CN210454539U - Concentric transmission angle adjuster and automobile seat - Google Patents
Concentric transmission angle adjuster and automobile seat Download PDFInfo
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- CN210454539U CN210454539U CN201921647367.7U CN201921647367U CN210454539U CN 210454539 U CN210454539 U CN 210454539U CN 201921647367 U CN201921647367 U CN 201921647367U CN 210454539 U CN210454539 U CN 210454539U
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Abstract
The utility model discloses a concentric transmission angle modulation ware and car seat, including outer pinion rack and interior pinion rack, the two relative off-centre rotates, still includes the concentric plate, with outer pinion rack with one in the interior pinion rack sets up with one is concentric, and another is equipped with the transmission boss, the concentric plate sets up the transmission hole, the transmission boss inserts the transmission hole, the transmission boss rotate the time can with the transmission hole is tangent in order to drive the concentric plate rotates. Through setting up the concentric plate that has the transmission hole, and the concentric plate is connected with the back, and the eccentric rotation of this moment concentric plate with interior pinion rack or outer pinion rack turns into concentric rotation, provides a concentric transmission angle modulation ware promptly, like this, in angle modulation process, eccentric swing can improve and even eliminate to improve user experience.
Description
Technical Field
The utility model relates to an angle modulation technical field, concretely relates to concentric transmission angle modulation ware and car seat.
Background
The recliner is one of the components equipped in the seat of the car so that the user can adjust the angle of the backrest with respect to the seat according to his or her own needs.
Chinese patent CN101941389B discloses a tooth difference planetary gear transmission angle adjuster, which mainly comprises an inner toothed plate with an inner gear ring fixedly connected with a backrest, an outer toothed plate with an outer gear ring fixedly connected with a seat, an eccentric wheel, a wedge block and a wedging torsion spring, all of which are assembled in a sheath. The eccentric wheel is integrally in an eccentric ring shape and forms a small tooth difference planetary gear transmission mechanism with the inner toothed plate and the outer toothed plate.
According to the transmission principle of the angle adjuster with the structure, the center of the outer toothed plate is O, the center of the inner toothed plate is O1, the center distance between the two is e, namely the two need eccentric rotation, the excircle of the outer toothed plate and the sheath are fixedly connected in a concentric mode, and a gap slightly larger than 2e is reserved between the excircle of the inner toothed plate and the sheath. In the accommodation process, the external tooth board is fixed, and the internal tooth board is eccentric rotation to the external tooth board, and the eccentricity is e, and consequently, the relative seat support of back also makes eccentric motion, and the beat range is 2e, and this will result in the passenger to carry out the back and adjust in-process back except that rotatory around the seat support pivot, still must be relative the seat support rotation center upper and lower, left and right eccentric swing, probably takes place shake or noise during the serious, influences passenger's comfort level.
SUMMERY OF THE UTILITY MODEL
The utility model provides a concentric transmission angle modulation ware, including outer pinion rack and interior pinion rack, the two relative off-centre rotates, still includes the concentric plate, with outer pinion rack with one in the interior pinion rack sets up with one is concentric, and another is equipped with the transmission boss, the concentric plate sets up the transmission hole, the transmission boss inserts the transmission hole, when the transmission boss rotates can with the transmission hole is tangent in order to drive the concentric plate rotates and realizes angle modulation.
Through setting up the concentric plate that has the transmission hole, the concentric plate is connected with the part that needs angle regulation, because the concentric plate is tangent to roll the setting with the transmission boss, and radially leave sufficient clearance, the radial motion of transmission boss is filtered by the transmission hole, consequently, the concentric plate only transmits pure rotation, do not do eccentric motion, then the eccentric rotation of concentric plate with interior pinion rack or outer pinion rack this moment turns into concentric rotation, a concentric transmission angle modulation ware has been provided promptly, thus, in angle modulation in-process, the eccentric swing can be improved and even eliminated, thereby improve user experience.
Optionally, the whole inner contour of the transmission hole is wholly or partially overlapped with the outer contour of the transmission boss after being uniformly expanded outwards by e.
Optionally, the transmission boss is a circular boss with a diameter d, and the transmission hole is a circular hole with a diameter d +2 e.
Optionally, the entire inner contour of the transmission hole coincides with the whole or part of the outer contour of the motion track area of the transmission boss.
Optionally, the transmission boss is a circular boss or a kidney-shaped boss, and the transmission hole is a circular hole or a kidney-shaped hole.
Optionally, the transmission hole is in the shape of a notch with one side open, and the opening faces to the center of the concentric plates.
Optionally, the number of the transmission bosses and the transmission holes is at least two, and at least two transmission bosses are tangent to the corresponding transmission holes at any positions where the inner toothed plate and the outer toothed plate rotate eccentrically relative to each other.
Optionally, the transmission bosses and the transmission holes are uniformly distributed along the circumferential direction.
This scheme still provides a car seat, is equipped with first part and relative first part angularly adjustable second part, still is equipped with the angle modulation ware, the angle modulation ware be any above-mentioned concentric transmission angle modulation ware, concentric plate with the second part is connected, with concentric plate sets up with one heart outer pinion rack or interior pinion rack, with first part is connected. The angle adjuster is the concentric transmission angle adjuster, so that the technical effects are the same as those of the concentric transmission angle adjuster.
Optionally, the first component is a seat of the car seat and the second component is a backrest.
Drawings
Fig. 1 is a schematic diagram of the eccentric states of an outer toothed plate and an inner toothed plate of an angle adjuster in embodiment 1;
figure 2 is an isometric view of the recliner from the side of the inner toothed plate in embodiment 1;
fig. 3 is an isometric view from the outer panel side in embodiment 1;
FIG. 4 is a front view of the side of the inner rocker of the recliner of FIG. 2;
fig. 5 is a cross-sectional view of fig. 4.
Fig. 6 is an envelope diagram of the motion track of the transmission boss of the inner toothed plate in the embodiment 1;
FIG. 7 is a schematic view showing a concentric plate with a blind transmission hole in embodiment 2;
FIG. 8 is a cross-sectional view of FIG. 7;
fig. 9 is an envelope graph of the motion locus of the transmission boss of the inner tooth plate of the angle adjuster in the embodiment 3;
FIG. 10 is a schematic view showing the transmission bosses provided on the outer side plate of the recliner in embodiment 4;
fig. 11 is a cross-sectional view of fig. 10.
The reference numerals in fig. 1-11 are illustrated as follows:
1. a sheath; 11. the inner circle of the sheath; 12. an inner end face of the sheath; 2. a concentric plate; 21. a drive bore; 22. concentric plate outer circles; 23. the outer end faces of the concentric plates; 24. concentric plate inner end faces; 3. an inner toothed plate; 31. 43 a drive boss; 32. the outer end face of the inner toothed plate; 33. a central hole of the inner toothed plate; 4. an outer toothed plate; 41. the outer circle of the outer gear plate; 42. and a central hole of the external toothed plate.
Detailed Description
In order to make those skilled in the art better understand the technical solution of the present invention, the present invention will be further described in detail with reference to the accompanying drawings and specific embodiments.
Example 1
Referring to fig. 1-5, fig. 1 is a schematic diagram illustrating an eccentric state of an outer tooth plate 4 and an inner tooth plate 3 of an angle adjuster in embodiment 1; figure 2 is an isometric view of the recliner from the side of the inner toothed plate 3 in embodiment 1; fig. 3 is an axonometric view seen from the side of the external tooth plate 4 in embodiment 1; fig. 4 is a front view of the inner toothed plate 3 side of the recliner of fig. 2; fig. 5 is a cross-sectional view of fig. 4.
The angle adjuster comprises an outer toothed plate 4, an inner toothed plate 3, an eccentric wheel, a wedge block and the like, wherein the outer toothed plate 4 is provided with an outer gear ring, the inner toothed plate 3 is provided with an inner gear ring, the outer gear ring is meshed with the inner gear ring, the outer toothed plate 4 is connected with the chair seat, and the inner toothed plate 3 is connected with the backrest. The center of interior pinion rack 3 has the shaft shoulder, the centre of outer toothed plate 4 is equipped with the axle center hole, the shaft shoulder inserts the axle center hole, shaft shoulder and axle center hole eccentric settings form radial eccentric area between shaft shoulder and the axle center hole, the eccentric wheel sets up in this radial eccentric area, the eccentric wheel wholly is eccentric annular structure, constitute few tooth difference planetary gear drive with interior pinion rack 3, outer toothed plate 4, when back angle was adjusted, eccentric rotation was made relatively to interior pinion rack 3 and outer toothed plate 4, concrete theory of operation is the same with the background technical description, can refer to and understand. In addition, the angle adjuster further comprises a sheath 1, the inner toothed plate 3, the outer toothed plate 4, the eccentric wheel and other components are assembled in the sheath 1, the sheath 1 can protect the components, coaxiality can be guaranteed, and meshing performance of the outer toothed plate 4 and the inner toothed plate 3 is kept.
As shown in fig. 1, inner tooth plate 3 has an inner tooth plate center hole 33, labeled O, and outer tooth plate 4 has an outer tooth plate center hole 42, labeled O1, which are eccentric, resulting in an eccentricity e.
In this embodiment, the recliner further includes a concentric plate 2, the concentric plate 2 is disposed concentrically with the external tooth plate 4 and the sheath 1, and the concentric plate 2 is rotatable relative to the external tooth plate 4 and the sheath 1. As shown in fig. 5, the sheath inner circle 11 is concentrically matched with the concentric plate outer circle 22 and the outer tooth plate outer circle 41, and the sheath inner circle 11 and the outer tooth plate outer circle 41 can be fixedly connected by welding or riveting. As shown in fig. 2, the concentric plate 2 is disposed between the inner tooth plate outer end surface 32 and the sheath inner end surface 12. Meanwhile, the concentric plate 2 is provided with a transmission hole 21, the outer end face 32 of the inner toothed plate is provided with a transmission boss 31, and after assembly, the transmission boss 31 of the inner toothed plate 3 can be inserted into the transmission hole 21. As shown in fig. 2 and 3, the concentric plate 2 has a concentric plate outer end face 23 facing the sheath inner end face 11, and a concentric plate inner end face 24 facing the inner tooth plate 3. In addition, in this embodiment, the concentric plate 2 is further provided with a concentric plate center hole 25, the concentric plate center hole 25 is a hole which is set aside, so as to avoid interference with other components, and in addition, the inner toothed plate 3 is arranged in a step shape, and the concentric plate 2 is also arranged in a step shape, so that the axial size of the core piece can be reduced, and the depth of the sheath 1 can also be reduced.
When the inner toothed plate 3 eccentrically rotates relative to the outer toothed plate 4, the transmission boss 31 moves in the transmission hole 21 and drives the concentric plate 2 to rotate, and because the concentric plate 2 is concentrically arranged with the sheath 1 and the outer toothed plate 4, the concentric plate 2 can only rotate around the central axis thereof and does not eccentrically move. In order to realize that the transmission boss 31 drives the concentric plate 2 to rotate, the arrangement of the transmission hole 21 needs to be ensured, and the transmission boss 31 can be tangent to the transmission hole 21 in the movement process, so that the transmission torque drives the concentric plate to rotate.
For this purpose, the arrangement of the transmission bosses 31 and the transmission holes 21 may be arranged according to a certain rule. Assuming that the transmission bosses 31 are arranged at a distance D from the center of the inner toothed plate 3, when the plurality of transmission bosses 31 are provided, the geometric centers of the plurality of transmission bosses 31 are distributed on a circle with the center of the inner toothed plate 3 as a circle center and a diameter D, and the transmission holes 21 are correspondingly arranged on a circle with the center of the concentric plate 2 as a circle center and a diameter D. In order to maintain tangency, it also satisfies: the inner contour (i.e. the contour of the hole wall) of the transmission hole 21 is formed by uniformly expanding e outwards on the basis of the outer contour of the transmission boss 31, wherein e is the eccentricity of the outer toothed plate 4 and the inner toothed plate 3.
Taking the example that the transmission boss 31 in this embodiment is a circular boss, the inner contour of the hole wall of the transmission hole 21 is formed by uniformly expanding the outer contour of the circular boss outward by e, the outer contour of the circular boss is still circular when uniformly expanding outward, the obtained transmission hole 21 is correspondingly a circular hole, the diameter of the circular boss is e, the diameter after uniformly expanding is d +2e, and the diameter of the transmission hole 21 is d +2e, although a tolerance is allowed to exist during actual assembly, which may be slightly larger than d +2 e.
Besides, the shape and the arrangement position of the transmission hole 21 can be obtained by an envelope method, so that the transmission boss 31 can be ensured to be tangential to the hole wall of the transmission hole 21 during the movement process. As shown in fig. 6, fig. 6 is an envelope diagram of the motion trajectory of the transmission boss 31 of the inner tooth plate 3 in embodiment 1.
When the inner toothed plate 3 eccentrically moves, the movement locus of the transmission boss 31 can be made, for example, the transmission boss 31 rotates 1 degree to be at the position 1, rotates 2 degrees to be at the position 2 …, rotates n degrees to be at the position n, the positions of the n transmission bosses 31 are overlapped to form the movement locus shown in fig. 6, the movement locus of the transmission boss 31 defines a movement area of the transmission boss 31 in the angle adjuster angle adjusting process, the outer contour of the movement area defines a circular area, the circular area corresponds to the concentric plate 2 and serves as the setting basis of the transmission hole 21, the transmission hole 21 and the circular area are overlapped, the diameter of the circular area is the diameter of the transmission hole 21, and the center distance between the transmission boss 31 and the inner toothed plate 3 is equal to the center distance between the transmission hole 21 and the concentric plate 2, namely, and is uniformly distributed on a circle with the diameter D. In this example, d is 10.4mm and e is 1.3mm, and the circular area defined by the envelope-based motion trajectory, which has a diameter of 13mm, is consistent with the conclusions drawn in the above d +2e manner.
In this embodiment, six transmission bosses 31 are provided, and correspondingly six transmission holes 21 are provided, the transmission bosses 31 and the transmission holes 21 are uniformly arranged along the inner toothed plate 3 and the concentric plate 2, respectively, and in the angle adjustment process, each transmission boss 31 and the corresponding transmission hole 21 are always tangent. It can be understood that the number of the transmission holes 21 and the transmission bosses 31 is not limited to six, but two or more transmission bosses 31 should be theoretically provided, so as to ensure that one or more transmission bosses 31 can be tangent to the transmission holes 21 in the clockwise direction, one or more transmission bosses 31 can be tangent to the transmission holes in the counterclockwise direction, and in the case of a small number, the transmission function can be stably realized after the tangency is required to be maintained, the concentric plate 2 is driven to stably rotate, for example, when two transmission holes 21 and two transmission bosses 31 are provided, the transmission holes 21 and the transmission bosses 31 can be symmetrically arranged relative to the centers of the concentric plate 2 and the inner toothed plate 3, and when three transmission holes 21 and three transmission bosses 31 are provided, the transmission holes 21. During actual design, the number and the distribution positions of the transmission holes 21 and the transmission bosses 31 can be reasonably determined according to transmission requirements, strength requirements and the like, and the scheme is not limited.
Example 2
As shown in fig. 7 and 8, fig. 7 is a schematic view of the concentric plate 2 of embodiment 2 with the transmission hole 21 being a blind hole; fig. 8 is a cross-sectional view of fig. 7.
In embodiment 1, the transmission hole 21 is a through hole penetrating through the inner toothed plate 3, and it should be understood that the transmission hole 21 is arranged to drive the concentric plate 2 to rotate by utilizing the tangential interference between the hole wall and the transmission boss 31, so that the transmission hole 21 is not limited to a through hole structure, but also can be a blind hole. As shown in embodiment 2, the same as embodiment 1, except that the transmission hole 21 is a blind hole structure, the orifice end of the blind hole faces the transmission boss 31, the transmission boss 31 is inserted into the blind hole to drive the concentric plate 2 to rotate, and other structures and principles are the same as those of embodiment 1 and are not repeated. It is clear that the drive bore 21 is blind and also suitable for other embodiments.
In embodiments 1 and 2, the concentric plate 2 is defined between the inner end surface 11 of the sheath and the outer end surface 32 of the inner toothed plate, and is sleeved on the transmission boss 31 of the inner toothed plate 3, and a certain axial gap is required to exist between the concentric plate 2 and the inner toothed plate 3 and between the concentric plate 2 and the sheath 1 to ensure that the concentric plate 2 can rotate freely, and of course, the axial gap should not be too large so as to avoid affecting the meshing effect of the outer toothed plate 4 and the inner toothed plate 3, and the axial gap can be set to be less than 0.5 mm.
It should be noted that, in the above embodiment, the transmission boss 31 is taken as an example of a circular boss, actually, the transmission boss 31 is not limited to a circular boss, and may be a boss with a regular geometric shape, or may be an arbitrary special-shaped boss, and the shape of the transmission hole 21 follows the above arrangement rule no matter how the shape of the transmission boss 31 is. That is, the transmission hole 21 and the transmission boss 31 are both geometrically distributed on a circle with a diameter D, and the inner contour of the transmission hole 21 is formed by uniformly expanding the outer contour of the transmission boss 31 outward, or the inner contour of the transmission hole 21 is formed according to an envelope method. The following embodiment also shows a scheme that the transmission boss 31 and the transmission hole 21 are in a kidney-shaped shape.
Example 3
Referring to fig. 9, fig. 9 is an envelope diagram of the motion trajectory of the transmission boss 31 of the inner tooth plate 3 of the recliner in embodiment 3.
This embodiment is the same as embodiment 1 except that both 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 correspondingly a waist-circular hole. The shape of the transmission hole 21 is determined according to the motion track of the transmission boss 31, the transmission boss 31 in a kidney-shaped shape is distributed on a circle with the diameter D, the circle center is the center of the inner toothed plate 3, the transmission hole 21 is also distributed on the circle with the diameter D, and the circle center is the center of the concentric plate 2. Of course, as described above, in addition to determining the shape of the transmission hole 21 by the envelope method, the inner contour of the transmission hole 21 may also be determined as a waist circle formed by the outer contour of the transmission boss 31 being uniformly enlarged outward by e.
Example 4
As shown in fig. 10 and 11, fig. 10 is a schematic view of the transmission boss 31 arranged on the outer side plate of the angle adjuster in embodiment 4; fig. 11 is a cross-sectional view of fig. 10.
In embodiments 1, 2, 3, outer toothed plate 4 and seat support are connected, and inner toothed plate 3 and back are connected, and inner toothed plate 3 is relative outer toothed plate 4 eccentric motion, can understand, and the angle modulation is the relative rotation regulation of seat support and back, and correspondingly, inner toothed plate 3 and outer toothed plate 4 are the relative motion relation, then outer toothed plate 4 also can be connected with the back, and inner toothed plate 3 is connected with the seat support to the seat support is the reference system, then outer toothed plate 4 is relative inner toothed plate 3 eccentric motion. At this time, as shown in fig. 10 and 11, the transmission boss 43 is disposed on the outer toothed plate 4, the transmission hole 21 of the concentric plate 2 is matched with the transmission boss 43 of the outer toothed plate 4, the operation principle and the determination manner of the transmission hole 21 are consistent with the above embodiments, except that the disposition position of the transmission boss 43 is changed from the inner toothed plate 3 to be disposed on the outer toothed plate 4, and the concentric plate 2 is located between the outer toothed plate 4 and the sheath 1, as shown in fig. 11, from left to right, the inner toothed plate 3, the outer toothed plate 4, the concentric plate 2, and the inner end surface 12 of the sheath are sequentially disposed. The inner toothed plate 3 is concentrically arranged with the sheath 1 and the concentric plate 2, and specifically, the excircle of the inner toothed plate and the inner circle 11 of the sheath can be fixedly connected in a welding or riveting manner.
In addition, as shown in fig. 10, similarly to embodiment 3, the transmission boss 43 provided on the external gear plate 4 is also of a kidney-round shape, except that the transmission hole 21 provided on the concentric plate 2 is not of a complete kidney-round shape, but is of a notched structure provided at the hole wall of the central hole of the concentric plate 2, that is, one side of the transmission hole 21 is opened toward the center thereof. By the arrangement, the weight of the concentric plates can be reduced, the opening faces to one side of the center, namely, the radial inward part is removed, and the transmission of circumferential transmission is not influenced.
It will be understood in conjunction with the above embodiments that the drive aperture 21 may be a full aperture (e.g., embodiments 1-3) or a notched aperture (e.g., embodiment 4). The transmission hole 21 has a complete hole shape, so that the whole outer contour of the transmission hole 21 is integrally overlapped with the outer contour of the transmission bosses 31 and 43 after being uniformly expanded outwards, or the whole inner contour of the transmission hole 21 is integrally overlapped with the outer contour of the motion track areas of the transmission bosses 31 and 43. The transmission hole 21 is in a hole shape with a notch, so that the whole outer contour of the transmission hole 21 is partially overlapped with the outer contours of the transmission bosses 31 and 43 after being uniformly expanded outwards by e, or the whole inner contour of the transmission hole 21 is partially overlapped with the outer contours of the motion track areas of the transmission bosses 31 and 43, namely after a part of the contour determined by the two modes is removed, the contour is used as the whole inner contour of the transmission hole 21, the removed area is necessary to ensure that circumferential transmission is not influenced, and at least two groups of tangent transmission bosses 31 and 43 and transmission holes 21 are always arranged in the rotating process.
Above-mentioned each embodiment, through setting up the concentric plate 2 that has transmission hole 21, concentric plate 2 is connected with the back, because concentric plate 2 and transmission boss 21, 43 tangent roll setting, and radially leave sufficient clearance, the radial motion of transmission boss 31, 43 is filtered by the transmission hole, consequently, concentric plate 2 only transmits pure rotation, does not do eccentric motion, then concentric plate 2 converts the eccentric rotation of internal tooth board 3 or external tooth board 4 into concentric rotation this moment, a concentric transmission angle modulation ware has been provided promptly, like this, in the angle control process, eccentric swing can improve and even eliminate, thereby improve user experience.
It should be noted that, in the above embodiment, the concentric plate 21 is concentric with the external toothed plate 4 or concentric with the internal toothed plate 3, and the setting principle is that when the external toothed plate 4 moves relative to the internal toothed plate 3, the concentric plate 21 is concentric with the internal toothed plate 3, and the transmission boss 43 is arranged on the external toothed plate; when the inner toothed plate 3 moves relative to the outer toothed plate 4, the concentric plate 21 is concentric with the outer toothed plate 3, and the transmission boss 31 is arranged on the inner toothed plate 3. I.e. concentric plate 21 is concentric with the one that is relatively stationary, and the transmission bosses 31, 43 are provided on the one that moves relatively, in the above embodiment, the outer toothed plate 4 and the inner toothed plate 3, the one that moves relatively being connected with the backrest, the one that is relatively stationary being connected with the seat.
It should be noted that the concentric transmission recliner provided above can be used for angle adjustment of other components besides angle adjustment of the backrest, for example, can also be used for working conditions requiring folding or angle adjustment on a seat pan four-bar linkage mechanism, and the application working conditions of the concentric transmission recliner are not limited herein. It can be summarized here that the car seat is provided with a first part and a second part which is angularly adjustable with respect to the first part, the concentric plate 2 of the concentric transmission recliner is connected with the second part, i.e. the concentric plate 2 is connected with the part which needs to be angularly adjusted, and said outer toothed plate 4 or said inner toothed plate 3, which is concentrically arranged with the concentric plate 2, is connected with the first part. Then, for the above embodiment, the first member is a seat and the second member is a back; for another example, when used with a seat pan and a four-bar linkage, the four-bar linkage and the seat pan are the first member and the second member, respectively.
The scheme further provides an embodiment of the automobile seat, the automobile seat is provided with an angle adjuster, and the angle adjuster is the concentric transmission angle adjuster in any one of the embodiments and is not described herein again.
The foregoing is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, a plurality of improvements and decorations can be made without departing from the principle of the present invention, and these improvements and decorations should also be regarded as the protection scope of the present invention.
Claims (10)
1. Concentric transmission angle modulation ware, including outer pinion rack and interior pinion rack, the two relative eccentric rotation, its characterized in that still includes concentric board, with outer pinion rack with one in the interior pinion rack sets up with one is concentric, and another is equipped with the transmission boss, concentric board sets up the transmission hole, the transmission boss inserts the transmission hole, during the rotation of transmission boss can with the transmission hole is tangent in order to drive concentric board rotates.
2. The concentric drive recliner as set forth in claim 1 wherein the entire inner contour of said drive bore is entirely or partially coincident with the outer contour of said drive boss after being uniformly enlarged outwardly by e.
3. The concentric drive recliner as set forth in claim 2 wherein the drive boss is a circular boss of diameter d and the drive bore is a circular bore of diameter d +2 e.
4. The concentric drive recliner as set forth in claim 1 wherein the entire inner contour of said drive bore coincides in whole or in part with the outer contour of the locus area of motion of said drive boss.
5. The concentric drive recliner as set forth in claim 2 or 4 wherein the drive boss is a circular boss or a kidney-circular boss and the drive hole is a circular hole or a kidney-circular hole.
6. The concentric drive recliner as set forth in claim 2 or 4 wherein said drive hole is in the shape of a notch open on one side, opening towards the center of said concentric plate.
7. The concentric drive recliner as set forth in any one of claims 1 to 4 wherein the number of drive bosses and drive holes is at least two, and at any position where the inner toothed plate and the outer toothed plate rotate eccentrically relative to each other, at least two of the drive bosses are tangent to the corresponding drive holes.
8. The concentric drive recliner of claim 7 wherein the drive bosses and the drive bores are circumferentially equispaced.
9. An automobile seat, which is provided with a first component and a second component with an angle adjustable relative to the first component, and is further provided with an angle adjuster, and is characterized in that the angle adjuster is the concentric transmission angle adjuster according to any one of claims 1 to 8, the concentric plate is connected with the second component, and the outer toothed plate or the inner toothed plate which is arranged concentrically with the concentric plate is connected with the first component.
10. The vehicle seat of claim 9, wherein the first member is a seat of the vehicle seat and the second member is a backrest.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921647367.7U CN210454539U (en) | 2019-09-27 | 2019-09-27 | Concentric transmission angle adjuster and automobile seat |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921647367.7U CN210454539U (en) | 2019-09-27 | 2019-09-27 | Concentric transmission angle adjuster and automobile seat |
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| CN210454539U true CN210454539U (en) | 2020-05-05 |
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| CN201921647367.7U Active CN210454539U (en) | 2019-09-27 | 2019-09-27 | Concentric transmission angle adjuster and automobile seat |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110497825A (en) * | 2019-09-27 | 2019-11-26 | 湖北航嘉麦格纳座椅系统有限公司 | Transmission angle adjustor and automotive seat with one heart |
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2019
- 2019-09-27 CN CN201921647367.7U patent/CN210454539U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110497825A (en) * | 2019-09-27 | 2019-11-26 | 湖北航嘉麦格纳座椅系统有限公司 | Transmission angle adjustor and automotive seat with one heart |
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