WO2024017138A1 - 一种高强度连续式座椅偏心调角器 - Google Patents

一种高强度连续式座椅偏心调角器 Download PDF

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Publication number
WO2024017138A1
WO2024017138A1 PCT/CN2023/107295 CN2023107295W WO2024017138A1 WO 2024017138 A1 WO2024017138 A1 WO 2024017138A1 CN 2023107295 W CN2023107295 W CN 2023107295W WO 2024017138 A1 WO2024017138 A1 WO 2024017138A1
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WIPO (PCT)
Prior art keywords
tooth plate
wedge
gear tooth
ring gear
continuous seat
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Application number
PCT/CN2023/107295
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English (en)
French (fr)
Inventor
胡建庸
梁红兵
唐韵华
Original Assignee
恺博座椅机械部件有限公司
恺博(常熟)座椅机械部件有限公司
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Application filed by 恺博座椅机械部件有限公司, 恺博(常熟)座椅机械部件有限公司 filed Critical 恺博座椅机械部件有限公司
Publication of WO2024017138A1 publication Critical patent/WO2024017138A1/zh

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
    • B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
    • B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
    • B60N2/22—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable
    • B60N2/235—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable by gear-pawl type mechanisms

Definitions

  • the present invention relates to automobile seats, and more specifically to a high-strength continuous seat eccentric recliner.
  • the present invention provides a high-strength continuous seat eccentric recliner.
  • the high-strength continuous seat eccentric recliner includes a gear tooth plate and a ring gear tooth plate that can rotate relative to each other, and the gear tooth plate and the ring gear tooth plate are connected to each other through intermeshing teeth; and an eccentric driven by a cam, which rotates in the circumferential direction to drive the relative rolling motion of the gear tooth plate and the ring gear tooth plate; wherein the ring gear tooth plate has a first axis point, and the gear tooth plate has The second axis center point, the eccentricity e of the ring gear tooth plate relative to the gear tooth plate is the straight line distance between the first axis center point and the second axis center point, e is 1.35mm-1.65mm.
  • the gear tooth plate has an external tooth gear
  • the ring gear tooth plate has an internal tooth ring.
  • the gear tooth plate and the ring gear tooth plate are connected to each other through the intermeshing external tooth gear and the internal tooth ring.
  • the inner part of the ring gear tooth plate The meshing amount between the teeth and the external teeth of the gear tooth plate is 0.5mm-0.9mm.
  • the eccentric member is cooperatively defined by a wedge and a spring to press the external toothed gear of the gear tooth plate into the internal toothed toothed ring of the ring gear tooth plate in the meshing position.
  • the cam has a drive segment and the wedge consists of two wedge segments inserted into the play between the narrow sides of the two wedge segments along the first and second pivot points.
  • the connections are symmetrically distributed.
  • the gear tooth plate and the ring gear tooth plate have first meshing points and second meshing points spaced apart from each other, and the two meshing points span 6 to 12 teeth and are symmetrically distributed along the connecting line.
  • the high-strength continuous seat eccentric recliner further includes a bushing, which is disposed between the curved outer surface of the wedge and the central hole of the ring gear tooth plate.
  • the curved outer surface of the wedge that is in contact with the bushing at the first contact tangent point follows a part of the logarithmic spiral, and the bushing acts on the wedge.
  • the load force of the logarithmic spiral profile is directed through the first contact tangent point to the first axis point.
  • the gear tooth plate has a cylinder concentric with respect to the external gear, and the cam has an annular column axially inserted into the cylinder and extending out.
  • the outer circumferential surface of the cylinder supports the wedge at the second contact tangent point, and the supporting force of the cylinder acting on the wedge is directed to the second contact tangent point through the second axis point.
  • the pressure angle between the load force and the support force is not greater than 6.9°.
  • the two ends of the spring are respectively connected to the broad sides of the two wedge-shaped segments facing each other so that the spring acts on the wedge-shaped segments in the circumferential direction to force the two wedge-shaped segments to open.
  • the high-strength continuous seat eccentric recliner further includes a clamp for holding the gear tooth plate and the ring gear tooth plate together.
  • the high-strength continuous seat eccentric recliner further includes a cover covering the cam and connected and fixed to the tooth plate of the ring gear.
  • the strength of the recliner is improved while maintaining the same strength.
  • the angle adjuster has a smaller diameter and a lighter weight, thereby achieving lightweight.
  • the structural innovation is carried out, which further simplifies the manufacturing and processing of parts, while reducing the weight and size, while ensuring a high strength level and meeting market demand.
  • Figure 1 is a schematic assembly diagram of a high-strength continuous seat eccentric recliner according to a preferred embodiment of the present invention
  • Figure 2 is a cross-sectional view of the high-strength continuous seat eccentric recliner of Figure 1;
  • Figure 3 is a first side view of the high-strength continuous seat eccentric recliner of Figure 1;
  • Figure 4 is a partial enlarged view of Figure 3;
  • Figure 5 is a schematic illustration of Figure 4.
  • Figure 6 is a second side view of the high-strength continuous seat eccentric recliner of Figure 1;
  • Figure 7 is a schematic illustration of Figure 6
  • Figure 8 is a schematic diagram of a wedge-shaped section of the wedge of the high-strength continuous seat eccentric recliner of Figure 1;
  • FIG. 9 is a third side view of the high-strength continuous seat eccentric recliner of FIG. 1 .
  • the high-strength continuous seat eccentric recliner 10 includes a hoop 18, a gear tooth plate 17 and a ring gear tooth plate 16, wherein the gear tooth plate
  • the gear tooth plate 17 and the ring gear tooth plate 16 are arranged to be rotatable relative to each other, and the hoop 18 is used to hold the gear tooth plate 17 and the ring gear tooth plate 16 together.
  • the hoop 18 for absorbing axial force is fixedly connected to the ring gear plate 16 . It should be understood that the hoop 18 does not hinder the relative rotation of the gear tooth plate 17 and the ring gear tooth plate 16 .
  • the gear tooth plate 17 can be installed on the seat, and the ring gear tooth plate 16 can be installed on the backrest to adjust the inclination angle of the backrest relative to the seat.
  • the installation positions of the gear tooth plate 17 and the ring gear tooth plate 16 can also be exchanged, that is, the gear tooth plate 17 can be installed on the backrest, and the ring gear tooth plate 16 can be installed on the seat.
  • the gear tooth plate 17 and the ring gear tooth plate 16 are connected to each other through gears for adjustment and fixation.
  • an external toothed gear is formed on the gear tooth plate 17, and an internal toothed toothed ring is formed on the ring gear tooth plate 16.
  • the external toothed gear and the internal toothed toothed ring mesh with each other to drive the coupling through tooth meshing.
  • the diameter of the external tooth addendum circle of the externally toothed gear is smaller than the diameter of the internal tooth root circle of the internally toothed ring gear by at least one tooth height.
  • the externally toothed gear and the internally toothed ring gear differ in the number of teeth by at least one tooth, which difference allows the internally toothed ring gear to perform rolling motion on the externally toothed gear.
  • the gear tooth plate 17 has a cylinder 17a concentric with the external gear.
  • the high-strength continuous seat eccentric recliner 10 according to this embodiment also includes a wedge 14, which is supported on the cylinder 17a through its curved inner surface, and carries the ring gear tooth plate 16 through its curved outer surface.
  • the high-strength continuous seat eccentric recliner 10 according to this embodiment also includes a bushing 15 disposed between the curved outer surface of the wedge 14 and the central hole 16 a of the ring gear plate 16 .
  • the bushing 15 and the ring gear plate 16 are coaxially riveted or welded into one body.
  • the high-strength continuous seat eccentric recliner 10 also It includes a cam 13, whose axially protruding annular column 13a is inserted into the cylinder 17a and is provided with a bore in the center for receiving and matching the drive shaft to brake the cam 13 through the drive shaft.
  • the cam 13 also has a driving section 13b.
  • the wedge 14 is composed of two wedge-shaped segments.
  • the driving segment 13b of the cam 13 is inserted into the clearance between the narrow sides of the two wedge-shaped segments to push the wedge 14 to rotate.
  • the two symmetrically arranged wedge-shaped segments are the core components of the radial support. , and is the core component for adaptively adjusting the meshing gap.
  • the high-strength continuous seat eccentric recliner 10 also includes a spring 12, the two ends of which are respectively connected to the wide sides of the two wedge-shaped segments facing each other, so that the spring 12 acts on the circumferential direction.
  • the wedge-shaped section forces the two wedge-shaped sections to spread apart, so that the wedge 14 contacts the bushing 15 .
  • the wedge 14 and the spring 12 cooperate to define an eccentric member for pressing the external toothed gear of the gear tooth plate 17 into the internal toothed toothed ring of the ring gear tooth plate 16 in the meshing position.
  • the high-strength continuous seat eccentric recliner 10 according to this embodiment also includes a cover 11 that covers the cam 13 and is connected and fixed to the ring gear plate 16 .
  • the specific assembly process of the high-strength continuous seat eccentric recliner 10 includes: the bushing 15 is pressed into the center hole 16a of the ring gear tooth plate 16, and the interference fit is tight; The gear meshes with the internal tooth ring of the ring gear plate 16; the annular column 13a of the cam 13 is embedded in the inner circumferential surface of the cylinder 17a of the gear tooth plate 17; both ends of the spring 12 are respectively inserted into the two wedge-shaped segments of the wedge 14 In the hole on the wide side of ; The cover 11 is welded to the ring gear plate 16.
  • the specific working mechanism of the high-strength continuous seat eccentric recliner 10 includes: in the process of driving through the rotating drive shaft, the torque is first transmitted to the cam 13, and then transmitted to the cam 13 through the driving section 13b.
  • the eccentric member formed by the wedge 14 and the spring 12
  • the eccentric member slides along the bushing 15, deflecting its eccentric direction, and thus causing the external toothed gear of the gear tooth plate 17 to slide against the internal teeth of the ring gear tooth plate 16.
  • the meshing position in the ring gear is offset, driving the relative rolling motion of the ring gear tooth plate 16 and the gear tooth plate 17, thereby allowing the inclination of the backrest to be continuously and variably adjusted.
  • the ring gear tooth plate 16 has an axis line in a three-dimensional space, and the axis line is projected on a two-dimensional plane to become a center point, that is, the first axis point M 16 , as shown in Figure 3 .
  • the gear tooth plate 17 has a second axis point M 17 .
  • the eccentricity e of the high-strength continuous seat eccentric angle adjuster according to this embodiment is the first axis point M 16 and the second axis point
  • the straight-line distance between M 17 , e is 1.35mm-1.65mm, thereby improving the strength of the angle adjuster.
  • the internal teeth of the ring gear tooth plate 16 and the external teeth of the gear tooth plate 17 have a meshing amount O vp .
  • the misalignment between the internal teeth of the ring gear tooth plate 16 and the external teeth of the gear tooth plate 17 exceeds the meshing amount O vp
  • the high-strength continuous seat eccentric recliner 10 exhibits sliding tooth failure.
  • the greater the engagement amount O vp the more the strength of the high-strength continuous seat eccentric recliner 10 is improved.
  • the meshing amount O vp of the internal teeth of the ring gear tooth plate 16 and the external teeth of the gear tooth plate 17 increases to 0.5mm-0.9mm.
  • the gear tooth plate 17 is fixed. Every time the wedge 14 rotates 360° around the second axis point M 17 , the ring gear tooth plate 16 engaged with the gear tooth plate 17 rolls across one tooth, intercepting the movement of any point on the ring gear tooth plate 16. The trajectory is from point A2 to point B2, the ring gear tooth plate 16 rotates at angle ⁇ , and the displacement stroke D is 2 times the eccentricity e.
  • the meshing amount O vp is equal to the eccentricity e, but the tooth shape design needs to be considered Strength and prevention of undercutting, etc.
  • the engagement amount O vp is usually less than the eccentricity e.
  • the wedge 14 is composed of two wedge-shaped segments, which are symmetrically distributed along the axis M 16 M 17 (see Figure 6).
  • the spring 12 acts on the wedge-shaped segments in the circumferential direction to force the two wedge-shaped segments.
  • Spread open so that the internal teeth of the ring gear tooth plate 16 mesh with the external teeth of the gear tooth plate 17 span 6 to 12 teeth and are symmetrically distributed along the axis M 16 M 17 of the wedge 14 . That is to say, as shown in FIG. 6 , the gear tooth plate 17 and the ring gear tooth plate 16 have first meshing points P1 and second meshing points P2 spaced apart from each other.
  • the ring gear tooth plate 16 and the gear tooth plate 17 are simplified to be replaced by the ring gear pitch circle 16b and the gear tooth plate 17b respectively, and straight lines are drawn to connect the first meshing point P 1 and the second axis point M 17 of the gear tooth plate 17 to obtain straight lines.
  • the wedge 14 of the continuous seat wedge eccentric structure recliner is The curved outer surface is formed as part of a logarithmic spiral (i.e., an equiangular spiral) L, as shown in Figure 8.
  • the cam 13 pushes the wedge 14 to rotate, and the curved outer surface of the wedge 14 contacts the inner circumferential surface of the bushing 15 .
  • the curved outer surface of the wedge 14 which is in contact with the bushing 15 at the first contact tangent point M follows a part of the path of the logarithmic spiral L.
  • the outer circumferential surface of the cylinder 17a of the gear tooth plate 17 at the second contact tangent point N supports the wedge 14.
  • the first contact tangent point M is the contact point between the logarithmic spiral profile of the wedge 14 and the inner circle profile of the bushing 15, and is also the tangent point between the logarithmic spiral profile of the wedge 14 and the inner circle of the bushing 15. point, so the first contact tangent point M is both on the inner circle of the bushing 15 and on the logarithmic spiral L of the wedge 14.
  • the second contact tangent point N is the contact point between the curved inner surface contour of the wedge 14 and the outer circular contour of the cylinder 17a, and is also the tangent point between the curved inner surface contour of the wedge 14 and the outer circle of the cylinder 17a.
  • the load force F 1 of the bushing 15 acting on the logarithmic spiral profile of the wedge 14 is directed to the first axis point M 16 of the ring gear tooth plate 16 through the first contact tangent point M.
  • the cylinder 17 a of the gear tooth plate 17 is The support force F 2 acting on the outer circumferential surface of the wedge 14 points to the second contact tangent point N through the second axis point M 17 , and the pressure angle between the load force F 1 and the support force F 2 Not greater than 6.9°.
  • the high-strength continuous seat eccentric recliner 10 of the above embodiment is used to adjust the inclination angle of the backrest relative to the seat, it should be understood that the recliner has wide applicability and can be used for seat backs, leg rests , shoulder adjustment and other joint parts, etc.

Landscapes

  • Engineering & Computer Science (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Chairs For Special Purposes, Such As Reclining Chairs (AREA)

Abstract

本发明涉及一种高强度连续式座椅偏心调角器，其包括可相对于彼此转动的齿轮齿板和齿圈齿板，所述齿轮齿板和齿圈齿板通过相互啮合的齿相互连接；以及由凸轮驱动的偏心件，所述偏心件在周向方向上旋转以驱动齿轮齿板和齿圈齿板的相对滚动运动；其中，齿圈齿板具有第一轴心点，齿轮齿板具有第二轴心点，齿圈齿板相对于齿轮齿板的偏心距e是第一轴心点和第二轴心点之间的直线距离，e为1.35mm-1.65mm。根据本发明的高强度连续式座椅偏心调角器，通过将齿圈齿板相对于齿轮齿板的偏心距e设置为1.35mm-1.65mm，提高调角器的强度，在保持强度不变的情况下，使得调角器具有较小的直径和较轻的重量，从而实现轻量化。

Description

一种高强度连续式座椅偏心调角器 技术领域
本发明涉及汽车座椅，更具体地涉及一种高强度连续式座椅偏心调角器。
背景技术
随着新能源汽车的崛起，以及碳中和政策的执行力度加强，零件级别的轻量化迫在眉睫。对于调角器产品来说，在保证强度等级不变的前提下，尽可能地减小尺寸，减轻重量，是市场对于该类产品的需求。而在缩小汽车座椅调角器尺寸的同时，对调角器强度要求有增无减，如何通过结构创新在保证强度的前提下减小调角器的尺寸及重量，是汽车座椅调角器制造企业所面临的一大难题。
发明内容
为了解决现有技术中的连续式座椅偏心调角器难以在确保强度的前提下减小尺寸的技术问题，本发明提供一种高强度连续式座椅偏心调角器。
根据本发明的高强度连续式座椅偏心调角器，其包括可相对于彼此转动的齿轮齿板和齿圈齿板，所述齿轮齿板和齿圈齿板通过相互啮合的齿相互连接；以及由凸轮驱动的偏心件，所述偏心件在周向方向上旋转以驱动齿轮齿板和齿圈齿板的相对滚动运动；其中，齿圈齿板具有第一轴心点，齿轮齿板具有第二轴心点，齿圈齿板相对于齿轮齿板的偏心距e是第一轴心点和第二轴心点之间的直线距离，e为1.35mm-1.65mm。
优选地，齿轮齿板具有外齿齿轮，齿圈齿板具有内齿齿环，齿轮齿板和齿圈齿板通过相互啮合的外齿齿轮和内齿齿环相互连接，齿圈齿板的内齿与齿轮齿板的外齿的啮合量为0.5mm-0.9mm。
优选地，所述偏心件由楔块和弹簧配合限定，以在啮合位置处将齿轮齿板的外齿齿轮压入到齿圈齿板的内齿齿环内。
优选地，凸轮具有驱动段，楔块由两个楔形段组成，驱动段插入两楔形段的窄侧之间的游隙中，两个楔形段沿着第一轴心点和第二轴心点的连线对称分布。
优选地，齿轮齿板和齿圈齿板具有彼此间隔开的第一啮合点和第二啮合点，这两个啮合点跨越6～12个齿沿着连线对称分布。
优选地，高强度连续式座椅偏心调角器还包括衬套，所述衬套设置于所述楔块的弯曲外表面和齿圈齿板的中心孔之间。
优选地，在所述楔块的周向转动过程中，在第一接触切点处与衬套贴靠的楔块的弯曲外表面沿循对数螺旋线的一部分路径，衬套作用于楔块的对数螺旋线轮廓的载荷力通过第一接触切点指向第一轴心点。
优选地，齿轮齿板具有相对于外齿齿轮同心的圆筒，凸轮具有轴向插入圆筒中伸出的圆环柱。
优选地，圆筒的外圆周表面在第二接触切点处支撑楔块，圆筒作用于楔块的支撑力通过第二轴心点指向第二接触切点。
优选地，载荷力与支撑力之间的压力夹角不大于6.9°。
优选地，弹簧的两端分别连接两楔形段的相互面对的宽侧以通过弹簧在周向方向上作用于楔形段迫使两楔形段撑开。
优选地，高强度连续式座椅偏心调角器还包括用于将齿轮齿板和齿圈齿板保持在一起的抱箍。
优选地，高强度连续式座椅偏心调角器还包括覆盖在凸轮上并连接固定于齿圈齿板的罩盖。
根据本发明的高强度连续式座椅偏心调角器，通过将齿圈齿板相对于齿轮齿板的偏心距e设置为1.35mm-1.65mm，提高调角器的强度，在保持强度不变的情况下，使得调角器具有较小的直径和较轻的重量，从而实现轻量化。总之，根据本发明的小型连续型调角器，在结构上进行创新，使得零件的制造加工进一步简化，在降低重量，减小尺寸的同时，保证高强度等级，满足市场需求。
附图说明
图1是根据本发明的一个优选实施例的高强度连续式座椅偏心调角器的装配示意图；
图2是图1的高强度连续式座椅偏心调角器的剖视图；
图3是图1的高强度连续式座椅偏心调角器的第一侧视图；
图4是图3的局部放大图；
图5是图4的原理说明图；
图6是图1的高强度连续式座椅偏心调角器的第二侧视图；
图7是图6的原理说明图；
图8是图1的高强度连续式座椅偏心调角器的楔块的一个楔形段的示意图；
图9是图1的高强度连续式座椅偏心调角器的第三侧视图。
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。
如图1-图2所示，根据本发明的一个优选实施例的高强度连续式座椅偏心调角器10包括抱箍18、齿轮齿板17和齿圈齿板16，其中，齿轮齿板17和齿圈齿板16被设置为可相对于彼此转动，抱箍18用于将齿轮齿板17和齿圈齿板16保持在一起。在本实施例中，用于吸收轴向作用力的抱箍18固定连接于齿圈齿板16。应该理解，抱箍18并不妨碍齿轮齿板17和齿圈齿板16的相对转动。
对于高强度连续式座椅偏心调角器10的安装而言，齿轮齿板17可安装到椅座上，而齿圈齿板16安装到靠背上，从而调节靠背相对于椅座的倾斜角度。当然，齿轮齿板17和齿圈齿板16的安装位置也可以进行调换，即齿轮齿板17可安装到靠背上，而齿圈齿板16安装到椅座上。
齿轮齿板17和齿圈齿板16通过齿轮连接到彼此以便调整和固定。为了形成齿轮连接，齿轮齿板17上形成外齿齿轮，齿圈齿板16上形成内齿齿环，外齿齿轮和内齿齿环相互啮合，以通过齿啮合传动联接。外齿齿轮的外齿齿顶圆的直径与内齿齿环的内齿齿根圆的直径相比小至少一个齿的高度。外齿齿轮和内齿齿环在齿数上相差至少一个齿的差异，该差异允许内齿齿环在外齿齿轮上进行滚动运动。
齿轮齿板17具有相对于外齿齿轮同心的圆筒17a。根据本实施例的高强度连续式座椅偏心调角器10还包括楔块14，通过其弯曲内表面支撑于圆筒17a上，并通过其弯曲外表面承载齿圈齿板16。相应地，根据本实施例的高强度连续式座椅偏心调角器10还包括衬套15，其设置于楔块14的弯曲外表面和齿圈齿板16的中心孔16a之间。具体地，衬套15与齿圈齿板16同轴心铆接或焊接成一体。另外，根据本实施例的高强度连续式座椅偏心调角器10还 包括凸轮13，其轴向伸出的圆环柱13a插入圆筒17a中并在中央设有用于接纳和匹配驱动轴的镗孔，以通过驱动轴制动凸轮13。另外，凸轮13还具有驱动段13b。楔块14由两个楔形段组成，凸轮13的驱动段13b插入两楔形段的窄侧之间的游隙中以推动楔块14旋转，对称布置的两个楔形段既是径向支撑的核心部件，又是自适应调节啮合间隙的核心部件。而且，根据本实施例的高强度连续式座椅偏心调角器10还包括弹簧12，其两端分别连接两楔形段的相互面对的宽侧，从而通过弹簧12在周向方向上作用于楔形段迫使两楔形段撑开，使得楔块14与衬套15接触。如此，楔块14和弹簧12配合限定偏心件，其用于在啮合位置处将齿轮齿板17的外齿齿轮压入到齿圈齿板16的内齿齿环内。进一步地，根据本实施例的高强度连续式座椅偏心调角器10还包括罩盖11，其覆盖在凸轮13上并连接固定于齿圈齿板16。
根据本实施例的高强度连续式座椅偏心调角器10的具体装配过程包括：衬套15压入齿圈齿板16的中心孔16a中，过盈紧密配合；齿轮齿板17的外齿齿轮与齿圈齿板16的内齿齿环啮合；凸轮13的圆环柱13a嵌入齿轮齿板17的圆筒17a的内圆周表面中；弹簧12的两端分别插入楔块14的两楔形段的宽侧的孔中；楔块14夹持在衬套15的内圆周表面与圆筒17a的外圆周表面形成的空间内，并保持紧贴；抱箍18与齿圈齿板16采用焊接连接；罩盖11与齿圈齿板16焊接连接。
根据本实施例的高强度连续式座椅偏心调角器10的具体工作机理包括：在通过旋转驱动轴进行驱动的过程中，转矩首先都被传递到凸轮13，然后通过驱动段13b传递到偏心件(由楔块14和弹簧12形成)上，偏心件沿着衬套15滑动，使其偏心方向偏移，并因而使得齿轮齿板17的外齿齿轮在齿圈齿板16的内齿齿环中的啮合位置偏移，驱动齿圈齿板16和齿轮齿板17的相对滚动运动，由此可以使得靠背的倾斜度进行连续可变地调节。
齿圈齿板16在立体三维空间具有轴心线，该轴心线投影在二维平面成为一个圆心点，即第一轴心点M16，如图3所示。同样地，齿轮齿板17具有第二轴心点M17。根据本实施例的高强度连续式座椅偏心调角器的偏心距e(即齿圈齿板16相对于齿轮齿板17的偏心距)是第一轴心点M16和第二轴心点M17之间的直线距离，e为1.35mm-1.65mm，从而提高调角器的强度。
如图4所示，齿圈齿板16的内齿与齿轮齿板17的外齿具有啮合量Ovp。当齿圈齿板16的内齿与齿轮齿板17的外齿发生错位的幅度超过啮合量Ovp 时，高强度连续式座椅偏心调角器10表现为滑齿失效。啮合量Ovp越大，高强度连续式座椅偏心调角器10的强度得到提高就越多。在本实施例中，由于偏心距e的适度增加，齿圈齿板16的内齿与齿轮齿板17的外齿的啮合量Ovp增大为0.5mm-0.9mm。
下面结合图5来说明调角器的强度得以提高的原因。固定齿轮齿板17，楔块14绕第二轴心点M17每旋转360°，与齿轮齿板17啮合传动的齿圈齿板16跨一个齿滚动，截取齿圈齿板16上任一点的运行轨迹从A2点到B2点一段，齿圈齿板16旋转角度α，位移行程D为2倍偏心距e，单纯从运动分解理论分析，啮合量Ovp等于偏心距e，但是齿形设计需要考虑强度及防止根切等因素，在工程实际中，啮合量Ovp通常小于偏心距e，当偏心距e＝1.35mm时，位移行程D＝2.7mm，啮合量Ovpt为0.5～0.6mm之间，当偏心距e＝1.55mm时，位移行程D＝3.1mm，啮合量Ovp为0.7～0.8mm之间，当偏心距e＝1.65mm时，位移行程D＝3.3mm，啮合量Ovp为0.8～0.9mm之间。如此，通过偏心距e的设置，调角器的强度得以提高。
回到图1，楔块14由两个楔形段组成，这两个楔形段沿着轴线M16M17(参见图6)对称分布，弹簧12在周向方向上作用于楔形段迫使两楔形段撑开，使得与齿轮齿板17的外齿啮合的齿圈齿板16的内齿跨越6～12个齿并沿着楔块14的轴线M16M17对称分布。也就是说，如图6所示，齿轮齿板17与齿圈齿板16具有彼此间隔开的第一啮合点P1和第二啮合点P2，这两个啮合点P1，P2跨越6～12个齿沿着轴线M16M17对称分布，进一步增加高强度连续式座椅偏心调角器10的强度。在本实施例中，跨越齿圈齿板16的10个内齿与齿轮齿板17的外齿啮合。
下面结合图7来说明调角器的强度得以进一步提高的原因。分别以齿圈节圆16b、齿轮节圆17b简化代替齿圈齿板16和齿轮齿板17，作直线分别连接第一啮合点P1和齿轮齿板17的第二轴心点M17得到直线P1M17，连接第二啮合点P2和齿轮齿板17的第二轴心点M17得到直线P2M17，P1M17和P2M17之间形成夹角β，偏心距e越大，啮合点P1与啮合点P2之间的直线距离增大，夹角β增大，啮合齿的跨越齿数越多，在啮合齿承受载荷发生微小形变时，可以接力周边临近齿啮合支撑，进一步增加高强度连续式座椅偏心调角器10的强度。
特别地，根据本实施例的连续式座椅楔块偏心结构调角器的楔块14的 弯曲外表面形成为对数螺旋线(即等角螺旋线)L的一部分，如图8所示。凸轮13推动楔块14旋转，楔块14的弯曲外表面与衬套15的内圆周表面接触。如图9所示，在楔块14周向转动过程中，在第一接触切点M处与衬套15贴靠的楔块14的弯曲外表面沿循对数螺旋线L的一部分路径，在第二接触切点N处齿轮齿板17的圆筒17a的外圆周表面支撑楔块14。应该理解，第一接触切点M是楔块14的对数螺旋线轮廓与衬套15的内圆轮廓的接触点，也是楔块14的对数螺旋线轮廓与衬套15的内圆的切点，所以第一接触切点M即在衬套15的内圆上，也在楔块14的对数螺旋线L上。同理，第二接触切点N是楔块14的弯曲内表面轮廓与圆筒17a的外圆轮廓的接触点，也是楔块14的弯曲内表面轮廓与圆筒17a的外圆的切点。
衬套15作用于楔块14的对数螺旋线轮廓的载荷力F1通过第一接触切点M指向齿圈齿板16的第一轴心点M16，齿轮齿板17的圆筒17a的外圆周表面作用于楔块14的支撑力F2通过第二轴心点M17指向第二接触切点N，载荷力F1与支撑力F2之间的压力夹角不大于6.9°，在承受更高的外载荷时，始终确保高强度连续式座椅偏心调角器10的楔块14处于自锁状态，压力夹角越小，自锁状态越稳定。
虽然上述实施例的高强度连续式座椅偏心调角器10用于调节靠背相对于椅座的倾斜角度，但是应该理解，该调角器具有广泛的适用性，可用于座椅靠背、腿托、肩部调节等关节部位等。
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 (13)

  1. 一种高强度连续式座椅偏心调角器，其特征在于，该高强度连续式座椅偏心调角器包括：
    可相对于彼此转动的齿轮齿板(17)和齿圈齿板(16)，所述齿轮齿板(17)和齿圈齿板(16)通过相互啮合的齿相互连接；以及
    由凸轮(13)驱动的偏心件(14，12)，所述偏心件(14，12)在周向方向上旋转以驱动齿轮齿板(17)和齿圈齿板(16)的相对滚动运动；
    其中，齿圈齿板(16)具有第一轴心点(M16)，齿轮齿板(17)具有第二轴心点(M17)，齿圈齿板(16)相对于齿轮齿板(17)的偏心距e是第一轴心点(M16)和第二轴心点(M17)之间的直线距离，e为1.35mm-1.65mm。
  2. 根据权利要求1所述的高强度连续式座椅偏心调角器，其特征在于，齿轮齿板(17)具有外齿齿轮，齿圈齿板(16)具有内齿齿环，齿轮齿板(17)和齿圈齿板(16)通过相互啮合的外齿齿轮和内齿齿环相互连接，齿圈齿板(16)的内齿与齿轮齿板(17)的外齿的啮合量(Ovp)为0.5mm-0.9mm。
  3. 根据权利要求2所述的高强度连续式座椅偏心调角器，其特征在于，所述偏心件(14，12)由楔块(14)和弹簧(12)配合限定，以在啮合位置处将齿轮齿板(17)的外齿齿轮压入到齿圈齿板(16)的内齿齿环内。
  4. 根据权利要求3所述的高强度连续式座椅偏心调角器，其特征在于，凸轮(13)具有驱动段(13b)，楔块(14)由两个楔形段组成，驱动段(13b)插入两楔形段的窄侧之间的游隙中，两个楔形段沿着第一轴心点(M16)和第二轴心点(M17)的连线(M16M17)对称分布。
  5. 根据权利要求4所述的高强度连续式座椅偏心调角器，其特征在于，齿轮齿板(17)和齿圈齿板(16)具有彼此间隔开的第一啮合点(P1)和第二啮合点(P2)，这两个啮合点(P1，P2)跨越6～12个齿沿着连线(M16M17)对称分布。
  6. 根据权利要求3所述的高强度连续式座椅偏心调角器，其特 征在于，高强度连续式座椅偏心调角器还包括衬套(15)，所述衬套(15)设置于所述楔块(14)的弯曲外表面和齿圈齿板(16)的中心孔(16a)之间。
  7. 根据权利要求6所述的高强度连续式座椅偏心调角器，其特征在于，在所述楔块(14)的周向转动过程中，在第一接触切点(M)处与衬套(15)贴靠的楔块(14)的弯曲外表面沿循对数螺旋线(L)的一部分路径，衬套(15)作用于楔块(14)的对数螺旋线轮廓的载荷力(F1)通过第一接触切点(M)指向第一轴心点(M16)。
  8. 根据权利要求7所述的高强度连续式座椅偏心调角器，其特征在于，齿轮齿板(17)具有相对于外齿齿轮同心的圆筒(17a)，凸轮(13)具有轴向插入圆筒(17a)中伸出的圆环柱(13a)。
  9. 根据权利要求8所述的高强度连续式座椅偏心调角器，其特征在于，圆筒(17a)的外圆周表面在第二接触切点(N)处支撑楔块(14)，圆筒(17a)作用于楔块(14)的支撑力(F2)通过第二轴心点(M17)指向第二接触切点(N)。
  10. 根据权利要求9所述的高强度连续式座椅偏心调角器，其特征在于，载荷力(F1)与支撑力(F2)之间的压力夹角不大于6.9°。
  11. 根据权利要求3所述的高强度连续式座椅偏心调角器，其特征在于，弹簧(12)的两端分别连接两楔形段的相互面对的宽侧以通过弹簧(12)在周向方向上作用于楔形段迫使两楔形段撑开。
  12. 根据权利要求1所述的高强度连续式座椅偏心调角器，其特征在于，高强度连续式座椅偏心调角器还包括用于将齿轮齿板(17)和齿圈齿板(16)保持在一起的抱箍(18)。
  13. 根据权利要求1所述的高强度连续式座椅偏心调角器，其特征在于，高强度连续式座椅偏心调角器还包括覆盖在凸轮(13)上并连接固定于齿圈齿板(16)的罩盖(11)。
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Publication number Priority date Publication date Assignee Title
CN115320460B (zh) * 2022-07-21 2023-08-18 恺博座椅机械部件有限公司 一种连续式座椅楔块偏心结构调角器
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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008206925A (ja) * 2007-02-28 2008-09-11 Toyota Boshoku Corp 連結装置
CN102548794A (zh) * 2009-08-28 2012-07-04 凯波有限责任两合公司 用于车辆座椅的装配件
DE102020112563A1 (de) * 2019-05-10 2020-11-12 Adient Engineering and IP GmbH Getriebebeschlag für einen fahrzeugsitz, sowie fahrzeugsitz
CN111959356A (zh) * 2020-08-31 2020-11-20 延锋安道拓座椅机械部件有限公司 一种连续式电动调角器系统
CN115320460A (zh) * 2022-07-21 2022-11-11 恺博座椅机械部件有限公司 一种连续式座椅楔块偏心结构调角器
CN115320459A (zh) * 2022-07-21 2022-11-11 恺博座椅机械部件有限公司 一种高强度连续式座椅偏心调角器

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2786446B1 (fr) * 1998-12-01 2001-02-16 Faure Bertrand Equipements Sa Siege de vehicule comportant un mecanisme d'articulation
DE29924597U1 (de) * 1999-08-14 2004-03-11 Keiper Gmbh & Co. Kg Verstellbeschlag für Sitze mit neigungseinstellbarer Lehne, insbesondere für Kraftfahrzeugsitze
DE102005039733A1 (de) * 2005-08-23 2007-03-01 Keiper Gmbh & Co.Kg Getriebestufe
EP2068040B1 (en) * 2006-07-31 2012-02-22 Toyota Boshoku Kabushiki Kaisha Gear and connection device using the gear

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008206925A (ja) * 2007-02-28 2008-09-11 Toyota Boshoku Corp 連結装置
CN102548794A (zh) * 2009-08-28 2012-07-04 凯波有限责任两合公司 用于车辆座椅的装配件
DE102020112563A1 (de) * 2019-05-10 2020-11-12 Adient Engineering and IP GmbH Getriebebeschlag für einen fahrzeugsitz, sowie fahrzeugsitz
CN111959356A (zh) * 2020-08-31 2020-11-20 延锋安道拓座椅机械部件有限公司 一种连续式电动调角器系统
CN115320460A (zh) * 2022-07-21 2022-11-11 恺博座椅机械部件有限公司 一种连续式座椅楔块偏心结构调角器
CN115320459A (zh) * 2022-07-21 2022-11-11 恺博座椅机械部件有限公司 一种高强度连续式座椅偏心调角器

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