WO2023116543A1 - 一种折叠方向盘 - Google Patents

一种折叠方向盘 Download PDF

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Publication number
WO2023116543A1
WO2023116543A1 PCT/CN2022/139248 CN2022139248W WO2023116543A1 WO 2023116543 A1 WO2023116543 A1 WO 2023116543A1 CN 2022139248 W CN2022139248 W CN 2022139248W WO 2023116543 A1 WO2023116543 A1 WO 2023116543A1
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WIPO (PCT)
Prior art keywords
steering wheel
gear
wheel according
folding steering
folding
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PCT/CN2022/139248
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English (en)
French (fr)
Inventor
唐勋
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延锋国际汽车技术有限公司
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Publication of WO2023116543A1 publication Critical patent/WO2023116543A1/zh

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D1/00—Steering controls, i.e. means for initiating a change of direction of the vehicle
    • B62D1/02—Steering controls, i.e. means for initiating a change of direction of the vehicle vehicle-mounted
    • B62D1/04—Hand wheels

Definitions

  • the invention relates to an automobile steering wheel, more particularly to a folding steering wheel.
  • the steering wheel folding mechanism of automobiles is mostly a motor combined with a gearbox or a screw mechanism, which is difficult to meet the performance of steering wheel clearance/strength/durability. Therefore, there is an urgent need for a steering wheel folding adjustment mechanism with zero clearance/high strength/durability in the market.
  • the present invention provides a folding steering wheel.
  • the folding steering wheel of the present invention includes a steering wheel and an adjustment mechanism, the output shaft of the adjustment mechanism is fixedly connected with the steering wheel to drive the steering wheel to rotate synchronously, and the adjustment mechanism includes a motor, a worm, a double gear, an output gear and a two-way clutch, wherein, The drive of the motor to the output gear is realized through the meshing worm and the duplex gear.
  • the output gear has at least one pair of claw assemblies protruding axially. It is connected with the steering wheel and is rotatably installed in the middle of the brake piece through a roller assembly, and the claw assembly cooperates with the roller assembly to control the clutch state of the two-way clutch.
  • the two-way clutch when the motor is not working, the two-way clutch is in a self-locking state, and the steering wheel maintains a stable static position.
  • the claw assembly controls the two-way clutch to be unlocked and disengaged to drive the steering wheel to rotate.
  • the dual gear has a helical gear and a transmission gear fixedly connected along its rotation axis, the helical gear is engaged with the worm for transmission, and the transmission gear is engaged with the output gear for transmission.
  • the clamping member has at least two radial bosses spaced apart in the circumferential direction and at least one wedge surface between the bosses
  • the claw assembly includes two claws distributed on opposite sides of the roller assembly.
  • the subassembly is composed of two rollers and an elastic body, and the two rollers are arranged between the inner ring surface of the braking part and the wedge surface of the clamping part with the elastic body in between.
  • the elastic body in the initial locked state, is always in a compressed state and pushes the two rollers to directly contact the inner ring surface and the wedge surface.
  • the gap between the finger and the adjacent boss is larger than the gap between the finger and the adjacent roller.
  • the finger when the finger is in contact with the adjacent roller, there is still a gap between the other finger and the adjacent boss, and the continued push of the finger to the adjacent roller causes the compression of the elastic body, making the roller leave the wedge face to form an annular gap to unlock the clamp.
  • the output gear drives the clamp to switch the steering wheel between the deployed and folded positions when the other finger is in contact with the adjacent boss.
  • the folding steering wheel further includes a mounting plate on which the steering wheel is rotatably mounted.
  • the folding steering wheel further includes a fastener, and the adjustment mechanism is mounted on the mounting plate through the fastener.
  • the adjustment mechanism includes a motor end cover, a gearbox end cover and a gear box, wherein the motor end cover and the gear box end cover are fixedly connected to opposite sides of the gear box, and the gear box is fixedly connected to the mounting plate through the fastener superior.
  • the fastener includes a pressure riveting bolt and a nut that cooperates with the pressure riveting bolt, the pressure riveting bolt is in clearance fit with the mounting hole of the gearbox, the pressure riveting bolt and the mounting hole of the brake part are press-fitted with interference, and the pressure riveting bolt As the installation interface, it is installed and fixed with the installation plate through nuts.
  • the motor, worm and duplex gear are installed between the motor end cover and the gearbox, and the output gear is installed between the gearbox end cover and the gearbox.
  • the duplex gear has a rear shaft and a front shaft positioned at two opposite ends of its axis of rotation, the rear shaft fits with the central hole of the motor end cover with clearance so as not to hinder the rotation in the central hole, and the front shaft and The restricted aperture of the gearbox end cover fits with clearance so as not to impede rotation within the restricted aperture.
  • the claw assembly fits with the central hole of the end cover of the gearbox with clearance and protrudes from the central hole.
  • the clamping member has an axially protruding clamping shaft which is inserted into the central hole of the gearbox with play so as not to hinder the rotation of the clamping member about its axis.
  • the central bore of the output gear has a clearance fit with the clamp shaft so as not to prevent the output gear from rotating thereabout.
  • the folding steering wheel further includes a counterweight, which is arranged opposite to the adjustment mechanism to ensure that the total weight on both sides of the folding steering wheel is equal, and the center of gravity is located on the axis of symmetry.
  • the folding steering wheel further includes another adjustment mechanism, which is arranged opposite to the adjustment mechanism and is synchronously connected with the adjustment mechanism through a connecting rod.
  • the other adjustment mechanism omits a motor and a worm.
  • the dual gears of the adjusting mechanism and the other adjusting mechanism respectively have connecting rod interfaces for inserting connecting rods.
  • the helical gear of the dual gear of the other adjustment mechanism is an invalid gear
  • the transmission gear is an effective gear
  • a large transmission ratio and high efficiency can be realized through the two-stage gear transmission of the double gear and the output gear, and the advantages of zero clearance, high strength and high efficiency can be achieved through the two-way clutch.
  • Fig. 1 is a schematic diagram of the overall structure of a folding steering wheel according to a preferred embodiment of the present invention
  • Fig. 2 is a front view of the folding steering wheel of Fig. 1;
  • Fig. 3 is a schematic diagram of the overall structure of the adjustment mechanism of the folding steering wheel in Fig. 1;
  • Fig. 4 is an exploded view of the adjustment mechanism of Fig. 3;
  • Fig. 5 shows the meshing state of the duplex gear and the output gear of the adjustment mechanism of Fig. 4;
  • Fig. 6 is the view of another angle of view of Fig. 4;
  • Fig. 7 is the view of another angle of view of Fig. 3;
  • Fig. 8 shows the initial state of the two-way clutch of the folding steering wheel of Fig. 1;
  • Fig. 9 shows the intermediate state of the two-way clutch of the folding steering wheel of Fig. 1;
  • Fig. 10 shows the unlocked state of the two-way clutch of the folding steering wheel of Fig. 1;
  • Figure 11 shows the direction of rotation of the pincer of the two-way clutch of Figure 1;
  • Fig. 12 is a front view of a folding steering wheel according to another preferred embodiment of the present invention.
  • Fig. 13 is a schematic diagram of the overall structure of the folding steering wheel in Fig. 12;
  • FIG. 14 shows the dual gear of the adjustment mechanism of FIG. 13 .
  • the folding steering wheel includes a steering wheel 1, a mounting plate 2, an adjustment mechanism 3 and fasteners 4, wherein the steering wheel 1 is rotatably mounted on the mounting plate 2 to freely rotate around its center of rotation
  • the adjustment mechanism 3 is installed on the mounting plate 2 through the fastener 4 and its output shaft is fixedly connected with the steering wheel 1 to drive the steering wheel 1 to rotate synchronously.
  • the steering wheel 1 is controlled by the adjustment mechanism 3 , and the output shaft of the adjustment mechanism 3 will drive the steering wheel 1 to rotate synchronously during operation, thereby realizing the switching between the unfolded position and the folded position of the steering wheel 1 .
  • the deployment position is the use position, as shown by the solid line in Figure 1, the driver can normally use the steering wheel 1 at this position to drive the car.
  • the folded position is the non-use position, as shown by the dotted line in Figure 1, where the steering wheel is folded and hidden and cannot be operated by the driver.
  • the adjustment mechanism 3 is arranged on the right side, and a counterweight 5 of equal weight is arranged on the corresponding left side, with equal weights on both sides, so as to ensure that the overall center of gravity is on the symmetry axis L.
  • the adjustment mechanism can also be arranged on the left side, and at the same time, a counterweight of equal weight is arranged on the corresponding right side.
  • adjustment mechanisms can also be arranged on both sides, and at this time, the adjustment mechanisms on both sides are controlled simultaneously to ensure that the rotation points on both sides of the steering wheel rotate synchronously.
  • the adjustment mechanism 3 includes a motor end cover 31, a gear box end cover 32 and a gear box 33, wherein the motor end cover 31 and the gear box end cover 32 are fixedly connected to opposite sides of the gear box 33, and the gear box 33 is fixedly connected to the mounting plate 2 (see FIG. 1 ) by fasteners 4 .
  • the motor end cover 31 and the gear case 33 can be assembled together by processes such as bayonet joints or screws or heat riveting or welding, and the gear case end cover 32 and the gear case 33 can also be assembled by bayonet joints or screws or heat riveting or welding. Craft fit together.
  • the adjustment mechanism 3 also includes a motor 34, a worm 35, a double gear 36 and an output gear 37, wherein the motor 34, the worm 35 and the double gear 36 are installed between the motor end cover 31 and the gear box 33 ,
  • the output gear 37 is installed between the gear case end cover 32 and the gear case 33 .
  • the double gear 36 has a helical gear 361 and a transmission gear 362 fixedly connected along its axis of rotation, the helical gear 361 is engaged with the worm screw 35 for transmission, and the transmission gear 362 passes through the gear box 33 and the output gear 37 is engaged for transmission (referring to FIG. 5 ), thereby The output gear 37 is driven to rotate around its axis by the motor 34 .
  • the double gear 36 also has a rear end shaft 363 and a front end shaft 364 positioned at two opposite ends of its axis of rotation.
  • the rear end shaft 363 cooperates with the center hole 311 of the motor end cover 31 with clearance to not hinder the movement in the center hole 311.
  • the front end shaft 364 cooperates with the restricting hole 321 of the gear box end cover 32 with clearance so as not to hinder the rotation in the restricting hole 321 .
  • the output gear 37 is limited by the gear box end cover 32 and the gear box 33 to prevent axial movement, and it has at least one pair of claw assemblies axially protruding on the side facing away from the motor 34 (in this case In the embodiment, there are three pairs), each pair of finger assemblies includes a first finger 371 and a second finger 372 that are circumferentially spaced apart from each other.
  • the claw assembly fits with the central hole 322 of the gear box end cover 32 with clearance and protrudes from the central hole 322 .
  • the adjustment mechanism 3 also includes a two-way clutch 38 , the clutch state of which is controlled by the claw assembly of the output gear 37 .
  • the motor 34 when the motor 34 is running, it drives the gear train (worm screw 35, double gear 36 and output gear 37) to move, and the claw assembly on the output gear 37 controls the two-way clutch 38 to unlock and separate, and then drives the steering wheel 1 to rotate; the motor 34 does not During work, the two-way clutch 38 is in a self-locking state, the steering wheel 1 cannot be rotated by external force, and is in a very stable position. As shown in FIG.
  • the two-way clutch 38 includes a braking member 381
  • the gearbox 33 is press-fitted on the braking member 381 through the fastener 4 , see FIGS. 3 and 7 .
  • the fastener 4 includes a pressure riveting bolt, which is loosely fitted with the mounting hole 331 (see FIG. 4 ) of the gear case 33 and is press-fitted with the mounting hole 3811 (see FIG. 4 ) of the braking member 381 with interference.
  • the fastener 4 also includes a nut (see FIG. 2 ) that cooperates with the rivet bolt, and the rivet bolt serves as an installation interface and is fixed to the installation plate 2 (see FIG. 1 ) through the nut.
  • the two-way clutch 38 also includes a pincer 382 and at least one pair of roller assemblies (three pairs in this embodiment), wherein the pincher 382 is rotatably mounted in the middle of the brake piece 381 through the roller assembly.
  • the clamping part 382 has a clamping shaft 3821 protruding axially, which is inserted into the center hole 332 (see FIG. 6 ) of the gear box 33 with a clearance so as not to hinder the rotation of the clamping part 382 around its axis.
  • the central hole of the output gear 37 373 (see FIG. 4 ) has a clearance fit with the clamp shaft 3821 so as not to interfere with the rotation of the output gear 37 thereabout.
  • the output end 3822 of the clamp 382 connected to the steering wheel 1 is hexagonal, which is a profiling structure of the steering wheel interface. It should be understood that the hexagons herein are by way of example only and not limitation.
  • the clamping member 382 has three radial projections 3823 , 3824 , 3825 spaced apart from each other in the circumferential direction and three wedge surfaces 3826 between adjacent radial projections.
  • the following will take one of the wedge surfaces 3826 as an example for specific description.
  • the first claw 371 and the second claw 372 are distributed on opposite sides of the roller assembly.
  • the roller assembly is composed of a first roller 383, a second roller 384 and an elastic body 385, that is, the first roller 383 and the second roller 384 are arranged on the inner ring surface 3812 of the braking member 381 and the elastic body 385 Between the wedge surfaces 3826 of the clamping member 382 .
  • roller assemblies cooperate with the wedge surfaces 3826 such that the number of roller assemblies is equal to the number of wedge surfaces 3826 .
  • the elastic body 385 is always in a compressed state, so it will push the first roller 383 and the second roller 384 to directly contact the inner ring surface 3812 and the wedge surface 3826, so that the two-way clutch 38 is locked in both clockwise and counterclockwise directions. stop state.
  • stopper 381 When the stopper 381 is fixed, no matter whether the clamper 382 is driven clockwise or counterclockwise, the clamper 382 cannot be driven to rotate.
  • the clamping part 382 is fixed, no matter whether the braking part 381 is driven clockwise or counterclockwise, the braking part 381 cannot be driven to rotate.
  • the motor 34 drives the worm 35 to rotate synchronously, and the worm 35 meshes with the helical gear 361 to drive the duplex gear 36 to rotate.
  • the transmission gear 362 meshes with the output gear 37 to drive the output gear 37 to rotate.
  • the claw assembly on the output gear 37 cooperates with the two-way clutch 38 to control its clutch state.
  • the gap b1 is larger than the second gap a1.
  • the output gear 37 rotates clockwise, the first claw 371 and the second claw 372 on it also rotate clockwise, the first claw 371 is getting closer to the first roller 383, and the second claw 372 is getting closer
  • the second boss 3824 that is, the second gap a1 becomes smaller, and the third gap b2 also becomes smaller.
  • the output gear 37 When the output gear 37 continues to rotate clockwise, the first finger 371 will push the first roller 383, thereby compressing the elastic body 385, so that the first roller 383 leaves the wedge surface 3826 to form an annular gap c, as shown in FIG. 10 , here
  • the hour clamp 382 is unlocked in the clockwise direction.
  • the output gear 37 continues to rotate clockwise to push the pincer 382 to rotate clockwise, as shown in FIG. 11 .
  • the steering wheel will run from the folded position (ie, the non-use position) shown by the dashed line in FIG. 1 to the unfolded position (ie, the use position) shown by the solid line in FIG. 1 .
  • the output gear 37 rotates clockwise, and the steering wheel moves from the folded position to the unfolded position, which corresponds to the situation that the motor 34 is arranged on the right side in this embodiment.
  • the output gear turns clockwise and the steering wheel travels from the unfolded position to the folded position.
  • the counterclockwise rotation of the output gear 37 can realize the counterclockwise rotation of the clamping member 382 , as shown in FIG. 11 .
  • the steering wheel will run from the unfolded position (ie the use position) shown by the solid line in FIG. 1 to the folded position (ie the non-use position) shown by the dashed line in FIG. 1 .
  • Embodiment 1 The difference from Embodiment 1 is mainly that the adjustment mechanism 3a, 3b is arranged on both sides, but only one side has a motor as the active part, and the other side has no motor as the passive part, and a synchronous link is used between the two to ensure that both sides For synchronous operation, the side without the motor should also be equipped with a counterweight to ensure that the total weight of both sides is equal, see Figure 12.
  • the parts that are different from those in Embodiment 1 will be mainly described below, and the parts that are the same as those in Embodiment 1 will not be repeated here.
  • the right side adjustment mechanism 3a and the left side adjustment mechanism 3b are respectively installed and fixed on the right side and the left side of the mounting plate, and they are connected by a connecting rod 6 to realize synchronous rotation on both sides.
  • the output shafts of the adjustment mechanisms 3a, 3b are fixedly connected to the two side interfaces of the steering wheel respectively, so as to drive the steering wheel to rotate synchronously.
  • the right adjustment mechanism 3a there is a motor in the right adjustment mechanism 3a as an active adjustment mechanism.
  • the left adjustment mechanism 3b has no motor and is a passive adjustment mechanism.
  • the two are connected by a connecting rod 6, and the motor of the right adjustment mechanism 3a will work
  • the adjustment mechanisms 3a and 3b on both sides are driven to run synchronously to adjust the position of the steering wheel.
  • the motor can also be installed in the left adjustment mechanism as an active adjustment mechanism, while there is no motor in the right adjustment mechanism as a passive adjustment mechanism.
  • the dual gear 36' of the right side adjustment mechanism 3a is additionally connected with the connecting rod 6 ( See Fig. 13) mating link interface 365. Both ends of the connecting rod 6 are respectively inserted into the connecting rod interfaces 365 of the adjustment mechanisms 3a and 3b on both sides, so that the dual gears on both sides rotate synchronously.
  • the helical gear 361' of the double gear 36' is an invalid gear, that is, when the steering wheel is adjusted synchronously, the helical gear 361' is inactive, and only the transmission gear 362' is an effective gear, that is, when the steering wheel is adjusted synchronously, the transmission gear 362' plays the role of power transmission, so the helical gear 361' can be omitted.
  • the dual gears 36' of the adjustment mechanisms 3a and 3b on both sides have the same structure, which is mainly considered to reduce the complexity of parts or reduce the number of molds and save costs.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Gear Transmission (AREA)
  • Power Steering Mechanism (AREA)

Abstract

一种折叠方向盘，其包括方向盘（1）和调节机构（3），调节机构（3）的输出轴与方向盘（1）固连在一起以带动方向盘（1）同步转动，调节机构（3）包括电机（34）、蜗杆（35）、双联齿轮（36）、输出齿轮（37）和双向离合器（38），其中，电机（34）对输出齿轮（37）的驱动通过啮合的蜗杆（35）和双联齿轮（36）实现，输出齿轮（37）具有轴向伸出的至少一对拨爪组件（371，372），双向离合器（38）包括制动件（381）、钳制件（382）和至少一对滚子组件（383，384），钳制件（382）与方向盘（1）连接并通过滚子组件（383，384）可转动地安装于制动件（381）的中部，拨爪组件（371，372）与滚子组件（383，384）配合以控制双向离合器（38）的离合状态。根据本申请的折叠方向盘，通过双联齿轮和输出齿轮的两级齿轮传动即可实现大传动比和高效率，通过双向离合器具有零间隙、高强度和高效率的优点。

Description

一种折叠方向盘 技术领域
本发明涉及汽车方向盘，更具体地涉及一种折叠方向盘。
背景技术
目前汽车方向盘折叠机构多为电机结合齿轮箱或者是丝杆机构，难以满足方向盘间隙/强度/耐久等性能，因此市场上急切需要一款零间隙/高强度/耐久性能好的方向盘折叠调节机构。
发明内容
为了解决上述现有技术中的方向盘折叠机构的间隙较大等问题，本发明提供一种折叠方向盘。
根据本发明的折叠方向盘，其包括方向盘和调节机构，调节机构的输出轴与方向盘固连在一起以带动方向盘同步转动，调节机构包括电机、蜗杆、双联齿轮、输出齿轮和双向离合器，其中，电机对输出齿轮的驱动通过啮合的蜗杆和双联齿轮实现，输出齿轮具有轴向伸出的至少一对拨爪组件，双向离合器包括制动件、钳制件和至少一对滚子组件，钳制件与方向盘连接并通过滚子组件可转动地安装于制动件的中部，拨爪组件与滚子组件配合以控制双向离合器的离合状态。
优选地，电机不工作时，双向离合器处于自锁状态，方向盘保持稳定的静止位置。
优选地，电机工作时，拨爪组件控制双向离合器解锁分离以带动方向盘转动。
优选地，双联齿轮具有沿其旋转轴线固定连接的斜齿轮和传动齿轮，斜齿轮与蜗杆啮合传动，传动齿轮与输出齿轮啮合传动。
优选地，钳制件具有周向间隔开的至少两个径向的凸台和位于凸台之间的至少一个楔面，拨爪组件包括分布在滚子组件的相对两侧的两拨爪，滚子组件由两滚子和弹性体组成，两滚子夹着弹性体设置在制动件的内环面与钳制件的楔面之间。
优选地，在初始的锁定状态下，弹性体始终处于压缩状态并推动两滚子直接与内环面和楔面接触。
优选地，在初始的锁定状态下，拨爪与相邻凸台之间的间隙大于拨爪与相邻滚子之间的间隙。
优选地，当拨爪与相邻滚子接触时，另一拨爪与相邻凸台之间还存在间隙，拨爪对相 邻滚子的继续推动导致弹性体的压缩，使得滚子离开楔面形成环形间隙以解锁钳制件。
优选地，当另一拨爪与相邻凸台接触时，输出齿轮驱动钳制件以使得方向盘在展开位置和折叠位置之间切换。
优选地，该折叠方向盘还包括安装板，方向盘可转动地安装在安装板上。
优选地，该折叠方向盘还包括紧固件，调节机构通过紧固件安装在安装板上。
优选地，调节机构包括电机端盖、齿轮箱端盖和齿轮箱，其中，电机端盖和齿轮箱端盖固定连接在齿轮箱的相对两侧，齿轮箱通过该紧固件固定连接在安装板上。
优选地，该紧固件包括压铆螺栓和与压铆螺栓配合的螺母，压铆螺栓与齿轮箱的安装孔间隙配合，压铆螺栓与制动件的安装孔过盈压装，压铆螺栓作为安装接口与安装板通过螺母安装固定。
优选地，电机、蜗杆和双联齿轮安装在电机端盖和齿轮箱之间，输出齿轮安装在齿轮箱端盖和齿轮箱之间。
优选地，双联齿轮具有位于其旋转轴线的两相对末端的后端轴和前端轴，后端轴与电机端盖的中心孔有间隙地配合以不妨碍在中心孔内的转动，前端轴与齿轮箱端盖的限制孔有间隙地配合以不妨碍在限制孔内的转动。
优选地，拨爪组件与齿轮箱端盖的中心孔有间隙地配合并从中心孔内伸出。
优选地，钳制件具有轴向伸出的钳制轴，钳制轴有间隙地插入到齿轮箱的中心孔中以不妨碍钳制件绕其轴线的转动。
优选地，输出齿轮的中心孔与钳制轴间隙配合以不妨碍输出齿轮绕其旋转。
优选地，该折叠方向盘还包括配重块，其与调节机构相对布置以保证折叠方向盘两侧总重量相等，重心位于其对称轴上。
优选地，该折叠方向盘还包括另一调节机构，其与调节机构相对布置并通过连杆与调节机构同步连接，该另一调节机构相对于调节机构省略电机和蜗杆。
优选地，该调节机构和另一调节机构的双联齿轮分别具有供连杆插入的连杆接口。
优选地，该另一调节机构的双联齿轮的斜齿轮是无效齿轮，传动齿轮是有效齿轮。
根据本发明的折叠方向盘，通过双联齿轮和输出齿轮的两级齿轮传动即可实现大传动比和高效率，通过双向离合器具有零间隙、高强度和高效率的优点。
附图说明
图1是根据本发明的一个优选实施例的折叠方向盘的整体结构示意图；
图2是图1的折叠方向盘的正视图；
图3是图1的折叠方向盘的调节机构的整体结构示意图；
图4是图3的调节机构的爆炸图；
图5示出了图4的调节机构的双联齿轮和输出齿轮的啮合状态；
图6是图4的另一视角的视图；
图7是图3的另一视角的视图；
图8示出了图1的折叠方向盘的双向离合器的初始状态；
图9示出了图1的折叠方向盘的双向离合器的中间状态；
图10示出了图1的折叠方向盘的双向离合器的解锁状态；
图11示出了图1的双向离合器的钳制件的转动方向；
图12是根据本发明的另一个优选实施例的折叠方向盘的正视图；
图13是图12的折叠方向盘的整体结构示意图；
图14示出了图13的调节机构的双联齿轮。
具体实施方式
下面结合附图，给出本发明的较佳实施例，并予以详细描述。
实施例1
如图1所示，根据本实施例的折叠方向盘包括方向盘1、安装板2、调节机构3和紧固件4，其中，方向盘1可转动地安装在安装板2上以绕其旋转中心自由旋转，调节机构3通过紧固件4安装在安装板2上且其输出轴与方向盘1固连在一起以带动方向盘1同步转动。如此，方向盘1通过调节机构3控制，调节机构3的输出轴运行时会带动方向盘1同步旋转，进而实现方向盘1在展开位置和折叠位置之间切换。展开位置即使用位置，如图1中的实线所示，驾驶人员可正常使用此位置的方向盘1驾驶汽车。折叠位置即非使用位置，如图1中的虚线所示，此位置方向盘被折叠隐藏，不能被驾驶人员操作。
在本实施例中，如图2所示，调节机构3布置在右侧，在其对应的左侧配置等重的配重块5，两侧等重，保证整体重心在对称轴L上。应该理解，调节机构也可以布置在左侧，同时在其对应的右侧配置等重的配重块。当然，也可以两侧均布置调节机构，此时两侧调节机构同时控制，保证方向盘两侧旋转点同步旋转。
如图3所示，调节机构3包括电机端盖31、齿轮箱端盖32和齿轮箱33，其中，电机端盖31和齿轮箱端盖32固定连接在齿轮箱33的相对两侧，齿轮箱33通过紧固件4固定连接在安装板2(参见图1)上。应该理解，电机端盖31和齿轮箱33可通过卡口或螺钉或热铆或焊接等工艺装配在一起，齿轮箱端盖32和齿轮箱33同样可通过卡口或螺钉或热铆或焊接 等工艺装配在一起。
如图4所示，调节机构3还包括电机34、蜗杆35、双联齿轮36和输出齿轮37，其中，电机34、蜗杆35和双联齿轮36安装在电机端盖31和齿轮箱33之间，输出齿轮37安装在齿轮箱端盖32和齿轮箱33之间。
电机34被电机端盖31和齿轮箱33固定，蜗杆35过盈压装在电机34的输出轴上并与双联齿轮36啮合以通过电机34驱动双联齿轮36绕其轴线旋转。双联齿轮36具有沿其旋转轴线固定连接的斜齿轮361和传动齿轮362，斜齿轮361与蜗杆35啮合传动，传动齿轮362穿过齿轮箱33与输出齿轮37啮合传动(参见图5)，从而通过电机34驱动输出齿轮37绕其轴线旋转。双联齿轮36还具有位于其旋转轴线的两相对末端的后端轴363和前端轴364，后端轴363与电机端盖31的中心孔311有间隙地配合以不妨碍在中心孔311内的转动，前端轴364与齿轮箱端盖32的限制孔321有间隙地配合以不妨碍在限制孔321内的转动。
如图6所示，输出齿轮37被齿轮箱端盖32和齿轮箱33限制以防止轴向窜动，其在背向电机34的侧面具有轴向伸出的至少一对拨爪组件(在本实施例中为三对)，每对拨爪组件包括彼此周向间隔开的第一拨爪371和第二拨爪372。拨爪组件与齿轮箱端盖32的中心孔322有间隙地配合并从中心孔322内伸出。
调节机构3还包括双向离合器38，其离合状态通过输出齿轮37的拨爪组件控制。具体地，电机34运行时，带动齿轮系(蜗杆35、双联齿轮36和输出齿轮37)运动，输出齿轮37上的拨爪组件控制双向离合器38解锁分离，进而带动方向盘1转动；电机34不工作时，双向离合器38处于自锁状态，方向盘1无法被外力转动，处于非常稳定的位置。如图4所示，双向离合器38包括制动件381，齿轮箱33通过紧固件4压装在制动件381上，参见图3和图7。具体地，紧固件4包括压铆螺栓，其与齿轮箱33的安装孔331(参见图4)间隙配合，而与制动件381的安装孔3811(参见图4)过盈压装。在本实施例中，紧固件4还包括与压铆螺栓配合的螺母(参见图2)，压铆螺栓作为安装接口与安装板2(参见图1)通过螺母安装固定。
双向离合器38还包括钳制件382和至少一对滚子组件(在本实施例中为三对)，其中，钳制件382通过滚子组件可转动地安装于制动件381的中部。钳制件382具有轴向伸出的钳制轴3821，其有间隙地插入到齿轮箱33的中心孔332(参见图6)中以不妨碍钳制件382绕其轴线的转动，输出齿轮37的中心孔373(参见图4)与钳制轴3821间隙配合以不妨碍输出齿轮37绕其旋转。在本实施例中，与方向盘1连接的钳制件382的输出端3822呈六边形，为方向盘接口的仿形结构。应该理解，这里的六边形仅作为示例而非限制。
在本实施例中，如图8所示，钳制件382具有周向上彼此间隔开的三个径向凸台3823， 3824，3825和位于相邻径向凸台之间的三个楔面3826。下面以其中的一个楔面3826为例进行具体说明。第一拨爪371和第二拨爪372分布在滚子组件的相对两侧。滚子组件由第一滚子383、第二滚子384和弹性体385组成，即第一滚子383和第二滚子384夹着弹性体385设置在制动件381的内环面3812与钳制件382的楔面3826之间。应该理解，滚子组件与楔面3826配合，因此滚子组件的数目与楔面3826的数目相等。弹性体385始终处于压缩状态，因此会推动第一滚子383和第二滚子384直接与内环面3812和楔面3826接触，使得双向离合器38在顺时针和逆时针两个方向均处于锁止状态。当固定制动件381时，无论是顺时针或逆时针驱动钳制件382，都无法驱使钳制件382转动。当固定钳制件382时，无论是顺时针或逆时针驱动制动件381，都无法驱使制动件381转动。
下面结合附图详细说明调节机构3的运行机理。电机34带动蜗杆35同步转动，蜗杆35与斜齿轮361啮合以带动双联齿轮36转动。传动齿轮362与输出齿轮37啮合以带动输出齿轮37转动。输出齿轮37上的拨爪组件与双向离合器38配合以控制其离合状态。在图8所示的初始状态下，第一拨爪371与第一凸台3823之间具有第一间隙b1，第一拨爪371与第一滚子383之间具有第二间隙a1，第一间隙b1大于第二间隙a1。第二拨爪372与第二凸台3824之间具有与第一间隙b1相等的第三间隙b2，第二拨爪372与第二滚子384之间具有与第二间隙a1相等的第四间隙a2，第三间隙b2大于第四间隙a2。
输出齿轮37顺时针转动，其上的第一拨爪371和第二拨爪372也顺时针转动，第一拨爪371越来越靠近第一滚子383，第二拨爪372越来越靠近第二凸台3824，即第二间隙a1变小，第三间隙b2也变小。当第一拨爪371接触到第一滚子383时，由于第三间隙b2大于第一间隙a1，第二拨爪372与第二凸台3824还存在间隙b2’，如图9所示。输出齿轮37顺时针继续转动，第一拨爪371就会推动第一滚子383，进而压缩弹性体385，使得第一滚子383离开楔面3826形成环形间隙c，如图10所示，此时钳制件382在顺时针方向解锁。当第二拨爪372接触到第二凸台3824时，输出齿轮37顺时针继续转动就可以推动钳制件382顺时针转动，如图11所示。方向盘将从图1的虚线示出的折叠位置(即非使用位置)运行到图1的实线示出的展开位置(即使用位置)。应该理解，这里输出齿轮37顺时针转动，方向盘从折叠位置运行到展开位置，对应的是本实施例的电机34布置在右侧的情况。在电机布置在左侧的实施例中，输出齿轮顺时针转动，方向盘是从展开位置运行到折叠位置。
同理，输出齿轮37逆时针转动，可以实现钳制件382逆时针转动，如图11所示。方向盘将从图1的实线示出的展开位置(即使用位置)运行到图1的虚线示出的折叠位置(即非使用位置)。
实施例2
与实施例1的区别主要在于调节机构3a，3b两侧布置，但是只有一侧有电机，作为主动件，另外一侧无电机，作为被动件，两者之间使用同步连杆，保证两侧同步运转，无电机一侧也要配备配重块，保证两侧总重量相等，参见图12。以下主要说明与实施例1不同的部分，与实施例1相同的部分不再赘述。
如图13所示，右侧调节机构3a与左侧调节机构3b被分别安装固定在安装板的右侧和左侧上，并由连杆6将它们连接起来，实现两侧同步转动，两侧的调节机构3a，3b的输出轴分别与方向盘的两侧接口固连在一起，即可带动方向盘的同步转动。
在本实施例中，右侧调节机构3a中有电机，作为主动调节机构，左侧调节机构3b没有电机，为被动调节机构，两者通过连杆6连接，右侧调节机构3a的电机工作会同时带动两侧的调节机构3a，3b同步运行，调节方向盘的位置。当然也可以将电机装在左侧调节机构中，作为主动调节机构，而右侧调节机构中没有电机，作为被动调节机构。
如图14所示，右侧调节机构3a的双联齿轮36’除了具有斜齿轮361’、传动齿轮362’、后端轴363’和前端轴364’之外，还额外增加与连杆6(参见图13)配合的连杆接口365。连杆6的两端分别插入到两侧的调节机构3a，3b的连杆接口365中，从而使得两侧的双联齿轮同步转动。
在本实施例中，对于左侧调节机构3b而言，其系统中没有电机和蜗杆，并且其中的双联齿轮36’的斜齿轮361’为无效齿轮，即在同步调节方向盘时，该斜齿轮361’是不起作用的，仅传动齿轮362’为有效齿轮，即在同步调节方向盘时，该传动齿轮362’起到动力传输的作用，因此可以省略该斜齿轮361’。本实施例中的两侧的调节机构3a，3b的双联齿轮36’的结构相同，主要是考虑可以减少零件复杂度或者是减少模具数量，节约成本。
以上所述的，仅为本发明的较佳实施例，并非用以限定本发明的范围，本发明的上述实施例还可以做出各种变化。即凡是依据本发明申请的权利要求书及说明书内容所作的简单、等效变化与修饰，皆落入本发明专利的权利要求保护范围。本发明未详尽描述的均为常规技术内容。

Claims (23)

  1. 一种折叠方向盘，其特征在于，该折叠方向盘包括方向盘和调节机构，调节机构的输出轴与方向盘固连在一起以带动方向盘同步转动，调节机构包括电机、蜗杆、双联齿轮、输出齿轮和双向离合器，其中，电机对输出齿轮的驱动通过啮合的蜗杆和双联齿轮实现，输出齿轮具有轴向伸出的至少一对拨爪组件，双向离合器包括制动件、钳制件和至少一对滚子组件，钳制件与方向盘连接并通过滚子组件可转动地安装于制动件的中部，拨爪组件与滚子组件配合以控制双向离合器的离合状态。
  2. 根据权利要求1所述的折叠方向盘，其特征在于，电机不工作时，双向离合器处于自锁状态，方向盘保持稳定的静止位置。
  3. 根据权利要求1所述的折叠方向盘，其特征在于，电机工作时，拨爪组件控制双向离合器解锁分离以带动方向盘转动。
  4. 根据权利要求1所述的折叠方向盘，其特征在于，双联齿轮具有沿其旋转轴线固定连接的斜齿轮和传动齿轮，斜齿轮与蜗杆啮合传动，传动齿轮与输出齿轮啮合传动。
  5. 根据权利要求1所述的折叠方向盘，其特征在于，钳制件具有周向间隔开的至少两个径向的凸台和位于凸台之间的至少一个楔面，拨爪组件包括分布在滚子组件的相对两侧的两拨爪，滚子组件由两滚子和弹性体组成，两滚子夹着弹性体设置在制动件的内环面与钳制件的楔面之间。
  6. 根据权利要求5所述的折叠方向盘，其特征在于，滚子组件的数目与楔面的数目相等。
  7. 根据权利要求5所述的折叠方向盘，其特征在于，在初始的锁定状态下，弹性体始终处于压缩状态并推动两滚子直接与内环面和楔面接触。
  8. 根据权利要求7所述的折叠方向盘，其特征在于，在初始的锁定状态下，拨爪与相邻凸台之间的间隙大于拨爪与相邻滚子之间的间隙。
  9. 根据权利要求8所述的折叠方向盘，其特征在于，当拨爪与相邻滚子接触时，另一拨爪与相邻凸台之间还存在间隙，拨爪对相邻滚子的继续推动导致弹性体的压缩，使得滚子离开楔面形成环形间隙以解锁钳制件。
  10. 根据权利要求9所述的折叠方向盘，其特征在于，当另一拨爪与相邻凸台接触时，输出齿轮驱动钳制件以使得方向盘在展开位置和折叠位置之间切换。
  11. 根据权利要求1所述的折叠方向盘，其特征在于，该折叠方向盘还包括安装板，方向盘可转动地安装在安装板上。
  12. 根据权利要求11所述的折叠方向盘，其特征在于，该折叠方向盘还包括紧固件，调节机构通过紧固件安装在安装板上。
  13. 根据权利要求12所述的折叠方向盘，其特征在于，调节机构包括电机端盖、齿轮箱端盖和齿轮箱，其中，电机端盖和齿轮箱端盖固定连接在齿轮箱的相对两侧，齿轮箱通过该紧固件固定连接在安装板上。
  14. 根据权利要求13所述的折叠方向盘，其特征在于，该紧固件包括压铆螺栓和与压铆螺栓配合的螺母，压铆螺栓与齿轮箱的安装孔间隙配合，压铆螺栓与制动件的安装孔过盈压装，压铆螺栓作为安装接口与安装板通过螺母安装固定。
  15. 根据权利要求13所述的折叠方向盘，其特征在于，电机、蜗杆和双联齿轮安装在电机端盖和齿轮箱之间，输出齿轮安装在齿轮箱端盖和齿轮箱之间。
  16. 根据权利要求13所述的折叠方向盘，其特征在于，双联齿轮具有位于其旋转轴线的两相对末端的后端轴和前端轴，后端轴与电机端盖的中心孔有间隙地配合以不妨碍在中心孔内的转动，前端轴与齿轮箱端盖的限制孔有间隙地配合以不妨碍在限制孔内的转动。
  17. 根据权利要求13所述的折叠方向盘，其特征在于，拨爪组件与齿轮箱端盖的中心孔有间隙地配合并从中心孔内伸出。
  18. 根据权利要求13所述的折叠方向盘，其特征在于，钳制件具有轴向伸出的钳制轴，钳制轴有间隙地插入到齿轮箱的中心孔中以不妨碍钳制件绕其轴线的转动。
  19. 根据权利要求18所述的折叠方向盘，其特征在于，输出齿轮的中心孔与钳制轴间隙配合以不妨碍输出齿轮绕其旋转。
  20. 根据权利要求1所述的折叠方向盘，其特征在于，该折叠方向盘还包括配重块，其与调节机构相对布置以保证折叠方向盘两侧总重量相等，重心位于其对称轴上。
  21. 根据权利要求1所述的折叠方向盘，其特征在于，该折叠方向盘还包括另一调节机构，其与调节机构相对布置并通过连杆与调节机构同步连接，该另一调节机构相对于调节机构省略电机和蜗杆。
  22. 根据权利要求21所述的折叠方向盘，其特征在于，该调节机构和另一调节机构的双联齿轮分别具有供连杆插入的连杆接口。
  23. 根据权利要求21所述的折叠方向盘，其特征在于，该另一调节机构的双联齿轮的斜齿轮是无效齿轮，传动齿轮是有效齿轮。
PCT/CN2022/139248 2021-12-20 2022-12-15 一种折叠方向盘 WO2023116543A1 (zh)

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