CN102562885A - Electromechanical brake system actuator of automobiles - Google Patents
Electromechanical brake system actuator of automobiles Download PDFInfo
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- CN102562885A CN102562885A CN2012100060925A CN201210006092A CN102562885A CN 102562885 A CN102562885 A CN 102562885A CN 2012100060925 A CN2012100060925 A CN 2012100060925A CN 201210006092 A CN201210006092 A CN 201210006092A CN 102562885 A CN102562885 A CN 102562885A
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Abstract
The invention discloses an electromechanical brake system actuator of automobiles used for solving the technical problem of complex structure of the existing electromechanical brake actuator of automobiles. The technical scheme is as follows: a rotor (7-1) of a motor (7), a motor output shaft (6) and a lead screw (5) of a roller screw pair are in an integral coaxial structure; a plurality of rollers (4) are uniformly distributed on the lead screw (5) of the roller screw pair and a roller screw pair nut (3), single-line screw threads are arranged at the outside of the rollers (4), and the pitches of the single-line screw threads are equal to those of the lead screw (5) of the roller screw pair and the roller screw pair nut (3); the screw threads of the lead screw (5) of the roller screw pair and the roller screw pair nut (3) are engaged with the rollers (4); and a brake caliper block (2) and the roller screw nut (3) are fastened into a whole. A permanent magnet brushless DC servo control motor is utilized and a planetary roller screw serves as an actuating part, therefore, a gear retarding mechanism is saved, and the structure of the actuator is simpler.
Description
Technical field
The present invention relates to a kind of braking system final controlling element, particularly relate to a kind of vehicle electromechanical braking system final controlling element.
Background technique
In order to improve the active safety performance of automobile, extensively carried out the research that employing electric mechanical braking (hereinafter to be referred as EMB) system replaces traditional hydraulic braking sytem in recent years.Existing EMB generally adopts brush DC servocontrol motor or switched reluctance machines as drive unit, and realizing slowing down through reduction gears mechanism increases the function of turning round, and realizes friction catch by actuator at last.
Common actuator has two kinds of forms, i.e. wedge mechanism and ball screw pair again.General and the larger-size driven gear one of wedge mechanism promotes brake calipers piece realization braking thereby voussoir rotates and produce axial displacement with gear.Adopt ball screw pair leading screw to be linked to each other with output gear as the EMB of brake actuator, feed screw nut and brake calipers piece one, rotatablely moving of leading screw is converted into moving axially of nut and pad the most at last.
With reference to Fig. 9.Document " automotive engineering 2008.10P24-27 such as the development of vehicle electromechanical brake actuator and pressure estimation research [J] Yang Kun " discloses a kind of vehicle electromechanical brake actuator, and this vehicle electromechanical brake actuator comprises motor, planetary gear speed reducing mechanism and ball screw three parts.Wherein rotor 9 is made open-core type, and its nested inside has ball screw pair nut 8 and guarantees moving axially of ball screw pair nut 8, and ball screw pair nut 8 left ends are brake calipers piece 2 fixedly.The right-hand member of rotor 9 and the sun gear of planetary gear train 15 are affixed, and two parts rotate together; The right-hand member of motor stator 10 and the gear ring of planetary gear train 11 are affixed.Planet wheel 12 is installed on sun gear 15 and keeps its revolution with gear ring 11 inside and by planet carrier 13.Ball screw pair leading screw 14 is with planet carrier 13 one and with its rotation.
During braking system work, rotor 9 rotates with sun gear 15, slows down to increase through planetary gear train and turns round the back by retainer 13 output torques.Retainer 13 is with 14 rotations of ball screw pair leading screw, and ball screw pair nut 8 is converted into rotatablely moving of ball screw pair leading screw 14 straight line motion of ball screw pair nut 8 and promotes brake calipers piece 2 and compresses brake disc 1, realizes braking.
During brake off, rotor 9 is with sun gear 15 counterrotatings, slows down to increase through planetary gear train and turns round the back by retainer 13 output torques.Retainer 13 is with ball screw pair leading screw 14 rotation, and the rotatablely moving of ball screw adjutant ball screw pair leading screw 14 is converted into the straight line motion of ball screw pair nut 8 and drives brake calipers piece 2 loosens brake disc 1 compressed brake off.
Disclosed rotor 9 is hollow in the document, and nested inside has ball screw pair nut 8, adopts planetary gear reducing mechanism to realize slowing down to increase turning round.Wherein the sun gear 15 of planetary gear train is fixing with rotor 9, and the gear ring 11 of planetary gear train is fixing with motor stator 10, and the retainer 13 of planetary gear train is fixing with the leading screw 14 of ball screw pair.Owing to will consider the affixed of parts such as each part of planetary gear train and motor, leading screw, the complicated in mechanical structure of system.
Summary of the invention
In order to overcome the baroque deficiency of existing vehicle electromechanical brake actuator, the present invention provides a kind of vehicle electromechanical braking system final controlling element.This final controlling element adopts brshless DC motor to drive, and do-part is selected the planetary roller leading screw for use, owing to saved reduction gears mechanism, can make the actuating device structure simpler.
The technical solution adopted for the present invention to solve the technical problems is: a kind of vehicle electromechanical braking system final controlling element; Comprise brake disc 1, brake calipers piece 2 and motor 7; Brake calipers piece 2 double team brake discs 1 are characterized in also comprising roller screw pair nut 3, roller 4 and roller screw pair leading screw 5.Rotor 7-1, the motor output shaft 6 of said motor 7 are coaxial with roller screw pair leading screw 5, and are integrated.Roller screw pair leading screw 5 has identical rotation direction with roller screw pair nut 3, the helix of identical pitch, identical helical pitch, and roller screw pair nut 3 is an internal thread, roller screw pair leading screw 5 is an outside thread.Roller screw pair leading screw 5 is uniformly distributed with several rollers 4 with roller screw pair nut 3, and there is the worm tooth of single line the outside of roller 4, and its pitch is identical with the pitch of roller screw pair leading screw 5 and roller screw pair nut 3.The worm tooth of roller screw pair leading screw 5 and roller screw pair nut 3 all are meshed with roller 4.Brake calipers piece 2 fastens as one with roller screw pair nut 3.
Said motor 7 is DC permanent-magnetic brushless servocontrol motors.
The invention has the beneficial effects as follows: owing to adopt DC permanent-magnetic brushless servocontrol motor, do-part is selected the planetary roller leading screw for use, has saved reduction gears mechanism, makes that the actuating device structure is simpler.
Below in conjunction with accompanying drawing and embodiment the present invention is elaborated.
Description of drawings
Fig. 1 is the sectional view of vehicle electromechanical braking system final controlling element of the present invention.
Fig. 2 is roller screw pair leading screw among Fig. 1, motor output shaft and rotor integral structure figure.
Fig. 3 is the axle side enlarged view of Fig. 2.
Fig. 4 is that the axle of roller screw pair nut is surveyed enlarged view among Fig. 1.
Fig. 5 is that roller screw pair nut and brake calipers is packaged after joining axle are surveyed enlarged view among Fig. 1.
Fig. 6 is a ball screw auxiliary structure enlarged view among Fig. 1.
The free-body diagram of single wheel when Fig. 7 is braking.
The free-body diagram of brake disc and brake calipers when Fig. 8 is braking.
Fig. 9 is the sectional view of background technique vehicle electromechanical braking system final controlling element.
Among the figure, the 1-brake disc; 2-brake calipers piece; 3-roller screw pair nut; The 4-roller; 5-roller screw pair leading screw; The 6-motor output shaft; The 7-motor; The 7-1-rotor; 8-ball screw pair nut; The 9-rotor; The 10-motor stator; The 11-gear ring; The 12-planet wheel; The 13-retainer; 14-ball screw pair leading screw; The 15-sun gear; V is a vehicle traveling direction; F
XbBe ground braking force; W is the normal load of wheel; Tp is the thrust of axletree to wheel; Fz faces the normal direction holding power of wheel with being; F is the malleation of brake calipers piece to brake disc; R is the rolling radius of wheel.
Embodiment
It is that example is carried out designing and calculating that present embodiment is got one-sided front-wheel with Santana of Shanghai Automobile Factory 2000 vehicles, and its parameters is as shown in table 1 below:
Table .1 major parameter table
| Project | The Vehicle preparation quality | Tyre model | The brake disc external diameter | Radius of clean-up R |
| Parameter | 1140kg | 185/70R1386T | 256mm | ?106mm |
The front axle axle load is 60% when supposing stationary vehicle, and two-wheeled load in the left and right sides is identical.During braking, the stressing conditions of wheel is as shown in Figure 2.Fxb is a ground braking force, and W is that normal load, the Tp of wheel is that axletree is the positive pressure of friction lining to brake disc to the thrust of wheel, normal direction holding power, the F that Fz faces wheel for ground, and unit is N.R is the rolling radius of wheel, and R is effective radius of clean-up of brake disc, and unit is mm.
Consider the influence of the reach of axle load in the braking process, the front-wheel normal force will increase by 50% when static.Therefore can calculate Fz.
Suppose pitch or rigid pavement that braking process is being done; Tire sliding ratio 15%-20%, then the peak adhesion coefficient on road surface
is 0.9.Road surface maximum braking force then:
Because be two brake calipers piece chucking brake discs during braking, in order to give full play to the usefulness of brake module, the braking force on the brake disc must be greater than ground braking force.That is:
2FμR≥F
xbr (2)
F is that brake shoe positive pressure, μ are the drag friction factor, gets 0.4, R is that the brake disc radius of clean-up, r are vehicle wheel roll radius.
Calculating the ground maximum braking force by formula (1) is 4617N.By table 1 can calculate for tire rolling radius r be 294.48mm.Bring related data into formula (2) calculating and can get F >=16000N.
1) ball screw is selected for use.
Advantages such as ball screw has the transmission efficiency height, precision is high, synchronism is good, long service life.Therefore adopt rotatablely moving of ball screw adjutant motor to be converted into the straight line motion of nut in this brake module.
Given data is following:
Maximum axial work loads F=16000N, material selection GCr15, HRC=60-62.The maximum axial work loads is regarded as maximum dynamic load C, and tabling look-up and selecting used ball screw model is RV20X2.
In EMB when work,, the torque of roller screw pair leading screw should be by formula:
Calculate.With leading screw pitch p=2mm, the secondary efficiency eta of leading screw efficient=0.82, nut shaft gets T=6.214Nm to work loads F=16000N substitution following formula.
2) motor selects for use.
Electromechanical braking system requires motor to have characteristics such as high frequency sound, low inertia.And can satisfy maximum brake torque requirement, therefore preferentially select DC permanent-magnetic brushless servocontrol motor for use.
Power of motor should satisfy:
T=6.214Nm wherein, n is that the rated speed of motor is set at 2000r/m.The power of the motor that the substitution following formula is asked is 1.3kw.
With reference to Fig. 1～8.Vehicle electromechanical braking system final controlling element of the present invention comprises brake disc 1, brake calipers piece 2, roller screw pair nut 3, roller 4, roller screw pair leading screw 5, motor output shaft 6 and motor 7.Brake calipers piece 2 double team brake discs 1, the rotor 7-1 and the output shaft 6 of said motor 7 are coaxial with roller screw pair leading screw 5, and are one.Roller screw pair leading screw 5 is uniformly distributed with several rollers 4 with roller screw pair nut 3, and the worm tooth of roller screw pair leading screw 5 and roller screw pair nut 3 all are meshed with roller 4.Brake calipers piece 2 fastens as one with roller screw pair nut 3.
During installation, place motor stator inner rotor 7-1 earlier, accomplish the assembling of motor.Then the roller 4 of roller screw pair is circumferentially placed uniformly the inboard of roller screw pair nut 3.After treating that nut 3 and roller 4 assemblings are accomplished, the leading screw 5 and the motor output shaft 6 of roller screw pair together screwed in the spiral circumference of being made up of roller 4 (be connected similar) with bolt, nut.
Brake calipers piece 2 is circle with the external diameter of roller screw pair nut 3.Four countersunk head unthreaded holes that socket head screw is installed of the circumference uniform distribution of brake calipers piece 2.And, four tapped holes are arranged then in the left side of roller screw pair nut 3.During installation, alignment back, the hole on brake calipers piece 2 and the roller screw pair nut 3 is screwed in socket head screw, brake calipers piece 2 fastens as one with roller screw pair nut 3 like this.Therefore, brake calipers piece 2 can be realized axially doing with roller screw pair nut 3.
Roller screw pair leading screw 5 contains identical rotation direction with roller screw pair nut 3, the helix of identical pitch, identical helical pitch.Different is that roller screw pair nut 3 is internal thread, and roller screw pair leading screw 5 is an outside thread.Be uniformly distributed with 5-13 the circular roller 4 that number is different at roller screw pair leading screw 5 and roller screw pair nut 3, there is the worm tooth of single line the outside of roller 4, and its pitch is identical with the pitch of roller screw pair leading screw 5 and roller screw pair nut 3.
During work, roller screw pair leading screw 5 because the worm tooth of roller screw pair leading screw 5 is meshed with roller 4, drives roller 4 around 5 revolution and the rotations of roller screw pair leading screw for driving link rotates, and is similar to the planet wheel in the planetary gear train.Drive roller screw pair nut 3 again in the time of roller 4 motions and produce axial displacement.Finally, the brake calipers piece 2 of roller screw pair nut 3 its left ends of drive is realized braking and brake off together.
Electromechanical braking system final controlling element workflow:
During braking, the output shaft 6 of control motor 7 is with 5 rotations of roller screw pair leading screw, and roller screw pair leading screw 5 is meshed with the worm tooth of roller 4, drives roller 4 and produces rotation and revolution.Roller 4 drives the axial displacement that roller screw pair nut 3 produces left in the process of motion.Because roller screw pair nut 3 and brake calipers piece 2 one are so thereby brake calipers piece 2 is implemented the braking function that positive pressure realizes system with roller screw pair nut 3 to left movement and to brake disc 1.
During brake off, the output shaft 6 of control motor 7 is with 5 counterrotatings of roller screw pair leading screw, and roller screw pair leading screw 5 is meshed with the worm tooth of roller 4, drives roller 4 and produces rotation and revolution.Roller 4 drives the axial displacement that roller screw pair nut 3 produces left in the process of motion.Because roller screw pair nut 3 and brake calipers piece 2 one are so thereby brake calipers piece 2 is implemented the braking function that positive pressure realizes system with roller screw pair nut 3 to left movement and to brake disc 1.
Present embodiment is changed into the structural type of motor-actuator with the form of original motor-reducing gear-actuator, no longer adopts reducing gear.
Claims (2)
1. a vehicle electromechanical braking system final controlling element comprises brake disc (1), brake calipers piece (2) and motor (7), and brake calipers piece (2) double team brake disc (1) is characterized in that: also comprise roller screw pair nut (3), roller (4) and roller screw pair leading screw (5); Rotor (7-1), the motor output shaft (6) of said motor (7) are coaxial with roller screw pair leading screw (5), and are integrated; Roller screw pair leading screw (5) has identical rotation direction with roller screw pair nut (3), the helix of identical pitch, identical helical pitch, and roller screw pair nut (3) is an internal thread, roller screw pair leading screw (5) is an outside thread; Roller screw pair leading screw (5) is uniformly distributed with several rollers (4) with roller screw pair nut (3), and there is the worm tooth of single line the outside of roller (4), and its pitch is identical with the pitch of roller screw pair leading screw (5) and roller screw pair nut (3); The worm tooth of roller screw pair leading screw (5) and roller screw pair nut (3) all are meshed with roller (4); Brake calipers piece (2) fastens as one with roller screw pair nut (3).
2. vehicle electromechanical braking system final controlling element according to claim 1 is characterized in that: said motor (7) is a DC permanent-magnetic brushless servocontrol motor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012100060925A CN102562885A (en) | 2012-01-10 | 2012-01-10 | Electromechanical brake system actuator of automobiles |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012100060925A CN102562885A (en) | 2012-01-10 | 2012-01-10 | Electromechanical brake system actuator of automobiles |
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| Publication Number | Publication Date |
|---|---|
| CN102562885A true CN102562885A (en) | 2012-07-11 |
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ID=46409153
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2012100060925A Pending CN102562885A (en) | 2012-01-10 | 2012-01-10 | Electromechanical brake system actuator of automobiles |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114954405A (en) * | 2022-05-13 | 2022-08-30 | 燕山大学 | Motor redundancy's commercial car EMB drive-by-wire mechanical braking system executor |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3726151A (en) * | 1970-06-01 | 1973-04-10 | Skf Ind Trading & Dev | Adjustable screw and nut device |
| US5788023A (en) * | 1995-05-19 | 1998-08-04 | Continental Aktiengesellschaft | Brake actuator for an electrically actuable vehicle brake |
| US6098479A (en) * | 1997-08-23 | 2000-08-08 | Hoermansdoerfer; Gerd | Linear actuator and preferred application |
| EP1085240A1 (en) * | 1999-09-14 | 2001-03-21 | Nissan Motor Company, Limited | Electromechanical brake system |
| JP2004150533A (en) * | 2002-10-30 | 2004-05-27 | Nsk Ltd | Ball screw for electric brake device |
| US20060021831A1 (en) * | 2004-07-29 | 2006-02-02 | Ken Yamamoto | Electric brake assembly |
| US20100236877A1 (en) * | 2009-03-21 | 2010-09-23 | Schaeffler Technologies Gmbh & Co., Kg | Breaking device, in particular for a motor vehicle |
-
2012
- 2012-01-10 CN CN2012100060925A patent/CN102562885A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3726151A (en) * | 1970-06-01 | 1973-04-10 | Skf Ind Trading & Dev | Adjustable screw and nut device |
| US5788023A (en) * | 1995-05-19 | 1998-08-04 | Continental Aktiengesellschaft | Brake actuator for an electrically actuable vehicle brake |
| US6098479A (en) * | 1997-08-23 | 2000-08-08 | Hoermansdoerfer; Gerd | Linear actuator and preferred application |
| EP1085240A1 (en) * | 1999-09-14 | 2001-03-21 | Nissan Motor Company, Limited | Electromechanical brake system |
| JP2004150533A (en) * | 2002-10-30 | 2004-05-27 | Nsk Ltd | Ball screw for electric brake device |
| US20060021831A1 (en) * | 2004-07-29 | 2006-02-02 | Ken Yamamoto | Electric brake assembly |
| US20100236877A1 (en) * | 2009-03-21 | 2010-09-23 | Schaeffler Technologies Gmbh & Co., Kg | Breaking device, in particular for a motor vehicle |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114954405A (en) * | 2022-05-13 | 2022-08-30 | 燕山大学 | Motor redundancy's commercial car EMB drive-by-wire mechanical braking system executor |
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Application publication date: 20120711 |