WO2021056991A1 - 同心传动调角器以及汽车座椅 - Google Patents

同心传动调角器以及汽车座椅 Download PDF

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Publication number
WO2021056991A1
WO2021056991A1 PCT/CN2020/080138 CN2020080138W WO2021056991A1 WO 2021056991 A1 WO2021056991 A1 WO 2021056991A1 CN 2020080138 W CN2020080138 W CN 2020080138W WO 2021056991 A1 WO2021056991 A1 WO 2021056991A1
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WIPO (PCT)
Prior art keywords
transmission
concentric
plate
tooth plate
hole
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PCT/CN2020/080138
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English (en)
French (fr)
Inventor
黄正坤
张勇
罗贤虎
江冲
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湖北航嘉麦格纳座椅系统有限公司
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Publication of WO2021056991A1 publication Critical patent/WO2021056991A1/zh

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    • 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
    • B60N2/225—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 cycloidal or planetary mechanisms
    • B60N2/2251—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 cycloidal or planetary mechanisms with gears having orbital motion, e.g. sun and planet gears

Definitions

  • the invention relates to the technical field of angle adjustment, in particular to a concentric transmission angle adjuster and a car seat.
  • the angle adjuster is one of the parts of the car seat, so that the user can adjust the angle of the backrest relative to the seat according to their needs.
  • Cid patent CN101941389B discloses a tooth difference planetary gear transmission angle adjuster, which mainly includes an inner tooth plate with an inner gear ring fixedly connected to the backrest, and an outer tooth plate with an outer gear ring fixedly connected to the seat.
  • the eccentric wheel, the wedge block and the wedge torsion spring are all assembled in the sheath.
  • the eccentric wheel has an eccentric ring shape as a whole and forms a planetary gear transmission mechanism with a small tooth difference with the inner tooth plate and the outer tooth plate.
  • the center of the outer tooth plate is O
  • the center of the inner tooth plate is O1
  • the center distance between the two is e, that is, the two need to rotate eccentrically.
  • the circle and the sheath are concentrically fixed, and a gap of slightly more than 2e is left between the outer circle of the inner tooth plate and the sheath.
  • the outer tooth plate is fixed, and the inner tooth plate rotates eccentrically relative to the outer tooth plate.
  • the eccentricity is e. Therefore, the backrest also moves eccentrically relative to the seat with a yaw amplitude of 2e, which will cause the occupant to adjust the backrest.
  • the backrest In addition to rotating around the seat rotation axis, the backrest must also swing up, down, left and right eccentrically relative to the seat rotation center. In severe cases, shaking or noise may occur, which affects the comfort of the occupants.
  • the present invention provides a concentric transmission angle adjuster, which includes an external tooth plate and an internal tooth plate, which rotate eccentrically relative to each other, and also includes a concentric plate, which is arranged concentrically with one of the external tooth plate and the internal tooth plate, The other is provided with a transmission boss, the concentric plate is provided with a transmission hole, the transmission boss is inserted into the transmission hole, and when the transmission boss rotates, it can be tangent to the transmission hole to drive the concentric plate to rotate Realize angle adjustment.
  • the concentric plate By setting the concentric plate with the transmission hole, the concentric plate is connected with the parts that need to adjust the angle. Because the concentric plate and the transmission boss are arranged to roll tangentially, and there is enough clearance in the radial direction, the radial movement of the transmission boss is controlled by the transmission hole. Filtered out, therefore, the concentric plate only transmits pure rotation without eccentric movement. At this time, the concentric plate converts the eccentric rotation of the inner tooth plate or the outer tooth plate into concentric rotation, which provides a concentric transmission angle adjuster. , During the angle adjustment process, the eccentric swing can be improved or even eliminated, thereby improving the user experience.
  • the entire inner contour of the transmission hole coincides with the outer contour of the transmission boss after uniformly expanding e outwardly or partially.
  • the transmission boss is a circular boss with a diameter d
  • the transmission hole is a circular hole with a diameter d+2e.
  • the entire inner contour of the transmission hole coincides with the outer contour of the movement track area of the transmission boss in whole or in part.
  • the transmission boss is a circular boss or a waist circular boss
  • the transmission holes are correspondingly circular holes or waist circular holes.
  • the transmission hole has a notch shape with one side opening, and the opening faces the center of the concentric plate.
  • the number of the transmission bosses and the transmission holes is at least two, and at any position where the inner tooth plate and the outer tooth plate rotate eccentrically, there are at least two transmission bosses and corresponding The driving hole is tangent.
  • the transmission bosses and the transmission holes are evenly distributed along the circumferential direction.
  • the solution also provides a car seat, which is provided with a first part and a second part whose angle is adjustable relative to the first part, and is also provided with an angle adjuster, the angle adjuster being the concentric transmission described in any one of the above
  • the concentric plate is connected with the second component
  • the external tooth plate or the internal tooth plate arranged concentrically with the concentric plate is connected with the first component. Since the angle adjuster is the concentric transmission angle adjuster described in any one of the above, it has the same technical effect as the above.
  • the first component is a seat of the car seat
  • the second component is a backrest.
  • Figure 1 is a schematic diagram of the eccentric state of the external tooth plate and the internal tooth plate of the angle adjuster in embodiment 1;
  • Figure 2 is an axonometric view of the angle adjuster in embodiment 1 viewed from the side of the inner tooth plate;
  • Figure 3 is an axonometric view seen from the side of the external tooth plate in embodiment 1;
  • Figure 4 is a front view of the inner tooth plate side of the angle adjuster in Figure 2;
  • Fig. 5 is a cross-sectional view of Fig. 4.
  • Fig. 6 is an envelope diagram of the movement track of the inner tooth plate transmission boss in embodiment 1;
  • Fig. 7 is a schematic diagram of the concentric plate provided with the driving holes as blind holes in the second embodiment
  • Figure 8 is a cross-sectional view of Figure 7;
  • FIG. 10 is a schematic diagram of a transmission boss provided on the outer plate of the angle adjuster in Embodiment 4.
  • Fig. 11 is a cross-sectional view of Fig. 10.
  • Figure 1 is a schematic diagram of the eccentric state of the external tooth plate 4 and the internal tooth plate 3 of the angle adjuster in embodiment 1;
  • Figure 2 embodiment 1 of the angle adjuster viewed from the side of the internal tooth plate 3 3 is an axonometric view from the side of the external tooth plate 4 in Example 1;
  • Figure 4 is a front view of the inner tooth plate 3 of the angle adjuster in Figure 2;
  • Figure 5 is a cross-sectional view of Figure 4.
  • the angle adjuster includes an outer gear plate 4, an inner gear plate 3, an eccentric wheel, a wedge block, etc., wherein the outer gear plate 4 has an outer gear ring, and the inner gear plate 3 has an inner gear ring.
  • the outer gear ring and the inner gear ring mesh with each other.
  • the outer tooth plate 4 is connected with the seat, and the inner tooth plate 3 is connected with the backrest.
  • the center of the inner gear plate 3 has a shaft shoulder, the middle of the outer gear plate 4 is provided with a shaft center hole, the shaft shoulder is inserted into the shaft center hole, the shaft shoulder and the shaft center hole are eccentrically arranged, and a radial eccentricity is formed between the shaft shoulder and the shaft center hole
  • the eccentric wheel is arranged in the radial eccentric region.
  • the eccentric wheel has an eccentric ring structure as a whole. It forms a planetary gear transmission mechanism with a small tooth difference with the inner tooth plate 3 and the outer tooth plate 4.
  • the angle adjuster also includes a sheath 1.
  • the above-mentioned inner tooth plate 3, outer tooth plate 4, eccentric wheel and other components are all assembled in the sheath 1.
  • the sheath 1 can protect the above-mentioned components and help ensure the coaxiality. , Maintain the meshing performance of the external tooth plate 4 and the internal tooth plate 3.
  • the inner tooth plate 3 has a central hole 33 of the inner tooth plate, marked as O
  • the outer tooth plate 4 has a central hole 42 of the outer tooth plate, marked as O1.
  • the two are eccentric, resulting in an eccentric distance e.
  • the angle adjuster further includes a concentric plate 2, the concentric plate 2 is arranged concentrically with the outer tooth plate 4 and the sheath 1, and the concentric plate 2 is rotatable relative to the outer tooth plate 4 and the sheath 1.
  • the inner circle 11 of the sheath is concentrically fitted with the outer circle 22 of the concentric plate and the outer circle 41 of the outer tooth plate.
  • the inner circle 11 of the sheath and the outer circle 41 of the outer tooth plate can be welded or riveted fixedly.
  • the concentric plate 2 is provided between the outer end surface 32 of the inner tooth plate and the inner end surface 12 of the sheath.
  • the concentric plate 2 is provided with a transmission hole 21, and the outer end surface 32 of the inner tooth plate is provided with a transmission boss 31. After assembly, the transmission boss 31 of the inner tooth plate 3 can be inserted into the transmission hole 21.
  • the concentric plate 2 has an outer end surface 23 of the concentric plate facing the inner end surface 12 of the sheath, and an inner end surface 24 of the concentric plate facing the inner tooth plate 3.
  • the concentric plate 2 is also provided with a concentric plate center hole 25.
  • the concentric plate center hole 25 is for opening to avoid interference with other components.
  • the inner tooth plate 3 is arranged in a stepped manner.
  • the concentric plate 2 It is also arranged in a stepped shape, which can reduce the axial size of the core component and also reduce the depth of the sheath 1.
  • the transmission boss 31 When the inner tooth plate 3 rotates eccentrically relative to the outer tooth plate 4, the transmission boss 31 will move in the transmission hole 21 and drive the concentric plate 2 to rotate. Because the concentric plate 2 is arranged concentrically with the sheath 1 and the outer tooth plate 4, concentric The plate 2 can only rotate around its central axis, without eccentric movement. In order to realize that the transmission boss 31 drives the concentric plate 2 to rotate, the setting of the transmission hole 21 needs to be ensured. The transmission boss 31 can be tangent to the transmission hole 21 during the movement, so that the transmission torque drives the concentric plate 2 to rotate.
  • the arrangement of the transmission boss 31 and the transmission hole 21 can be arranged according to a certain rule. Assuming that the transmission boss 31 is arranged at a distance D from the center of the inner tooth plate 3, when a plurality of transmission bosses 31 are provided, the geometric centers of the plurality of transmission bosses 31 are distributed with the center of the inner tooth plate 3 as the center and the diameter is D Correspondingly, the transmission hole 21 is set on the circle with the center of the concentric plate 2 and the diameter D.
  • the inner contour of the transmission hole 21 (that is, the contour of the hole wall) is equivalent to the outer contour of the transmission boss 31, formed by uniformly expanding e outward, where e is the outer tooth The eccentricity of the plate 4 and the inner tooth plate 3.
  • the inner contour of the hole wall of the transmission hole 21 is formed by uniformly expanding the outer contour of the circular boss, and the outer contour of the circular boss If it expands outwards evenly, it is still circular.
  • the resulting transmission hole 21 is a circular hole.
  • the diameter of the circular boss is e, and the diameter after uniform expansion is d+2e. Then the diameter of the transmission hole 21 is d+2e.
  • tolerances are allowed during actual assembly, which can be slightly larger than d+2e.
  • Fig. 6 is an envelope diagram of the movement trajectory of the transmission boss 31 of the inner tooth plate 3 in the first embodiment.
  • the internal tooth plate 3 can make the trajectory of the transmission boss 31 when it moves eccentrically.
  • the transmission boss 31 rotates 1 degree and is at position 1, when it rotates 2 degrees, it is at position 2..., when it rotates by n degrees, it is at position n.
  • the positions of n transmission bosses 31 are superimposed to form the movement trajectory shown in Fig. 6.
  • the movement trajectory of the transmission boss 31 defines the movement area of the transmission boss 31 during the angle adjustment of the angle adjuster, and the outer contour of the movement area defines When the circular area corresponds to the concentric plate 2, it is used as the basis for setting the transmission hole 21.
  • the transmission hole 21 overlaps the circular area.
  • the diameter of the circular area is the diameter of the transmission hole 21.
  • the transmission boss The center distance between 31 and the inner tooth plate 3 is equal to the center distance between the transmission hole 21 and the concentric plate 2, that is, they are all distributed on a circle with a diameter D.
  • d is 10.4 mm and e is 1.3 mm.
  • the diameter of the circular area defined by the motion trajectory made by the envelope method is 13 mm, which is consistent with the conclusion drawn by the above-mentioned d+2e method.
  • a total of six transmission bosses 31 are provided, and six transmission holes 21 are correspondingly provided.
  • the transmission bosses 31 and the transmission holes 21 are arranged uniformly along the inner tooth plate 3 and the concentric plate 2 respectively. During the angle adjustment process, Each transmission boss 31 and the corresponding transmission hole 21 always keep tangent. It can be understood that the number of transmission holes 21 and transmission bosses 31 is not limited to six, but in theory, two or more than two should be provided to ensure that one or more transmission bosses 31 can be tangent to the transmission hole 21 in a clockwise direction. , One or more transmission bosses 31 can be tangent in the counterclockwise direction.
  • the tangency needs to be maintained and the transmission function can be stably realized to drive the concentric plate 2 to rotate stably, for example, two transmissions
  • the holes 21 and the transmission boss 31 can be arranged symmetrically with respect to the center of the concentric plate 2 and the inner tooth plate 3. When the three transmission holes 21 and the transmission boss 31 are provided, they can be evenly distributed along the circumferential direction. In actual design, the number and distribution positions of the transmission holes 21 and the transmission bosses 31 can be reasonably determined according to the transmission requirements, strength requirements, etc., and this solution is not limited.
  • Fig. 7 is a schematic diagram of the concentric plate 2 provided with a driving hole 21 as a blind hole in Embodiment 2;
  • Fig. 8 is a cross-sectional view of Fig. 7.
  • the transmission hole 21 is a through hole penetrating the inner tooth plate 3. It should be understood that the transmission hole 21 is provided by using the tangential interference between the hole wall and the transmission boss 31 to drive the concentric plate 2 to rotate, so the transmission hole 21 It is not limited to the through-hole structure, but may also be a blind hole. As shown in embodiment 2, it is the same as embodiment 1, except that the transmission hole 21 is a blind hole structure, and the hole end of the blind hole faces the transmission boss 31, and the transmission boss 31 is inserted in the blind hole to drive the concentric plate 2 Rotation, other structures and principles are the same as in Embodiment 1, and will not be repeated. Obviously, the driving hole 21 being a blind hole is also applicable to other embodiments.
  • the concentric plate 2 is defined between the inner end surface 12 of the sheath and the outer end surface 32 of the inner tooth plate, and is sleeved with the transmission boss 31 of the inner tooth plate 3, which is combined with the inner tooth plate 3 and the sheath
  • the axial gap should not be too large, so as not to affect the meshing effect of the outer tooth plate 4 and the inner tooth plate 3.
  • the axial gap can be set to be smaller than 0.5mm.
  • the transmission boss 31 is a circular boss as an example.
  • the transmission boss 31 is not limited to a circular boss, it can be a regular geometric boss, or it can be arbitrary.
  • the shape of the transmission hole 21 follows the above-mentioned arrangement rule. That is, both the transmission hole 21 and the transmission boss 31 are geometrically centered on a circle with a diameter of D, and the inner contour of the transmission hole 21 is formed by the outer contour of the transmission boss 31 being uniformly expanded e, or the transmission hole 21 The inner contour is made according to the envelope method.
  • the following embodiments also provide a scheme in which the transmission boss 31 and the transmission hole 21 are waist-round.
  • FIG. 9 is an envelope diagram of the movement trajectory of the transmission boss 31 of the inner tooth plate 3 of the angle adjuster in the third embodiment.
  • This embodiment is the same as Embodiment 1, except that the transmission boss 31 and the transmission hole 21 are non-circular, the transmission boss 31 is a waist circular boss, and the transmission hole 21 is a waist circular hole correspondingly.
  • the shape of the transmission hole 21 is determined according to the movement trajectory of the transmission boss 31.
  • the transmission boss 31 with a waist circular shape is distributed on a circle with a diameter of D.
  • the center of the circle is the center of the inner tooth plate 3, and the transmission holes 21 are also distributed with a diameter of D On the circle of, the center of the circle is the center of the concentric plate 2.
  • the inner contour of the transmission hole 21 can also be determined as a waist circle formed by the outer contour of the transmission boss 31 uniformly expanding e outward.
  • Fig. 10 is a schematic diagram of a transmission boss 31 provided on the outer plate of the angle adjuster in Embodiment 4;
  • Fig. 11 is a cross-sectional view of Fig. 10.
  • the outer tooth plate 4 is connected to the seat, the inner tooth plate 3 is connected to the backrest, and the inner tooth plate 3 moves eccentrically relative to the outer tooth plate 4.
  • the angle adjustment is the relative adjustment of the seat and back Rotation adjustment.
  • the inner tooth plate 3 and the outer tooth plate 4 are in a relative movement relationship.
  • the outer tooth plate 4 can also be connected with the backrest, and the inner tooth plate 3 is connected with the seat. Taking the seat as the reference frame, the outer tooth plate 4 can also be connected to the seat. The tooth plate 4 moves eccentrically relative to the inner tooth plate 3.
  • the transmission boss 43 is provided on the external gear plate 4, and the transmission hole 21 of the concentric plate 2 is matched with the transmission boss 43 of the external gear plate 4.
  • the working principle and the determination of the transmission hole 21 The method is the same as the above embodiment, except that the setting position of the transmission boss 43 is changed from the inner tooth plate 3 to the outer tooth plate 4, and the concentric plate 2 is located between the outer tooth plate 4 and the sheath 1, as shown in FIG. 11, From left to right, it is the inner tooth plate 3, the outer tooth plate 4, the concentric plate 2, the inner end surface 12 of the sheath.
  • the inner tooth plate 3 is arranged concentrically with the sheath 1 and the concentric plate 2. Specifically, the outer circle of the inner tooth plate and the inner circle 11 of the sheath can be welded or riveted to be fixedly connected.
  • the transmission boss 43 provided on the outer tooth plate 4 is also a waist circle, but the transmission hole 21 provided on the concentric plate 2 is not a complete waist circle, but is arranged in a concentric The notch structure at the wall of the central hole of the plate 2, that is, one side of the drive hole 21 is open, facing the center.
  • the weight of the concentric plate 2 can be reduced, and the opening faces the center side, which is equivalent to removing the radially inward part, and does not affect the transmission of the circumferential transmission.
  • the transmission hole 21 may be a complete hole shape (such as Embodiment 1-3), or a hole shape with a gap (such as Embodiment 4). If the transmission hole 21 has a complete hole shape, the entire outer contour of the transmission hole 21 coincides with the outer contour of the transmission bosses 31 and 43 after uniformly expanding e outwards, or the entire inner contour of the transmission hole 21 and the transmission convex The outer contours of the movement trajectory regions of the stages 31 and 43 overlap as a whole.
  • the entire outer contour of the transmission hole 21 coincides with the outer contour of the transmission bosses 31 and 43 after uniformly expanding e, or the entire inner contour of the transmission hole 21 is in line with the transmission
  • the partial coincidence of the outer contours of the movement trajectory area of the bosses 31 and 43 is equivalent to removing a part of the contour determined by the above two methods as the entire inner contour of the transmission hole 21.
  • the removed area should ensure that the circumferential transmission is not affected. If necessary, ensure that there are always at least two sets of tangent transmission bosses 31, 43 and transmission holes 21 during the rotation.
  • the concentric plate 2 by providing a concentric plate 2 with a transmission hole 21, the concentric plate 2 is connected to the backrest. Because the concentric plate 2 and the transmission bosses 21, 43 are arranged tangentially and rolling, and there is sufficient clearance in the radial direction, the transmission convex The radial movement of the tables 31 and 43 is filtered out by the transmission holes. Therefore, the concentric plate 2 only transmits pure rotation without eccentric movement. At this time, the concentric plate 2 converts the eccentric rotation of the inner tooth plate 3 or the outer tooth plate 4 into Concentric rotation provides a concentric transmission angle adjuster. In this way, the eccentric swing can be improved or eliminated during the angle adjustment process, thereby improving the user experience.
  • the concentric plate 21 is concentric with the outer tooth plate 4 or concentric with the inner tooth plate 3.
  • the arrangement principle is that when the outer tooth plate 4 moves relative to the inner tooth plate 3, the concentric plate 21 is concentric with the inner tooth plate 3.
  • the plate 3 is concentric, and the transmission boss 43 is arranged on the outer tooth plate; when the inner tooth plate 3 moves relative to the outer tooth plate 4, the concentric plate 21 is concentric with the outer tooth plate 3, and the transmission boss 31 is arranged on the inner tooth plate 3. That is, the concentric plate 21 is concentric with the relatively stationary one, and the transmission bosses 31, 43 are provided on the relatively moving one.
  • the outer tooth plate 4 and the inner tooth plate 3, the one that moves relative to each other, is connected to the backrest , The relatively stationary one is connected to the seat.
  • the concentric transmission angle adjuster in addition to the angle adjustment of the backrest, can also be used for the angle adjustment of other parts. For example, it can also be used for the four-bar linkage of the seat basin that requires folding or angle adjustment.
  • This article does not limit the application conditions of the concentric transmission angle adjuster. It can be summarized here as follows: the car seat is provided with a first part and a second part whose angle is adjustable relative to the first part.
  • the concentric plate 2 of the concentric transmission angle adjuster is connected to the second part, that is, the concentric plate 2 is connected to the angle that needs to be adjusted.
  • the external tooth plate 4 or the internal tooth plate 3 arranged concentrically with the concentric plate 2 is connected to the first component.
  • the first part is the seat and the second part is the backrest; for example, when used in the seat basin and the four-bar linkage mechanism, the four-bar linkage mechanism and the seat basin are the first part and the second part respectively. part.
  • This solution also provides an embodiment of a car seat.
  • the car seat is provided with an angle adjuster, and the angle adjuster is the concentric transmission angle adjuster described in any of the above embodiments, and will not be repeated here.

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

Abstract

一种同心传动调角器，包括相对偏心转动的外齿板（4）和内齿板（3），还包括同心板（2），与外齿板和内齿板中的一者同心设置，另一者设有传动凸台（31），同心板设置传动孔（21），传动凸台插入传动孔，传动凸台转动时能够与传动孔相切以带动同心板转动。通过设置具有传动孔的同心板，将内齿板或外齿板的偏心转动转化为同心转动，消除了偏心摆动。一种汽车座椅也被公开。

Description

同心传动调角器以及汽车座椅
本申请要求于2019年09月27日提交中国专利局、申请号为201910927306.4、发明名称为“同心传动调角器以及汽车座椅”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本发明涉及角度调节技术领域，具体涉及一种同心传动调角器以及汽车座椅。
背景技术
调角器是汽车座椅配备的部件之一，以便使用者根据自己的需求调节靠背相对座椅的角度。
中国专利CN101941389B公开了一种齿差行星齿轮传动调角器，该调角器主要包括与靠背固定连接的带内齿圈的内齿板、与椅座固定连接的带外齿圈的外齿板、偏心轮、楔形块以及楔紧扭簧，都装配在护套内。偏心轮整体呈偏心环状且与内齿板和外齿板构成少齿差行星齿轮传动机构。
该结构的调角器，根据其传动原理，外齿板的中心为O，内齿板的中心为O1，两者之间的中心距为e，即二者需要偏心转动，外齿板的外圆与护套之间同心固联，内齿板外圆与护套之间留有略大于2e的间隙。调节过程中，外齿板固定，内齿板相对外齿板做偏心转动，偏心距为e，因此，靠背相对椅座也作偏心运动，偏摆幅度为2e，这将导致乘员在进行靠背调 节过程中靠背除绕椅座转轴旋转外，还必然相对椅座旋转中心上、下、左、右偏心摆动，严重时可能发生抖动或噪音，影响乘员舒适度。
发明内容
本发明提供一种同心传动调角器，包括外齿板和内齿板，二者相对偏心转动，还包括同心板，与所述外齿板和所述内齿板中的一者同心设置，另一者设有传动凸台，所述同心板设置传动孔，所述传动凸台插入所述传动孔，所述传动凸台转动时能够与所述传动孔相切以带动所述同心板转动实现角度调节。
通过设置具有传动孔的同心板，同心板与需要调节角度的部件连接，由于同心板与传动凸台相切滚动设置，且径向留有足够的间隙，传动凸台的径向运动被传动孔过滤掉，因此，同心板只传递纯转动，不做偏心运动，则此时同心板将内齿板或外齿板的偏心转动转化为同心转动，即提供了一种同心传动调角器，这样，在角度调节过程中，偏心摆动得以改善乃至消除，从而改善用户体验。
可选地，所述传动孔的整个内轮廓，与所述传动凸台的外轮廓向外均匀扩大e后的整体或局部重合。
可选地，所述传动凸台为直径为d的圆形凸台，所述传动孔为直径为d+2e的圆形孔。
可选地，所述传动孔的整个内轮廓，与所述传动凸台的运动轨迹区域的外轮廓的整体或局部重合。
可选地，所述传动凸台为圆形凸台或腰圆形凸台，所述传动孔对应为 圆形孔或腰圆形孔。
可选地，所述传动孔为一侧开口的缺口形状，开口朝向所述同心板的中心。
可选地，所述传动凸台和所述传动孔的数量至少为两个，所述内齿板和所述外齿板相对偏心转动的任意位置，至少有两个所述传动凸台与对应的所述传动孔相切。
可选地，所述传动凸台和所述传动孔均沿周向均布。
本方案还提供一种汽车座椅，设有第一部件和相对第一部件角度可调的第二部件，还设有调角器，所述调角器为上述任一项所述的同心传动调角器，所述同心板与所述第二部件连接，与所述同心板同心设置的所述外齿板或所述内齿板，与所述第一部件连接。由于所述调角器为上述任一项所述的同心传动调角器，则具有与上述相同的技术效果。
可选地，所述第一部件为所述汽车座椅的椅座，所述第二部件为靠背。
附图说明
图1为实施例1中调角器的外齿板和内齿板的偏心状态示意图；
图2实施例1中调角器从内齿板侧看的轴测图；
图3是实施例1中从外齿板侧看的轴测图；
图4是图2中调角器内齿板侧的主视图；
图5是图4的剖视图。
图6为实施例1中内齿板传动凸台的运动轨迹包络图；
图7为实施例2中同心板设置传动孔为盲孔的示意图；
图8为图7的剖视图；
图9为实施例3中调角器的内齿板的传动凸台运动轨迹的包络图；
图10为实施例4中调角器外侧板设置传动凸台的示意图；
图11为图10的剖视图。
图1-11中附图标记说明如下：
1.护套；11.护套内圆；12.护套内端面；2.同心板；21.传动孔；22.同心板外圆；23.同心板外端面；24.同心板内端面；3.内齿板；31、43传动凸台；32.内齿板外端面；33.内齿板中心孔；4.外齿板；41.外齿板外圆；42.外齿板中心孔。
具体实施方式
为了使本领域的技术人员更好地理解本发明的技术方案，下面结合附图和具体实施例对本发明作进一步的详细说明。
实施例1
请参考图1-5，图1为实施例1中调角器的外齿板4和内齿板3的偏心状态示意图；图2实施例1中调角器从内齿板3侧看的轴测图；图3是实施例1中从外齿板4侧看的轴测图；图4是图2中调角器内齿板3侧的主视图；图5是图4的剖视图。
调角器包括外齿板4、内齿板3、偏心轮、楔形块等，其中，外齿板4具有外齿圈，内齿板3具有内齿圈，外齿圈和内齿圈相啮合，外齿板4与椅座连接，内齿板3与靠背连接。内齿板3的中心具有轴肩，外齿板4的 中间设有轴心孔，轴肩插入轴心孔，轴肩和轴心孔偏心设置，轴肩和轴心孔之间形成径向偏心区域，偏心轮设置于该径向偏心区域内，偏心轮整体呈偏心环状结构，与内齿板3、外齿板4构成少齿差行星齿轮传动机构，靠背角度调节时，内齿板3和外齿板4相对作偏心转动，具体的工作原理与背景技术描述相同，可参照理解。另外，调角器还包括护套1，上述的内齿板3、外齿板4、偏心轮等构件均装配在护套1内，护套1可以保护上述构件，并有利于保证同轴度，保持外齿板4和内齿板3的啮合性能。
如图1所示，内齿板3具有内齿板中心孔33，标为O，外齿板4具有外齿板中心孔42，标为O1，二者偏心，产生偏心距e。
在本实施例中，调角器还包括同心板2，同心板2与外齿板4、护套1同心设置，且同心板2相对外齿板4、护套1可转动。如图5所示，护套内圆11与同心板外圆22以及外齿板外圆41均同心配合，护套内圆11与外齿板外圆41可以焊接或铆接固连。如图2、3所示，同心板2设于内齿板外端面32和护套内端面12之间。与此同时，同心板2设有传动孔21，内齿板外端面32设有传动凸台31，装配后，内齿板3的传动凸台31能够插入到传动孔21中。如图2、3所示，同心板2具有朝向护套内端面12的同心板外端面23，和朝向内齿板3的同心板内端面24。另外，本实施例中，同心板2还设有同心板中心孔25，同心板中心孔25为让开孔，避免与其他构件干涉，另外，内齿板3台阶状设置，这里的同心板2也呈台阶状设置，可减小核心件的轴向尺寸，也可减小护套1的深度。
当内齿板3相对外齿板4作偏心转动时，传动凸台31会在传动孔21中移动，并带动同心板2转动，由于同心板2与护套1、外齿板4同心设 置，同心板2只能绕其中心轴线转动，而不会作偏心运动。为实现传动凸台31带动同心板2转动，传动孔21的设置需要保证，传动凸台31在运动过程中，能够与传动孔21相切，从而传递扭矩带动同心板2转动。
为实现此目的，传动凸台31和传动孔21的布置可按照一定的规律布置。假设传动凸台31布置在与内齿板3中心相距D的位置，设置多个传动凸台31时，则多个传动凸台31的几何中心分布在以内齿板3中心为圆心、直径为D的圆上，与之对应的，传动孔21设置在同心板2中心为圆心、直径为D的圆上。而为了保持相切，还满足：传动孔21的内轮廓(即孔壁的轮廓)，相当于在传动凸台31外轮廓的基础上，向外均匀扩大e后形成，其中，e为外齿板4和内齿板3的偏心距。
以本实施例中的传动凸台31设置为圆形凸台为例，则传动孔21的孔壁内轮廓为在圆形凸台的外轮廓均匀向外扩大e形成，圆形凸台外轮廓向外均匀扩大则仍为圆形，得到的传动孔21相应为圆形孔，圆形凸台直径为e，均匀扩大后的直径为d+2e，则传动孔21的直径为d+2e，当然实际装配时允许存在公差，可略大于d+2e。
除此以外，还可以通过包络法获得传动孔21的形状和布置位置，以保证传动凸台31能够在运动过程与传动孔21的孔壁保持相切。如图所6示，图6为实施例1中内齿板3传动凸台31的运动轨迹包络图。
内齿板3在作偏心运动时，可以作出传动凸台31的运动轨迹，比如，传动凸台31转动1度处于位置1，转动2度时处于位置2…,转动n度时，处于位置n，n个传动凸台31的位置叠加形成图6所示的运动轨迹，传动凸台31的运动轨迹限定出传动凸台31在调角器角度调节过程中的运动区 域，运动区域的外轮廓限定出圆形区域，该圆形区域对应于同心板2时，即作为传动孔21的设置依据，传动孔21和该圆形区域重合，圆形区域的直径为传动孔21的直径，传动凸台31与内齿板3的中心距，等于传动孔21与同心板2的中心距，即均分布在直径为D的圆上。该实施例中，d为10.4mm，e为1.3mm，利用包络法作出的运动轨迹限定的圆形区域，其直径为13mm，与上述d+2e方式得出的结论一致。
该实施例中，共设置六个传动凸台31，相应地设置六个传动孔21，传动凸台31和传动孔21，分别沿内齿板3、同心板2均匀布置，角度调节过程中，每个传动凸台31与对应的传动孔21，始终保持相切。可以理解，传动孔21和传动凸台31的数量不限于六个，但理论上应当设置两个或多余两个，保证一个或以上的传动凸台31能够沿顺时针方向与传动孔21相切，一个或以上的传动凸台31能够沿逆时针方向相切，在数量较小的情况下，需要保持相切后能够稳定地实现传动功能，驱动同心板2稳定地转动，比如设置两个传动孔21和传动凸台31时，可以相对同心板2、内齿板3的中心对称设置，设置三个传动孔21、传动凸台31时，可以沿周向均布。实际设计时，可以传动需求、强度需求等，合理地确定传动孔21和传动凸台31的数量以及分布位置，本方案并不做限制。
实施例2
如图7、8所示，图7为实施例2中同心板2设置传动孔21为盲孔的示意图；图8为图7的剖视图。
实施例1中，传动孔21为贯穿内齿板3的通孔，应当知晓，设置传动孔21是利用其孔壁与传动凸台31的相切干涉，带动同心板2转动，故传 动孔21不限于通孔结构，也可以是盲孔。如实施例2所示，与实施例1相同，只是传动孔21为盲孔结构，盲孔的孔口端朝向传动凸台31，传动凸台31插装在盲孔内，以驱动同心板2转动，其他结构和原理与实施例1一致，不再赘述。显然，传动孔21是盲孔也适用于其他实施例。
实施例1、2中，同心板2被限定在护套内端面12与内齿板外端面32之间，并与内齿板3的传动凸台31套装，其与内齿板3、护套1之间需要存在一定的轴向间隙以保证同心板2能自由转动，当然，轴向间隙不宜过大，以免影响外齿板4和内齿板3的啮合效果，轴向间隙可以设置为小于0.5mm。
需要说明的是，上述实施例中以传动凸台31为圆形凸台为例，实际上，传动凸台31不限于圆形凸台，可以是规则几何形状的凸台，也可以是任意的异形凸台，无论传动凸台31形状如何，传动孔21的形状都遵循上述的布置规律。即，传动孔21和传动凸台31都是几何中心分布在直径为D的圆上，且传动孔21的内轮廓为传动凸台31外轮廓向外均匀扩大e形成，或者，传动孔21的内轮廓是按照包络法作出。下述实施例还给出传动凸台31和传动孔21是腰圆形的方案。
实施例3
请参考图9，图9为实施例3中调角器的内齿板3的传动凸台31运动轨迹的包络图。
该实施例与实施例1相同，只是传动凸台31和传动孔21均非圆形，传动凸台31为腰圆形的凸台，传动孔21相应为腰圆孔。根据传动凸台31的运动轨迹确定传动孔21的形状，腰圆形的传动凸台31分布在直径为D的圆上，圆心为内齿板3的中心，传动孔21也分布在直径为D的圆上，圆心为同心板2的中心。当然，如上所述，除了通过包络法确定传动孔21的形状，传动孔21的内轮廓也可确定为传动凸台31外轮廓向外均匀扩大e形成的腰圆形。
实施例4
如图10、11所示，图10为实施例4中调角器外侧板设置传动凸台31的示意图；图11为图10的剖视图。
实施例1、2、3中，外齿板4和椅座连接，内齿板3和靠背连接，内齿板3相对外齿板4偏心运动，可以理解，角度调节为椅座和靠背的相对转动调节，相应地，内齿板3和外齿板4是相对运动关系，则外齿板4也可以与靠背连接，而内齿板3与椅座连接，以椅座为参考系，则外齿板4相对内齿板3偏心运动。此时，可以如图10、11所示，传动凸台43设置在外齿板4，同心板2的传动孔21与外齿板4的传动凸台43相配合，工作原理和传动孔21的确定方式与上述实施例一致，只是传动凸台43的设置位置由内齿板3变动为设置到外齿板4，同心板2处于外齿板4和护套1之间，如图11所示，从左至右，依次为内齿板3、外齿板4、同心板2、护套内端面12。内齿板3与护套1、同心板2同心设置，具体地，内齿板外圆与护套内圆11可以焊接或铆接固连。
另外，如图10所示，与实施例3相似，外齿板4设置的传动凸台43也是腰圆形，只是同心板2设置的传动孔21并非完整的腰圆形，而是设置在同心板2中心孔孔壁处的缺口结构，即传动孔21的一侧开口，朝向其中心。如此设置，可以减轻同心板2的重量，开口朝向中心一侧，相当于去掉径向向内的部分，并不影响周向传动的传递。
结合上述实施例可以理解，传动孔21可以是完整的孔形(比如实施例1-3)，也可以是具有缺口的孔形(比如实施例4)。传动孔21具有完整的孔形，则传动孔21的整个外轮廓，与传动凸台31、43的外轮廓向外均匀扩大e后的整体重合，或者传动孔21的整个内轮廓，与传动凸台31、43的运动轨迹区域的外轮廓的整体重合。传动孔21为具有缺口的孔形，则传动孔21的整个外轮廓，与传动凸台31、43的外轮廓向外均匀扩大e后的局部重合，或者传动孔21的整个内轮廓，与传动凸台31、43的运动轨迹区域的外轮廓的局部重合，相当于通过上述两种方式确定的轮廓去除一部分后，作为传动孔21的整个内轮廓，去除的面积应当以保证不影响周向传动为必要，保证转动过程中始终具有至少两组相切的传动凸台31、43和传动孔21。
上述各实施例，通过设置具有传动孔21的同心板2，同心板2与靠背连接，由于同心板2与传动凸台21、43相切滚动设置，且径向留有足够的间隙，传动凸台31、43的径向运动被传动孔过滤掉，因此，同心板2只传递纯转动，不做偏心运动，则此时同心板2将内齿板3或外齿板4的偏心转动转化为同心转动，即提供了一种同心传动调角器，这样，在角度调节过程中，偏心摆动得以改善乃至消除，从而改善用户体验。
值得注意的是，上述实施例中，同心板21与外齿板4同心或与内齿板3同心，设置原则是，外齿板4相对内齿板3运动时，则同心板21与内齿板3同心，传动凸台43设置于外齿板；内齿板3相对外齿板4运动时，则同心板21与外齿板3同心，传动凸台31设置于内齿板3。即，同心板21与相对静止的一者同心，传动凸台31、43设置于相对运动的一者，以上实施例中，外齿板4和内齿板3，相对运动的一者与靠背连接，相对静止的一者与椅座连接。
需要说明的是，上述提供的同心传动调角器除了用于靠背的角度调节外，还可以用于其他部件的角度调节，比如，还可以用于座盆四连杆机构上需要折叠或角度调节的工况，本文对同心传动调角器的应用工况不做限制。在这里可概括为，汽车座椅设有第一部件和相对第一部件角度可调的第二部件，同心传动调角器的同心板2与第二部件连接，即同心板2与需要调节角度的部件连接，与同心板2同心设置的所述外齿板4或所述内齿板3，与第一部件连接。则，对于上述实施例的第一部件为椅座，第二部件为靠背；再比如，用于座盆和四连杆机构时，则四连杆机构和座盆分别是第一部件和第二部件。
本方案还提供一种汽车座椅的实施例，汽车座椅设置调角器，调角器为上述任一实施例所述的同心传动调角器，此处不再赘述。
以上仅是本发明的优选实施方式，应当指出，对于本技术领域的普通技术人员来说，在不脱离本发明原理的前提下，还可以做出若干改进和润饰，这些改进和润饰也应视为本发明的保护范围。

Claims (10)

  1. 同心传动调角器，包括外齿板和内齿板，二者相对偏心转动，其特征在于，还包括同心板，与所述外齿板和所述内齿板中的一者同心设置，另一者设有传动凸台，所述同心板设置传动孔，所述传动凸台插入所述传动孔，所述传动凸台转动时能够与所述传动孔相切以带动所述同心板转动。
  2. 如权利要求1所述的同心传动调角器，其特征在于，所述传动孔的整个内轮廓，与所述传动凸台的外轮廓向外均匀扩大e后的整体或局部重合。
  3. 如权利要求2所述的同心传动调角器，其特征在于，所述传动凸台为直径为d的圆形凸台，所述传动孔为直径为d+2e的圆形孔。
  4. 如权利要求1所述的同心传动调角器，其特征在于，所述传动孔的整个内轮廓，与所述传动凸台的运动轨迹区域的外轮廓的整体或局部重合。
  5. 如权利要求2或4所述的同心传动调角器，其特征在于，所述传动凸台为圆形凸台或腰圆形凸台，所述传动孔对应为圆形孔或腰圆形孔。
  6. 如权利要求2或4所述的同心传动调角器，其特征在于，所述传动孔为一侧开口的缺口形状，开口朝向所述同心板的中心。
  7. 如权利要求1-4任一项所述的同心传动调角器，其特征在于，所述传动凸台和所述传动孔的数量至少为两个，所述内齿板和所述外齿板相对偏心转动的任意位置，至少有两个所述传动凸台与对应的所述传动孔相切。
  8. 如权利要求7所述的同心传动调角器，其特征在于，所述传动凸台和所述传动孔均沿周向均布。
  9. 汽车座椅，设有第一部件和相对第一部件角度可调的第二部件，还 设有调角器，其特征在于，所述调角器为权利要求1-8任一项所述的同心传动调角器，所述同心板与所述第二部件连接，与所述同心板同心设置的所述外齿板或所述内齿板，与所述第一部件连接。
  10. 如权利要求9所述的汽车座椅，其特征在于，所述第一部件为所述汽车座椅的椅座，所述第二部件为靠背。
PCT/CN2020/080138 2019-09-27 2020-03-19 同心传动调角器以及汽车座椅 WO2021056991A1 (zh)

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CN115107597B (zh) * 2022-05-20 2024-03-22 恺博(常熟)座椅机械部件有限公司 一种小型连续型调角器

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