CN108001517B - Steering transmission mechanism - Google Patents
Steering transmission mechanism Download PDFInfo
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- CN108001517B CN108001517B CN201610969420.XA CN201610969420A CN108001517B CN 108001517 B CN108001517 B CN 108001517B CN 201610969420 A CN201610969420 A CN 201610969420A CN 108001517 B CN108001517 B CN 108001517B
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- transmission
- central shaft
- ball
- driving
- guide rail
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D3/00—Steering gears
- B62D3/02—Steering gears mechanical
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Power Steering Mechanism (AREA)
- Friction Gearing (AREA)
Abstract
The invention provides a steering transmission mechanism and a vehicle, wherein the steering transmission mechanism comprises: a driving part and a driven part; the transmission ball is provided with a central shaft, the transmission ball can rotate around the central shaft, the driving part and the driven part are respectively attached to and matched with the transmission ball in a leaning mode so that the driving part can drive the driven part to rotate through the transmission ball, and the central shaft can rotate around a transmission ratio adjusting axis of the transmission ball, so that linear distances between the driving part and the central shaft and between the driven part and the central shaft are changed, and the transmission ratio is changed. The steering transmission mechanism can enable steering to be more accurate, is simple in structure and has low requirement on arrangement space.
Description
Technical Field
The invention relates to the technical field of vehicles, in particular to a steering transmission mechanism.
Background
The variable transmission ratio of the steering system in the related art mostly adopts a planetary gear mechanism, the structure needs to arrange a planetary gear carrier in the mechanism, needs to transmit a plurality of pairs of gears, and has the disadvantages of complex structure, high machining precision requirement and difficult control of assembly clearance.
Disclosure of Invention
In view of the above, the present invention is directed to a steering transmission mechanism, so as to make steering more accurate, simplify the structure, and reduce the requirement for the layout space.
In order to achieve the purpose, the technical scheme of the invention is realized as follows:
a steering gear, comprising: a driving part and a driven part; the transmission ball is provided with a central shaft, the transmission ball can rotate around the central shaft, the driving part and the driven part are respectively attached to and matched with the transmission ball in a leaning mode so that the driving part can drive the driven part to rotate through the transmission ball, and the central shaft can rotate around a transmission ratio adjusting axis of the transmission ball, so that linear distances between the driving part and the central shaft and between the driven part and the central shaft are changed, and the transmission ratio is changed.
Further, the steering transmission mechanism further includes: the two ends of the central shaft can respectively slide along the first guide rail and the second guide rail.
Further, the transmission ball is a round ball, and the first guide rail and the second guide rail are part of a circular guide rail.
Further, the driving member includes: the peripheral surface of the driving wheel is a concave spherical surface so as to be attached to the transmission ball; the follower includes: the outer peripheral surface of the driven wheel is a concave spherical surface so as to be attached to the transmission ball.
Further, the steering transmission mechanism further includes: and the output shaft of the first driving motor and the output shaft of the second driving motor are respectively connected with two ends of the central shaft so as to drive the central shaft to rotate around the transmission ratio adjusting axis of the transmission ball.
Furthermore, an output shaft of the first driving motor is connected with a first lead screw, the first lead screw is matched with a first transmission block, and the first transmission block is fixed at one end of the central shaft;
and an output shaft of the second driving motor is connected with a second lead screw, the second lead screw is matched with a second transmission block, and the second transmission block is fixed at the other end of the central shaft.
Further, a transmission bearing is arranged between the central shaft and the transmission ball.
Furthermore, a shoulder and a clamp spring groove are arranged on the central shaft, a clamp spring is arranged in the clamp spring groove, and the transmission bearing is arranged between the shoulder and the clamp spring.
Further, the steering transmission mechanism further includes: the casing, the driving piece with be provided with the driving piece bearing between the casing, the follower with be provided with the follower bearing between the casing, first guided way with the second guided way sets up on the inside wall of casing.
Furthermore, the outer peripheral surface of the transmission ball is provided with transmission ball gear teeth, the driving part is provided with driving part gear teeth, the driven part is provided with driven part gear teeth, the driving part gear teeth and the driven part gear teeth are respectively meshed with the transmission ball gear teeth, and the driving part gear teeth and the driven part gear teeth can slide along the transmission ball gear teeth.
Compared with the prior art, the steering transmission mechanism has the following advantages:
the steering transmission mechanism has the advantages of simple overall structure and small occupied space, and the transmission ratio between the driving part and the driven part can be adjusted in a stepless manner.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate an embodiment of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:
FIG. 1 is a schematic view of a steering gear according to an embodiment of the present invention;
FIG. 2 is a partial schematic view of a steering gear according to an embodiment of the present invention;
FIG. 3 is a partial exploded view of the steering gear according to an embodiment of the present invention;
fig. 4 is an exploded view of the central shaft and drive bearing combination according to an embodiment of the present invention.
Description of reference numerals:
the steering transmission mechanism 100 is provided with a steering transmission mechanism,
a driving member 110, an input shaft 111, a driving wheel 112, a driving member bearing 113,
a follower 120, an output shaft 121, a follower 122, a follower bearing 123,
a drive ball 130, a central shaft 131, a first end 131a, a second end 131b, a drive bearing 132, a shoulder 133, a snap spring 134, a snap spring groove 101,
a first driving motor 161, a second driving motor 162,
the first lead screw 171, the second lead screw 172,
the first transmission block 181 is provided with a first transmission block,
Detailed Description
It should be noted that the embodiments and features of the embodiments may be combined with each other without conflict.
The steering transmission mechanism 100 of the present invention will be described in detail with reference to the embodiments with reference to the drawings.
As shown in fig. 1 to 3, a steering gear 100 according to an embodiment of the present invention may include a driving member 110, a driven member 120, and a drive ball 130.
The driving ball 130 has a central axis 131, the driving ball 130 can rotate around the central axis 131, and the driving element 110 and the driven element 120 are respectively attached to the driving ball 130 so that the driving element 110 drives the driven element 120 to rotate through the driving ball 130.
In other words, the driving member 110 drives the driving ball 130 to rotate, and then the driving ball 130 drives the driven member 120 to rotate, thereby completing the power transmission from the driving member 110 to the driven member 120.
It will be appreciated that the center shaft 131 passes through the center of the drive ball 130 or the extension of the center shaft 131 passes through the center of the drive ball 130, so that the drive ball 130 can be stably rotated without eccentric rotation, which is important to the stability of the driving member 110 and the driven member 120 during operation.
The central shaft 131 may rotate about the transmission ratio adjustment axis of the transmission ball 130, thereby changing a linear distance between the driving member 110 and the central shaft 131 and a linear distance between the driven member 120 and the central shaft 131.
The central shaft 131 can rotate around the transmission ratio adjustment axis of the transmission ball 130, and since the positions of the driving element 110 and the driven element 120 are not changed, the linear distance between the driving element 110 and the central shaft 131 and the linear distance between the driven element 120 and the central shaft 131 are changed.
Therefore, the purpose of changing the transmission ratio between the driving part 110 and the driven part 120 is achieved, the transmission ratio between the driving part 110 and the driven part 120 can be changed under different working conditions of the vehicle, and the steering accuracy is improved.
The steering transmission mechanism 100 of the embodiment of the invention has the advantages of simple structure, easy installation and low requirement on arrangement space, and can change the transmission ratio between the driving part 110 and the driven part 120 in a stepless manner, thereby steering more conveniently and accurately.
It can be understood that the transmission ratio adjustment axis of the transmission ball 130 passes through the center of the sphere, that is, the central shaft 131 can rotate around its own midpoint (center of the sphere), so that the transmission ball 130 does not rotate eccentrically, and the driving member 110 and the driven member 120 are ensured to rotate only around their own axes without shifting in three directions, thereby ensuring the stability of the operation of the driving member 110 and the driven member 120.
The central shaft 131 has a first end 131a and a second end 131b, the first end 131a is located on the same side of the driving member 110, and the second end 131b is located on the same side of the driven member 120. When the first end 131a is far away from the driving part 110, the straight distance (R shown in fig. 1) of the driving part 110 from the central axis 131 becomes large; meanwhile, the second end 131b is close to the driven member 120, the linear distance (r shown in fig. 1) from the central axis 131 of the driven member 120 becomes smaller, and the transmission ratio between the driving member 110 and the driven member 120 becomes smaller.
When the first end 131a approaches the driving part 110, the linear distance from the driving part 110 to the central axis 131 becomes smaller; meanwhile, the second end 131b is far away from the driven member 120, the linear distance from the driven member 120 to the central axis 131 is increased, and the transmission ratio between the driving member 110 and the driven member 120 is increased.
Thus, the change of the transmission ratio between the driving part 110 and the driven part 120 can be achieved by the rotation of the transmission ball 130 about the transmission ratio adjustment axis of the transmission ball 130, and since the spherical surface of the transmission ball 130 is always in smooth contact with the driving part 110 and the driven part 120, the stepless speed change between the driving part 110 and the driven part 120 can be achieved.
As shown in fig. 1, the steering gear 100 according to the embodiment of the present invention further includes a first guide rail 140 and a second guide rail 150 facing each other, and both ends of the central shaft 131 can slide along the first guide rail 140 and the second guide rail 150, respectively. The first guide rail 140 and the second guide rail 150 are formed in the same shape as the driving ball 130.
Specifically, the first end 131a of the central shaft 131 can slide along the first guide rail 140, and the second end 131b of the central shaft 131 can slide along the second guide rail 150, thereby enabling the central shaft 131 to rotate about the transmission ratio adjustment axis of the transmission ball 130.
The drive ball 130 of the present embodiment is a circular ball and the first guide rail 140 and the second guide rail 150 are portions of a circular guide rail. The transmission ball 130 is a round ball, so that the transmission ball 130 cannot force the driving member 110 and the driven member 120 to move in the rotating process, and the driving member 110 and the driven member 120 only rotate around respective axes, thereby ensuring the running stability of the driving member 110 and the driven member 120.
In a particular example of the present invention, the ratio adjustment axis is orthogonal to the plane formed by the first guide rail 140 and the second guide rail 150, and the ratio adjustment axis passes through the center of the sphere of the drive ball 130.
Of course, it is understood that the transmission ratio adjustment axis is not limited to the above-mentioned one, as long as it is ensured that the linear distance between the driving member 110 and the intermediate shaft 131 and the linear distance between the driven member 120 and the intermediate shaft 131 are changed when the central shaft 131 rotates around the transmission ratio adjustment axis. The gear ratio adjustment axis may vary with the position of the first guide rail 140 and the second guide rail 150.
Specifically, the driving member 110 includes an input shaft 111 and a driving wheel 112, and an outer peripheral surface of the driving wheel 112 is a concave spherical surface to be attached to the transmission ball 130; the follower 120 includes an output shaft 121 and a follower 122, and the outer peripheral surface of the follower 122 is a concave spherical surface to be fitted with the transmission ball 130.
Therefore, the driving wheel 112 and the driven wheel 122 are ensured to be tightly attached to the transmission balls 130, power transmission between the driving wheel 112 and the transmission balls 130 is realized by friction force, and power transmission between the transmission balls 130 and the driven wheel 122 is realized by friction force.
Of course, it will be appreciated that the transmission of power between the driving member 110 and the drive ball 130, and between the drive ball 130 and the driven member 120, may be accomplished in other ways.
For example, the driving ball 130 may have driving ball gear teeth on an outer circumferential surface thereof, the driving wheel 112 may have driving member gear teeth thereon, the driven wheel 122 may have driven member gear teeth thereon, the driving member gear teeth and the driven member gear teeth may be respectively engaged with the driving ball gear teeth, and the driving member gear teeth and the driven member gear teeth may slide along the driving ball gear teeth. Thereby achieving power transmission between the driving member 110 and the driven member 120 and a change in the transmission ratio between the driving member 110 and the driven member 120.
In some embodiments of the present invention, as shown in fig. 1 to 3, the steering transmission mechanism 100 further includes a first driving motor 161 and a second driving motor 162, and an output shaft of the first driving motor 161 and an output shaft of the second driving motor 162 are respectively connected to both ends of the central shaft 131 to drive the central shaft 131 to rotate about the transmission ratio adjustment axis of the transmission ball 130.
Specifically, the output shaft of the first driving motor 161 is connected to a first lead screw 171, the first lead screw 171 is engaged with a first transmission block 181, and the first transmission block 181 is fixed to the first end 131a of the central shaft 131. The output shaft of the first driving motor 161 can drive the first lead screw 171 to rotate, and the first lead screw 171 is matched with the first transmission block 181, so that the rotary motion of the output shaft of the first driving motor 161 can be converted into linear motion, and the first end 131a of the central shaft 131 is driven to move up and down.
The output shaft of the second driving motor 162 is connected to a second lead screw 172, and the second lead screw 172 is engaged with a second transmission block (not shown) fixed to the second end 131b of the central shaft 131. The output shaft of the second driving motor 162 can drive the second lead screw 172 to rotate, and the second lead screw 172 is matched with the second transmission block, so that the rotary motion of the output shaft of the second driving motor 162 can be converted into linear motion, and the second end 131b of the central shaft 131 is driven to move up and down.
A transmission bearing 132 is arranged between the central shaft 131 and the transmission ball 130, the outer ring of the transmission bearing 132 is in interference fit with the transmission ball 130, and the inner ring of the transmission bearing 132 is in interference fit with the central shaft 131. Optionally, the drive bearing 132 is a needle bearing.
As shown in fig. 4, a shoulder 133 and a snap spring groove 101 are formed on the central shaft 131, a snap spring 134 is disposed in the snap spring groove 101, an outer diameter of the snap spring 134 is larger than that of the central shaft 130, and the transmission bearing 132 can be clamped between the shoulder 133 and the snap spring 134. Thus, the drive bearing 132 is easily installed and removed.
In some embodiments of the present invention, as shown in fig. 1, the steering transmission mechanism 100 further includes a housing 190, a driving member bearing 113 is disposed between the driving member 110 and the housing 190, and a driven member bearing 123 is disposed between the driven member 120 and the housing 190. Thereby ensuring smooth rotation of the driving member 110 and the driven member 120 with respect to the housing 190.
Further, the first guide rail 140 and the second guide rail 150 are disposed on the inner side wall of the housing 190, and both ends of the central shaft 131 slide in the first guide rail 140 and the second guide rail 150, respectively.
The vehicle of the embodiment of the invention is briefly described below.
The vehicle according to the embodiment of the invention comprises the steering transmission mechanism 100 of the embodiment, and the vehicle according to the embodiment of the invention is provided with the steering transmission mechanism 100, so that the vehicle is convenient to steer, the aim of steplessly changing the transmission ratio between the driving part 110 and the driven part 120 can be fulfilled, and the steering of the vehicle is more stable and accurate.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.
Claims (9)
1. A steering gear (100), comprising:
a driving part (110) and a driven part (120);
a transmission ball (130), wherein the transmission ball (130) is provided with a central shaft (131), the transmission ball (130) can rotate around the central shaft (131), the driving part (110) and the driven part (120) are respectively in abutting fit with the transmission ball (130) so that the driving part (110) drives the driven part (120) to rotate through the transmission ball (130), and the central shaft (131) can rotate around a transmission ratio adjusting axis of the transmission ball (130), so that the linear distances between the driving part (110) and the central shaft (131) and between the driven part (120) and the central shaft (131) are changed, and the transmission ratio is changed;
the outer peripheral surface of transmission ball (130) is provided with the transmission ball teeth of a cogwheel, be provided with the driving part teeth of a cogwheel on driving part (110), be provided with the follower teeth of a cogwheel on follower (120), the driving part teeth of a cogwheel with the follower teeth of a cogwheel respectively with the meshing of transmission ball teeth of a cogwheel just the driving part teeth of a cogwheel with the follower teeth of a cogwheel can be followed the transmission ball teeth of a cogwheel slide.
2. The steering gear (100) according to claim 1, further comprising: the guide rail comprises a first guide rail (140) and a second guide rail (150) which are opposite to each other, and two ends of the central shaft (131) can respectively slide along the first guide rail (140) and the second guide rail (150).
3. The steering gear (100) according to claim 2, wherein the drive ball (130) is a spherical ball and the first guide rail (140) and the second guide rail (150) are part of a circular guide rail.
4. The steering gear (100) according to claim 1, wherein the driving member (110) comprises: the input shaft (111) and the driving wheel (112), the peripheral surface of the driving wheel (112) is a concave spherical surface so as to be attached to the transmission ball (130);
the follower (120) includes: and an output shaft (121) and a driven wheel (122), wherein the outer peripheral surface of the driven wheel (122) is a concave spherical surface so as to be attached to the transmission ball (130).
5. The steering gear (100) according to claim 1, further comprising: the transmission mechanism comprises a first driving motor (161) and a second driving motor (162), wherein an output shaft of the first driving motor (161) and an output shaft of the second driving motor (162) are respectively connected with two ends of a central shaft (131) so as to drive the central shaft (131) to rotate around a transmission ratio adjusting axis of the transmission ball (130).
6. The steering gear (100) according to claim 5, wherein the output shaft of the first drive motor (161) is connected to a first lead screw (171), the first lead screw (171) being engaged with a first transmission block (181), the first transmission block (181) being fixed to one end of the central shaft (131);
an output shaft of the second driving motor (162) is connected with a second lead screw (172), the second lead screw (172) is matched with a second transmission block, and the second transmission block is fixed to the other end of the central shaft (131).
7. Steering gear (100) according to claim 6, characterized in that a drive bearing (132) is arranged between the central shaft (131) and the drive ball (130).
8. The steering gear (100) according to claim 7, wherein the central shaft (131) is provided with a shoulder (133) and a circlip groove (101), wherein a circlip (134) is provided in the circlip groove (101), and wherein the gear bearing (132) is provided between the shoulder (133) and the circlip (134).
9. The steering gear (100) according to claim 2, further comprising: the bearing device comprises a shell (190), a driving part bearing (113) is arranged between the driving part (110) and the shell (190), a driven part bearing (123) is arranged between the driven part (120) and the shell (190), and the first guide rail (140) and the second guide rail (150) are arranged on the inner side wall of the shell (190).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610969420.XA CN108001517B (en) | 2016-10-28 | 2016-10-28 | Steering transmission mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610969420.XA CN108001517B (en) | 2016-10-28 | 2016-10-28 | Steering transmission mechanism |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108001517A CN108001517A (en) | 2018-05-08 |
| CN108001517B true CN108001517B (en) | 2020-06-09 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610969420.XA Active CN108001517B (en) | 2016-10-28 | 2016-10-28 | Steering transmission mechanism |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108001517B (en) |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1104731A (en) * | 1993-12-30 | 1995-07-05 | 李蕴藻 | Stepless speed change with centrigual friction |
| FR2996276A1 (en) * | 2012-09-28 | 2014-04-04 | Renault Sa | Continuously variable speed transmission for use as automatic transmission in e.g. electric car, has actuating element cooperating with support to swivel axis relative to frame to vary transmission ratio between input and output shafts |
| CN105402343A (en) * | 2008-08-26 | 2016-03-16 | 福博科知识产权有限责任公司 | Continuously Variable Transmission |
| CN105443710A (en) * | 2015-12-16 | 2016-03-30 | 山东农业大学 | Friction-ball power split type continuously variable transmission |
-
2016
- 2016-10-28 CN CN201610969420.XA patent/CN108001517B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1104731A (en) * | 1993-12-30 | 1995-07-05 | 李蕴藻 | Stepless speed change with centrigual friction |
| CN105402343A (en) * | 2008-08-26 | 2016-03-16 | 福博科知识产权有限责任公司 | Continuously Variable Transmission |
| FR2996276A1 (en) * | 2012-09-28 | 2014-04-04 | Renault Sa | Continuously variable speed transmission for use as automatic transmission in e.g. electric car, has actuating element cooperating with support to swivel axis relative to frame to vary transmission ratio between input and output shafts |
| CN105443710A (en) * | 2015-12-16 | 2016-03-30 | 山东农业大学 | Friction-ball power split type continuously variable transmission |
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| Publication number | Publication date |
|---|---|
| CN108001517A (en) | 2018-05-08 |
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