleeve 12 and a third valve core 13, the first valve core 2 and the second valve core 6 move to the right under the action of differential pressure along with the pressure reduction of a #1 hydraulic system, the I port is communicated with the M port through the second valve sleeve 5, the second valve core 6 and the throttler 25, and the I port is communicated with the first valve core 2 and the second valve core 6 which return oil and rapidly move to the rightmost end;
pressure oil of a #2 hydraulic system is communicated with an E port of a steering engine pressure supply port through a D port, a C port of a steering engine oil return port is communicated with a B port of a #2 hydraulic system oil return port, a F port of a #1 hydraulic system pressure supply port is sealed and isolated by a valve core 2, an H port of the #1 hydraulic system oil return port is isolated from a G port of the steering engine oil return port, the #1 hydraulic system is disconnected with a steering engine loop, the #2 hydraulic system is communicated with the steering engine loop, and pressure is supplied to the steering engine from the #2 hydraulic system through a redundancy conversion device.
The redundancy conversion device of the airborne hydraulic system can be applied to airplane hydraulic systems with redundant design, and through comparison of pressure difference among the redundant hydraulic systems, when 1 set of hydraulic system fails, the backup hydraulic system can automatically replace the failed system, so that hydraulic energy is provided for a steering engine of a control system. The method has the advantages of high reliability and quick response. The invention can be used for an airplane hydraulic system, can optimize the airplane hydraulic redundancy configuration and provides the reliability of the hydraulic system.
Drawings
Fig. 1 is a schematic structural diagram of a redundancy converting apparatus according to an embodiment of the present invention, illustrating a state of the redundancy converting apparatus in a normal state of a #1 hydraulic system;
FIG. 2 is a diagram illustrating interface definitions according to an embodiment of the present invention;
FIG. 3 is a cross-sectional view of a redundancy switching apparatus according to an embodiment of the present invention, in conjunction with a #1 hydraulic system and a #2 hydraulic system;
fig. 4 is a diagram showing a state of the redundancy switching means when the #1 hydraulic system is switched to the #2 hydraulic system in accordance with the embodiment of the present invention;
the throttle valve comprises a valve body, a first valve sleeve, a first valve core, a first sealing ring, a 4-first protection ring, a second valve sleeve, a second valve core, a first valve seat, a first spring, a first back nut, a second sealing ring, a second protection ring, a third valve sleeve, a third valve core, a third sealing ring, a third protection ring, a 15-third protection ring, a fourth valve core, a fourth valve sleeve, a fourth sealing ring, a 18-fourth sealing ring, a 19-fourth protection ring, a throttle valve, a second spring seat, a second spring, a second back nut, a casing, a 24-first throttle valve and a second throttle valve, wherein the first valve sleeve, the second valve sleeve, the third valve sleeve, the fourth valve sleeve, the throttle valve, the second spring, the throttle valve sleeve, the second spring, the second throttle valve, the throttle valve and the throttle valve.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
The embodiment of the invention provides a redundancy conversion device of a hydraulic system, which comprises: a housing 23, a first throttle valve 24, a second throttle valve 25, a main directional control valve and a linkage directional control valve;
a plurality of channels for flowing hydraulic oil are arranged on the shell, and the first throttling valve and the second throttling valve are embedded into the channels of the shell in an interference fit manner; the main reversing valve and the linkage reversing valve are respectively installed in the shell flow channel through clearance fit and are fixed through a back nut.
Specifically, as shown in fig. 1, the main directional control valve includes a first valve sleeve 1, a first valve core 2, a first seal ring 3, a first retainer 4, a second valve sleeve 5, a second valve core 6, a first spring seat 7, a first spring 8, a first back-fastening nut 9, a second seal ring 10, and a second protective ring 11;
the first valve sleeve 1 is arranged in a flow channel of the shell, and the second valve sleeve 5 compresses the first valve sleeve 1 and is coaxially arranged with the first valve sleeve 1;
gaps between the first valve sleeve 1 and the second valve sleeve 5 and the shell are respectively sealed by a first sealing ring 3 and a first protection ring 4;
the first valve core 2 is arranged in the first valve sleeve 1 through clearance fit, and the first valve core 2 can move axially along the first valve sleeve 1; the second valve core 6 is arranged in the second valve sleeve 5 through clearance fit, and the second valve core 6 presses the first valve core 2 and moves along the axial direction of the first valve sleeve 1 along with the first valve core 2;
first spring holder 7 is installed at 6 right-hand members of second valve core, and first spring 8 is installed between first spring holder 7 and first back nut 9, and first back nut 9 is fixed first valve barrel 1 and second valve barrel 5 in the runner, seals through second sealing washer 10 and second guard circle 11 between first back nut 9 and the casing.
Specifically, as shown in fig. 1, the linked slide valve includes a third valve sleeve 12, a third valve core 13, a third seal ring 14, a third retainer ring 15, a fourth valve core 16, a fourth valve sleeve 17, a fourth seal ring 18, a fourth retainer ring 19, a second spring seat 20, a second spring 21, and a second back nut 22;
the third valve sleeve 12 is arranged in a flow passage of the shell, and the fourth valve sleeve 17 compresses the third valve sleeve 1 and is coaxially arranged with the third valve sleeve 12;
gaps between the third valve sleeve 12 and the shell and between the fourth valve sleeve 17 and the shell are sealed through a third sealing ring 14 and a third protective ring 15 respectively;
the third valve core 13 is arranged in the third valve sleeve 12 through clearance fit, and the third valve core 13 can move axially along the third valve sleeve 12; the fourth valve core 16 is arranged in the fourth valve sleeve 17 through clearance fit, and the fourth valve core 16 compresses the third valve core 13 and moves along the fourth valve sleeve 17 along with the third valve core 13;
the second spring seat 20 is installed at the right end of the fourth valve core 16, the second spring 21 is installed between the second spring seat 20 and the second back nut 22, the second back nut 22 fixes the third valve sleeve 12 and the fourth valve sleeve 17 in the flow passage, and the second back nut 22 is sealed with the casing through the fourth sealing ring 18 and the fourth protection ring 19.
Specifically, as shown in fig. 2, it is defined that port a is the left end of the first spool 2 of the main directional control valve, port B and port L are the oil return ports of the #2 hydraulic system, port C and port G are the oil return ports of the steering engine, port D and port K are the pressure supply ports of the #2 hydraulic system, port K is communicated with the left side of the third spool 13 of the linkage slide valve, port E is the pressure supply port of the steering engine, port F, port I and port N are the pressure supply ports of the #1 hydraulic system, port I is communicated with the right end of the second spool 6, port N is communicated with the right end of the fourth spool 16, and port H and port M are the oil return ports of the #1 hydraulic system.
Specifically, as shown in fig. 3, the redundancy conversion device is connected to the #1 hydraulic system and the #2 hydraulic system at the same time, and when the pressures of the #1 hydraulic system and the #2 hydraulic system are normal, the #1 hydraulic system supplies pressure to the steering engine through the redundancy conversion device; when the pressure of the #1 hydraulic system is reduced to a set value, the redundancy conversion device automatically isolates the #1 hydraulic system and switches to supply pressure to the steering engine from the #2 hydraulic system.
The port A is communicated with pressure oil of the #2 hydraulic system, the port B is communicated with return oil of the #2 hydraulic system, pressure is supplied to the steering engine through a port E of the redundancy conversion device, the port C is communicated with the port G through a shell oil way, return oil of the steering engine returns to the redundancy conversion device through the port C and the port G, the port F is communicated with the pressure oil of the #1 hydraulic system, and the port H is communicated with return oil of the #1 hydraulic system; the port A, the port D and the port K are communicated through a shell oil way, the port B and the port L are communicated through a shell oil way, the port F, the port I and the port N are communicated through a shell oil way, and the port H and the port M are communicated through a shell oil way.
The embodiment of the invention also provides a redundancy conversion method of the hydraulic system, which is applied to the redundancy conversion device.
When the pressure of the #1 hydraulic system is normal, as shown in fig. 1, the left end a of the first valve core 2 of the main reversing valve is subjected to the pressure of the #2 hydraulic system, the right end I port of the second valve core 6 is subjected to the pressure of the #1 hydraulic system, and the force-bearing area of the right end of the second valve core 6 is larger than the force-bearing area of the left end of the first valve core 2;
the taste of K on the left side of the third valve core 13 of the linkage slide valve is under the pressure of a #2 hydraulic system, N ports on the right end of the fourth valve core 16 sense the pressure of a #1 hydraulic system, and the stress area of the right end of the fourth valve core 16 is larger than that of the left end of the third valve core 13;
pressure oil of a #1 hydraulic system enters the redundancy conversion device through an F port, then pressure is supplied to the steering engine through an E port, return oil of the steering engine enters the redundancy conversion device through a G port, and then returns to the #1 hydraulic system through an H port;
pressure oil of a #2 hydraulic system is communicated with a port D, and the port D is sealed by the first valve core 2 and the first valve sleeve 1; the port C and the port B are sealed and isolated by the first valve core 2 and the first valve sleeve 1, so that return oil of the steering engine cannot enter a #2 hydraulic system;
the pressure oil of the No. 2 hydraulic system enters the third valve core 13 through the K port, passes through a throttling port on the third valve core 13 and the third valve sleeve 12, and returns to the No. 2 hydraulic system through the L port; the throttle hole on the third valve element 13 enables the #2 hydraulic system to build pressure, the pressure before the throttle hole is high, the pressure after the throttle hole is low, and the working state of the redundancy conversion device is judged by monitoring the pressure after the throttle hole.
When the pressure of the #1 hydraulic system is reduced, as shown in fig. 4, the third spool 13 and the fourth spool 16 move to the right first under the action of the pressure difference between the #1 hydraulic system and the #2 hydraulic system, the throttle hole on the third spool 13 is not communicated with the L port, the pressure changes from low pressure to high pressure after the throttle hole, and monitoring the pressure at the position can indicate that the redundancy switching device works in a switching state;
the M port on the shell is communicated with a throttle valve 25 through a third valve sleeve 12 and a third valve core 13, the first valve core 2 and the second valve core 6 move to the right under the action of differential pressure along with the pressure reduction of a #1 hydraulic system, the I port is communicated with the M port through the second valve sleeve 5, the second valve core 6 and the throttler 25, and the I port is communicated with the first valve core 2 and the second valve core 6 which return oil and rapidly move to the rightmost end;
pressure oil of a #2 hydraulic system is communicated with an E port of a steering engine pressure supply port through a D port, a C port of a steering engine oil return port is communicated with a B port of a #2 hydraulic system oil return port, a F port of a #1 hydraulic system pressure supply port is sealed and isolated by a valve core 2, an H port of the #1 hydraulic system oil return port is isolated from a G port of the steering engine oil return port, the #1 hydraulic system is disconnected with a steering engine loop, the #2 hydraulic system is communicated with the steering engine loop, and pressure is supplied to the steering engine from the #2 hydraulic system through a redundancy conversion device.
The redundancy conversion device of the airborne hydraulic system can be applied to airplane hydraulic systems with redundant design, and through comparison of pressure difference among the redundant hydraulic systems, when 1 set of hydraulic system fails, the backup hydraulic system can automatically replace the failed system, so that hydraulic energy is provided for a steering engine of a control system. The method has the advantages of high reliability and quick response. The invention can be used for an airplane hydraulic system, can optimize the airplane hydraulic redundancy configuration and provides the reliability of the hydraulic system.
The foregoing is merely a detailed description of the embodiments of the present invention, and some of the conventional techniques are not detailed. The scope of the present invention is not limited thereto, and any modifications or substitutions that can be easily made by those skilled in the art within the technical scope of the present invention will be covered by the present invention. The protection scope of the present invention shall be subject to the protection scope of the claims.

Claims (1)

1. The redundancy conversion device of the hydraulic system is characterized in that the redundancy conversion device is simultaneously connected with a #1 hydraulic system and a #2 hydraulic system, when the pressures of the #1 hydraulic system and the #2 hydraulic system are normal, the #1 hydraulic system supplies pressure to a steering engine through the redundancy conversion device, when the pressure of the #1 hydraulic system is reduced to a set value, the redundancy conversion device automatically isolates the #1 hydraulic system and switches to supply pressure to the steering engine from the #2 hydraulic system;
the hydraulic system redundancy conversion device comprises a shell (23), a first throttling valve (24), a second throttling valve (25), a main reversing valve and a linkage reversing valve;
a plurality of channels for flowing hydraulic oil are arranged on the shell, and the first throttling valve and the second throttling valve are embedded into the channels of the shell in an interference fit manner; the main reversing valve and the linkage reversing valve are respectively arranged in the shell flow channel through clearance fit and are fixed through a back-tightening nut;
the main reversing valve comprises a first valve sleeve (1), a first valve core (2), a first sealing ring (3), a first protection ring (4), a second valve sleeve (5), a second valve core (6), a first spring seat (7), a first spring (8), a first back nut (9), a second sealing ring (10) and a second protection ring (11);
the first valve sleeve (1) is arranged in a flow channel of the shell, and the second valve sleeve (5) compresses the first valve sleeve (1) and is coaxially arranged with the first valve sleeve (1);
gaps between the first valve sleeve (1) and the second valve sleeve (5) and the shell are respectively sealed through a first sealing ring (3) and a first protection ring (4);
the first valve core (2) is arranged in the first valve sleeve (1) through clearance fit, and the first valve core (2) can axially move along the first valve sleeve (1); the second valve core (6) is arranged in the second valve sleeve (5) in a clearance fit mode, and the second valve core (6) compresses the first valve core (2) and moves along the axial direction of the first valve sleeve (1) along with the first valve core (2);
a first spring seat (7) is arranged at the right end of the second valve core (6), a first spring (8) is arranged between the first spring seat (7) and a first back nut (9), the first back nut (9) fixes the first valve sleeve (1) and the second valve sleeve (5) in a flow channel, and the first back nut (9) is sealed with the shell through a second sealing ring (10) and a second protection ring (11);
the linkage reversing valve comprises a third valve sleeve (12), a third valve core (13), a third sealing ring (14), a third protective ring (15), a fourth valve core (16), a fourth valve sleeve (17), a fourth sealing ring (18), a fourth protective ring (19), a second spring seat (20), a second spring (21) and a second back nut (22);
the third valve sleeve (12) is arranged in a flow channel of the shell, and the fourth valve sleeve (17) compresses the third valve sleeve (12) and is coaxially arranged with the third valve sleeve (12);
gaps between the third valve sleeve (12) and the fourth valve sleeve (17) and the shell are respectively sealed through a third sealing ring (14) and a third protective ring (15);
the fourth valve core (16) is arranged in the fourth valve sleeve (17) in a clearance fit manner, and the fourth valve core (16) compresses the third valve core (13) and moves along the axial direction of the fourth valve sleeve (17) along with the third valve core (13);
a second spring seat (20) is arranged at the right end of the fourth valve core (16), a second spring (21) is arranged between the second spring seat (20) and a second back nut (22), the second back nut (22) fixes a third valve sleeve (12) and a fourth valve sleeve (17) in a flow channel, and the second back nut (22) is sealed with the shell through a fourth sealing ring (18) and a fourth protection ring (19);
a port A is defined as the left end of a first valve core (2) of a main reversing valve, a port B and a port L are oil return ports of a #2 hydraulic system, a port C and a port G are oil return ports of a steering engine, a port D and a port K are pressure supply ports of the #2 hydraulic system, the port K is communicated with the left side of a third valve core (13) of a linkage reversing valve, a port E is a pressure supply port of the steering engine, a port F, a port I and a port N are pressure supply ports of the #1 hydraulic system, the port I is communicated with the right end of a second valve core (6), the port N is communicated with the right end of a fourth valve core (16), and the port H and the port M are oil return ports of the #1 hydraulic system;
the port A is communicated with pressure oil of a #2 hydraulic system, the port B is communicated with return oil of the #2 hydraulic system, pressure is supplied to a steering engine through a port E of a redundancy conversion device, the port C is communicated with the port G through a shell oil way, the return oil of the steering engine returns to the redundancy conversion device through the port C and the port G, the port F is communicated with the pressure oil of the #1 hydraulic system, and the port H is communicated with the return oil of the #1 hydraulic system;
when the pressure of the #1 hydraulic system is normal, the left end of a first valve core (2) of the main reversing valve senses the pressure of the #2 hydraulic system, the right end of a second valve core (6) senses the pressure of the #1 hydraulic system, and the stress area of the right end of the second valve core (6) is larger than that of the left end of the first valve core (2);
the left side of a third valve core (13) of the linkage reversing valve senses the pressure of a #2 hydraulic system, the right end of a fourth valve core (16) senses the pressure of a #1 hydraulic system, and the stress area of the right end of the fourth valve core (16) is larger than that of the left end of the third valve core (13);
pressure oil of a #1 hydraulic system enters the redundancy conversion device through an F port, then pressure is supplied to the steering engine through an E port, return oil of the steering engine enters the redundancy conversion device through a G port, and then returns to the #1 hydraulic system through an H port;
pressure oil of a #2 hydraulic system is communicated with a port D, the port D is sealed by the first valve core (2) and the first valve sleeve (1), and a port C and a port B are sealed and isolated by the first valve core (2) and the first valve sleeve (1), so that return oil of a steering engine cannot enter the #2 hydraulic system;
the pressure oil of the 2# hydraulic system enters a third valve core (13) through a K port, passes through a throttling port on the third valve core (13), a third valve sleeve (12) and returns to the 2# hydraulic system through an L port, the throttling port on the third valve core (13) enables the 2# hydraulic system to build pressure, the pressure before the throttling port is high, the pressure after the throttling port is low, and the working state of the redundancy conversion device is judged by monitoring the pressure after the throttling port;
when the pressure of the #1 hydraulic system is reduced, the third valve spool (13) and the fourth valve spool (16) move rightwards firstly under the action of the pressure difference of the #1 hydraulic system and the #2 hydraulic system, the throttling hole in the third valve spool (13) is not communicated with the L port, the pressure is converted into high pressure from low pressure after the throttling hole, and the monitoring of the pressure can indicate that the redundancy switching device works in a switching state;
m ports on the shell are communicated with a second throttle valve (25) through a third valve sleeve (12) and a third valve core (13), along with the pressure reduction of a #1 hydraulic system, a first valve core (2) and a second valve core (6) move to the right under the action of differential pressure, an I port is communicated with the M ports through a second valve sleeve (5), a second valve core (6) and a second throttle valve (25), and the I port is communicated with an oil return first valve core (2) and the second valve core (6) and moves to the rightmost end rapidly;
pressure oil of a #2 hydraulic system is communicated with an E port of a steering engine pressure supply port through a D port, a C port of a steering engine oil return port is communicated with a B port of a #2 hydraulic system oil return port, a F port of a #1 hydraulic system pressure supply port is sealed and isolated by a first valve core (2), an H port of a #1 hydraulic system oil return port is isolated from a G port of the steering engine oil return port, the #1 hydraulic system is disconnected with a steering engine loop, the #2 hydraulic system is communicated with the steering engine loop, and pressure is supplied to the steering engine from the #2 hydraulic system through a redundancy conversion device.
CN201911229093.4A 2019-12-04 2019-12-04 Hydraulic system redundancy conversion device and method Active CN110953202B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201911229093.4A CN110953202B (en) 2019-12-04 2019-12-04 Hydraulic system redundancy conversion device and method

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201911229093.4A CN110953202B (en) 2019-12-04 2019-12-04 Hydraulic system redundancy conversion device and method

Publications (2)

Publication Number Publication Date
CN110953202A CN110953202A (en) 2020-04-03
CN110953202B true CN110953202B (en) 2022-09-06

Family

ID=69979775

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201911229093.4A Active CN110953202B (en) 2019-12-04 2019-12-04 Hydraulic system redundancy conversion device and method

Country Status (1)

Country Link
CN (1) CN110953202B (en)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6625982B2 (en) * 2000-06-28 2003-09-30 Airbus France Electronically controlled hydraulic actuating system
CN1653273A (en) * 2002-05-16 2005-08-10 贝尔直升机泰克斯特龙公司 Integrated three function valve
CN1914426A (en) * 2003-12-23 2007-02-14 Hr德克斯特隆公司 Redundant flow control for hydraulic actuator systems
JP2007040534A (en) * 2006-10-12 2007-02-15 Nabtesco Corp Actuation system
CN101230869A (en) * 2007-01-24 2008-07-30 神钢建设机械株式会社 Hydraulic control device of construction machine
CN101878371A (en) * 2007-11-27 2010-11-03 伍德沃德Hrt公司 Dual redundant servovalve
CN101983289A (en) * 2008-03-11 2011-03-02 伍德沃德Hrt公司 Hydraulic actuator with floating pistons

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105523174B (en) * 2014-09-28 2017-10-31 中国航空工业集团公司西安飞机设计研究所 A kind of door cylinder separation type hydraulic servo actuator
US10458557B2 (en) * 2016-04-20 2019-10-29 Sikorsky Aircraft Corporation Hydraulic actuator force fight mitigation mechanism

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6625982B2 (en) * 2000-06-28 2003-09-30 Airbus France Electronically controlled hydraulic actuating system
CN1653273A (en) * 2002-05-16 2005-08-10 贝尔直升机泰克斯特龙公司 Integrated three function valve
CN1914426A (en) * 2003-12-23 2007-02-14 Hr德克斯特隆公司 Redundant flow control for hydraulic actuator systems
JP2007040534A (en) * 2006-10-12 2007-02-15 Nabtesco Corp Actuation system
CN101230869A (en) * 2007-01-24 2008-07-30 神钢建设机械株式会社 Hydraulic control device of construction machine
CN101878371A (en) * 2007-11-27 2010-11-03 伍德沃德Hrt公司 Dual redundant servovalve
CN101983289A (en) * 2008-03-11 2011-03-02 伍德沃德Hrt公司 Hydraulic actuator with floating pistons

Also Published As

Publication number Publication date
CN110953202A (en) 2020-04-03

Similar Documents

Publication Publication Date Title
EP3222520B1 (en) Local backup hydraulic actuator for aircraft control systems
US6981439B2 (en) Redundant flow control for hydraulic actuator systems
EP3447315B1 (en) Dual valve systems for actuator control
EP2263012B1 (en) Hydraulic actuator with floating pistons
EP3501922B1 (en) Hydraulic failure isolation valve
CN1323244C (en) Integrated three function valve
US10968832B2 (en) Combined overspeed and fuel stream selector systems
EP2867119B1 (en) Zonal hydraulic systems and methods
CA3025039A1 (en) Distributed trailing edge wing flap systems
US3933176A (en) Fail operative split tandem valve
EP3176443B1 (en) Hydraulic valve
CN110953202B (en) Hydraulic system redundancy conversion device and method
US4120469A (en) In-line actuator monitoring and control apparatus
CN103453177B (en) A kind of Dual-pipeline hydraulic safety valve
CN107588052B (en) Two-stage electrohydraulic servo valve with built-in valve core and piston type high-flow force feedback jet pipe
CN112594244B (en) Mechanical hydraulic control reversing valve
CN111022435B (en) Reversing hydraulic insurance
CN111765004B (en) Conversion valve mechanism of fuel pump regulator
US2399719A (en) Aircraft structure
CN212797292U (en) Double-channel multifunctional integrated brake module
US20210317851A1 (en) Electrohydraulic poppet valve device control that maintains the last commanded position of a device upon power interruption and provides back-up position control
RU2241143C1 (en) Electrohydraulic redundant servo drive
CN109240074B (en) Method for switching main and standby work of actuator in dual-redundancy control mode
US9657756B2 (en) Actuator system
US2755777A (en) Locking, damping and rate control means for fluid pressure servo systems

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant