CN103273957A - Non-circular-gear transmission type automobile steering device - Google Patents
Non-circular-gear transmission type automobile steering device Download PDFInfo
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- CN103273957A CN103273957A CN2013102079738A CN201310207973A CN103273957A CN 103273957 A CN103273957 A CN 103273957A CN 2013102079738 A CN2013102079738 A CN 2013102079738A CN 201310207973 A CN201310207973 A CN 201310207973A CN 103273957 A CN103273957 A CN 103273957A
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- circular gear
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Abstract
The invention provides a non-circular-gear transmission type automobile steering device which is characterized in that a pair of non-circular gears is used, and the non-circular gears are matched with each other. The left non-circular gear and the right non-circular gear drive a left steering wheel and a right steering wheel to steer respectively through a left transmission device and a right transmission device, so that two front steering wheels can be in pure rolling movement all the time in the steering process, and when the two front steering wheels steer left or right, the maximum continuous change of a steering angle can be 90 degrees, and stability of steering of an automobile can be increased. Abrasion of tires is reduced, energy is saved, flexibility is increased, and particularly parking, starting and u-turn can be conveniently carried out in short and small places.
Description
Technical field
The present invention relates to automobile steering transmission device.
Background technology
Trapezoidal four link type steering gear is widely used that on current automobile, as shown in Figure 1.
Trapezoidal double leval jib transmission mechanism is made up of track rod 1-2, left waist 1-1, right waist 1-3, trapezoidal bottom 1-4, and A is the pivoting point of left steering wheel I, and D is the pivoting point of right turn wheel II.
Left waist 1-1 and the one of left steering wheel I, right waist 1-3 and the one of right turn wheel II.
When left steering wheel I is rotated to the right, track rod 1-2, which moves right, promotes right waist 1-3, even if right turn wheel II is turned right, and because track rod 1-2 is shorter than trapezoidal bottom 1-4, therefore the corner of right turn wheel II is more than left steering wheel I.Required when turning to the left conversely, meeting to turn in this way.
Automobile is when turning to, and the extended line of two steering front wheel wheel shafts must be intersected in a point P in hind axle extended line, and otherwise steering front wheel occurs and ground friction, i.e., be not pure rolling, not only influences stability during automobile turning, also damages tire, also waste energy.
Trapezoidal four link type steering gear is easily fabricated, low cost.Weak point is it cannot be guaranteed that in all corners, two steering front wheels are to be in pure rolling, and rotational angle is limited by structure, it is impossible to rotate too big, within general 45 degree.If the friction of the excessive deflecting roller of corner can not just be ignored, steering moment can also diminish because angle becomes greatly, or even can not rotate.
At present, front-drive cars because drive shaft be cardan drive, transmission angle can not be too big, therefore the wide-angle that also limit forerunner's automobile steering front wheel is turned to.
The content of the invention
It is an object of the invention to provide a kind of non-circular gear drive formula auto steerer, to ensure that two steering front wheels are all run in pure rolling all the time in steering, and make preceding two deflecting roller in left and right steering, corner consecutive variations maximum is reachable 90 °.
Non-circular gear drive formula auto steerer of the present invention, it is characterized in that, coordinated using a pair of non-circular gears, left and right non-circular gear drives left and right deflecting roller to turn to by left and right transmission device respectively.
The present invention includes uni-drive gear box 1, Left Drive axle 2a, right power transmission shaft 2b, left umbrella tooth drives steering mechanism 4a, right umbrella tooth drives steering mechanism 4b, the non-circular gear 1a coordinated in uni-drive gear box 1 provided with a pair of meshing, 1b, active non-circular gear 1a is stretched on the shaft end in uni-drive gear box 1 installed in wheel steering machine take-off (propeller) shaft 1c, driven non-circular gear 1b is arranged in uni-drive gear box 1 by rotating shaft and engages cooperation with active non-circular gear 1a, left side bevel gear group 3a and right side umbrella tooth group 3b is additionally provided with uni-drive gear box 1, left side bevel gear group 3a driving bevel gear 3a1 and active non-circular gear 1a coaxial parallel-connections, driven bevel pinion 3a2 is connected with Left Drive axle 2a, right side bevel gear group 3b driving bevel gear 3b1 and driven non-circular gear 1b coaxial parallel-connections, driven bevel pinion 3b2 is connected with right power transmission shaft 2b, left umbrella tooth driving steering mechanism 4a driving bevel gear 4a1 and Left Drive axle 2a, which is installed, to be connected, driven bevel pinion 4a2 is installed with the steering spindle 5a of left steering wheel and is connected, right umbrella tooth driving steering mechanism 4b driving bevel gear 4b1 and right power transmission shaft 2b, which is installed, to be connected, install and be connected with the steering spindle 5b of right turn wheel from bevel gear 4b2, the side umbrella tooth group 3a in left side, left side drive shafts 2a, the gearratio and the side umbrella tooth group 3b on right side for the left side transmission device that left side umbrella tooth driving steering mechanism 4a is constituted, right side power transmission shaft 2b, the gearratio for the right side transmission device that right side umbrella tooth driving steering mechanism 4b is constituted is equal.
Referring to accompanying drawing 3.Distance between the pivoting point A of front left deflecting roller I and the pivoting point D of front right deflecting roller II is set to B；The wheelbase of vehicle front and trailing wheel is L.
The corner of front left deflecting roller I is, the corner of front right deflecting roller II is
,With
When must follow following relation, it just can guarantee that the wheel shaft extended line of front left deflecting roller I and the wheel shaft extended line of front right deflecting roller II always meet in a point P on hind axle extended line.
If variable PE is
； PC=
E is vertical points of the pivoting point D of front right deflecting roller II on trailing wheel axis；
C is vertical points of the pivoting point A of front left deflecting roller I on trailing wheel axis；
PE is the spacing between P points and E points；
PC is the spacing between P points and C points；
∵ 
=
∴ 
Pitch curve on non-circular gear pair is calculated：
The pitch curve radius of non-circular gear pair
、Following relationship should be met：
Wherein：
For the pitch curve radius of driven non-circular gear；
For the pitch curve radius of active non-circular gear；
= × (
) ＇
=
× × (
) ＇
=
×
×
×(
) ＇
∴
=
× 
× × 
After arrangement：
Solution linear equation in two unknowns group is drawn：
Then a pair of non-circular gear pitch curve radiuses can be drawn
With
Pitch curve figure, its be point symmetry figure.
If wheelbase
For 3 meters, the pivoting point spacing B of two deflecting rollers is 1.8 meters, a pair of the non-circular gear pitch curve radiuses drawn
With
Pitch curve figure, it is shown in Figure 4, in figure horizontal number axis 0,20 two points be respectively cooperation two non-circular gears axle center.
The non-circular gear pair manufactured by above-mentioned relation, active non-circular gear 1a angles of rotation=
When, driven non-circular gear 1b corners certainty=
。
Method of proof is as follows：
Active non-circular gear 1a angles of rotation=
When, then its pitch curve length turned over
Be necessarily equal to driven non-circular gear 1b angles of rotation=
The pitch curve length turned over
。
∵ 
Substitute into
Drawn according to bound with the requirement of variable change：
∵ 
So, active non-circular gear 1a angles of rotation=
When, driven non-circular gear 1b corners certainty=
.So can ensure that two steering front wheels are all run in pure rolling all the time in steering.
The present invention works as steering wheel rotation, steering machine drives the active non-circular gear 1a and passive non-circular gear 1b that engagement coordinates, the axle rotational angle of two non-circular gears is different, its angular relationship has been previously described in detail, active non-circular gear 1a and passive non-circular gear 1b drive left side bevel gear group 3a and right side umbrella tooth group 3b respectively, left side umbrella tooth group 3a driven bevel pinion 3a2 band Left Drive axles 2a, Left Drive axle 2a drives left umbrella tooth to drive steering mechanism 4a driving bevel gear 4a1, is rotated from steering spindle 5as of the bevel gear 4a2 with left steering wheel；Right side umbrella tooth group 3b driven bevel pinion 3b2 is with right power transmission shaft 2b, and right power transmission shaft 2b drives right umbrella tooth to drive steering mechanism 4b driving bevel gear 4b1, is rotated from steering spindle 5bs of the bevel gear 4b2 with right turn wheel.It is equal because side umbrella tooth group 3a, left side drive shafts 2a, left side umbrella tooth driving the steering mechanism 4a in the left side gearratios of left side transmission device constituted drive the gearratio of the right side transmission device of steering mechanism 4b compositions with the side umbrella tooth group 3b, right side power transmission shaft 2b, right side umbrella tooth on right side, that is the ratio of both gearratios is 1 to 1 relation, so active non-circular gear 1a and by active non-circular gear 1b corner be by grade ratio transmission, the corner of transmission front left deflecting roller I and the corner of front right deflecting roller II, realize the requirement of deflecting roller pure rolling respectively.
Non-circular gear rotational angle is equal to deflecting roller actual rotational angle, and left side transmission device, the gearratio of right side transmission device are 1.When the corner that non-circular gear is designed is more than steering wheel angle, that is when the corner ratio of non-circular gear and deflecting roller is q, left side transmission device, the gearratio of right side transmission device are 1/q, and same to ensure two deflecting rollers and the corresponding angle relation of non-circular gear, that is, it is pure rolling to ensure two deflecting rollers.
Provided with universal joint, i.e. power transmission shaft it is that two sections of the left and right axle connected by universal joint is constituted on Left Drive axle 2a and right power transmission shaft 2b for forerunner's independent suspension vehicle.
The present invention can make automobile increase the stability of bend, reduce tire wear, save energy, increase flexibility, particularly also can easily be stopped in very short and small place, carry car and u-turn.
Brief description of the drawings
Fig. 1 is prior art construction schematic diagram.
Fig. 2 is new embodiment structural representation of the present invention.
Fig. 3 is steering front wheel rotational angle schematic diagram of the present invention.
Fig. 4 is the pitch curve figure of embodiment of the present invention non-circular gear pair.
Embodiment
The present invention includes uni-drive gear box 1, Left Drive axle 2a, right power transmission shaft 2b, left umbrella tooth drives steering mechanism 4a, right umbrella tooth drives steering mechanism 4b, the non-circular gear 1a coordinated in uni-drive gear box 1 provided with a pair of meshing, 1b, active non-circular gear 1a is stretched on the shaft end in uni-drive gear box 1 installed in wheel steering machine take-off (propeller) shaft 1c, driven non-circular gear 1b is arranged in uni-drive gear box 1 by rotating shaft and engages cooperation with active non-circular gear 1a, left side bevel gear group 3a and right side umbrella tooth group 3b is additionally provided with uni-drive gear box 1, left side bevel gear group 3a driving bevel gear 3a1 and active non-circular gear 1a coaxial parallel-connections, driven bevel pinion 3a2 is connected with Left Drive axle 2a, right side bevel gear group 3b driving bevel gear 3b1 and driven non-circular gear 1b coaxial parallel-connections, driven bevel pinion 3b2 is connected with right power transmission shaft 2b, left umbrella tooth driving steering mechanism 4a driving bevel gear 4a1 and Left Drive axle 2a, which is installed, to be connected, driven bevel pinion 4a2 is installed with the steering spindle 5a of left steering wheel and is connected, right umbrella tooth driving steering mechanism 4b driving bevel gear 4b1 and right power transmission shaft 2b, which is installed, to be connected, install and be connected with the steering spindle 5b of right turn wheel from bevel gear 4b2, the side umbrella tooth group 3a in left side, left side drive shafts 2a, the gearratio and the side umbrella tooth group 3b on right side for the left side transmission device that left side umbrella tooth driving steering mechanism 4a is constituted, right side power transmission shaft 2b, the gearratio for the right side transmission device that right side umbrella tooth driving steering mechanism 4b is constituted is equal.
Claims (4)
1. non-circular gear drive formula auto steerer, it is characterized in that, coordinated using a pair of non-circular gears, left and right non-circular gear drives left and right deflecting roller to turn to by left and right transmission device respectively.
2. non-circular gear drive formula auto steerer according to claim 1, it is characterized in that, include uni-drive gear box (1), Left Drive axle (2a), right power transmission shaft (2b), left umbrella tooth driving steering mechanism (4a), right umbrella tooth driving steering mechanism (4b), non-circular gear (the 1a coordinated in uni-drive gear box (1) provided with a pair of meshing, 1b), active non-circular gear (1a) is stretched on the shaft end in uni-drive gear box (1) installed in wheel steering machine take-off (propeller) shaft (1c), driven non-circular gear (1b) is arranged in uni-drive gear box (1) by rotating shaft and engages cooperation with active non-circular gear (1a), left side bevel gear group (3a) and right side umbrella tooth group (3b) are additionally provided with uni-drive gear box (1), the driving bevel gear (3a1) of left side bevel gear group (3a) and active non-circular gear (1a) coaxial parallel-connection, driven bevel pinion (3a2) is connected with Left Drive axle (2a), the driving bevel gear (3b1) of right side bevel gear group (3b) and driven non-circular gear (1b) coaxial parallel-connection, driven bevel pinion (3b2) is connected with right power transmission shaft (2b), the driving bevel gear (4a1) of left umbrella tooth driving steering mechanism (4a) is installed with Left Drive axle (2a) to be connected, driven bevel pinion (4a2) is installed with the steering spindle (5a) of left steering wheel and is connected, the driving bevel gear (4b1) of right umbrella tooth driving steering mechanism (4b) is installed with right power transmission shaft (2b) to be connected, install and be connected with the steering spindle (5b) of right turn wheel from bevel gear (4b2), the side umbrella tooth group in left side（3a）, left side drive shafts（2a）, left side umbrella tooth driving steering mechanism（4a）The gearratio of the left side transmission device of composition and the side umbrella tooth group on right side（3b）, right side power transmission shaft（2b）, right side umbrella tooth driving steering mechanism（4b）The gearratio of the right side transmission device of composition is equal.
3. non-circular gear drive formula auto steerer according to claim 1 or 2, it is characterized in that, when the corner ratio of non-circular gear and deflecting roller is q, left side transmission device, the gearratio of right side transmission device are 1/q.
4. non-circular gear drive formula auto steerer according to claim 1 or 2, it is characterized in that, universal joint is provided with Left Drive axle (2a) and right power transmission shaft (2b).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013102079738A CN103273957A (en) | 2013-05-30 | 2013-05-30 | Non-circular-gear transmission type automobile steering device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013102079738A CN103273957A (en) | 2013-05-30 | 2013-05-30 | Non-circular-gear transmission type automobile steering device |
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| Publication Number | Publication Date |
|---|---|
| CN103273957A true CN103273957A (en) | 2013-09-04 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2013102079738A Pending CN103273957A (en) | 2013-05-30 | 2013-05-30 | Non-circular-gear transmission type automobile steering device |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105946969A (en) * | 2016-05-27 | 2016-09-21 | 北京航空航天大学 | Steering mechanism capable of solving steering problem of vehicle with balance rocker arm type chassis |
| US11945497B2 (en) | 2022-03-11 | 2024-04-02 | Gn Technologies Inc. | Vehicle steering wheels system |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001278091A (en) * | 2000-03-30 | 2001-10-10 | Kubota Corp | Riding paddy field working machine |
| JP2006062631A (en) * | 2004-08-30 | 2006-03-09 | Yoshio Abe | Apparatus for achieving nearly right angle steered angle of tire with different steered angle |
| CN101293534A (en) * | 2007-04-26 | 2008-10-29 | 上海市七宝中学 | Vehicle steering mechanism |
| JP2010023809A (en) * | 2008-07-24 | 2010-02-04 | Denso Corp | Actuator for driving vehicle |
| KR20100030742A (en) * | 2008-09-11 | 2010-03-19 | 최진만 | Self steering appratus |
| CN101791992A (en) * | 2009-12-30 | 2010-08-04 | 清华大学 | Automobile steering system |
-
2013
- 2013-05-30 CN CN2013102079738A patent/CN103273957A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001278091A (en) * | 2000-03-30 | 2001-10-10 | Kubota Corp | Riding paddy field working machine |
| JP2006062631A (en) * | 2004-08-30 | 2006-03-09 | Yoshio Abe | Apparatus for achieving nearly right angle steered angle of tire with different steered angle |
| CN101293534A (en) * | 2007-04-26 | 2008-10-29 | 上海市七宝中学 | Vehicle steering mechanism |
| JP2010023809A (en) * | 2008-07-24 | 2010-02-04 | Denso Corp | Actuator for driving vehicle |
| KR20100030742A (en) * | 2008-09-11 | 2010-03-19 | 최진만 | Self steering appratus |
| CN101791992A (en) * | 2009-12-30 | 2010-08-04 | 清华大学 | Automobile steering system |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105946969A (en) * | 2016-05-27 | 2016-09-21 | 北京航空航天大学 | Steering mechanism capable of solving steering problem of vehicle with balance rocker arm type chassis |
| US11945497B2 (en) | 2022-03-11 | 2024-04-02 | Gn Technologies Inc. | Vehicle steering wheels system |
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Application publication date: 20130904 |