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CN111189477A - Instruction sensor and method for determining structural parameters thereof - Google Patents

Instruction sensor and method for determining structural parameters thereof Download PDF

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Publication number
CN111189477A
CN111189477A CN202010123790.8A CN202010123790A CN111189477A CN 111189477 A CN111189477 A CN 111189477A CN 202010123790 A CN202010123790 A CN 202010123790A CN 111189477 A CN111189477 A CN 111189477A
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spring
determining
sensor
tension spring
piston
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Inventor
张鹏亮
黄岩
韩亚国
丁磊
牛祖军
郭育秦
刘忠平
张娟
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Xian Aviation Brake Technology Co Ltd
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Xian Aviation Brake Technology Co Ltd
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Priority to CN202010123790.8A priority Critical patent/CN111189477A/en
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    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01D—MEASURING NOT SPECIALLY ADAPTED FOR A SPECIFIC VARIABLE; ARRANGEMENTS FOR MEASURING TWO OR MORE VARIABLES NOT COVERED IN A SINGLE OTHER SUBCLASS; TARIFF METERING APPARATUS; MEASURING OR TESTING NOT OTHERWISE PROVIDED FOR
    • G01D5/00—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable
    • G01D5/12—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable using electric or magnetic means
    • G01D5/14—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable using electric or magnetic means influencing the magnitude of a current or voltage
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01D—MEASURING NOT SPECIALLY ADAPTED FOR A SPECIFIC VARIABLE; ARRANGEMENTS FOR MEASURING TWO OR MORE VARIABLES NOT COVERED IN A SINGLE OTHER SUBCLASS; TARIFF METERING APPARATUS; MEASURING OR TESTING NOT OTHERWISE PROVIDED FOR
    • G01D11/00—Component parts of measuring arrangements not specially adapted for a specific variable
    • G01D11/16—Elements for restraining, or preventing the movement of, parts, e.g. for zeroising
    • G01D11/18—Springs
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01D—MEASURING NOT SPECIALLY ADAPTED FOR A SPECIFIC VARIABLE; ARRANGEMENTS FOR MEASURING TWO OR MORE VARIABLES NOT COVERED IN A SINGLE OTHER SUBCLASS; TARIFF METERING APPARATUS; MEASURING OR TESTING NOT OTHERWISE PROVIDED FOR
    • G01D11/00—Component parts of measuring arrangements not specially adapted for a specific variable
    • G01D11/24—Housings ; Casings for instruments
    • G01D11/245—Housings for sensors

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Force Measurement Appropriate To Specific Purposes (AREA)

Abstract

Provided are a command sensor and a method for determining structural parameters of the command sensor. A tension spring is added in the instruction sensor, the force sense adjustment is realized through the matching of a threaded sleeve and a nut, and the zero voltage of the instruction sensor is adjusted through an adjusting nut on the piston; the output end of the stay wire type displacement sensor is fixed by the cover plate; two symmetrical slideway grooves are processed in the inner cavity of the shell, the steel ball is placed in the piston ball socket in a nesting mode, and when the command sensor moves, the steel ball rolls along the slideway and plays a role in positioning to prevent the piston from twisting in work. The tension spring is arranged between the shell and the piston and used for buffering the impact on the stay wire type displacement sensor when the command sensor is reset. The invention solves the problem that the impact caused by the resetting of the command sensor in the use process of the prior art affects the pull rope of the pull wire sensor; meanwhile, the rubber sleeve structure is improved, and the problem of breakage in use is avoided.

Description

Instruction sensor and method for determining structural parameters thereof
Technical Field
The invention relates to the field of airplane brake systems, in particular to an instruction sensor for an airplane pilot and a method for determining structural parameters of the instruction sensor.
Background
The command sensor is an accessory in an airplane brake system, and is hinged with the pedals. When the automobile seat is in work, a driver steps on the pedals, the pedals are subjected to acting force given by the driver, the acting force drives the instruction sensor hinged with the pedals to move, and the instruction sensor outputs a voltage signal in direct proportion to displacement under the acting force transmitted by the pedals. The voltage signal is provided to a brake control unit, and the brake control unit receives the voltage signal and converts the voltage signal into a current signal which can be received by a servo valve, so that the brake pressure of the wheel brake device is controlled.
The invention with the application number of CN204718618U creates a dual-redundancy vibration-resistant type brake command sensor. The command sensor comprises a left support, a piston, a shell, a right support, a pressure rod type displacement sensor, a spring, an adjusting nut, a sleeve, a front cover, a push rod and the like. The command sensor is hinged with the brake pedal through a left support and a right support, the left support end of the command sensor is a moving end after the command sensor is hinged, and the right support end of the command sensor is a fixed end. When the airplane brakes, a pilot steps on the pedals to apply an acting force to the left bracket, and the left bracket is compressed inwards under the action of the acting force, so that mechanical idle stroke of the command sensor is eliminated firstly; after the mechanical idle stroke is eliminated, the push rod is driven to move by the contact of the push rod, the push rod drives the piston to move along the inner wall of the sleeve by the contact of the push rod and the piston, and the compression bar type displacement sensor and the piston are fixed into a whole through the adjusting nut, so that in the whole moving process, the compression bar on the compression bar type displacement sensor is finally driven to move, the resistance value in the compression bar type displacement sensor is changed by the movement of the compression bar, and a changed voltage signal is output. First, for realizing two redundancy designs, this utility model during operation is the contact sliding state between piston and the sleeve, and at the pedal during operation, the running-board is not linear motion, but circular motion, consequently exerts the power of giving on this kind of command sensor and must have a yawing force, and under the effect of this yawing force, this command sensor during operation piston structure forms the jamming easily, leads to the piston not return. Secondly, the spring of this structural design only is used for restoring the piston structure, can not restore mechanical idle stroke, needs to lean on external force to realize the return of instruction sensor mechanical idle stroke. Third, the displacement measured by this type of command sensor is small for the same mounting dimension of 180 mm.
The invention with the application number of 201710086646.X relates to an instruction sensor and a method for determining design parameters of the instruction sensor, and the instruction sensor comprises a left bracket, a locking nut, a piston, a shell, a cover plate and a right bracket; the left support is in threaded fit with the piston and is fixed by a locking nut, and the right support, the shell and the rear cover plate form an integrated structure; the left end of the shell is provided with a spring, force sense adjustment is realized through the matching of a threaded sleeve and a nut, and the zero voltage of the instruction sensor is adjusted through a locking nut on the piston; the output end of the pull-wire type linear displacement sensor is fixed by the cover plate; two symmetrical slideway grooves are processed in the inner cavity of the shell, the steel balls are placed in the piston ball sockets in a nesting mode, and the steel balls roll along the slideways when the command sensor moves. The invention has the advantages of extremely high structural integration level, force sensing characteristic, large working stroke of the command sensor and short installation distance. However, the command sensor for protection created by the invention cannot solve the following problems:
firstly, the rubber sleeve part in the invention has a large stroke in work, and when the rubber sleeve part is compressed to a certain stroke, the rubber sleeve part can be contacted with the tooth-shaped gasket, the tooth-shaped gasket is a metal part, and the rubber sleeve is a rubber part, so that the rubber part is abraded and broken after long-term work, and the rubber sleeve can not meet the use requirement of the command sensor. And secondly, after the pull-wire type sensor pull rope is compressed to the full stroke for working, when the operating force is released, the command sensor can recover the initial state under the action of the reset force of the spring. At the moment, because the operating force of the instruction sensor is large, impact can be generated when the force is suddenly released, and the impact force is applied to the pull rope of the pull-wire type sensor, so that the pull rope of the pull-wire type sensor is easy to break, and the function of the instruction sensor is lost.
The invention with application number 201910551564.7 creates a variable gain brake command sensor and a method for determining design parameters, wherein a first force sensing spring and a second force sensing spring with different lengths are arranged in the brake command sensor, so that the variable gain brake command sensor has different operating force and stroke gain to meet the requirements of an airplane on different landing states. When the airplane is in abnormal landing, the maximum operating force is output, the stroke of the command sensor reaches the maximum, and the first force sensing spring and the second force sensing spring work simultaneously, so that the safe braking of the airplane is ensured; when the airplane is in normal landing and braking, the output operating force is not greater than the median operating force, and only the first force sensing spring works to ensure that the airplane does not slip in the braking process, so that the requirements of various landing states of the airplane on a braking system are met, the adaptability of the braking system to various take-off and landing states of the airplane is improved, the anti-slip times of the airplane wheels are reduced or even the airplane wheels do not slip in the landing and braking process of the airplane, the abrasion of the tires is ensured to be uniform, the service life of the braking airplane wheels is prolonged, and the braking efficiency is improved. However, the invention does not take measures to reduce the friction force between the housing and the piston, nor to prevent the piston from twisting during the movement of the command sensor. The friction force of the command sensor in the working process is increased, a certain torsional moment exists in the working process, and the service life of the command sensor is shortened. Meanwhile, the invention can not solve the problem that the function of the command sensor is lost due to the fact that the pull rope of the pull-wire type sensor is easy to break.
Disclosure of Invention
The invention provides an instruction sensor and a method for determining structural parameters thereof, aiming at overcoming the defects that a stay cord of a stay-supported sensor is easy to break and the service life of the instruction sensor is shortened due to friction and torsional moment during working in the prior art.
The command sensor provided by the invention comprises a shell, a piston, a stay wire type displacement sensor, a spring,A movable bracket and a fixed bracket; the piston is positioned on the inner surface of the open end of the shell and slides in the shell slideway through steel balls arranged in two ball sockets on the outer circumferential surface of the piston to move axially. One end of the movable support is installed in the internal thread blind hole of the movable support installation rod of the piston through threads. The fixed bracket is fixed on a stay wire type displacement sensor mounting chamber positioned at the closed end of the shell; the closed stay wire type displacement sensor installation chamber is composed of a shell, a cover plate and a fixed support. The stay wire type displacement sensor is arranged in the stay wire type displacement sensor mounting chamber; the stay wire of the stay wire type displacement sensor passes through an end plate in the shell and is fixed on the end plate of the piston. Universal bearings are respectively arranged on the support frame of the fixed support and the movable support. And a tension spring is arranged in the shell, one end of the tension spring is fixed on the inner end surface of the piston, and the other end of the tension spring is fixed on the inner end surface of the end plate of the shell. The tension spring is sleeved with a spring, and two ends of the spring are respectively fixed with the inner end face of the piston and the inner end face of the shell end plate. The tension spring, the spring and the piston are coaxial; the distance between the inner end surface of the piston and the end surface of the limiting step on the shell is L; the central line of the movable support is spatially coincident with the central line of the support frame. When the movable support is in an initial state, the distance between the center line of the universal bearing on the movable support and the center line of the universal bearing on the support frame is L1。
The distance L between the center line of the universal bearing on the movable support and the center line of the universal bearing positioned on the support frame1180 mm. The distance L between the inner end face of the piston and the end face of the limiting step is 30 mm; the length of the slideway is 40 mm;
and the movable support is sleeved with a locking nut and a tooth-shaped gasket from outside to inside in sequence, and the tooth-shaped gasket is attached to the outer end face of the movable support mounting rod of the piston. The outer circumferential surface of the locking nut is sleeved with a protective sleeve, the protective sleeve is in clearance fit with the locking nut, and the protective sleeve is used for preventing the tooth-shaped gasket from scratching the dustproof sleeve.
The shell is divided into two chambers by an end plate in the shell: one end of the opening of the shell is an operating force chamber, and the other end of the opening of the shell, the cover plate and the fixed support form a pull-wire type displacement sensor mounting chamber; the operating force chamber is not coaxial with the mounting chamber of the stay wire type displacement sensor. Two semicircular slide ways extending axially are symmetrically processed on the inner circumferential surface of the shell operating force chamber close to the opening of the shell. The inner surface of the shell end plate is provided with a tension spring fixing block and a strip-shaped hole which are axially protruded, and the strip-shaped hole is positioned below the lug boss.
The outer diameter of the piston is slightly smaller than the inner diameter of the housing manipulation force chamber. Two ball sockets for placing steel balls are symmetrically distributed on the outer circumferential surface of the piston. The center of the cylinder bottom plate of the piston is provided with a tension spring fixing block which axially protrudes.
The included angle between the two side walls of the ball socket is 90 degrees. The radius of the opening of the ball socket is 2.1mm, and the hole depth is 1.7 mm.
The invention provides a method for determining structural parameters of an instruction sensor, which comprises the following specific processes:
step one, determining the relation between the stroke and the voltage of a command sensor
The maximum stroke L of the command sensor is 30 mm. When the maximum stroke L of the command sensor is 30mm, the corresponding output voltage is 6.0V.DC +/-0.1 V.DC.
Step two, determining structural parameters of a spring and a tension spring of a command sensor
Determining the operating force Q of the command sensor through a spring and a tension spring;
respectively determining parameters of the spring and the tension spring according to the use requirements of the spring and the tension spring; the method comprises the following steps:
i determining the parameters of the spring:
the spring is made of 65Si2MnWA material; selecting a spring at normal temperature;
respectively determining the spring pitch diameter D, the winding ratio c, the spring curvature coefficient K and the maximum allowable load P of the spring through formulas (1) to (4):
D1＝Dw1-d1(1)
Figure BDA0002393801010000041
Figure BDA0002393801010000042
Figure BDA0002393801010000043
in the formula: d1Is the diameter of the steel wire; dw1Is the outer diameter of the spring; k is the spring curvature coefficient; [ tau ] to]Allowable stress of the spring steel wire; f. of1The deformation of the single coil of the spring is the deformation,
Figure BDA0002393801010000044
g is the shear modulus of elasticity;
determining spring rate k1：
By the formula k1＝(Q1max-Q1min) S determining the spring rate; in the formula, Q1maxIs the maximum operating force of the spring, Q1minIs the minimum operating force of the spring;
determining the total deformation F of the spring1：
By the formula F1＝P÷k1Determination of the Total deformation F1(ii) a Wherein, P is the maximum allowable load; k is a radical of1Is the spring rate;
determining the number n of working turns of the spring1：
By the formula n1＝F1÷f1Determining the number of working turns n1(ii) a In the formula, f1The single-turn deformation is adopted;
determining the spring pitch t1：
By the formula H01＝t1×n1+(nz-0.5)d1Determining a pitch t; in the formula, H0Is the free dimension of the spring; n iszThe number of support turns is.
II, determining the parameters of the tension spring:
the tension spring materialSelecting 65Si2MnWA, normal temperature, I-grade precision and B-type spring; the parameters of the tension spring are respectively obtained as follows: diameter d of tension spring steel wire2Outer diameter D of tension springw2And single turn deformation f2；
Determining the rigidity of the tension spring: k is a radical of2＝(P2max-P2min)÷S2
Determining total deformation F of tension spring2：F2＝P2÷k2
Inner diameter D of tension springn2＝DW2-2d2
Number of working turns n of tension spring2：
n2＝F2÷f2；
f2Is the deformation of the tension spring in a single circle
Free height H of tension spring02：
H02＝Dn2+(n2+1)d2
Height H of tension spring under allowable load2：
H2＝H02+F2；
Step three, determining the parameters of the steel ball and the slideway of the command sensor:
i, determining the diameter of the steel ball: determining the diameter of the steel ball to be 3 mm;
II, determining parameters of the steel ball socket: the parameters of the steel ball socket comprise the maximum diameter and the hole depth of the ball socket and the included angle between two side walls of the socket;
III, determining slide parameters: the parameters of the slide way are the radius of the cross section of the slide way and the roughness of the slide way;
IV, determining the number of the slide ways and the number of the steel balls.
At this point, the structural parameters of the command sensor are determined.
The invention reduces the length of the command sensor, realizes the maximization of the working stroke and solves the problem of small displacement of the command sensor. The invention adds two semicircular slideways with the length of 40mm and the radius of 1.6mm on the shell and is used for ensuring that a phi 3mm rigid ball and the slideways realize rolling motion; two ball sockets with the maximum diameter of 4.2mm and the hole depth of 1.7mm are additionally arranged on the piston, so that the steel ball is stressed uniformly, the rolling effect is good, and the steel ball is ensured to be fixed firmly. The defect that the piston is blocked in the using process in the prior art is overcome; the tension spring structure is added, the rubber sleeve structure is improved, and the influence of impact on the pull rope of the pull sensor caused by resetting the command sensor in the use process in the prior art is solved; meanwhile, the rubber sleeve structure is improved, and the problem of breakage in use is avoided.
Drawings
Fig. 1 is a schematic view of a prior art structure.
Fig. 2 is a schematic structural diagram of the present invention.
FIG. 3 is a block diagram of a piston; where 3a is the right view, 3b is the front view, and 3c is the left view.
FIG. 4 is a view of the housing structure; where 4a is a right view, 4b is a front view, and 4c is a left view.
Fig. 5 is a partial enlarged view of the present invention.
FIG. 6 is a schematic structural view of the housing; where 6a is the front view and 6b is the view from the A-A direction in 6 a.
1. A movable support; 2. a piston; 3. a dust-proof sleeve; 4. a threaded sleeve; 5. a nut; 6. a housing; 7. a cover plate; 8. fixing a bracket; 9. a pull-string type displacement sensor; 10. a spring; 11. a steel ball; 12. locking the nut; 13. a protective sleeve; 14 adjusting the nut; 15. a toothed washer; 16. a tension spring; 17. an electrical connector; 18. a slideway; 19. a tension spring fixing block; 20. a stay wire type displacement sensor installation chamber; 21. a ball socket; 22. a strip-shaped hole; 23. and a stay wire type displacement sensor mounting chamber.
Detailed Description
In order to solve the above disadvantages of the prior art, the present embodiment provides a command sensor, which includes a movable bracket 1, a piston 2, a dust-proof sleeve 3, a threaded sleeve 4, a nut 5, a housing 6, a cover plate 7, a fixed bracket 8, a stay wire type displacement sensor 9, a spring 10, a steel ball 11, a lock nut 12, a protective sleeve 13, an adjusting nut 14, a tooth-shaped washer 15, a tension spring 16 and an electrical connector 17.
The piston 2 is located on the inner surface of the open end of the housing 6 and is moved axially by sliding steel balls 11 in two ball sockets located on the outer circumferential surface of the piston in the housing slides. The distance between the inner end surface of the piston and the end surface of the limit step is L; the limiting step is positioned on the inner circumferential surface of the shell and close to one side of the shell end cover; in this example, L is 30 mm. A tension spring 16 is mounted in the housing, and one end of the tension spring is fixed to the inner end surface of the piston, and the other end of the tension spring is fixed to the inner end surface of the end plate of the housing. The tension spring 16 is sleeved with a spring 10, and two ends of the spring are respectively fixed with an inner end surface of the piston and an inner end surface of the end plate of the shell. The tension spring 16, the spring 10 and the piston 2 are coaxial. The stay wire type displacement sensor 9 is arranged in a stay wire type displacement sensor mounting chamber at one end of the shell 6; the stay wire of the stay wire type displacement sensor passes through an end plate in the shell and is fixed on the end plate of the piston 2.
The outer circumferential surface of one end of the shell, which is provided with the piston, is sleeved with a threaded sleeve 4 and is fastened through a nut 5. The small opening end of the dustproof sleeve 3 is sleeved on the outer surface of the movable support mounting rod of the piston, and the large opening end of the dustproof sleeve is fixed on the outer end face of the threaded sleeve 4. One end of the movable support 1 is installed in the internal thread blind hole of the movable support installation rod through threads.
The movable support 1 is sleeved with a locking nut 12 and a tooth-shaped gasket 15 from outside to inside in sequence, and the tooth-shaped gasket is attached to the outer end face of the movable support mounting rod of the piston. A protective sleeve 13 is sleeved on the outer circumferential surface of the locking nut, the protective sleeve is in clearance fit with the locking nut, and the protective sleeve 13 is used for preventing the dustproof sleeve 3 from being scratched by the tooth-shaped gasket 15.
A horizontal support frame is fixed on the outer end face of the fixed support 8. The support frame is provided with a radial through hole for mounting a universal bearing. When the movable support 1 is in an initial state, the distance L between the center line of the universal bearing on the movable support 1 and the center line of the universal bearing on the support frame1＝180mm。
The central line of the movable support 1 is spatially coincident with the central line of the support frame.
The electrical connector 17 is located outside the housing 6. The lead of the electrical connector 17 is in communication with the electrical input port of the pull-wire displacement sensor 9.
The housing 6 is a hollow rotary body. There is an end plate within the housing through which the housing is divided into two chambers: one end of the opening of the shell is an operating force chamber, and the other end of the opening of the shell, the cover plate 7 and the fixed support 8 form a stay wire type displacement sensor mounting chamber; the operating force chamber is not coaxial with the mounting chamber of the stay wire type displacement sensor. Two semicircular grooves extending axially are symmetrically processed on the inner circumferential surface of the shell operating force chamber close to the opening of the shell, and the grooves are used as slideways 18 of the steel balls 11. The radius of the slideway is 1.6mm, and the length of the slideway is 40 mm; the groove roughness of the slideway surface is less than Ra1.6. The inner surface of the shell end plate is provided with a tension spring fixing block 19 which axially protrudes; the height of extension spring fixed block is 7mm, and its top is that the diameter is 8mm circular-arc. And a strip-shaped hole 22 through which the stay wire type displacement sensor 9 passes is formed in the end plate and is positioned below the boss. The width of the strip-shaped hole is 4mm, and two ends of the strip-shaped hole are semicircular with the radius of 2 mm; the distance between the centers of the semi-circles at the two ends is 16 mm.
The outer circumferential surface of the open end of the housing 6 is a threaded surface for mounting the threaded sleeve 4 and the nut 5, and the initial positions of the stay wire type displacement sensor 9 and the spring 10 are adjusted by the threaded sleeve and the nut.
The stay wire type displacement sensor installation chamber 23 positioned at one end of the shell is a rectangular cavity. In order to meet the requirement of installing the stay wire type displacement sensor, the circumferential surface of one end of the shell, which is provided with the stay wire type displacement sensor installation chamber, is protruded, so that the radial height of the shell is increased. The projected circumferential surface has a groove for inserting the lead of the electrical connector 17.
And the upper surface of the stay wire type displacement sensor mounting chamber is provided with an opening for mounting a lead of an electric connector. When the electrical connector wires are inserted, the opening is closed by a cover plate 7. And a fixed bracket 8 is fixed on the end surface of the stay wire type displacement sensor mounting chamber. The closed stay wire type displacement sensor mounting chamber 20 is formed by the shell 6, the cover plate 7 and the fixed bracket 8.
The piston 2 is cylindrical and has an outer diameter slightly smaller than an inner diameter of the housing manipulation force chamber. Two conical ball sockets 21 are symmetrically distributed on the outer circumferential surface of the piston and used for placing the steel ball 11. The included angle between the two side walls of the ball socket is 90 degrees. The radius of the opening of the ball socket is 2.1mm, the hole depth is 1.7mm, and when a steel ball with the diameter of 3mm is placed in the ball socket, the steel ball is stressed uniformly and rolls stably. The center of the cylinder bottom plate of the piston is provided with a tension spring fixing block which axially protrudes; the height of extension spring fixed block is 7mm, and its top is that the diameter is 8mm circular-arc. Two threaded holes of M3 are distributed on the tube bottom plate, and the two threaded holes of M3 are positioned below the tension spring fixing block.
The outer end surface of the cylinder bottom plate of the piston 2 is provided with the movable bracket mounting rod which extends axially; the movable support mounting bar is in the form of a cantilever beam. The center of the end face of the movable bracket mounting rod is provided with an internal thread blind hole for mounting the movable bracket 1. In this embodiment, the diameter of the movable support mounting rod is 14 mm.
The movable support 1 is in a circular rod shape. One end of the movable support is a threaded rod matched with the internal thread blind hole on the movable support mounting rod, and the other end of the movable support is provided with a radial through hole for mounting the universal bearing. The universal bearing is used for connecting pedals of an airplane cab.
The stay wire type displacement sensor 9 is installed in a stay wire type displacement sensor installation room composed of the housing 6, the cover plate 7 and the fixing bracket 8 by adopting the prior art. The electric signal output lead of the stay wire type displacement sensor 9 penetrates out of the through hole between the shell 6 and the cover plate 7 and is communicated with an electric connector 17. The stay wire end of the stay wire type displacement sensor 9 passes through a strip-shaped hole on the inner end plate of the shell to enter the operating force chamber, is fixed on the piston 2 through the adjusting nut 14, and the initial state of the stay wire type displacement sensor 9 is adjusted to meet the requirement through the adjusting nut 14.
The present embodiment realizes the operating force characteristic of the command sensor by the spring 10 and the tension spring 16. When the command sensor is not operated in the initial state, the spring 10 is in a pre-compressed state and the tension spring 16 is in a stretched state. At this time, the minimum restoring force of the spring 10 is greater than the maximum restoring force of the tension spring 16, so that the piston 2 is in the initial state. When a pilot pedals the pedals to work, the command sensor moves along with the movement of the pedals; the operating force of the command sensor is gradually increased, the resetting force of the spring 10 is gradually increased, the resetting force of the tension spring 16 is gradually reduced, when the command sensor works to the maximum stroke, once the pedal operation is released, the piston 2 is restored to the initial position under the action of the resetting force of the spring 10, and in the whole restoration process, the resetting force of the spring 10 is gradually reduced, and the resetting force of the tension spring 16 is gradually increased. Through the two springs 10 and the tension springs 16 with completely opposite stress directions, the impact applied to the wire displacement sensor when the springs return instantly is effectively relieved and eliminated, and the phenomenon that a pull rope of the wire-pulling type displacement sensor is broken instantly is avoided.
The dustproof sleeve 3 is of a leather cup-shaped structure and is made of rubber materials. The size of one end hole of the dustproof sleeve 3 is slightly smaller than that of the piston rod, and the dustproof sleeve is tightly hooped on the sensor piston through the contractility of the dustproof sleeve, so that the dustproof of the command sensor is realized. The other end of the dustproof sleeve 3 is provided with 4 mounting holes and is fixed on the threaded sleeve 4 through 4 countersunk head screws. The dustproof sleeve repeatedly performs the cycle process of compression, recovery and compression during working. The protective sleeve 13 is used for preventing the rubber parts from being directly contacted with the steel parts to cause part damage.
The steel ball 11 is placed in the ball socket of the piston 2 in a nested mode, in the motion process of the command sensor, the steel ball 11 rolls along the slide way, the friction force between the shell 6 and the steel ball 11 in the motion process of the command sensor is reduced, and meanwhile, the steel ball 11 plays a positioning role and prevents the piston 2 from being twisted in the motion process of the command sensor. The reliability of the operation of the command sensor is increased.
In the embodiment, the movable support is in threaded fit with the piston and is fixed by the locking nut; the fixed support, the shell and the cover plate form an integrated structure; a spring is arranged in the shell, force sense adjustment is realized through the matching of a threaded sleeve and a nut, and zero voltage of the instruction sensor is adjusted through an adjusting nut on the piston; the output end of the stay wire type displacement sensor is fixed by the cover plate; two symmetrical slideway grooves are processed in the inner cavity of the shell, the steel ball is placed in the piston ball socket in a nesting mode, and when the command sensor moves, the steel ball rolls along the slideway and plays a role in positioning to prevent the piston from twisting in work. The stay wire type displacement sensor realizes the dual redundancy function by two cables. And a dustproof sleeve is adopted between the piston and the threaded sleeve for dust prevention, and a protective sleeve is used for protection. The tension spring is arranged between the shell and the piston and used for buffering the impact on the stay wire type displacement sensor when the command sensor is reset.
The embodiment also provides a parameter method for determining the command sensor.
Step one, determining the relation between the stroke and the voltage of a command sensor:
the command sensor maximum stroke L is 30 mm.
When the pilot does not step on the brake pedal, the voltage value output by the command sensor is the idle stroke voltage; when the pilot steps on the brake pedal, the output voltage of the command sensor is increased. The idle stroke of the embodiment is 2mm, and the output voltage corresponding to the idle stroke of the command sensor is 1.8V.DC +/-0.1 V.DC; the working stroke S of the command sensor is 27mm, and the corresponding output voltage is 5.6V.DC +/-0.1 V.DC. When the maximum stroke L of the command sensor is 30mm, the corresponding output voltage is 6.0V.DC +/-0.1 V.DC.
Step two, determining structural parameters of a command sensor spring and a tension spring:
the command sensor operating force Q is determined by the spring 10 and the tension spring 16. The command sensor operating force needs to meet the following use requirements:
1. minimum operating force Q of command sensormin＝25N±5N；
2. Maximum operating force Q of command sensormax＝175N±10N；
Wherein: minimum operating force Q of the command sensorminFor commanding the operating force of the initial state of the sensor, the maximum operating force Q of the sensor is commandedmaxThe operating force of the sensor is instructed when the working stroke S is 27 mm;
3. the working stroke S of the command sensor is 27mm, the maximum stroke L is 30mm, and the idle stroke Sn＝2mm。
Command sensing is realized through spring 10 and tension spring 16The operating force characteristics of the implement. When the command sensor is not operated in the initial state, or the force applied to the command sensor is smaller than the minimum operating force QminAt this time, the spring 10 is in a pre-compressed state and the tension spring 16 is in a stretched state. The minimum reset force of the spring 10 is greater than the maximum reset force of the tension spring 16, so that the piston 2 is in an initial state, and the stroke of the command sensor is the idle stroke S n2 mm. When a pilot pedals the pedals to work, the command sensor moves along with the movement of the pedals; when the maximum operating force Q is applied to the command sensormaxWhen the operating stroke S of the command sensor is 27mm, the return force of the spring 10 increases and the return force of the tension spring 16 decreases, and when the command sensor operates to the maximum stroke L of 30mm, the return force of the spring 10 is the maximum and the return force of the tension spring 16 is the minimum.
I, the spring needs to meet the following use requirements:
1. operating force Q to the spring1Including a spring minimum operating force Q1min80N ± 5N; maximum spring operating force P1max＝180N±10N；
Wherein: q1minFor commanding the operating force on the spring in the initial state of the sensor, Q1maxThe operating force of the sensor on the spring is instructed when the working stroke of the sensor is 27 mm.
2. The length and outer diameter of the spring are determined by the inner diameter of the housing 6, the inner diameter of the housing 6 is phi 40mm, and the outer diameter of the spring is DwIs 38 mm. Determining the free height H of the spring based on a constraint that dictates the length of the sensor housing and the initial installation location0Is 92 mm.
II, the tension spring needs to meet the following use requirements:
1. operating force Q of tension spring2Including tension spring minimum operating force Q2min5N ± 1N; maximum operating force Q of tension spring2max＝55N±3N；
Wherein: q2minFor commanding the operating force of the sensor on the tension spring in the working stroke S, Q2maxThe operating force to the tension spring when the sensor is in the initial state is instructed;
and respectively determining the parameters of the spring and the tension spring according to the trial requirements on the spring and the tension spring. The method comprises the following steps:
i, determining the parameters of the tension spring:
according to HB3-53-2008 standard, the spring is made of 65Si2MnWA material; selecting a spring at normal temperature.
Determining the pitch diameter D, the winding ratio c, the spring curvature coefficient K and the maximum allowable load P of the spring:
the spring pitch diameter D, the winding ratio c, the spring curvature coefficient K and the maximum allowable load P of the spring are respectively determined by formulas (1) to (4):
D1＝Dw1-d1(1)
Figure BDA0002393801010000111
Figure BDA0002393801010000112
Figure BDA0002393801010000113
in the formula: d1Is the diameter of the spring wire, d1＝3mm；Dw1Is the outer diameter of the spring Dw138 mm; k is the spring rate, K1.123. [ tau ] to]Is the allowable stress of the spring steel wire, 745 MPa; f. of1The deformation of the single coil of the spring is the deformation,
Figure BDA0002393801010000114
g is the shear modulus of elasticity, 74500; the maximum allowable load P is 202N; spring pitch diameter D135 mm; the winding ratio c is 11.67.
Determining spring rate k1：
By the formula k1＝(Q1max-Q1min) S determines the spring rate. In the formula, Q1maxIs the maximum operating force of the spring, Q1minIs the minimum operating force of the spring.
In this embodiment, Q1max＝180N±10N、Q1min＝80N±5N。k1＝(Q1max-Q1min)÷S＝(180-80)÷27＝3.704N/mm。
Determining the total deformation F of the spring1：
By the formula F1＝P÷k1Determination of the Total deformation F1. In this example, F1＝P÷k1202 ÷ 3.704 ÷ 54.54 mm. Wherein, P is the maximum allowable load, and P is 202N; k is a radical of1Is the spring rate.
Determining the number of working turns n1：
By the formula n1＝F1÷f1Determining the number of working turns n1. In this formula, f1The single-turn deformation of the spring. In this example, n1＝F1÷f1＝54.54÷11.48＝4.75。
Determining the pitch t1：
By the formula H01＝t1×n1+(nz-0.5)d1Determining the pitch t1. In the formula, H01Is the spring free dimension. n iszIs the number of supporting turns, nz＝2.5。
In this example, H0＝92mm；n1Take 4.75, t1＝18.1。
Finally, determining the spring parameters: number of working turns n14.8, wire diameter d13mm, spring outside diameter Dw138mm, spring free dimension H092mm, pitch t118.1, spring single-turn deflection f1＝11.48。
II, determining the parameters of the tension spring:
according to the navigation mark HB 3-55-2008, selecting 65Si2MnWA as a material with normal temperature and I-level precision, and forming a B-type spring, wherein the parameters are as follows: d2＝1.5mm，Dw213mm, single-turn deformation f of tension spring21.86mm, tension spring operating force Q2＝57.8N。
Working length S of tension spring2＝27mm
Determining the rigidity of the tension spring: k is a radical of2＝(P2max-P2min)÷S2＝(55-5)÷27＝1.85N/mm
Determining total deformation F of tension spring2：F2＝P2÷k2＝57.8÷1.85＝31.2mm
Inner diameter D of tension springn2＝DW2-2d2＝13-2×1.5＝10mm
Wherein: dW2The outer diameter of the tension spring; d2The diameter of the tension spring steel wire;
determining the number n of working turns of the tension spring2：
n2＝F2÷f216.5 is taken as 31.2 ÷ 1.86 ÷ 16.8.
Determining free height H of tension spring02：
H02＝Dn2+(n2+1)d2＝10+(16.5+1)×1.5＝36.25mm
Determining the height H of the tension spring under allowable load2：
H2＝H02+F2＝36.25+31.2＝67.45mm
Determining the installation size of the initial space of the tension spring: 55/1.85 +36.25 ═ 66mm
Final parameters of the tension spring are determined: HB 3-55-B1.5X 13X 36.25-I.
Step three, determining the parameters of the steel ball and the slideway of the command sensor:
i determining the diameter of the steel ball
The steel ball has a large diameter, the size and the weight of the piston and the shell matched with the steel ball are increased, and meanwhile, the steel ball has a small diameter, so that the capacity of limiting the piston torsion is weakened, and the strength is correspondingly reduced. In order to satisfy the requirements of light weight and short structure of the command sensor, and simultaneously, the strength is not reduced. The diameter of the steel ball selected in the embodiment is phi 3 mm.
II determining parameters of steel ball socket
In this embodiment, a ball socket with a maximum diameter of 4.2mm and a hole depth of 1.7mm is machined on the piston, and the included angle between the two side walls of the ball socket is 90 degrees. Through the ball socket, the steel ball is stressed uniformly and rolls stably and reliably.
III determination of slideway parameters
The cross-section of the slideway 18 is a semi-circle with a radius R1.6mm. The roughness of the slideway is more than Ra1.6, so that the rigid ball can smoothly roll in the slideway.
In this embodiment: the piston stroke is 30mm, the lengths of the two slide ways are 40mm, and the command sensor rolls through the combination of the ball and the slide ways.
IV, determining the number of the slide ways and the number of the steel balls
The number of the slide ways and the number of the steel balls are required to ensure that the piston 2 can freely roll along the slide ways after assembly, and the command sensor cannot twist during operation. When single-point limiting is adopted, although the situation of torsion can be avoided, stress deformation is easily caused due to over concentrated single-point stress; adopt 3 or more spacing formation of point to cross the location, can cause the assembly nature poor, require too high to command sensor production and processing, form the jamming easily between 3 points during the assembly. Therefore, a symmetrical 2-point limiting mode and a slideway operation are adopted.
The number of the slideways is determined to be two. The number of the determined steel balls is two.
Through the steps, the structural parameters of the command sensor are determined.

Claims (7)

1. A command sensor comprises a shell, a piston, a stay wire type displacement sensor, a spring, a movable bracket and a fixed bracket; the piston is positioned on the inner surface of the open end of the shell, slides in the shell slideway through steel balls arranged in two ball sockets on the outer circumferential surface of the piston and moves axially; one end of the movable bracket is arranged in an internal thread blind hole of a movable bracket mounting rod of the piston through threads; the fixed bracket is fixed on a stay wire type displacement sensor mounting chamber positioned at the closed end of the shell; a closed stay wire type displacement sensor installation chamber consisting of a shell, a cover plate and a fixed bracket; the stay wire type displacement sensor is arranged in the stay wire type displacement sensor mounting chamber; the stay wire of the stay wire type displacement sensor passes through an end plate in the shell and is fixed on the end plate of the piston; universal bearings are respectively arranged on the support frame of the fixed support and the movable support; the method is characterized in that:
a tension spring is arranged in the shell and drivesOne end of the tension spring is fixed on the inner end face of the piston, and the other end of the tension spring is fixed on the inner end face of the shell end plate; the tension spring is sleeved with a spring, and two ends of the spring are respectively fixed with the inner end surface of the piston and the inner end surface of the shell end plate; the tension spring, the spring and the piston are coaxial; the distance between the inner end surface of the piston and the end surface of the limiting step on the shell is L; the central line of the movable bracket is spatially superposed with the central line of the support frame; when the movable support is in an initial state, the distance between the center line of the universal bearing on the movable support and the center line of the universal bearing on the support frame is L1。
2. The command sensor of claim 1, wherein a distance L between a center line of the gimbal bearing on the movable bracket and a center line of the gimbal bearing on the support bracket1180 mm; the distance L between the inner end face of the piston and the end face of the limiting step is 30 mm; the length of the slide way is 40 mm.
3. The command sensor according to claim 1, wherein a lock nut and a tooth-shaped washer are sequentially sleeved on the movable support from outside to inside, and the tooth-shaped washer is attached to the outer end face of the movable support mounting rod of the piston; the outer circumferential surface of the locking nut is sleeved with a protective sleeve, the protective sleeve is in clearance fit with the locking nut, and the protective sleeve is used for preventing the tooth-shaped gasket from scratching the dustproof sleeve.
4. The command sensor of claim 1, wherein the housing is divided into two chambers by an end plate within the housing: one end of the opening of the shell is an operating force chamber, and the other end of the opening of the shell, the cover plate and the fixed support form a pull-wire type displacement sensor mounting chamber; the operating force chamber is not coaxial with the mounting chamber of the stay wire type displacement sensor; two semicircular slideways which extend axially are symmetrically processed on the inner circumferential surface of the shell operating force chamber close to the opening of the shell; the inner surface of the shell end plate is provided with a tension spring fixing block and a strip-shaped hole which are axially protruded, and the strip-shaped hole is positioned below the lug boss.
5. The command sensor of claim 1 wherein the outer diameter of the piston is slightly smaller than the inner diameter of the housing manipulation force chamber; two ball sockets for placing steel balls are symmetrically distributed on the outer circumferential surface of the piston; the center of the cylinder bottom plate of the piston is provided with a tension spring fixing block which axially protrudes.
6. The command sensor of claim 5, wherein the angle between the two side walls of the socket is 90 °;
the radius of the opening of the ball socket is 2.1mm, and the hole depth is 1.7 mm.
7. A method of determining a parameter indicative of a sensor structure according to claim 1,
step one, determining the relation between the stroke and the voltage of a command sensor:
the maximum stroke L of the command sensor is 30 mm; when the maximum stroke L of the command sensor is 30mm, the corresponding output voltage is 6.0V.DC +/-0.1 V.DC;
step two, determining structural parameters of a command sensor spring and a tension spring:
determining the operating force Q of the command sensor through a spring and a tension spring;
respectively determining parameters of the spring and the tension spring according to the use requirements of the spring and the tension spring; the method comprises the following steps:
i determining the parameters of the spring:
the spring is made of 65Si2MnWA material; selecting a spring at normal temperature;
determining the spring pitch diameter D, the winding ratio c, the spring curvature coefficient K and the maximum allowable load P of the spring through formulas (1) to (4) respectively:
D1＝Dw1-d1(1)
Figure FDA0002393799000000021
Figure FDA0002393799000000022
Figure FDA0002393799000000023
in the formula: d1Is the diameter of the steel wire; dw1Is the outer diameter of the spring; k is the spring curvature coefficient; [ tau ] to]Allowable stress of the spring steel wire; f. of1The deformation of the single coil of the spring is the deformation,
Figure FDA0002393799000000024
g is the shear modulus of elasticity;
determining spring rate k1：
By the formula k1＝(Q1max-Q1min) S determining the spring rate; in the formula, Q1maxIs the maximum operating force of the spring, Q1minIs the minimum operating force of the spring;
determining the total deformation F of the spring1：
By the formula F1＝P÷k1Determination of the Total deformation F1(ii) a Wherein, P is the maximum allowable load; k is a radical of1Is the spring rate; determining the number n of working turns of the spring1：
By the formula n1＝F1÷f1Determining the number of working turns n1(ii) a In the formula, f1The single-turn deformation is adopted;
determining the spring pitch t1：
By the formula H01＝t1×n1+(nz-0.5) d determines the pitch t; in the formula, H0Is the free dimension of the spring; n iszThe number of supporting turns is;
II, determining the parameters of the tension spring:
the tension spring material is 65Si2MnWA, normal temperature, I-level precision, B-type spring; the parameters of the tension spring are respectively obtained as follows: diameter d of tension spring steel wire2Outer diameter D of tension springw2And single turn deformationQuantity f2；
Determining the rigidity of the tension spring: k is a radical of2＝(P2max-P2min)÷S2；
Determining total deformation F of tension spring2：F2＝P2÷k2；
Inner diameter D of tension springn2＝DW2-2d2；
Number of working turns n of tension spring2：
n2＝F2÷f2；f2Is the deformation of the tension spring in a single circle
Free height H of tension spring02：H02＝Dn2+(n2+1)d2；
Height H of tension spring under allowable load2：H2＝H02+F2；
Step three, determining the parameters of the steel ball and the slideway of the command sensor:
i, determining the diameter of the steel ball: determining the diameter of the steel ball to be 3 mm;
II, determining parameters of the steel ball socket: the parameters of the steel ball socket comprise the maximum diameter and the hole depth of the ball socket and the included angle between two side walls of the socket;
III, determining slide parameters: the parameters of the slide way are the radius of the cross section of the slide way and the roughness of the slide way;
IV, determining the number of the slide ways and the number of the steel balls;
at this point, the structural parameters of the command sensor are determined.
CN202010123790.8A 2020-02-27 2020-02-27 Instruction sensor and method for determining structural parameters thereof Pending CN111189477A (en)

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