CN110979642B - Release mechanism of electric brake device and method of using the same - Google Patents
Release mechanism of electric brake device and method of using the same Download PDFInfo
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- CN110979642B CN110979642B CN201911058286.8A CN201911058286A CN110979642B CN 110979642 B CN110979642 B CN 110979642B CN 201911058286 A CN201911058286 A CN 201911058286A CN 110979642 B CN110979642 B CN 110979642B
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B64—AIRCRAFT; AVIATION; COSMONAUTICS
- B64C—AEROPLANES; HELICOPTERS
- B64C25/00—Alighting gear
- B64C25/32—Alighting gear characterised by elements which contact the ground or similar surface
- B64C25/42—Arrangement or adaptation of brakes
- B64C25/44—Actuating mechanisms
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
- B60T13/74—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with electrical assistance or drive
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T17/00—Component parts, details, or accessories of power brake systems not covered by groups B60T8/00, B60T13/00 or B60T15/00, or presenting other characteristic features
- B60T17/18—Safety devices; Monitoring
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transportation (AREA)
- Aviation & Aerospace Engineering (AREA)
- Braking Arrangements (AREA)
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Abstract
一种电刹车装置的释放机构及其使用方法。本发明提出的释放机构由电刹车作动器中的螺母、滚珠螺母、下壳体，和压紧盘组件中的垫块共同构成，并与电刹车作动器与压紧盘配合工作：具体是，在电刹车作动器中的螺母封闭端端面四个均布的扇形凸块，各所述扇形凸块之间的凹槽形成了位于压紧盘表面垫块的移动槽。在电刹车作动器的下壳体中的滚珠螺母敞口端端口处的外圆周上对称地安装有扩胀管，在各扩胀管内嵌装有导向球。压紧盘组件中压紧盘的非摩擦面上有四个均布的腰形凹槽，在各腰形凹槽内分别固定有垫块。本发明使电刹车作动器中的滚珠丝杠卡死时能够及时释放刹车力，避免滚珠丝杠卡死可能导致的飞机爆胎或刹车机轮过热。
A release mechanism for an electric brake device and a method for using the same. The release mechanism proposed in the present invention is composed of a nut, a ball nut, a lower shell, and a pad in a pressure plate assembly in an electric brake actuator, and cooperates with the electric brake actuator and the pressure plate to work: specifically, there are four evenly distributed fan-shaped protrusions on the closed end face of the nut in the electric brake actuator, and the grooves between the fan-shaped protrusions form a movable groove for the pad on the surface of the pressure plate. Expansion tubes are symmetrically installed on the outer circumference of the open end port of the ball nut in the lower shell of the electric brake actuator, and guide balls are embedded in each expansion tube. There are four evenly distributed waist-shaped grooves on the non-friction surface of the pressure plate in the pressure plate assembly, and a pad is fixed in each waist-shaped groove. The present invention enables the brake force to be released in time when the ball screw in the electric brake actuator is stuck, avoiding the possibility of aircraft tire blowout or brake wheel overheating caused by the ball screw being stuck.
Description
Technical Field
The invention relates to the technical field of aircraft electric brakes, in particular to a release mechanism in an electric brake device and a use method thereof.
Background
Electric brakes are a new technology that begins to be applied in aircraft brakes. The electric brake device generally comprises an electric brake actuator, an actuating support, a brake shell and a brake disc. The electric brake actuator is arranged on the actuating support, and the brake disc is arranged on the brake shell. When the electric brake actuator is braked, the piston of the electric brake actuator stretches out under the instruction of the controller to press the brake disc, braking thrust is generated, and when the brake is released, the piston retreats under the instruction of the controller, so that a certain gap is kept between the piston and the brake disc. The electric brake actuator generally comprises a shell, a motor, a ball screw, a force sensor and the like.
In the electric brake actuator, the ball screw is used for converting the motor torque amplified by the reduction gear into a linear force required for pressing the brake disc. The ball screw is generally composed of a ball nut and a ball screw, a steel ball and a reverser. Under certain conditions of use, such as a broken ball or a broken return, the ball screw may create a failure mode known as seizure. When the jamming fault occurs, the ball screw can lose the torque/linear force conversion function, the ball nut and the ball screw cannot generate relative movement, and the piston of the actuator cannot extend or retract according to the braking instruction requirement.
The ball screw in the electric brake actuator is stuck and can lead to unacceptable aircraft brake failure. In the process of high-speed landing braking, the braking force can not be released quickly when the braking force is blocked, so that the tire of an aircraft can be burst, and in the process of sliding braking, the braking wheel is overheated due to long-time non-instruction braking when the braking force is blocked.
In use, the ball screw of the electric brake actuator is blocked, so that the fault with smaller occurrence probability is generated. In the prior art, the fault form can only be passively processed, and after the aircraft returns to the stand, the electric brake actuator with the fault is detached and a new electric brake actuator is replaced. Due to the delay of the processing time, the processing method cannot avoid tire burst or machine wheel overheating possibly caused by the clamping of the ball screw, and potential safety hazards exist.
Disclosure of Invention
In order to overcome the defects of potential safety hazards caused by tire burst or overheat of a wheel possibly caused by clamping of a ball screw and delay of processing time in the prior art, the invention provides a release mechanism of an electric brake device and a use method thereof.
The release mechanism of the electric brake device comprises a nut, a ball nut, a lower shell and a cushion block in a compression disc assembly, wherein the nut, the ball nut and the lower shell are arranged in an electric brake actuator, the electric brake actuator and the compression disc are matched to work, in particular, an annular boss protruding axially is added on the end face of the closed end of the nut in the electric brake actuator, four uniformly distributed fan-shaped convex blocks are processed on the end face of the boss, and a moving groove of the cushion block positioned on the surface of the compression disc is formed by grooves among the fan-shaped convex blocks. Expansion tubes are symmetrically arranged on the outer circumference of an opening end port of a ball nut arranged in a lower shell of the electric brake actuator, and guide balls are embedded in each expansion tube. Two guide ball grooves with arc-shaped cross sections are symmetrically formed in the inner hole wall of the lower shell, and the positions of the guide ball grooves correspond to the positions of the guide balls.
For being matched with the ball nut, the non-friction surface of the pressing disc is provided with four uniformly distributed kidney-shaped grooves. Cushion blocks are respectively fixed in the kidney-shaped grooves. Four fan-shaped convex blocks are uniformly distributed around the geometric center of each cushion block. The upper surface of each protruding block is 3-6 mm higher than the surface of the pressing disc. The height of each lug is the same as the height of the fan-shaped lug on the ball nut. The surfaces at the two ends of each cushion block are respectively provided with a riveting installation surface.
The height of the fan-shaped protruding block is larger than the axial elastic deformation of the brake device caused by loading when the electric brake actuator pushes the brake disc to squeeze towards the tail end of the brake shell.
The included angle of the two inclined edges of the fan-shaped convex block is 40 degrees, and the included angle of the two inclined edges of the cushion block moving groove is 50 degrees.
A ball nut is mounted in the lower housing of the electric brake actuator. A pair of arc grooves are symmetrically distributed on the inner surface of the lower shell, and the radius of each arc groove is matched with the radius of the guide ball.
One end of the expansion pipe is an expansion section for installing a guide ball, the outer diameter of the expansion section is the same as the inner diameter of the blind hole on the nut, the inner diameter of the expansion pipe is the same as the diameter of the guide ball, and the end face of the other end of the expansion pipe is in contact with the bottom surface of the blind hole.
The guide ball is made of bearing steel, and the hardness is higher than HRC 55. The expansion tube is made of GH600 superalloy seamless tube with hardness not more than HRC 30.
A pair of blind holes for installing the expansion tube are symmetrically distributed on the outer circumference of the open end port of the ball nut.
The cushion blocks are waist-shaped blocks, and each cushion block is riveted on the compaction disc through rivets. Four fan-shaped convex blocks with the same height are uniformly distributed in the middle of each cushion block, and the circumferential angle of each fan-shaped convex block is 40 degrees.
The invention provides a method for releasing actuating force by using a release mechanism of an electric brake device, which comprises the following specific processes:
And 1, setting the maximum working current of a motor in the electric brake actuator.
The controller limits the maximum operating current of the motor in each electric brake actuator in the brake device prior to actuation of the brake device. The operating current of the motor has a linear correspondence with the driving torque of the motor, the driving torque being greater as the current is greater.
The maximum operating current of the motor is set to not more than 3A, and the maximum driving torque corresponding to the motor is set to not more than 3 N.m. Step 2, monitoring the working state of the electric brake actuator:
And detecting the working state of the electric brake actuator to judge whether the ball screw in the electric brake actuator has a clamping fault or not. If a certain electric brake actuator has a clamping fault, the step 3 is carried out;
the standard for judging whether the ball screw in the electric brake actuator has a clamping fault is as follows:
the I controller sends out an instruction to the electric brake actuator corresponding to the brake release;
The motor current II is large enough but not exceeding the limit. If the motor current is greater than 1A and less than 3A, namely the driving torque corresponding to the motor is greater than 1 N.m;
the III motor speed continues to be zero for 10 ms.
Step3, release of braking force:
When the ball screw in the electric brake actuator has a clamping fault, a command for starting the release mechanism is sent out, and the release of brake actuating force is completed, specifically:
When the ball screw in the electric brake actuator is judged to have a clamping fault, a controller sends out a command for starting a release mechanism, a motor in the faulty electric brake actuator rotates in a brake loosening direction with a large current, the current of the motor is larger than 4A, and the driving torque of the motor is larger than 4 N.m. At this time, because the driving torque of the motor is large enough, the extrusion force of the guide ball to the expansion tube can cause the expansion tube to expand and deform, the guide ball moves towards the small end of the expansion tube to get rid of the limitation of the arc-shaped groove, and the ball nut rotates relative to the arc-shaped groove.
When the motor rotates by 42 degrees, the motor is powered off, the motor has no current output, so that the four convex fan-shaped blocks on the nut are aligned and embedded into the grooves among the convex fan-shaped blocks on the cushion block, and the actuating force applied by the fault electric brake actuator on the brake disc is released.
The invention can release braking force in time when the ball screw in the electric brake actuator is blocked, and avoid tire burst or overheat of the brake wheel of the aircraft caused by the blocking of the ball screw.
The invention monitors the working state of an electric brake actuator in the braking process. If the monitoring analysis determines that the ball screw of the electric brake actuator is blocked in the braking process, a release mechanism of the electric brake device is started, and the braking thrust of the electric brake actuator, which is blocked by the ball screw, is released in time. Because the processing mode can timely process the fault electric brake actuator in the aircraft braking process, rather than waiting for the aircraft to return to the stand and then processing the fault, the processing mode can avoid the possible tire burst or overheat of the brake wheel of the aircraft caused by the locking of the ball screw, and ensures the flight safety.
Drawings
FIG. 1 is a block diagram of an electric brake device;
FIG. 2 is a block diagram of a pinch plate assembly;
FIG. 3 is a block diagram of an electric brake actuator;
FIG. 4 is a block diagram of the ball nut, wherein FIG. 4a is a front view and FIG. 4b is a cross-sectional view taken along line A-A of FIG. 4 a;
FIG. 5 is a schematic view of an arcuate slot in the lower housing;
FIG. 6 is a force analysis diagram of a guide ball and an expansion tube, wherein FIG. 6a is a force diagram of a ball nut after the ball nut is matched with a lower shell, FIG. 6b is a force diagram of the guide ball, FIG. 6c is a force diagram of the expansion tube, and FIG. 6d is an exploded view of the force exerted by the guide ball on the expansion tube;
FIG. 7 is a schematic view of the structure of the release mechanism;
FIG. 8 is a schematic illustration of the release mechanism operating to a release position;
Fig. 9 is a schematic three-dimensional structure of the release mechanism.
1, An electric brake actuator; 2, an actuating support, 3, a pressing disc assembly, 4, a moving disc assembly, 5, a static disc, 6, a pressure bearing disc assembly, 7, a brake shell, 8, a pressing disc, 9, a cushion block, 10, a rivet, 11, an upper shell, 12, a lower shell, 13, a motor, 14, a ball screw, 15, a ball nut, 16, a force sensor, 17, a nut, 18, a guide ball, 19, an expansion tube and 20, a guide ball groove.
Detailed Description
This embodiment is a release mechanism in an electric brake device.
The release mechanism is obtained by improving the electric brake actuator in the prior art. The improvement is that an annular boss protruding axially is added at the outer edge of the end face of the closed end of the nut 17 in the electric brake actuator, four uniformly distributed fan-shaped convex blocks are processed on the end face of the boss, and the boss is positioned outside the lower end face of the lower shell 12 in the electric brake actuator. The grooves between the fan-shaped convex blocks form a moving groove of the cushion block positioned on the surface of the pressing disc. The height of the fan-shaped protruding block is required to be larger than the axial elastic deformation generated by the loading of the brake device when the electric brake actuator 1 pushes the brake disc to press towards the tail end of the brake shell, and in the embodiment, the height of the fan-shaped protruding block is 3-6 mm. The included angle of the two inclined edges of the fan-shaped convex block is 40 degrees, and the included angle of the two inclined edges of the cushion block moving groove is 50 degrees. A pair of blind holes are symmetrically distributed on the outer circumference of the open end port of the ball nut, expansion pipes 19 are respectively arranged in the blind holes, guide balls 18 are embedded in the expansion pipes, and the guide balls are steel balls with the hardness of HRC55 or more.
The ball nut is mounted in the lower housing of the electric brake actuator 1. A pair of arc grooves 20 are symmetrically distributed on the inner surface of the lower shell, and the radius of the arc grooves is matched with the radius of the guide balls.
For use with the ball nut, a compression plate in the brake device is modified. Specifically, four uniformly distributed kidney-shaped grooves are processed on the non-friction surface of the pressing disc. Cushion blocks are respectively fixed in the kidney-shaped grooves. Four fan-shaped convex blocks are uniformly distributed around the geometric center of each cushion block. The upper surface of each protruding block is 3-6 mm higher than the surface of the pressing disc. The height of each lug is the same as the height of the fan-shaped lug on the ball nut. The surfaces at the two ends of each cushion block are respectively provided with a riveting installation surface.
The electric brake actuator 1 is in the prior art and comprises an upper shell 11, a lower shell 12, a motor 13, a ball screw and a force sensor 16. Wherein the ball screw comprises a ball screw 14, a ball nut 15, balls and a return. When the electric brake actuator 1 works, the motor drives the ball screw 14 to rotate, and the ball nut 15 moves linearly. During braking, the ball nut acts as a piston to be directly pressed against the pad 9 on the pressing plate. Two radial blind holes are uniformly distributed on the outer circumferential surface of the open end of the nut 17, expansion tubes 19 are respectively arranged in the blind holes, and guide balls 18 are arranged at the top ends of the expansion tubes. Two guide ball grooves 20 with arc-shaped cross sections are symmetrically formed on the inner hole wall of the lower shell 12, and the positions of the guide ball grooves correspond to the positions of the guide balls on the expansion tube.
The expansion tube 19 is a metal tube, one end of the expansion tube is an expansion section for installing the guide ball 18, the outer diameter of the expansion section is the same as the inner diameter of the blind hole on the nut, the inner diameter is the same as the diameter of the guide ball, and the end face of the other end of the expansion tube 19 is in contact with the bottom surface of the blind hole. The guide ball 18 is made of bearing steel such as GCr15 material with a hardness above HRC 55. The expansion tube is made of a metal material with relatively low hardness and small change of yield strength within the temperature range of-55 ℃ to 150 ℃. In the embodiment, the expansion tube is a GH600 superalloy seamless tube with the hardness not more than HRC 30. Because the hardness of the guide ball 18 and the hardness of the expansion tube 19 are greatly different, when the extrusion force of the guide ball 18 on the expansion tube 19 exceeds the expansion force of the expansion tube, the unexpanded part of the inner diameter of the expansion tube 19 can be continuously expanded, and the guide ball 18 slides in the inner cavity of the expansion tube 19 from the large end to the small end. The bottom end of the nut 17 is provided with four fan-shaped protruding blocks uniformly distributed at four positions, and the circumferential angle and the protruding height of each fan-shaped protruding block are the same as those of each fan-shaped protruding block on the cushion block 9. The nut 17 is contacted with the cushion block 9 after extending out, and the four fan-shaped convex blocks on the bottom end of the nut 17 are equal to the four fan-shaped convex blocks on the cushion block 9 in size and opposite in position.
The spacer 9, the arcuate slot 20 and the ball nut 15 together form a release mechanism for the electric brake device.
As shown in fig. 2, the pinch plate assembly 3 is comprised of a pinch plate 8, a spacer 9, and rivets 10. The number of the cushion blocks 9 is the same as that of the electric brake actuators on the electric brake device. The cushion block 9 is a waist-shaped block and is made of a metal material with small heat conductivity coefficient, such as titanium alloy or stainless steel. The cushion blocks 9 are respectively riveted to the pressing disk 8 by rivets 10. Four fan-shaped convex blocks with the same height are uniformly distributed in the middle of each cushion block 9, and the circumferential angle of each fan-shaped convex block is 40 degrees. The protruding height of the fan-shaped protruding block is larger than the maximum value of axial deformation generated in the use process of the brake device. The inner diameter of the pressing disc 8 is provided with a key slot matched with the brake shell during braking. The pressing disc 8 and the cushion block 9 can only slide along the axial direction in the brake shell. Each electric brake actuator 1 on the brake device corresponds to one cushion block 9, and the piston of the electric brake actuator stretches out and is directly pressed on the cushion block 9 during braking.
When the ball screw is not locked, the ball nut 15 is guided by the guide ball 18 by the driving of the ball screw 14, and slides in the arc groove 20 of the lower housing 12. When the ball screw is locked, the ball screw 14 and the ball nut 15 are completely locked, and the ball nut 15 can only rotate and cannot perform linear motion. After the clamping, the force analysis of the guide ball 18 and the expansion tube 19 is shown in fig. 6. Where M Driving of is the driving torque of the ball screw 14 to the ball nut 15. M Friction of is the friction resistance torque experienced by the ball nut 15, and the magnitude of M Friction of can be determined experimentally. F Lower shell is the holding force of the arcuate slot 20 against the guide ball 18. From the stress relation in the figure, according to a moment balance equation, M Driving of 、M Friction of and F Lower shell meet that M Driving of -M Friction of ＝F Lower shell ×L.F expansion pipe is the supporting force of the expansion tube 19 on the guide ball 18. f Lower shell and F expansion pipe are equal in size when the guide ball is stationary. F Ball with ball body is the compression force of the guide ball 18 against the expansion tube 19. F expansion pipe and F Ball with ball body are a pair of forces and reaction forces of equal magnitude. F Ball with ball body can be split into two mutually perpendicular force components F Ball with ball body 1 and F Ball with ball body 2. From the above force correlations, it can be deduced that F Ball with ball body 2＝F Lower shell is sin θ. Thus, the larger M Driving of , the larger F Lower shell , and consequently the greater the compressive force component F Ball with ball body 2 of the guide ball 18 against the expansion tube 19. When M Driving of exceeds a certain value, an increase in F Ball with ball body 2 causes the unexpanded portion of the inner diameter of the tube 19 to continue to expand, and the guide ball 18 slides within the lumen of the tube 19 from the large end to the small end.
The release mechanism works as shown in fig. 7 and 8. In normal use, a part of the guide ball 18 is exposed out of the flaring end of the flaring tube 19, and the exposed part is matched with the arc-shaped groove 20 to guide the ball nut 15 to perform linear motion. In order to disengage the guide ball 18 from the guide of the arc groove 20, the guide ball 18 must be moved toward the small end of the expansion tube 19, i.e., the small end of the inner diameter of the expansion tube 19 is enlarged, and the expansion tube 19 is expanded against the expansion force of the expansion tube 19. The minimum axial compression force required to initiate an expansion deformation of the expanded tube 19 is defined as the magnitude of the expansion force F 1.F1, which is determined by the tube yield strength and tube wall thickness of the expanded tube 19. After the structural dimensions of the expanded tube 19 are determined, the size of F 1 is determined. When the extrusion force F Ball with ball body 2 of the guide ball 18 to the expansion tube 19 is smaller than the expansion force F 1, the expansion tube 19 cannot be expanded and deformed, and only when F Ball with ball body 2 is larger than the expansion force F 1, the expansion tube cannot be expanded and deformed. The expansion force F 1 of the expansion tube 19 is designed such that the minimum driving torque of the ball nut 15 to rotate relative to the arcuate slot 20 is M 1 by the guide ball 18 moving towards the small end of the expansion tube against the expansion force F 1 of the expansion tube 19. In normal operation of the electric brake actuator, the torque M Driving of of the ball screw 14 driving the ball nut 15 does not exceed M 1 by controlling the output torque of the motor 13. Thus, in normal use, no matter whether the nut 17 is in contact with the spacer 9 or not, the guide ball 18 is caused to move towards the small end of the tube against the expansion force F 1 of the tube 19. In this way the position of the guide ball 18 in the expansion tube 19 remains stable all the time, and the ball nut 15 is guided by the guide ball 18 and can only slide on the arcuate slot 20. In this condition, after the ball nut 15 is extended, the four fan-shaped projections at the bottom end thereof are opposite to the four fan-shaped projections on the pad 9. When the ball screw is stuck, the braking system can recognize the fault state. At this time, the system commands the motor to counter-rotate with a torque much greater than that in normal use, so that the torque value of the driving torque M Driving of minus the friction resistance torque M Friction of is sufficiently large to actuate the release mechanism. Since the driving torque acting on the ball nut 15 is sufficiently large, the pressing force F Ball with ball body 2 exerted by the guide ball 18 on the expansion tube 19 is greater than the expansion force F 1. In this way, the unexpanded inner diameter portion of the expansion tube 19 continues to expand under the action of the pressing force F Ball with ball body 2, and the guide ball 18 slides in the inner cavity of the expansion tube 19 from the large end to the small end, so that the guide ball is separated from the restriction of the arc-shaped groove 20, and the ball nut 15 continuously rotates relative to the lower housing 12. After the ball nut 15 has rotated 41 ° relative to the initial position, the four scallops on the nut 17 are in direct opposition to the grooves between the four scallops on the pad 9. And the axial clearance between the nut 17 and the spacer 9 increases, the increased clearance being equal to the four segment bump heights on the nut 17. Since the bump height of the segment is greater than the maximum axial deformation of the brake in use, an axial distance will remain between the nut 17 and the spacer 9. Therefore, after the ball screw is blocked, the linear force applied to the brake disc by the fault electric brake actuator is actively unloaded.
The embodiment also provides a method for releasing the actuating force by using the release mechanism, which comprises the following specific steps:
And 1, setting the maximum working current of a motor in the electric brake actuator.
The controller limits the maximum operating current of the motor in each electric brake actuator in the brake device prior to actuation of the brake device. The operating current of the motor has a linear correspondence with the driving torque of the motor, the driving torque being greater as the current is greater.
The maximum operating current of the motor is set to not more than 3A, and the maximum driving torque corresponding to the motor is set to not more than 3 N.m. When the driving torque of the motor is not more than 3n·m, the pressing force generated by the guide ball 18 does not cause the expansion tube to undergo expansion deformation, and the release mechanism can be prevented from being triggered when the ball screw does not undergo a seizure failure.
And 2, monitoring the working state of the electric brake actuator, and judging whether the ball screw in the electric brake actuator has a clamping fault or not.
After the braking device is started, continuous real-time monitoring is carried out on the command state of the controller, the motor current, the motor rotating speed and the motor rotating angle corresponding to each electric brake actuator. The controller command status is monitored to determine whether the current command of the controller corresponds to a loose brake. The motor current is monitored to determine whether the motor has an open-circuit fault or a short-circuit fault and whether the driving torque of the motor is large enough. The motor speed is monitored to determine if the motor has a speed response at a sufficiently large drive torque.
In the detection, if a certain electric brake actuator simultaneously meets the following 3 conditions at a certain moment, the ball screw is considered to have a clamping fault:
1. The controller sends out an instruction to the electric brake actuator corresponding to the brake release;
2. The motor current is large enough but not exceeding the limit value. If the motor current is greater than 1A and less than 3A, namely the driving torque corresponding to the motor is greater than 1 N.m;
3. The motor speed continues to be zero for 10 ms.
The stuck fault is expressed as that the controller instructs the electric brake actuator to perform loose braking, the motor does not have an open/short circuit fault and the driving torque of the motor is large enough, but the motor cannot rotate.
The electric brake actuator is in the prior art.
The transmission part of the electric brake actuator comprises a transmission gear, a bearing and a ball screw. In the use of electric brake actuators, wear occurs in the drive gears, bearings and ball screws. Excessive wear of the transmission gear, the bearing and the ball screw is manifested in unstable transmission of the electric brake actuator, but mechanical jamming is not caused. In use, the ball screw is blocked by itself, which is the only reason for mechanical blocking of the electric brake actuator. The working state of the electric brake actuator at a certain moment meets the above 3 conditions at the same time, and the working state can be used as a basis for judging the occurrence of the locking fault of the ball screw. If the electric brake actuator is judged not to have the locking fault, the electric brake actuator continues to brake or release the brake according to the instruction of the controller, and the step 3 is entered.
And step 3, when the ball screw in the electric brake actuator has a clamping fault, a command for starting the release mechanism is sent out, and the release of the brake actuating force is completed.
And (2) according to the judging condition of the ball screw locking fault in the step (2), after the ball screw in the electric brake actuator is judged to have the locking fault, a controller sends a command for starting a release mechanism, a motor in the failed electric brake actuator rotates in a releasing brake direction with a large current, the current of the motor is larger than 4A, and the driving torque of the motor is larger than 4 N.m. At this time, since the driving torque of the motor is large enough, the extrusion force of the guide ball 18 to the expansion tube 19 causes the expansion tube to expand and deform, the guide ball moves toward the small end of the expansion tube to get rid of the limitation of the arc groove 20, and the ball nut 15 rotates relative to the arc groove 20.
When the motor rotates by 42 degrees, the motor is powered off, no current is output by the motor, the four convex fan-shaped blocks on the nut 17 are aligned and embedded into grooves among the convex fan-shaped blocks on the cushion block 9, and the actuating force applied by the fault electric brake actuator on the brake disc is released.
Claims (8)
1. A release mechanism of an electric brake device is characterized by comprising a ball nut in an electric brake actuator, a lower shell and a cushion block in a compression disc assembly, wherein the electric brake actuator and the compression disc assembly work in a matched manner;
The end face of the closed end of the ball nut in the electric brake actuator is provided with an annular boss which protrudes axially, four fan-shaped convex blocks which are uniformly distributed are processed on the end face of the boss, a moving groove which is positioned on a cushion block on the surface of a pressing disc is formed by grooves among the fan-shaped convex blocks, expansion pipes are symmetrically arranged on the outer circumference of an opening end port of the ball nut in a lower shell of the electric brake actuator, guide balls are embedded in the expansion pipes, two guide ball grooves with arc-shaped cross sections are symmetrically arranged on the inner wall of the lower shell, the positions of the guide ball grooves correspond to the positions of the guide balls, one end of each expansion pipe is an expansion section for installing the guide balls, the outer diameter of each expansion section is identical to the inner diameter of a blind hole on the ball nut, the inner diameter of each expansion pipe is identical to the diameter of the guide balls, and the end face of the other end face of each expansion pipe is contacted with the bottom surface of the blind hole;
For being matched with the ball nut, four uniformly distributed kidney-shaped grooves are formed in the non-friction surface of the pressing disc;
Four cushion blocks are respectively fixed in each kidney-shaped groove, the four cushion blocks are four sector cushion blocks uniformly distributed around the geometric center of the cushion blocks, the upper surface of each sector cushion block is 3-6 mm higher than the surface of the pressing disc, the height of each sector cushion block is the same as the height of a sector lug on the ball nut, and the surfaces at two ends of each sector cushion block are respectively provided with a riveting installation surface;
the height of the fan-shaped protruding block is larger than the axial elastic deformation of the brake device caused by loading when the electric brake actuator pushes the brake disc to squeeze towards the tail end of the brake shell;
The extrusion force of the guide ball to the expansion tube can cause the expansion tube to expand and deform, the guide ball moves towards the small end of the expansion tube to get rid of the limitation of the guide ball groove, the ball nut rotates relative to the guide ball groove, the four fan-shaped convex blocks on the ball nut are aligned and embedded into the groove formed by the fan-shaped cushion block on the pressing disc component, and the actuating force applied by the fault electric brake actuator to the brake disc is released.
2. The release mechanism of claim 1, wherein the angle between the two beveled edges of the fan-shaped projection is 40 ° and the angle between the two beveled edges of the travel slot of the pad is 50 °.
3. A release mechanism for an electric brake apparatus as defined in claim 1, wherein a pair of guide ball grooves are symmetrically formed in an inner surface of the lower housing, and wherein a radius of the guide ball grooves is adapted to a radius of the guide balls.
4. The release mechanism of an electric brake apparatus according to claim 1, wherein the guide ball is made of bearing steel with a hardness of more than HRC55, and the expansion tube is made of GH600 superalloy seamless tube with a hardness of not more than HRC 30.
5. The release mechanism of an electric brake apparatus as recited in claim 1, wherein a pair of blind holes for mounting the expansion tube are symmetrically distributed on an outer circumference of the ball nut at the open end port.
6. The release mechanism of an electric brake apparatus of claim 1, wherein the pads are kidney-shaped blocks, each of which is riveted to the pressure plate by a rivet.
7. A method of releasing actuating force by using the release mechanism of the electric brake apparatus according to claim 1, wherein the specific process is:
step 1, setting the maximum working current of a motor in an electric brake actuator:
Before starting the brake device to work, limiting the maximum working current of the motor in each electric brake actuator in the brake device by a controller, wherein the working current of the motor has a linear corresponding relation with the driving torque of the motor, and the larger the current is, the larger the driving torque is;
setting the maximum working current of the motor to be not more than 3A, and setting the maximum driving torque of the motor to be not more than 3 N.m;
step 2, monitoring the working state of the electric brake actuator:
judging whether the ball screw in the electric brake actuator has a clamping fault or not through detecting the working state of the electric brake actuator, and if so, entering the step 3;
step3, release of braking force:
when the ball screw in the electric brake actuator has a clamping fault, a command for starting the release mechanism is sent out, and the release of brake actuating force is completed:
When the ball screw in the electric brake actuator is judged to have a clamping fault, a controller sends a command for starting a release mechanism, a motor in the electric brake actuator with the fault rotates in a loosening braking direction with a large current, the current of the motor is larger than 4A, and the driving torque of the motor is larger than 4 N.m;
When the motor rotates by 42 degrees, the motor is powered off, the motor has no current output, so that four fan-shaped protruding blocks on the ball nut are aligned and embedded into a groove formed by fan-shaped cushion blocks on the pressing disc assembly, and the actuating force applied to the brake disc by the fault electric brake actuator is released.
8. The method for releasing actuating force by using a release mechanism of an electric brake apparatus as recited in claim 7, wherein the criterion for determining whether the ball screw in the electric brake actuator has a stuck fault is:
the I controller sends out an instruction to the electric brake actuator corresponding to the brake release;
The motor current is larger than 1A and smaller than 3A, namely the driving torque corresponding to the motor is larger than 1 N.m;
the III motor speed continues to be zero for 10 ms.
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| ATE481576T1 (en) * | 2004-06-04 | 2010-10-15 | Goodrich Corp | ELECTRIC BRAKE FOR AIRCRAFT |
| US10683880B2 (en) * | 2012-06-04 | 2020-06-16 | Aero Controlex Group Inc. | Blow down actuator assembly having a drag brake |
| JP6130235B2 (en) * | 2013-06-11 | 2017-05-17 | Ntn株式会社 | Electric linear actuator |
| CN103661345B (en) * | 2013-12-05 | 2015-10-21 | 西安航空制动科技有限公司 | The actuator of Electric Brake System of Aircraft device |
| US9527584B2 (en) * | 2015-01-16 | 2016-12-27 | Goodrich Corporation | Electromechanically actuated brake with supplemental back drive |
| US10081342B2 (en) * | 2015-05-22 | 2018-09-25 | Goodrich Corporation | Systems and methods for brake actuator operation under load cell failure |
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| JP6595902B2 (en) * | 2015-12-24 | 2019-10-23 | Ｋｙｂ株式会社 | Brake device actuator and brake device including the same |
| KR102383332B1 (en) * | 2016-11-29 | 2022-04-05 | 현대자동차주식회사 | Ball Screw Type Electro-Mechanical Brake |
| US20190031170A1 (en) * | 2017-07-26 | 2019-01-31 | Goodrich Corporation | Failsafe synthetic angle generation algorithm for aircraft electric braking system |
| CN109398683B (en) * | 2017-08-17 | 2023-12-05 | 中电科特种飞机系统工程有限公司 | Aircraft electric brake device and aircraft with same |
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