CN113983165A - Disc brake with integrated parking function and parking input and output characteristic calculation method - Google Patents
Disc brake with integrated parking function and parking input and output characteristic calculation method Download PDFInfo
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- CN113983165A CN113983165A CN202111300382.6A CN202111300382A CN113983165A CN 113983165 A CN113983165 A CN 113983165A CN 202111300382 A CN202111300382 A CN 202111300382A CN 113983165 A CN113983165 A CN 113983165A
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- 238000004364 calculation method Methods 0.000 title claims abstract description 9
- 229910000831 Steel Inorganic materials 0.000 claims abstract description 58
- 239000010959 steel Substances 0.000 claims abstract description 58
- 238000003780 insertion Methods 0.000 claims abstract description 8
- 230000037431 insertion Effects 0.000 claims abstract description 8
- 230000006835 compression Effects 0.000 claims description 21
- 238000007906 compression Methods 0.000 claims description 21
- 238000006073 displacement reaction Methods 0.000 claims description 14
- 238000005096 rolling process Methods 0.000 claims 1
- 238000006243 chemical reaction Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000001681 protective effect Effects 0.000 description 3
- 210000000078 claw Anatomy 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 1
- 230000001960 triggered effect Effects 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
- F16H63/34—Locking or disabling mechanisms
- F16H63/3416—Parking lock mechanisms or brakes in the transmission
- F16H63/345—Parking lock mechanisms or brakes in the transmission using friction brakes, e.g. a band brakes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/02—Braking members; Mounting thereof
- F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
- F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
- F16D65/095—Pivots or supporting members therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
- F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
- F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
- F16H63/34—Locking or disabling mechanisms
- F16H63/3416—Parking lock mechanisms or brakes in the transmission
- F16H63/3483—Parking lock mechanisms or brakes in the transmission with hydraulic actuating means
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/10—Geometric CAD
- G06F30/15—Vehicle, aircraft or watercraft design
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/10—Geometric CAD
- G06F30/17—Mechanical parametric or variational design
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2121/00—Type of actuator operation force
- F16D2121/02—Fluid pressure
- F16D2121/04—Fluid pressure acting on a piston-type actuator, e.g. for liquid pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2121/00—Type of actuator operation force
- F16D2121/14—Mechanical
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- General Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Theoretical Computer Science (AREA)
- Computer Hardware Design (AREA)
- Computational Mathematics (AREA)
- Mathematical Analysis (AREA)
- Mathematical Optimization (AREA)
- Pure & Applied Mathematics (AREA)
- Evolutionary Computation (AREA)
- Aviation & Aerospace Engineering (AREA)
- Automation & Control Theory (AREA)
- Braking Arrangements (AREA)
Abstract
The invention relates to the technical field of engineering elements, in particular to a disc brake with an integrated parking function and a parking input and output characteristic calculation method, wherein a guide bush is connected with a shell and an operation ejector rod, a pull arm is connected with the operation ejector rod, an actuator is connected with the shell, three steel balls are connected with the operation ejector rod and are respectively positioned in a roller path of the actuator, a plane bearing is connected with the operation ejector rod and a screw rod, a threaded sleeve is connected with the screw rod, an insertion plate is connected with the threaded sleeve, a piston is connected with the threaded sleeve and the shell, a brake block is connected with a caliper body, a brake disc is connected with the caliper body, the pull arm is rotated, so that the operation ejector rod drives the steel ball to slide out of the raceway, the operation ejector rod drives the screw rod to slide in the threaded sleeve until the screw rod is contacted with the insertion plate and then pushes the piston, make piston promotion brake pad and brake disc contact, the angle of rotation single arm-drag is big more, and the brake force that the brake pad gave the brake disc is big more, has solved the linear relatively poor problem of hand brake power of current parking brake.
Description
Technical Field
The invention relates to the technical field of engineering elements, in particular to an integrated parking function disc brake and a parking input and output characteristic calculation method.
Background
A parking brake is a device having a function of decelerating, stopping, or maintaining a stopped state of a moving member. Is a mechanical part that stops or decelerates moving parts in a machine. The existing parking brake enables a rocker arm to trigger a brake caliper by swinging the rocker arm, so that the purpose of braking is achieved. However, the brake caliper can be triggered only by swinging the rocker arm to a preset position, and the braking force cannot be controlled according to the swinging degree of the rocker arm, namely the hand braking force linearity of the parking brake is poor.
Disclosure of Invention
The invention aims to provide an integrated parking function disc brake and a parking input and output characteristic calculation method, and aims to solve the problem that the hand brake force linearity of the conventional parking brake is poor.
In order to achieve the above object, in a first aspect, the present invention provides an integrated parking function disc brake, including a force application mechanism and a force receiving mechanism;
the force application mechanism comprises a shell, a guide bush, an operation ejector rod, a pull arm, an actuator, steel balls, a plane bearing, a screw rod, a screw sleeve, a plug board and a piston, wherein the guide bush is fixedly connected with the shell and positioned on the inner side wall of the shell, the operation ejector rod is rotatably connected with the guide bush and penetrates through the guide bush, the pull arm is in threaded connection with the operation ejector rod and positioned on one side far away from the shell, the actuator is fixedly connected with the shell and positioned in the shell, the actuator is provided with three roller paths, the three steel balls are respectively in sliding connection with the operation ejector rod and respectively positioned in the roller paths, the plane bearing is fixedly connected with the operation ejector rod and positioned on one side far away from the pull arm, the screw rod is fixedly connected with the plane bearing and positioned on one side far away from the operation ejector rod, the screw sleeve is connected with the screw rod in a sliding manner and is positioned on the outer side wall of the screw rod, the plug board is fixedly connected with the screw sleeve and is positioned on the outer side wall of the screw sleeve, the outer ring of the piston is rotationally connected with the shell, and the inner ring of the piston is connected with the screw sleeve in a sliding manner and is positioned between the shell and the screw sleeve;
the stress mechanism comprises a caliper body, a brake block and a brake disc, the caliper body is rotatably connected with the shell and is positioned on the outer side wall of the shell, the brake block is slidably connected with the caliper body and is positioned on one side close to the piston, and the brake disc is fixedly connected with the caliper body and is positioned on one side close to the brake block.
The pull arm is rotated to enable the pull arm to drive the steel ball on the operation ejector rod to slide in the actuator towards the force application direction and gradually slide out of the roller path, so that the steel ball increases the distance between the actuator and the operating ejector rod, the operating ejector rod drives the screw rod to slide in the threaded sleeve until the screw rod is contacted with the plug board, and pushing the piston through the plug plate so that the piston extends out of the shell and pushes the brake block towards the brake disc until the brake block is contacted with the brake disc, when the reaction force to the brake disk on the caliper body is larger than the sliding resistance of the brake disk on the caliper body, the caliper body realizes parking braking, and the larger the angle for rotating the pull arm is, the larger the braking force applied to the brake disc by the brake block is.
The force application mechanism further comprises an anti-rotation pin, and the anti-rotation pin is fixedly connected with the shell and penetrates through the actuator.
The rotation-proof pin is used for fixing the actuator on the shell, and the actuator is prevented from rotating along the rotating direction of the operation ejector rod.
The force application mechanism further comprises an ejector rod oil seal, the outer ring of the ejector rod oil seal is fixedly connected with the shell, and the inner ring of the ejector rod oil seal is rotatably connected with the operation ejector rod and located between the shell and the operation ejector rod.
The ejector rod oil seal fills the gap between the shell and the operation ejector rod, and the sealing performance of the shell is improved.
The force application mechanism further comprises an ejector rod nut, and the ejector rod nut is in threaded connection with the operation ejector rod and is located on the outer side wall of the operation ejector rod.
The ejector rod nut further fixes the pull arm on the operation ejector rod.
The force application mechanism further comprises a first spring seat and a compression spring, the first spring seat is fixedly connected with the actuator and located on the periphery of the operation ejector rod, one side of the compression spring is fixedly connected with the screw rod, and the other side of the compression spring is fixedly connected with the first spring seat and located between the screw rod and the first spring seat.
When the screw rod slides towards the direction of the inserting plate, the screw rod extrudes the compression spring on the first spring seat, the compression spring can absorb the vibration generated when the screw rod slides on the screw sleeve, and when the pull arm is rotated reversely to drive the screw rod to reset, the resilience force of the compression spring can increase the resetting speed and the resetting effect of the screw rod.
The force application mechanism further comprises a second spring seat, a disc spring and a ball bearing, the second spring seat is fixedly connected with the piston and located on the inner side wall of the piston, the disc spring is fixedly connected with the second spring seat and located on one side close to the insertion plate, the outer ring of the ball bearing is fixedly connected with the disc spring, and the inner ring of the ball bearing is fixedly connected with the screw sleeve.
When the screw rod slides towards the direction of the inserting plate, the screw sleeve extrudes the disc spring on the second spring seat through the ball bearing, the disc spring can absorb the vibration generated when the screw rod slides on the screw sleeve, and when the pull arm is rotated reversely to drive the screw rod to reset, the resilience force of the disc spring can increase the resetting speed and the resetting effect of the screw rod.
In a second aspect, the present invention provides a parking input output characteristic calculation method including:
dividing a raceway into three circular arcs;
establishing a mathematical mechanical model based on the three circular arcs;
deriving a relational expression of the included angle between the rotation angle of the pull arm and the included angle between the connecting line of the tangent point of the arc and the steel ball and the central point of the steel ball and the Y axis based on the model to obtain a first relational expression;
deriving a relational expression of an included angle between a connecting line of the tangent point of the circular arc and the steel ball and the central point of the steel ball and the Y axis and the axial displacement of the operating top rod on the basis of the model to obtain a second relational expression;
deriving a relational expression of the travel of the inhaul cable and the axial displacement of the operating top rod based on the first relational expression and the second relational expression to obtain a third relational expression;
deriving a relational expression of the braking torque, jaw deformation of the caliper body and brake block compression based on the third relational expression to obtain a fourth relational expression;
deriving a relational expression of the braking torque and the axial displacement of the operating top rod based on the fourth relational expression, thereby deriving a relational expression of the braking torque and the travel of the inhaul cable to obtain a fifth relational expression;
and deriving a relational expression of the cable input force and the clamping force of the caliper body and a relational expression of the guide cable input force and the braking torque based on the fifth relational expression.
The invention relates to a disc brake with integrated parking function, which is characterized in that the pull arm is rotated to enable the pull arm to drive the steel ball on the operation ejector rod to slide in the actuator in a force application direction and gradually slide out of the roller way, so that the steel ball increases the distance between the actuator and the operation ejector rod, the operation ejector rod drives the screw rod to slide in the screw sleeve until the screw rod is contacted with the insertion plate, the piston is pushed by the insertion plate, the piston extends out of the shell and pushes the brake block on the brake disc until the brake block is contacted with the brake disc, when the reaction force applied to the brake disc on the caliper body is greater than the sliding resistance of the brake disc on the caliper body, the caliper body realizes parking brake, the larger the angle of rotating the pull arm is, the greater the brake force applied to the brake disc by the brake block is, the problem of current parking brake's manual brake power linearity is relatively poor is solved.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.
Fig. 1 is a sectional view of an integrated parking function disc brake provided in the present invention;
FIG. 2 is an operational view of the pull arm;
FIG. 3 is a cross-sectional view of the steel ball, actuator and raceway;
FIG. 4 is a schematic structural diagram of an arc AB;
FIG. 5 is a schematic structural diagram of a segment BC;
FIG. 6 is a schematic view of the operation of the actuator;
FIG. 7 is a ramp diagram of the actuator;
fig. 8 is a flowchart of a parking input-output characteristic calculation method according to the present invention.
1-a force application mechanism, 2-a force bearing mechanism, 3-a shell, 4-a guide bush, 5-an operation ejector rod, 6-a pull arm, 7-an actuator, 8-a roller path, 9-a steel ball, 10-a plane bearing, 11-a screw rod, 12-a screw sleeve, 13-a plug board, 14-a piston, 15-a caliper body, 16-a brake block, 17-a brake disc, 18-an anti-rotation pin, 19-an ejector rod oil seal, 20-an ejector rod nut, 21-a first spring seat, 22-a compression spring, 23-a second spring seat, 24-a disc spring, 25-a ball bearing, 26-a guide plate and 27-a protective cover.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are illustrative and intended to be illustrative of the invention and are not to be construed as limiting the invention.
In the description of the present invention, it is to be understood that the terms "length", "width", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like, indicate orientations or positional relationships based on the orientations or positional relationships illustrated in the drawings, and are used merely for convenience in describing the present invention and for simplicity in description, and do not indicate or imply that the devices or elements referred to must have a particular orientation, be constructed in a particular orientation, and be operated, and thus, are not to be construed as limiting the present invention. Further, in the description of the present invention, "a plurality" means two or more unless specifically defined otherwise.
Referring to fig. 1 to 2, the present invention provides an integrated parking disc brake, including a force applying mechanism 1 and a force receiving mechanism 2;
the force application mechanism 1 comprises a shell 3, a guide bush 4, an operation ejector rod 5, a pull arm 6, an actuator 7, a steel ball 9, a plane bearing 10, a screw rod 11, a threaded sleeve 12, a plug board 13 and a piston 14, wherein the guide bush 4 is fixedly connected with the shell 3 and is positioned on the inner side wall of the shell 3, the operation ejector rod 5 is rotatably connected with the guide bush 4 and penetrates through the guide bush 4, the pull arm 6 is in threaded connection with the operation ejector rod 5 and is positioned on one side far away from the shell 3, the actuator 7 is fixedly connected with the shell 3 and is positioned in the shell 3, the actuator 7 is provided with three roller paths 8, the three steel balls 9 are respectively in sliding connection with the operation ejector rod 5 and are respectively positioned in the roller paths 8, the plane bearing 10 is fixedly connected with the operation ejector rod 5 and is positioned on one side far away from the pull arm 6, the screw 11 is fixedly connected with the plane bearing 10 and is positioned at one side far away from the operation ejector rod 5, the screw sleeve 12 is connected with the screw 11 in a sliding manner and is positioned on the outer side wall of the screw 11, the plugboard 13 is fixedly connected with the screw sleeve 12 and is positioned on the outer side wall of the screw sleeve 12, the outer ring of the piston 14 is rotationally connected with the shell 3, and the inner ring of the piston 14 is connected with the screw sleeve 12 in a sliding manner and is positioned between the shell 3 and the screw sleeve 12;
the stress mechanism 2 comprises a caliper body 15, a brake block 16 and a brake disc 17, the caliper body 15 is rotatably connected with the housing 3 and is positioned on the outer side wall of the housing 3, the brake block 16 is slidably connected with the caliper body 15 and is positioned on one side close to the piston 14, and the brake disc 17 is fixedly connected with the caliper body 15 and is positioned on one side close to the brake block 16.
In this embodiment, the operating mandril 5 of the force application mechanism 1 is connected with the housing 3 through the guide bush 4 and rotates on the housing 3 through the guide bush 4, the pull arm 6 is rotated to make the pull arm 6 drive the steel ball 9 on the operating mandril 5 to slide in the actuator 7 in the force application direction and gradually slide out of the roller path 8, so that the steel ball 9 increases the distance between the actuator 7 and the operating mandril 5, the operating mandril 5 drives the screw 11 to slide in the screw sleeve 12 until contacting with the plug plate 13, and pushes the piston 14 through the plug plate 13, so that the piston 14 extends out of the housing 3 and pushes the brake block 16 in the brake disc 17 direction of the force application mechanism 2 until the brake block 16 contacts with the brake disc 17, when the reaction force of the brake block 16 to the brake disc 17 on the caliper body 15 is greater than the sliding resistance of the brake disc 17 on the caliper body 15, the caliper body 15 performs parking braking, the larger the angle of rotating the pull arm 6 is, the more the position of the steel ball 9 sliding out of the raceway 8 is, the larger the braking force applied by the brake block 16 to the brake disc 17 is, and when the operation push rod 5 is rotated by the pull arm 6, the operation push rod 5 rotates on the screw rod 11 through the plane bearing 10, so that the problem of poor hand braking force linearity of the conventional parking brake is solved.
Further, the force application mechanism 1 further comprises an anti-rotation pin 18, and the anti-rotation pin 18 is fixedly connected with the shell 3 and penetrates through the actuator 7; the force application mechanism 1 further comprises a mandril oil seal 19, the outer ring of the mandril oil seal 19 is fixedly connected with the shell 3, and the inner ring of the mandril oil seal 19 is rotatably connected with the operating mandril 5 and is positioned between the shell 3 and the operating mandril 5; the force application mechanism 1 further comprises a mandril nut 20, and the mandril nut 20 is in threaded connection with the operation mandril 5 and is positioned on the outer side wall of the operation mandril 5; the force application mechanism 1 further comprises a first spring seat 21 and a compression spring 22, the first spring seat 21 is fixedly connected with the actuator 7 and is positioned around the operation ejector rod 5, one side of the compression spring 22 is fixedly connected with the screw rod 11, and the other side of the compression spring 22 is fixedly connected with the first spring seat 21 and is positioned between the screw rod 11 and the first spring seat 21; the force application mechanism 1 further comprises a second spring seat 23, a disc spring 24 and a ball bearing 25, the second spring seat 23 is fixedly connected with the piston 14 and is located on the inner side wall of the piston 14, the disc spring 24 is fixedly connected with the second spring seat 23 and is located on one side close to the insertion plate 13, the outer ring of the ball bearing 25 is fixedly connected with the disc spring 24, and the inner ring of the ball bearing 25 is fixedly connected with the screw sleeve 12.
In this embodiment, the rotation-preventing pin 18 fixes the actuator 7 on the housing 3 to prevent the actuator 7 from rotating along with the rotation direction of the operation rod 5, the rod oil seal 19 fills the gap between the housing 3 and the operation rod 5 to increase the sealing performance of the housing 3, the rod nut 20 further fixes the pull arm 6 on the operation rod 5, when the screw rod 11 slides towards the insertion plate 13, the screw rod 11 presses the compression spring 22 on the first spring seat 21, the screw sleeve 12 presses the disc spring 24 on the second spring seat 23 through the ball bearing 25, the compression spring 22 and the disc spring 24 can absorb the vibration generated when the screw rod 11 slides on the screw sleeve 12, and when the pull arm 6 is rotated reversely to drive the screw rod 11 to reset, the resilience of the compression spring 22 and the disc spring 24 increases the speed and effectiveness of the return of the screw 11.
Further, the force applying mechanism 1 further includes a guide plate 26, the guide plate 26 is fixedly connected to the housing 3 and is located at a side close to the pull arm 6, and the force applying mechanism 1 further includes a protective cover 27, and the protective cover 27 is fixedly connected to the housing 3 and is located at a side close to the brake block 16.
In the present embodiment, the guide plate 26 guides the pull arm 6, increasing the centripetal force generated when the pull arm 6 rotates, and the protection cover 27 can protect the piston 14.
Referring to fig. 2 to 8, in a second aspect, the present invention provides a parking input output characteristic calculation method, including:
s101, dividing a raceway 8 into three circular arcs;
dividing one raceway 8 into an arc AB, an arc BC and a linear slope CD, wherein the arc AB, the arc BC and the linear slope CD are symmetrically distributed, and when the actuator 7 does not work, the three steel balls 9 are respectively positioned at the bottom end of the arc AB of the raceway 8. When the vehicle is in a parking state, the position of the steel ball 9 depends on the rotation angle theta of the pull arm 6 (corresponding to the axial displacement S of the operation ejector rod 5 and the stroke of the pull arm 6), and along with the increase of the rotation angle theta of the pull arm 6, the steel ball 9 gradually rolls on the arc AB, the arc BC and the linear slope CD in sequence, and the axial displacement S of the operation ejector rod 5 correspondingly and continuously increases.
S102, establishing a mathematical mechanical model based on the three circular arcs;
since the raceway 8 of the actuator 7 is fixed, the operation push rod 5 and the raceway 8 of the actuator 7 rotate together with the pull arm 6, the steel ball 9 rotates relatively, that is, assuming that the steel ball 9 is stationary, the raceway 8 of the actuator 7 rotates, so as to establish a mathematical mechanical model based on three circular arcs;
s103, deriving a relational expression of the included angle between the corner of the pull arm 6 and the included angle between the connecting line of the tangent point of the arc and the steel ball 9 and the central point of the steel ball 9 and the Y axis based on the model to obtain a first relational expression;
s104, deriving a relational expression between an included angle between a connecting line of a tangent point of the circular arc and the steel ball 9 and a central point of the steel ball 9 and the Y axis and the axial displacement of the operation ejector rod 5 based on the model to obtain a second relational expression;
in steps S103-S104, point O is the center of the steel ball 9, and Do is the diameter of the steel ball 9; the point O1 is the center of the circular arc AB of the raceway 8, and Do is the diameter of the circular arc AB of the raceway 8; when the pull arm 6 rotates by an angle theta, the raceway 8 also rotates by an angle theta, and the point O1 at the center of the arc AB of the raceway 8 rotates to the point O1';
the relationship between the rotating angle of the pull arm 6 and the axial strokes S of the actuator 7 and the operation mandril 5 at the arc AB section of the raceway 8 is as follows:
θ1: the critical angle of rotation of the pull arm 6, the point B of the raceway 8 is tangent to the steel ball 9 (as shown in point B of fig. 3);
θ: the pull arm 6 and the operation ejector rod 5 rotate;
s: axial displacement- Δ of the operating ram 51FIG. 2;
△1: before the steel ball 9 moves, the distance between the operating ejector rod 5 and the actuator 7 is reduced;
△2: after the steel ball 9 moves, the distance between the operation ejector rod 5 and the actuator 7 is reduced;
D0: the diameter of the circular arc AB of the raceway 8 in fig. 3;
d0: the diameter of the steel ball 9 in fig. 3;
α: fig. 3 shows the included angle between the connecting line of the tangent point of the circular arc AB of the raceway 8 and the steel ball 9 and the central point o of the steel ball 9 and the Y axis;
α1: FIG. 3. alpha. when point B of the circular arc AB of the raceway 8 rotates tangentially to the steel ball 9;
L1: after the circular arc AB of the raceway 8 shown in FIG. 3 is rotationally cut and straightened, the point B of the circular arc is positioned on the Y axis.
The arc BC section is as follows: when the rotation angle theta of the pull arm 6 is larger than theta1Sometimes less than theta2The steel ball 9 enters the segment BC. At the moment, the center O of the circular arc BC of the raceway 82To O2′：
θ2: when the pull arm 6 is rotated, and the C point of the raceway 8 is tangent to the steel ball 9 (the C point of figure 3),
R2: the arc radius of the arc BC of the raceway 8 (fig. 3, 5);
θ1: the critical angle of rotation of the pull arm 6 is when the point B of the raceway 8 is tangent to the steel ball 9 (point B of fig. 3);
θ: the pull arm 6 and the operation ejector rod 5 rotate;
s: axial displacement Δ of the actuating ram 52-△1FIG. 2;
△1: before the steel ball 9 moves, the distance between the operating ejector rod 5 and the actuator 7 is reduced;
△2: after the steel ball 9 moves, the distance between the operation ejector rod 5 and the actuator 7 is reduced;
D0: the diameter of the circular arc AB of the raceway 8 in fig. 3;
d0: the diameter of the steel ball 9 in fig. 3;
α: an included angle between a connecting line of a tangent point of an arc AB of the raceway 8 and the steel ball 9 and a center o point of the steel ball 9 and the Y axis in the figure 3 is shown;
α1: fig. 3 a when point B of the arc AB of the raceway 8 rotates tangentially to the ball 9;
L1: the horizontal distance from the point B of the circular arc to the axis Y after the raceway 8 is rotationally straightened in the figure 3;
L2: the horizontal distance from the point C of the circular arc to the axis Y after the raceway 8 is straightened by rotating and splitting in the figure 3;
d: the diameter of the distribution circle of the raceway 8;
R2: the arc radius of the arc BC of the raceway 8 (fig. 3, 5);
θ2: when the C point of the roller path 8 is tangent to the steel ball 9, the pull arm 6 and the operation ejector rod 5 rotate;
the linear slope CD section: when the rotation angle theta of the pull arm 6 is larger than theta2When the steel ball 9 enters the linear slope CD section:
k: ramp angle for CD segment (fig. 3);
θ2: of raceways 8And when the point C is tangent to the steel ball 9, the pull arm 6 and the operation push rod 5 rotate.
S105, deriving a relational expression between the travel of the inhaul cable and the axial displacement of the operation ejector rod 5 based on the first relational expression and the second relational expression to obtain a third relational expression;
the relationship between the rotation angle theta of the pull arm 6 and the travel T of the parking cable is as follows: t ═ BC-BC';
and (B) point A: the rotation center of the pull arm 6;
and B, point: a cable seat;
and C, point: the pull arm 6 and the stay cable ball head (rotate around the point A under the action of the manual operation force of the vehicle);
AC ═ n; AB is m; angle a ═ β;
then: BC2＝m2+n2-2×m×n×cosβ；
BC＇2＝m2+n2-2×m×n×cos(β-θ)；
S106, deriving a relational expression of the braking torque, jaw deformation of the caliper body 15 and compression of the brake block 16 based on the third relational expression to obtain a fourth relational expression;
the relationship between the displacement S of the ram of the actuator 7, the clearance Δ between the brake pad 16 and the brake disc 17, the clearance δ between the screw 11 and the thread insert 12, the deformation γ of the claw portion of the caliper body 15, and the compression μ of the brake pad 16 is set to Δ + δ + γ + μ;
the deformation γ of the claw portion of the caliper body 15 and the compression μ of the brake pad 16 are related to the brake hydraulic pressure P and the area a of action of the caliper piston 14:
k1: the jaw portion stiffness of the caliper body 15;
k2: the brake pad 16 stiffness;
the values of delta and delta are constants.
S107, deriving a relational expression of the braking torque and the axial displacement of the operation ejector rod 5 based on the fourth relational expression so as to derive a relational expression of the braking torque and the travel of the inhaul cable and obtain a fifth relational expression;
establishing a relationship F (P multiplied by A) between the clamp force F of the caliper, the brake torque M and the ejector rod displacement S of the actuator 7; m ═ P × a × R × μf×2；
R: the effective application radius of the brake;
μ f: the coefficient of friction of the brake pads 16.
And S108, deriving a relational expression of the cable input force and the clamping force of the caliper body 15 and a relational expression of the guide cable input force and the braking torque based on the fifth relational expression.
The clamping force F of the caliper body 15, the braking torque M and the input force F of the pull arm 6lThe relationship of (1):
the following equation is derived from the moment balance: the pulling force of the pull arm 6 multiplied by the acting length of the pull arm 6 is equal to the circumferential force of the steel ball 9 to the raceway 8 multiplied by the distribution circle radius of the raceway 8;
1) AB section and BC section:
Fl＝m×sin B；
angle B is as in FIG. 6;
Fl: the inhaul cable inputs force;
Fα: the steel ball 9 acts on the circumferential force of the ramp of the raceway 8;
d: the diameter of the distribution circle of the raceway 8;
2) CD section:
M＝F×R×μf×2。
although the above embodiments are only examples of the present invention, it is understood that the scope of the present invention is not limited thereto, and all or part of the processes of the above embodiments can be realized by those skilled in the art, and the equivalent variations made by the claims of the present invention are still within the scope of the present invention.
Claims (7)
1. The disc brake with the integrated parking function is characterized by comprising a force application mechanism (1) and a stress mechanism (2);
the force application mechanism (1) comprises a shell (3), a guide bushing (4), an operation ejector rod (5), a pull arm (6), an actuator (7), a steel ball (9), a plane bearing (10), a screw rod (11), a threaded sleeve (12), an insertion plate (13) and a piston (14), wherein the guide bushing (4) is fixedly connected with the shell (3) and is positioned on the inner side wall of the shell (3), the operation ejector rod (5) is rotatably connected with the guide bushing (4) and penetrates through the guide bushing (4), the pull arm (6) is in threaded connection with the operation ejector rod (5) and is positioned on one side far away from the shell (3), the actuator (7) is fixedly connected with the shell (3) and is positioned in the shell (3), the actuator (7) is provided with three rolling ways (8), and the three steel balls (9) are respectively in sliding connection with the operation ejector rod (5), the two-way sliding type connecting device is respectively positioned in the roller path (8), the plane bearing (10) is fixedly connected with the operation ejector rod (5) and positioned at one side far away from the pull arm (6), the screw rod (11) is fixedly connected with the plane bearing (10) and positioned at one side far away from the operation ejector rod (5), the screw sleeve (12) is slidably connected with the screw rod (11) and positioned at the outer side wall of the screw rod (11), the plug board (13) is fixedly connected with the screw sleeve (12) and positioned at the outer side wall of the screw sleeve (12), the outer ring of the piston (14) is rotatably connected with the shell (3), and the inner ring of the piston (14) is slidably connected with the screw sleeve (12) and positioned between the shell (3) and the screw sleeve (12);
the stress mechanism (2) comprises a caliper body (15), a brake block (16) and a brake disc (17), the caliper body (15) is rotatably connected with the shell (3) and is positioned on the outer side wall of the shell (3), the brake block (16) is slidably connected with the caliper body (15) and is positioned on one side close to the piston (14), and the brake disc (17) is fixedly connected with the caliper body (15) and is positioned on one side close to the brake block (16).
2. Integrated parking function disc brake according to claim 1,
the force application mechanism (1) further comprises an anti-rotation pin (18), and the anti-rotation pin (18) is fixedly connected with the shell (3) and penetrates through the actuator (7).
3. Integrated parking function disc brake according to claim 2,
force application mechanism (1) still includes ejector pin oil blanket (19), the outer lane of ejector pin oil blanket (19) with casing (3) fixed connection, the inner circle of ejector pin oil blanket (19) with operation ejector pin (5) rotate to be connected, and be located casing (3) with between operation ejector pin (5).
4. Integrated parking function disc brake according to claim 3,
the force application mechanism (1) further comprises an ejector rod nut (20), and the ejector rod nut (20) is in threaded connection with the operation ejector rod (5) and is located on the outer side wall of the operation ejector rod (5).
5. Integrated parking function disc brake according to claim 4,
force application mechanism (1) still includes first spring holder (21) and compression spring (22), first spring holder (21) with actuator (7) fixed connection, and be located operation ejector pin (5) are all around, one side of compression spring (22) with screw rod (11) fixed connection, the opposite side of compression spring (22) with first spring holder (21) fixed connection, and be located screw rod (11) with between first spring holder (21).
6. Integrated parking function disc brake according to claim 5,
force application mechanism (1) still includes second spring holder (23), dish spring (24) and ball bearing (25), second spring holder (23) with piston (14) fixed connection, and be located piston (14) inside wall, dish spring (24) with second spring holder (23) fixed connection, and be located and be close to one side of plugboard (13), the outer lane of ball bearing (25) with dish spring (24) fixed connection, the inner circle of ball bearing (25) with swivel nut (12) fixed connection.
7. A parking input-output characteristic calculation method applied to the integrated parking function disc brake of any one of claims 1 to 6, characterized by comprising:
one raceway (8) is divided into three circular arcs;
establishing a mathematical mechanical model based on the three circular arcs;
deducing a relational expression of an included angle between a connecting line of a corner of the pull arm (6), a tangent point of the arc and the steel ball (9) and a central point of the steel ball (9) and a Y axis based on the model to obtain a first relational expression;
deriving a relational expression between an included angle between a connecting line of a tangent point of the arc and the steel ball (9) and a central point of the steel ball (9) and the Y axis and the axis displacement of the operation ejector rod (5) based on the model to obtain a second relational expression;
deriving a relational expression of the travel of the inhaul cable and the axial displacement of the operation ejector rod (5) based on the first relational expression and the second relational expression to obtain a third relational expression;
deriving a relational expression of the braking torque, jaw deformation of the caliper body (15) and compression of the brake block (16) based on the third relational expression to obtain a fourth relational expression;
deriving a relational expression of the braking torque and the axial displacement of the operation ejector rod (5) based on the fourth relational expression, thereby deriving a relational expression of the braking torque and the travel of the inhaul cable to obtain a fifth relational expression;
and deriving a relational expression of the cable input force and the clamping force of the caliper body (15) and a relational expression of the cable guide input force and the braking torque based on the fifth relational expression.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111300382.6A CN113983165B (en) | 2021-11-04 | 2021-11-04 | Disc brake with integrated parking function and parking input and output characteristic calculation method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111300382.6A CN113983165B (en) | 2021-11-04 | 2021-11-04 | Disc brake with integrated parking function and parking input and output characteristic calculation method |
Publications (2)
| Publication Number | Publication Date |
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| CN113983165A true CN113983165A (en) | 2022-01-28 |
| CN113983165B CN113983165B (en) | 2022-10-14 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202111300382.6A Withdrawn - After Issue CN113983165B (en) | 2021-11-04 | 2021-11-04 | Disc brake with integrated parking function and parking input and output characteristic calculation method |
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| CN213039704U (en) * | 2020-05-20 | 2021-04-23 | 浙江亚太机电股份有限公司 | Brake caliper integrating traveling and parking functions |
| DE102020110427A1 (en) * | 2020-04-16 | 2021-10-21 | Liebherr-Aerospace Lindenberg Gmbh | Brake device for control systems of aircraft |
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2021
- 2021-11-04 CN CN202111300382.6A patent/CN113983165B/en not_active Withdrawn - After Issue
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1600609A (en) * | 2003-09-26 | 2005-03-30 | 重庆红宇精密工业有限责任公司 | Brake tongs with brake for stationed vehicle |
| CN102865321A (en) * | 2012-10-16 | 2013-01-09 | 广东中博汽车零部件有限公司 | Brake calipers with parking braking mechanism |
| CN203442027U (en) * | 2013-05-10 | 2014-02-19 | 陈光华 | Hydraulic disc type parking brake |
| CN204175837U (en) * | 2014-10-24 | 2015-02-25 | 安思通（厦门）制动系统有限公司 | The modified node method of the parking locking device for a vehicle of integral type |
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| CN113983165B (en) | 2022-10-14 |
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