CN102556157A - Front double-trapezoidal electric power steering mechanism - Google Patents
Front double-trapezoidal electric power steering mechanism Download PDFInfo
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- CN102556157A CN102556157A CN201010596602XA CN201010596602A CN102556157A CN 102556157 A CN102556157 A CN 102556157A CN 201010596602X A CN201010596602X A CN 201010596602XA CN 201010596602 A CN201010596602 A CN 201010596602A CN 102556157 A CN102556157 A CN 102556157A
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Abstract
The invention relates to a front double-trapezoidal electric power steering mechanism, which comprises a left trapezoidal arm, a left segmented transverse pull rod, a rack of a steering transmission mechanism, a trapezoidal mechanism and a corresponding steering transmission mechanism, wherein the trapezoidal mechanism consists of a right segmented transverse pull rod and a right trapezoidal arm. An included angle between the Front double-trapezoidal electric power steering mechanism or right segmented transverse pull rod of the trapezoidal mechanism and the rack of the steering transmission mechanism ranges from 11.5 degrees to 12.5 degrees. The front double-trapezoidal electric power steering mechanism solves the technical problem of poor maneuverability and steering capacity of existing steering mechanisms, and the smoothness factor of the steering mechanism is extremely close to one by adopting proper dimensional parameters.
Description
Technical field
The present invention relates to a kind of electric power steering mechanism.
Background technology
The function of steering gear is with the power output of deflector and the Motion Transmission steering swivel to the steeraxle both sides; Make both sides wheel flutter deflection, and it is as far as possible little to make two wheel flutter angle of inclination change when guaranteeing motor turning wheel and ground-surface slide relative according to certain rule.Transmission device mainly by pitman arm, steering drag link, track arm, steering trapezoidal arm (about) and tierod etc. form.
Usually, the car steering linkage mechanism design-calculated is fine or not, directly influences its manoevreability and turning ability.So in the design of steering gear, guarantee to have little turning ability, wheel can be done pure rolling around instantaneous center of turn in the time of also will guaranteeing to turn to as far as possible.Because of the steering gear on the automobile will be complementary with independent suspension, so select split type tie rod linkage.
During motor turning, each wheel is all only rolled do not slide, each wheel must rotate around a center-point O, and is as shown in Figure 1.Obviously this center will be dropped on the extended line of rear shaft center's line; And inside and outside front-wheel must be that rotate in the center of circle with this center-point O also; Be under the ideal situation, interior foreign steamer angle relation should satisfy the Ackermann steering geometry principle when turning to, and is called for short the Ackermam law:
ctgα＝ctgβ+B/L (1)
But in reality, be difficult in during the design of Vehicular turn tie rod linkage and all satisfy this condition in the whole steering range, just satisfy approx usually.So can only be to change the tie rod linkage size in the practical application as far as possible, foreign steamer corner curve be unlimited near foreign steamer curve in desirable in making; Because B, L are the fixed values in the automobile population parameter, when with β during as the independent variable of this model, parameter alpha is a dependent variable, can obtain the characteristic curve of perfect condition lower trapezoid mechanism according to formula (1).Specific as follows:
(the wheelspan wheelbase is the master data of a certain vehicle according to known wheelbase L, wheelspan LQ earlier; So in design as known quantity); Initial setting cross steering lever length (reaching in the past according to bulk, model elder generation just decides); And then can calculate B=1240 (distance between two main pin axis and ground intersection point) according to formula (2), with B and L substitution formula (1), the most frequent angle of wheel steering angle is 10 ° during motor turning usually; Here getting β is allowed to condition at as the independent variable of this model and increases by 0.05 ° (step-length of each computing is got 0.05 °) at every turn in 0 °～25 ° scopes; Matlab written program then capable of using calculates a series of α through formula 1, and then can simulate desirable inside and outside angular curve, like Fig. 2.
Relation below B parameter and front wheel tread and cross steering lever length satisfy:
B＝LQ-2ZB (2)
Wherein: the ZB-cross steering lever length.
The tie rod linkage of general-utility car can not satisfy the inside and outside desirable angle relation of wheel accurately, can only be with enough engineering precision near desirable tie rod linkage.L value no longer is the wheelbase of automobile in the actual tie rod linkage, but is worth L ' less than of wheelbase, and L '＜L; Referring to Fig. 3, if make L '/L=ξ, ξ is more near 1; The requirement that then tie rod linkage of this car just can more accurate reaction equation (1) turns to also just smooth and easy more.Therefore call the ride comfort coefficient that turns to ξ.
Summary of the invention
The object of the invention provides a kind of forward type double trapezoid electric power steering mechanism, and it adopts the suitable dimensions parameter, makes the ride comfort coefficient of steering hardware be in close proximity to 1, has solved the technical matters of existing steering hardware manoevreability and turning ability difference.
Technical solution of the present invention is:
A kind of forward type double trapezoid electric power steering mechanism, it comprise by left ladder type arm, part on the left side segmentation intermediate rod, steering gear tooth bar, part ladder type mechanism and corresponding steering gear that segmentation intermediate rod and right ladder type arm constitute on the right side;
Its special character is:
The angle that parts the segmentation intermediate rod on the left side or part on the right side between the tooth bar of segmentation intermediate rod and steering gear of said tie rod linkage is 11.5 ° to 12.5 °.
Above-mentioned steering gear comprises the gear of electrical motor, Worm and worm-wheel gearing, differential gear train mechanism and rack and pinion drive mechanism; The worm screw 1 of said Worm and worm-wheel gearing is driven by electrical motor 9; The worm gear 2 of said Worm and worm-wheel gearing and the big sun wheel of differential gear train 5 coaxial being connected; The small sun gear 3 of said differential gear train and steering axles 8 coaxial being connected; The center shaft of the satellite gear 4 of said differential gear train and the gear of rack and pinion drive mechanism 6 coaxial being connected; The gear 6 of said rack and pinion drive mechanism can drive tooth bar 7 drive wheels and turn to.
The angle that parts the segmentation intermediate rod on the left side or part on the right side between the tooth bar of segmentation intermediate rod and steering gear of above-mentioned tie rod linkage is 12 °.
The present invention has following advantage:
It is 12 ° that the present invention selects the angle that parts the segmentation intermediate rod on the left side or part on the right side between the tooth bar of segmentation intermediate rod and steering gear of tie rod linkage; Make the ride comfort coefficient of steering hardware be in close proximity to 1, steering hardware manoevreability and turning ability are optimized and promote.
It is consistent or approaching that the present invention need not satisfy the rotating speed of rotating speed and bearing circle behind the motor deceleration.Differential gear train mechanism has two degree of freedom, and promptly given two input motions can have definite output movement.When chaufeur turned to, the mean speed that different people acts on the bearing circle was different, and different road conditions when turning to mean speed also different.And the electrical motor of selecting can only provide the rotating speed of confirming numerical value according to fixing transmitting ratio.When directly adopting the worm gearing power-assisted, then preferably require two tachometer values equal or approaching, otherwise the steering shaft life-span is reduced.Lift a simple example: people pulls a cart harder, if a guy's help is drawn together, the muscle power that then everyone paid can obviously reduce.But precondition must let two people act in agreement, and promptly will guarantee that still the degree of freedom of car is 1 after two people's combineds action.
Description of drawings
Fig. 1 when turning under the ideal situation in foreign steamer angle relation scheme drawing; Wherein: the wheel base of L-automobile; Distance between B-two main pin axis and ground intersection point: α-outboard wheels deflection angle; β-inboard wheel deflection angle; The R-minimum turning radius;
Fig. 2 is an interior foreign steamer angle Curve under the ideal state;
Fig. 3 when turning under the actual conditions in foreign steamer angle relation scheme drawing;
Fig. 4 is the structural representation of rack and pinion steering gear forward type double trapezoid steering hardware of the present invention; Wherein: D-tooth bar two ends ball pivot width between centers; φ-sectional type intermediate rod and steering box angle; E-sectional type intermediate rod length; The W-steering box is apart from the mounting distance of front axle; θ-tie rod arm is installed the base angle; N-steering trapezium arm lengths;
Fig. 5 is the structure diagram of rack and pinion steering gear forward type double trapezoid steering hardware of the present invention; Wherein: the distance between B-two main pin axis and ground intersection point; The M-tierod; The N-steering trapezoidal arm; The wheel base of L-automobile; θ-installation base angle;
Fig. 6 be φ=12 when spending trapezoidal in foreign steamer corner calculated curve and theoretical curve graph of a relation;
Fig. 7 is the structural principle scheme drawing of steering gear of the present invention;
Fig. 8 is the structural representation of steering gear of the present invention.
The specific embodiment
Rack and pinion steering mechanism self has the sectional type intermediate rod, regards it as integral type intermediate rod with simplified design, and doing like this to influence the design-calculated precision.Known parameters: L, B; Need definite parameter: tierod M, steering trapezoidal arm N installs base angle θ.
Among Fig. 6 solid line represent desirable in foreign steamer corner curve, the steering curve of counter structure emulation gained data fitting when the dotted line line is represented φ=12 °, one group of data when * point is represented actual computation.One group of data that corresponding geometric parameter was calculated when φ=12 ° were described near desirable cornering properties curve so finally confirm that the tie rod linkage parameter is in the EPS model: B=1240mm; D=562mm; N=213mm; E=255.59mm; W=137.15mm; φ=12 °; θ=63.3 °.
Claims (3)
1. forward type double trapezoid electric power steering mechanism, it comprise by left ladder type arm, part on the left side segmentation intermediate rod, steering gear tooth bar, part ladder type mechanism and corresponding steering gear that segmentation intermediate rod and right ladder type arm constitute on the right side;
It is characterized in that:
The angle that parts the segmentation intermediate rod on the left side or part on the right side between the tooth bar of segmentation intermediate rod and steering gear of said tie rod linkage is 11.5 ° to 12.5 °.
2. forward type double trapezoid electric power steering according to claim 1 mechanism, it is characterized in that: said steering gear comprises the gear of electrical motor, Worm and worm-wheel gearing, differential gear train mechanism and rack and pinion drive mechanism; The worm screw of said Worm and worm-wheel gearing is by direct motor drive; Coaxial being connected of big sun wheel of the worm gear of said Worm and worm-wheel gearing and differential gear train; The small sun gear of said differential gear train is connected with steering axles is coaxial; The center shaft of the satellite gear of said differential gear train is connected with the gear of rack and pinion drive mechanism is coaxial; The gear of said rack and pinion drive mechanism can drive the rack drives wheel steering.
3. forward type double trapezoid electric power steering according to claim 1 and 2 mechanism is characterized in that: the angle that parts the segmentation intermediate rod on the left side or part on the right side between the tooth bar of segmentation intermediate rod and steering gear of said tie rod linkage is 12 °.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010596602XA CN102556157A (en) | 2010-12-20 | 2010-12-20 | Front double-trapezoidal electric power steering mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010596602XA CN102556157A (en) | 2010-12-20 | 2010-12-20 | Front double-trapezoidal electric power steering mechanism |
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| Publication Number | Publication Date |
|---|---|
| CN102556157A true CN102556157A (en) | 2012-07-11 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201010596602XA Pending CN102556157A (en) | 2010-12-20 | 2010-12-20 | Front double-trapezoidal electric power steering mechanism |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107704692A (en) * | 2017-10-12 | 2018-02-16 | 西安工业大学 | A kind of global optimization computation method of ackerman steering |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1587941A (en) * | 2004-09-22 | 2005-03-02 | 湖北汽车工业学院 | Automobile electric power-assisted steering mechanism using magnetic sensitive torque sensor |
| CN201052790Y (en) * | 2007-02-14 | 2008-04-30 | 杭州世宝汽车方向机有限公司 | Gear form synchronization belt decelerating electric power assistant steering mechanism |
| EP1650103B1 (en) * | 2004-10-25 | 2008-09-10 | Denso Corporation | Vehicular steering apparatus with capability of providing suitable steering angle correction and power assistance |
| CN201347125Y (en) * | 2008-12-05 | 2009-11-18 | 北京理工大学 | Electric power steering mechanism having coupling control of force and displacement |
-
2010
- 2010-12-20 CN CN201010596602XA patent/CN102556157A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1587941A (en) * | 2004-09-22 | 2005-03-02 | 湖北汽车工业学院 | Automobile electric power-assisted steering mechanism using magnetic sensitive torque sensor |
| EP1650103B1 (en) * | 2004-10-25 | 2008-09-10 | Denso Corporation | Vehicular steering apparatus with capability of providing suitable steering angle correction and power assistance |
| CN201052790Y (en) * | 2007-02-14 | 2008-04-30 | 杭州世宝汽车方向机有限公司 | Gear form synchronization belt decelerating electric power assistant steering mechanism |
| CN201347125Y (en) * | 2008-12-05 | 2009-11-18 | 北京理工大学 | Electric power steering mechanism having coupling control of force and displacement |
Non-Patent Citations (1)
| Title |
|---|
| 杨芬: "汽车电动助力转向系统操纵性能分析和模型仿真研究", 《西安理工大学硕士学位论文》 * |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107704692A (en) * | 2017-10-12 | 2018-02-16 | 西安工业大学 | A kind of global optimization computation method of ackerman steering |
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Application publication date: 20120711 |