Recliner handle with overload protection device

Abstract

A recliner handle having an overload protection device for a vehicle seat having a recliner attached to a recliner B bracket is provided. The recliner handle is attached to a handle spline having a disc shaft aperture configured to engage with a disc shaft of the recliner. A stop flange attached to the handle spline is configured to frictionally engage with an overload stop attached to the recliner B bracket. The handle spline is rotatable in a first rotational direction between a first position in which the stop flange is frictionally engaged with the overload stop and the disc shaft aperture is disengaged from the disc shaft, and a second position in which the disc shaft aperture is engaged with the disc shaft. Rotation of the handle spline in a second rotational direction from the first position is limited by the stop flange frictionally engaged with the overload stop.

Description

[0001] Cross-reference to related applications

[0002] This application claims priority and all benefits to U.S. Provisional Application 63 / 011,604, filed April 17, 2020, entitled “Recliner Handle With Overload Protection Device,” the entire disclosure of which is incorporated herein by reference. Background of the Invention 1. Technical Field

[0004] This invention relates to a recliner handle configured to unlock a vehicle seat recliner, allowing the vehicle seat to recline. More specifically, this invention relates to an overload protection device that prevents abuse torque applied to the recliner handle from being transferred to the recliner of the vehicle seat. 2. Background Technology

[0006] Many modern vehicles feature seats with backrests that are rotatably connected to the seat cushion via a recliner. A typical recliner has a locked position, in which the seat backrest is locked relative to the seat cushion at a selected rotational position. Additionally, a typical recliner has an unlocked position, in which the seat backrest can recline. A known recliner has a disc axle protruding from it. Rotating the disc axle between an initial angular position and a release angular position allows the known recliner to be reconfigured between the locked and unlocked states.

[0007] The recliner handle is typically operatively connected to the disc shaft of a known recliner for rotating the disc shaft between an initial angular position and a release angular position. Typically, the recliner handle has an initial position corresponding to the disc shaft being in the initial angular position when the known recliner is locked. Furthermore, the recliner handle typically has a recliner release position corresponding to the disc shaft being in the release angular position when the known recliner is unlocked. When the recliner handle is in the initial position, lifting the recliner handle upwards applies torque to the recliner handle. The upward torque applied to the recliner handle causes the recliner handle and the connected disc shaft to rotate. When the recliner handle reaches the recliner release position, the disc shaft correspondingly rotates to the release angular position, and the known recliner is unlocked.

[0008] The known recliner includes a return spring that biases the recliner handle toward its original position to ensure that the known recliner is in a locked state when no upward torque is applied to the recliner handle. Therefore, removing the upward torque on the recliner handle causes the recliner handle to rotate back to its original position, which also causes the disc shaft to rotate back to its original angular position, and returns the known recliner to the locked state.

[0009] However, when the recliner handle is in its original position and is pushed downwards, the known recliner may be overloaded and potentially damaged. In this situation, the downward torque applied to the recliner handle transfers excessive or abusive torque to the known recliner, which may damage the internal components within the known recliner.

[0010] Therefore, it is desirable to prevent damage to the recliner when excessive downward pressure (abuse torque) is applied to the recliner handle while it is in its original position. Furthermore, it is desirable to divert the abuse torque applied to the recliner handle away from the recliner. Finally, it is desirable to include an overload protection device between the recliner handle and the recliner, configured to prevent overloading of the recliner when downward torque is applied to the recliner handle. Summary of the Invention

[0011] This invention relates to a recliner handle with an overload protection device for use in a vehicle seat having a recliner attached to a recliner bracket B. The recliner handle is fixedly connected to a handle spline having a disc bore configured to engage with a disc shaft operatively connected to the recliner. A stop flange attached to the handle spline is configured to frictionally engage with an overload stop portion attached to the recliner bracket B. The handle spline is rotatable in a first rotational direction between a first position and a second position, in which the stop flange frictionally engages with the overload stop portion and the disc bore is disengaged from the disc shaft, and in the second position, the disc bore engages with the disc shaft. Rotation of the handle spline in the second rotational direction from the first position is limited by the stop flange frictionally engaging with the overload stop portion. Attached Figure Description

[0012] The advantages of the present invention will be readily appreciated, as they become more readily understood when considered in conjunction with the following detailed description, in which:

[0013] Figure 1 This is a partial perspective view of a vehicle seat having an overload protection device operatively connected between a recliner and a recliner handle, according to an embodiment of the present invention.

[0014] Figure 2 This is according to one embodiment of the present invention. Figure 1An exploded view of the overload protection device shows the tilting device, the tilting device B bracket with a notch, the spring bracket, the clamping ring, the handle spline, and the handle inertia spring.

[0015] Figure 3 yes Figure 2 A perspective view of the tilting device, illustrating the disc shaft protruding from the tilting device;

[0016] Figure 4A and Figure 4B yes Figure 2 A 3D view of the spring bracket;

[0017] Figure 5 yes Figure 2 A three-dimensional view of the clamping ring;

[0018] Figure 6A yes Figure 2 A partially transparent 3D view of the handle spline, illustrating the disc shaft hole inside the handle spline;

[0019] Figure 6B yes Figure 6A A 3D view of the spline on the handle;

[0020] Figure 7 It is along Figure 1 Enlarged sectional perspective view of the handle spline and disc shaft taken by section line 7-7, showing the disc shaft bore and disc shaft in the handle spline in a neutral position, wherein the disc shaft bore is disconnected from the disc shaft.

[0021] Figure 8 yes Figure 7 An enlarged sectional perspective view of the handle spline and the disc shaft, showing the handle spline rotating clockwise relative to the disc shaft, wherein the disc shaft orifice engages with the disc shaft.

[0022] Figure 9 yes Figure 7 An enlarged sectional perspective view of the handle spline and the disc shaft, showing the handle spline rotating counterclockwise relative to the disc shaft, wherein the disc shaft orifice engages with the disc shaft.

[0023] Figure 10 yes Figure 1 An exploded perspective view of the tilting device, illustrating the assembly of the spring support and handle spline with the tilting device's disc shaft;

[0024] Figure 11 This is after assembling the spring bracket and the handle spline. Figure 10 A perspective view of the tilting device, illustrating the insertion of the clamping ring into the spline of the handle;

[0025] Figure 12 It is along Figure 1The cross-sectional view of the tilting device and overload protection device taken by section line 12-12 shows the handle spline, spring bracket and clamping ring assembled with the disc shaft.

[0026] Figure 13 This is after the clamping ring and handle spline are assembled. Figure 11 A perspective view of the tilting device and overload protection device, illustrating the assembly of the handle inertia spring with the spring bracket and the tilting device B bracket;

[0027] Figure 14 It is in the original angular position. Figure 13 A perspective view of the recliner and overload protection device, wherein the stop flange of the spring bracket is frictionally engaged with the cutout attached to the recliner B bracket, and the illustration shows the handle spline rotating toward the recliner release position.

[0028] Figure 15 It is in the original angular position. Figure 14 An enlarged sectional perspective view of the tilting device and overload protection device, which shows the handle spline rotating toward the release angle position;

[0029] Figure 16 This is after the handle spline is rotated to the release angle position. Figure 14 A perspective view of the tilting device and overload protection device, showing that the stop flange of the spring bracket is spaced apart from the cutout of the tilting device B bracket.

[0030] Figure 17 This is after the handle spline is rotated towards its original angle position. Figure 16 A perspective view of the tilting device and overload protection device, showing the frictional engagement of the stop flange of the spring bracket with the cutout of the tilting device B bracket.

[0031] Figure 18 It is in the original angular position. Figure 17 A cross-sectional view of the tilting device and overload protection device, showing the handle spline and disc shaft in the neutral position, wherein the disc shaft bore of the handle spline is disconnected from the disc shaft.

[0032] Figure 19 It is in the original angular position. Figure 18 A cross-sectional view of the tilting device and overload protection device, illustrating that abuse torque is applied to the handle spline while the disc shaft orifice remains disengaged from the disc shaft.

[0033] Figure 20 yes Figure 19 A perspective view of the recliner and overload protection device, illustrating the abusive torque applied to the handle spline causing a load to be applied to the cut of the recliner B bracket;

[0034] Figure 21This is a partial perspective view of a vehicle seat having an overload protection device operatively connected between a recliner and a recliner handle, according to a second embodiment of the present invention.

[0035] Figure 22 It is according to the second embodiment of the present invention. Figure 21 An exploded view of the overload protection device shows the tilting device, the tilting device B bracket with a cutout having an overload stop, the handle spline with an integrated stop flange, and the handle inertia spring.

[0036] Figure 23 yes Figure 22 A sectional perspective view of the overload protection device, showing the frictional engagement between the integrated stop flange of the handle spline and the overload stop portion on the cutout of the tilter B bracket.

[0037] Figure 24 yes Figure 23 A partially transparent 3D view of the handle spline, illustrating the disc shaft hole passing through the handle spline;

[0038] Figure 25 yes Figure 24 A three-dimensional view of the handle spline, illustrating the outer surface of the handle spline; and

[0039] Figure 26 yes Figure 23 An enlarged sectional perspective view of the handle spline and disc shaft, showing the disc shaft bore and disc shaft in the handle spline in a neutral position, wherein the disc shaft bore is disengaged from the disc shaft. Detailed Implementation

[0040] Figures 1 to 26 The illustration shows an overload protection device 10, 10' for connecting the recliner handle 14 to the recliner 18 of the vehicle seat 22 according to an embodiment described herein. Directional designations such as top, bottom, upper, lower, upward, downward, longitudinal, lateral, left, right, etc., used or shown in the specification, drawings, or claims are relative terms used for ease of description and are not intended to limit the scope of the invention in any way. Referring to the drawings, the same reference numerals denote the same or corresponding parts throughout several views.

[0041] Figure 1 A perspective view of a portion of a vehicle seat 22 according to a first embodiment is shown. The vehicle seat 22 has a seat back 26 rotatably connected to a seat cushion 30 via a recliner 18. A recliner handle 14 is fixedly connected to an overload protection device 10 and rotatably connected to the recliner 18. Figure 1As shown, the recliner handle 14 can be repositioned about the rotation axis 34 of the recliner 18 between its original position 14A and its recline release position 14B. The original position 14A of the recliner handle 14 corresponds to the original angular position 36A of the recliner 18. Furthermore, the recline release position 14B of the recliner handle 14 corresponds to the release angular position 36B of the recliner 18.

[0042] An upward torque is applied to the reclining handle 14 and the reclining handle 14 is rotated in the first direction A (by...). Figure 1 (As shown in the diagram, arrow A) rotates about the axis of rotation 34 of the recliner 18 from its original position 14A toward the recline release position 14B, thus unlocking the recliner 18 and allowing the seat back 26 to rotate relative to the seat cushion 30. Figure 1 In the embodiment shown, the recliner handle 14 is rotated upward in a clockwise direction A relative to the rotation axis 34 of the recliner 18 to unlock the recliner 18.

[0043] Reference Figure 11 The return spring 38 is operatively connected between the recliner 18 and the recliner handle 14. For example... Figure 1 As shown, the return spring 38 rotatably biases the recliner handle 14 toward its original position 14A. When the recliner handle 14 is spaced out from its original position 14A, the return spring 38 causes the recliner handle 14 to automatically rotate in a second rotation direction B (arrow B) toward its original position 14A when the recliner handle 14 is released. The second rotation direction B is opposite to the first rotation direction A. If the recliner handle 14 is rotated upward in the clockwise direction A to reposition the recliner handle 14 from its original position 14A to its recliner release position 14B, then the recliner handle 14 is rotated downward in the counterclockwise direction B to reposition the recliner handle 14 from its recliner release position 14B back to its original position 14A.

[0044] For some recliners 18, the recliner handle 14 moves beyond its original position 14A in the second rotation direction B (by...). Figure 1 Further rotation (as shown by arrow C in the diagram) can overload the recliner 18 and damage its internal components. Furthermore, rotational movement of the recliner handle 14 in the direction of arrow C beyond its original position 14A can cause the recliner 18 to become over-locked. Over-locking the recliner 18 can potentially damage it. The overload protection device 10 prevents the recliner 18 from becoming over-locked when a downward torque is applied to the recliner handle 14 while it is in its original position 14A. More specifically, the overload protection device 10 limits the recliner handle 14 from rotating in the second rotational direction C beyond its original position 14A and transfers the torque applied to the recliner handle 14 away from the recliner 18.

[0045] Figure 2 An exploded view of the overload protection device 10 is shown. (Refer to...) Figure 2 The recliner 18 includes a disc recliner assembly 42 having a guide plate 42A rotatably coupled to a toothed plate 42B. An exemplary disc recliner assembly 42 is the iDiSC 5 disc recliner assembly manufactured by Magna Seating Inc. (e.g.) Figure 1 As shown, the guide plate 42A of the disc recliner assembly 42 is fixedly connected to the recliner B bracket 44, which in turn is fixedly connected to the seat cushion 30. The guide plate 42A includes a plurality of bosses 46, 48 configured to engage with corresponding recesses 50, 52 in the recliner B bracket 44. It is understood that, in alternative embodiments, without altering the scope of the invention, the attachment of the disc recliner assembly 42 to the recliner B bracket 44 may include different methods of fixedly connecting the guide plate 42A to the recliner B bracket 44.

[0046] like Figure 10 As best shown, the toothed plate 42B is fixedly connected to the seat back 26. (Refer to...) Figure 1 and Figure 10 When the toothed plate 42B is unlocked relative to the guide plate 42A (by rotating the recliner handle 14 to the recliner release position 14B), the seat back 26 is able to rotate relative to the recliner B bracket 44 and the attached seat cushion 30. In some embodiments, when the guide plate 42A and the toothed plate 42B are unlocked relative to each other, the recliner B bracket 44 and the attached seat cushion 30 are also able to rotate relative to the seat back 26.

[0047] Reference Figure 1 and Figure 10 When the recliner handle 14 is in its original position 14A, the toothed plate 42B is locked to the guide plate 42A. Rotation of the toothed plate 42B relative to the guide plate 42A is prevented when the recliner handle 14 is in its original position 14A. Therefore, rotation of the seat back 26 relative to the seat cushion 30 is prevented when the recliner handle 14 is in its original position 14A.

[0048] Reference Figure 2A disc shaft 62 protrudes from the disc recliner assembly 42, wherein the longitudinal axis 34A of the disc shaft 62 is aligned with the rotation axis 34 of the recliner 18. The disc shaft 62 is formed of metal, plastic, and / or a combination thereof. Furthermore, the disc shaft 62 is configured to lock and unlock the rotation of the toothed plate 42B relative to the guide plate 42A based on the angular positions 36A, 36B of the disc shaft 62. Rotating the disc shaft 62 from its initial angular position 36A along a first rotation direction A to a release angular position 36B unlocks the guide plate 42A and the toothed plate 42B, allowing one of the guide plate 42A and the toothed plate 42B to rotate relative to the other. In other embodiments, when the disc recliner assembly 42 is unlocked, both the guide plate 42A and the toothed plate 42B can rotate about the rotation axis 34. Therefore, in some embodiments, the seat cushion 30 may rotate toward and / or away from the seat back 26, and the seat back 26 may rotate toward and / or away from the seat cushion 30.

[0049] Figure 3 An enlarged view of the recliner 18 is shown. (Refer to...) Figure 2 and Figure 3 The disc shaft 62 includes an elongated shaft end portion 66 extending along its longitudinal axis 34A. The elongated shaft end portion 66 has a rounded rectangular cross-section and includes opposing flat shaft side portions 72, 74, curved shaft side portions 78, 78' extending between adjacent flat shaft side portions 72, 74, and a distal end surface 80. The distal end surface 80 of the elongated shaft end portion 66 of the disc shaft 62 is also... Figure 7 , Figure 8 and Figure 9 As shown in the image.

[0050] like Figure 2 and Figure 3 As shown, the disc shaft 62 has a base portion 82 having a generally cylindrical cross-sectional shape, and the base portion 82 has a plurality of flat sides 86, 90, 90' and a base end face 94. Figure 12 A cross-sectional view of a portion of the overload protection device 10 is shown, and other details of the disc shaft 62 are illustrated. (See reference...) Figure 12A central cylindrical portion 98 protrudes from the base end face 94 of the base portion 82 along the longitudinal axis 34A of the disc shaft 62. The central cylindrical portion 98 has an outer diameter 98A, which is smaller than the maximum diameter 82A of the base portion 82. Furthermore, the central cylindrical portion 98 has a central end face 102 that extends substantially parallel to and spaced apart from the base end face 94 of the base portion 82. A channel 106 extends circumferentially around the outer periphery 98' of the central cylindrical portion 98, which is spaced apart from both the central end face 102 and the base end face 94. The channel 106 has an outer diameter 106A, which is smaller than the outer diameter 98A of the central cylindrical portion 98. An elongated shaft end portion 66 protrudes from the central end face 102 of the central cylindrical portion 98. Furthermore, the elongated shaft end portion 66 has a maximum diameter 66A that is smaller than the outer diameter 98A of the central cylindrical portion 98. Additionally, the base portion 82, the central cylindrical portion 98, and the elongated shaft end portion 66 are aligned with the longitudinal axis 34A of the disc shaft 62. It is understood that the size, shape, and length of the disc shaft 62 can be varied without changing the scope of the invention.

[0051] Reference Figure 2 , Figure 3 and Figure 11The return spring 38 is a helical torsion spring having a first spring end 38A fixedly connected to the base portion 82 of the disc shaft 62 and a second spring end 38B fixedly connected to a groove 142 in a boss 146 protruding from the guide plate 42A. The first spring end 38A of the return spring 38 is wound around the base portion 82 of the disc shaft 62 such that it frictionally engages with one or more of the flat sides 86, 90, 90' of the base portion 82. In some embodiments, the return spring 38 is sized and shaped such that the spring tension maintains the first spring end 38A in frictional engagement with the base portion 82 of the disc shaft 62 and holds the second spring end 38B in a position engaging with the groove 142 in the boss 146 protruding from the guide plate 42A. In alternative embodiments, one or both of the first spring end 38A and the second spring end 38B are fixedly connected to the disc shaft 62 and the groove 142, respectively, by mechanical fasteners, welding connections, etc. With the second spring end 38B of the return spring 38 held within the groove 142 in the boss 146 protruding from the guide plate 42A, rotating the recliner handle 14 upward from its original position 14A toward the recliner release position 14B causes the disc shaft 62 to rotate from its original angle position 36A to the release angle position 36B, preloading the return spring 38. When the recliner handle 14 is released, the spring torque in the return spring 38 causes the disc shaft 62 to rotate toward its original angle position 36A. Returning the disc shaft 62 to its original angle position 36A causes the recliner handle 14 to return to its original position 14A and locks the disc recliner assembly 42. It will be understood that the size and shape of the return spring 38 can be changed without changing the scope of the invention.

[0052] like Figure 2 As shown, the overload protection device 10 includes a disc shaft 62 protruding from the recliner 18, a spring bracket 158, a clamping ring 162, a handle spline 166, a handle inertia spring 170, and a protrusion 174 formed on the recliner B bracket 44. It will be understood that the overload protection device 10 may include additional components without changing the scope of the invention.

[0053] Reference Figure 2 , Figure 4A and Figure 4BThe spring support 158 ​​has a generally flat main support portion 186 with opposing upper support surface 190 and lower support surface 194, which are spaced apart by a first support sidewall 198 and a second support sidewall 202 defining the width of the spring support 158. Extending from the main support portion 186 are a first flange 206, a second flange 207, and a stop flange 208. The first flange 206 extends upward from a first end 210 of the main support portion 186 such that the first flange 206 and the upper support surface 190 of the main support portion 186 are generally perpendicular to each other and form an "L" shape. The first flange 206 has opposing inner surfaces 206A and outer surfaces 206B, and an elongated spring groove 214 extending between the opposing inner surfaces 206A and outer surfaces 206B. The second flange 207 extends upward from a second end 222 of the main support portion 186. The second flange 207 includes a flange base portion 226 adjacent to the main support portion 186 and a distal flange end portion 230 projecting at an angle from the flange base portion 226. The flange base portion 226 is generally parallel to the first flange 206, and the distal flange end portion 230 is generally parallel to the main support portion 186. A stop flange 208 extends downward from the second support sidewall 202 of the main support portion 186. The stop flange 208 includes a distal sidewall 238 and a proximal sidewall 242. The proximal sidewall 242 includes a stop surface 246.

[0054] like Figure 2 , Figure 4A and Figure 4B As shown, the alignment aperture 250 extends between the upper support surface 190 and the lower support surface 194 of the main support portion 186. The alignment aperture 250 has a defined inner profile 250' with a plurality of splines 254 extending between the opposing upper support surface 190 and lower support surface 194. The plurality of splines 254 includes at least one narrow spline 254A and at least one wide spline 254B configured to mate with at least one narrow spline 286A and at least one wide spline 286B located on the handle spline 166. The wide spline 254B of the alignment aperture 250 is an alignment feature for assembling the spring support 158 ​​and the handle spline 166 in a predetermined relative orientation. Furthermore, the alignment aperture 250 has a minimum opening diameter 250A and a maximum opening diameter 250B. Figure 12As shown, the minimum opening diameter 250A of the alignment aperture 250 is smaller than the maximum diameter 82A of the base portion 82 of the disc 62. With the disc 62 passing through the alignment aperture 250, the spring support 158 ​​is assembled with the disc 62. After assembly, the lower support surface 194 of the spring support 158 ​​is supported by the base end face 94 of the base portion 82 of the disc 62. Furthermore, the spring support 158 ​​is formed of metal, plastic, and / or a combination thereof. It will be understood that the size and shape of the spring support 158, including the first flange 206 and the second flange 207, the stop flange 208, the spring groove 214, and the alignment aperture 250, can vary without changing the scope of the invention.

[0055] like Figure 5 As shown, the clamping ring 162 is a generally annular disc having opposing top surfaces 162A and bottom surfaces 162B, an outer surface 162C extending between the opposing top surfaces 162A and bottom surfaces 162B, and a passage 258 extending between the opposing top surfaces 162A and bottom surfaces 162B, forming a notch 258' in the clamping ring 162. The notch 258' defining the passage 258 includes a first inlet surface 266, a second inlet surface 266', and an inner cylindrical surface 262 extending between the inner ends 266A and 266B of adjacent first inlet surfaces 266 and second inlet surfaces 266'. The inner cylindrical surface 262 has an annular inner radius 262A that is approximately equal to or greater than half the outer diameter 106A of the channel 106 in the central cylindrical portion 98 of the disc shaft 62. The first inlet surface 266 and the second inlet surface 266' are configured to allow the clamping ring 162 to be attached to the disc 62 within a channel 106 in the central cylindrical portion 98 of the disc 62. The clamping ring 162 is formed of metal, plastic, and / or a combination thereof. It will be understood that the size and shape of the clamping ring 162 may be varied without changing the scope of the invention.

[0056] like Figure 2 , Figure 6A and Figure 6B As shown, the handle spline 166 has a spline portion 270 with a generally cylindrical shape and an outer surface 274 extending between an upper end surface 278 and a lower end surface 282. The outer surface 274 of the handle spline 166 has an outer contour 274' that is sized and shaped to engage with the inner contour 250' of the alignment aperture 250 in the spring support 158. (See reference...) Figure 6A and Figure 6B The outer surface 274 of the handle spline 166 includes a plurality of splines 286, which are spaced apart around the outer contour 274' of the spline portion 270 and extend along the longitudinal axis 34B of the handle spline 166. Figure 2As shown, when the handle spline 166 is assembled with the disc shaft 62, the longitudinal axis 34B of the handle spline 166 is aligned with the rotation axis 34 of the tilter 18 and the longitudinal axis 34A of the disc shaft 62.

[0057] Reference Figure 4A and Figure 6B The handle spline 166 includes at least one narrow spline 286A and at least one wide spline 286B configured to engage with at least one narrow spline 254A and at least one wide spline 254B within the alignment aperture 250 of the spring bracket 158 ​​when the handle spline 166 is assembled with the spring bracket 158. The wide spline 254B of the alignment aperture 250 and the wide spline 286B of the handle spline 166 are alignment features for assembling the spring bracket 158 ​​and the handle spline 166 in a predetermined relative orientation.

[0058] Figure 10 The image shows the assembly of the handle spline 166 and spring bracket 158 ​​on the disc shaft 62. Figure 12 A cross-sectional view of a handle spline 166 assembled with a spring bracket 158 ​​is shown, wherein the lower end surface 282 of the handle spline 166 is inserted into an alignment hole 250 in the spring bracket 158.

[0059] like Figure 6A As shown, the splined portion 270 of the handle spline 166 optionally includes a handle channel 288 that extends around the outer periphery of the splined portion 270 and is spaced apart from the upper end surface 278 of the splined portion 270. The handle channel 288 is sized and shaped to engage and retain a snap-fit ​​feature on the recliner handle 14. In other embodiments, the handle channel 288 is sized and shaped to receive a clamping ring or similar fastening device to hold the recliner handle 14 in an engaged position using the handle spline 166. In some embodiments, the handle channel 288 is omitted from the handle spline 166 when an alternative method of attaching the recliner handle 14 to the handle spline 166 is chosen.

[0060] Reference Figure 6A and Figure 6BThe handle spline 166 includes a cylindrical ring 290 projecting from the spline portion 270. The cylindrical ring 290 is generally cylindrical in shape and has a longitudinal axis aligned with the longitudinal axis 34B of the handle spline 166. Furthermore, the cylindrical ring 290 is spaced apart from the upper end surface 278 and the lower end surface 282 of the handle spline 166. A handle channel 288 is also spaced apart from the cylindrical ring 290 and positioned between the cylindrical ring 290 and the upper end surface 278 of the handle spline 166. The cylindrical ring 290 has an outer cylindrical surface 294 having an outer diameter 290A larger than the maximum diameter 270A of the spline portion 270. Furthermore, the cylindrical ring 290 includes opposing upper surfaces 298 and lower surfaces 298', which extend between the corresponding upper edges 294A and lower edges 294B of the outer cylindrical surface 294 and the outer surface 274 of the spline portion 270. The lower surface 298' of the cylindrical ring 290 is spaced apart from the lower end surface 282 of the handle spline 166, such that when the lower end surface 282 of the handle spline 166 is inserted into the alignment hole 250 of the spring support 158, the lower surface 298' of the cylindrical ring 290 frictionally engages with the upper support surface 190 of the spring support 158, as... Figure 12 As shown in the image.

[0061] Reference Figure 6A and Figure 12 The handle spline 166 includes an elongated disc shaft aperture 310 aligned with the longitudinal axis 34B of the handle spline 166. The elongated disc shaft aperture 310 has a lower opening 314 extending through the lower end surface 282 of the handle spline 166. The disc shaft aperture 310 is sized and shaped to engage with the disc shaft 62. Therefore, the disc shaft aperture 310 has an elongated inner aperture portion 310A, which is sized and shaped to engage with the elongated shaft end portion 66 of the disc shaft 62, while maintaining approximately 6 degrees of lossy movement between the disc shaft 62 and the disc shaft aperture 310. It is understood that, without changing the scope of the invention, the amount of lossy movement between the disc shaft 62 and the disc shaft aperture 310 can be greater than or less than approximately 6 degrees. Furthermore, the disc shaft orifice 310 has an elongated outer orifice portion 310B, which is sized and shaped to engage with the central cylindrical portion 98 of the disc shaft 62. Additionally, the disc shaft orifice 310 has an upper end surface 310C, which is configured to frictionally engage with the distal end surface 80 of the disc shaft 62 when assembled as part of the overload protection device 10.

[0062] Reference Figures 7 to 9 When the handle spline 166 rotates, there is a loss motion of about 6 degrees between the handle spline 166 and the disc shaft 62. Figure 7 It shows along Figure 1The cross-sectional view of the handle spline 166 and the disc shaft 62 taken by section line 7-7 shows the disc shaft 62 and the handle spline 166 in the neutral position 322. Figure 7 The neutral position 322 shown corresponds to the disc shaft 62 being in its original angular position 36A, where the tilting handle 14 is unconstrained and aligned with its original position 14A, as shown. Figure 1 and Figure 3 As shown. Figure 7 As shown, the elongated shaft end portion 66 of the disc shaft 62 has opposite flat shaft side portions 72, 74 and curved shaft side portions 78, 78' extending between the opposite flat shaft side portions 72, 74.

[0063] On the contrary, such as Figure 7 As shown, the cross-sectional shape of the inner bore portion 310A of the disc bore 310 in the handle spline 166 has a bow-shaped appearance, more generally described as an irregular concave hexagonal shape. The inner bore portion 310A includes opposing first sidewalls 324 and second sidewalls 325, and opposing first endwalls 326 and second endwalls 327. The first sidewall 324 includes a first side portion 328 extending at an angle from the second side portion 328', such that the interior angle 328A between the first side portion 328 and the second side portion 328' is greater than 180 degrees, as measured within the disc bore 310. Similarly, the second sidewall 325 includes a third side portion 329 extending at an angle from the fourth side portion 329', such that the interior angle 329A between the third side portion 329 and the fourth side portion 329' is greater than 180 degrees, as measured within the disc bore 310. Furthermore, the first side portion 328 and the fourth side portion 329' are generally parallel and spaced apart. Similarly, the second side portion 328' and the third side portion 329' are generally parallel and spaced apart. Additionally, the first side portion 328 and the second side portion 328' are not parallel. Likewise, the third side portion 329 and the fourth side portion 329' are not parallel. In some embodiments, one or more of the first side portion 328, the second side portion 328', the third side portion 329, and the fourth side portion 329' include curved surfaces, tapered surfaces, and / or generally flat surfaces.

[0064] For example Figure 7 As shown, a first end wall 326 extends between the end 328B of the first side portion 328 and the end 329B of the third side portion 329 of the disc shaft orifice 310. Similarly, a second end wall 327 extends between the end 328C of the second side portion 328' and the 329C of the fourth side portion 329'. Figure 7In the illustrated embodiment, the first end wall 326 and the second end wall 327 are curved walls. The inner orifice portion 310A of the disc shaft orifice 310 is sized and shaped such that the first joint 331 between the first side portion 328 and the second side portion 328', and the second joint 331' between the third side portion 329 and the fourth side portion 329', frictionally engage with the corresponding adjacent flat side portions 72, 74 of the disc shaft 62 during assembly. It is understood that in some embodiments, without changing the scope of the invention, the first joint 331 and the second joint 331' are spaced apart from the adjacent flat side portions 72, 74. When the disc shaft 62 is centered within the disc shaft orifice 310... Figure 7 In the neutral position 322 shown, each of the first to fourth side portions 328, 328', 329, 329' of the disc shaft orifice 310 tapers away from the adjacent axial flat side portions 72, 74 of the disc shaft 62 with approximately loss motion angles 332, 332'. Therefore, when the handle spline 166 and the disc shaft 62 are in... Figure 7 In the neutral position 322 shown, each of the first to fourth side portions 328, 328', 329, 329' of the disc shaft orifice 310 is substantially disengaged from the adjacent axial flat side portions 72, 74 of the disc shaft 62. The approximate loss motion angles 332, 332' represent the loss motion between the handle spline 166 and the disc shaft 62 when the handle spline 166 is rotated.

[0065] In order for the disc shaft hole 310 of the handle spline 166 to engage with the disc shaft 62, the handle spline 166 rotates through approximately loss motion angles 332 and 332', such as Figure 8 As shown in Figure 9. Once the disc shaft orifice 310 is fully engaged with the disc shaft 62, the additional rotation of the handle spline 166 causes the disc shaft 62 to rotate together with the handle spline 166.

[0066] When the tilting handle 14 is in Figure 1 In the original position 14A shown, the handle spline 166 and the disc shaft 62 are in the neutral position 322, wherein the second side portion 328' of the disc shaft orifice 310 is disengaged from the adjacent flat side portion 72 of the disc shaft 62, as shown. Figure 7 As shown in the diagram. More specifically, when the handle spline 166 and the disc shaft 62 are in the neutral position 322, the second side portion 328' of the disc shaft orifice 310 tapers away from the adjacent flat side portion 72 of the disc shaft 62 at a loss motion angle 332.

[0067] The upward torque applied to the recliner handle 14 causes the recliner handle 14 and the attached handle spline 166 to move along... Figure 1 The clockwise rotation A shown in the diagram. The clockwise rotation A of the tilting lever handle 14 causes the handle spline 166 to rotate along... Figure 8 The clockwise rotation is 333 as shown. An initial rotation of the handle spline 166 less than the loss angle of motion 332 does not cause the disc shaft 62 to rotate because the disc shaft orifice 310 is disengaged from the disc shaft 62. Therefore, applying torque to the recliner handle 14 in the clockwise direction A and causing the recliner handle 14 to rotate less than the loss angle of motion 332 causes the handle spline 166 to rotate independently of the disc shaft 62 because the disc shaft 62 is disengaged from the disc shaft orifice 310. When the recliner handle 14 and the attached handle spline 166 rotate clockwise 333 approximately the loss angle of motion 332, the disc shaft 62 engages with the disc shaft orifice 310. After the recliner handle 14 and the handle spline 166 have rotated beyond the loss angle of motion 332, the disc shaft 62 rotates together with the handle spline 166.

[0068] like Figure 8 As shown, when the tilting handle 14 is spaced from its original position 14A by at least a loss angle of motion 332, the disc shaft 62 engages with the disc shaft orifice 310. (Refer to...) Figure 8 When the handle spline 166 from Figure 7 When the neutral position 322 is rotated clockwise 333, the second side portion 328' of the disc shaft orifice 310 pivots toward the adjacent flat side portion 72 of the disc shaft 62. When the handle spline 166 rotates clockwise 333 through the loss motion angle 332, the second side portion 328' of the disc shaft orifice 310 engages frictionally with the adjacent flat side portion 72 of the disc shaft 62. When the handle spline 166 rotates clockwise 333, the third side portion 329 of the disc shaft orifice 310 similarly engages frictionally with the adjacent flat side portion 74 of the disc shaft, because the third side portion 329 and the second side portion 328' of the disc shaft orifice 310 are substantially parallel. The additional rotation of the handle spline 166 in the clockwise direction 333 causes the disc shaft 62 to rotate together with the handle spline 166, because the second side portion 328' and the third side portion 329 of the disc shaft orifice 310 have already engaged with the adjacent axial flat side portions 72, 74 of the disc shaft 62. Therefore, the loss motion angle 332 illustrates the amount of loss motion between the handle spline 166 and the disc shaft 62 when the handle spline 166 rotates clockwise 333 from the neutral position 322.

[0069] like Figure 7 As shown, when the handle spline 166 and the disc shaft 62 are in the neutral position 322, the fourth side portion 329' of the disc shaft orifice 310 tapers away from the adjacent flat side portion 74 of the disc shaft 62 with a loss motion angle 332'. When the handle spline 166 from Figure 7 When the neutral position 322 rotates counterclockwise 333', the fourth side portion 329' pivots toward the adjacent flat side portion 74 of the disc shaft 62, as... Figure 9As shown in the diagram, when the handle spline 166 rotates counterclockwise 333' through a loss motion angle 332', the fourth side portion 329' engages frictionally with the adjacent flat side portion 74 of the disc shaft 62. When the handle spline 166 rotates counterclockwise 333', the first side portion 328 of the disc shaft bore 310 also engages frictionally with the adjacent flat side portion 72, because the fourth side portion 329' and the first side portion 328 of the disc shaft bore 310 are substantially parallel. The additional rotation of the handle spline 166 counterclockwise 333' causes the disc shaft 62 to rotate together with the handle spline 166, because the first side portion 328 and the fourth side portion 329' of the disc shaft bore 310 have already engaged with the adjacent flat side portions 72, 74 of the disc shaft 62. Therefore, the loss motion angle 332' describes the amount of loss motion between the handle spline 166 and the disc shaft 62 when the handle spline 166 rotates counterclockwise 333' from the neutral position 322. In some embodiments, the loss motion angle 332 is approximately equal to the loss motion angle 332'. However, it will be understood that the loss motion angle 332 can be greater than or less than the loss motion angle 332' without changing the scope of the invention. Furthermore, as in Figure 8 and Figure 9 As observed, the clockwise direction 333 and the counterclockwise direction 333' of the handle spline 166 are generally described as the first rotation direction 333 and the second rotation direction 333', respectively.

[0070] like Figure 6A and Figure 12 As shown, the handle spline 166 has a clamping ring groove 334 extending radially through a portion of the cylindrical ring 290. The clamping ring groove 334 is configured to allow the clamping ring 162 to be inserted into the clamping ring groove 334. Furthermore, the clamping ring groove 334 is sized and shaped such that the clamping ring 162 is aligned with the channel 106 of the disc shaft 62 when the spring support 158 ​​and the handle spline 166 are assembled on the disc shaft 62, as shown. Figure 12 As shown in the diagram, the channels 106 in the clamping ring 162, clamping ring groove 334, and disc shaft 62 are sized and shaped such that the insertion of the clamping ring 162 into the clamping ring groove 334 does not restrict the rotational movement of the handle spline 166 relative to the disc shaft 62. Specifically, when the handle spline 166 is removed from... Figure 7 When the neutral position 322 shown rotates along the first rotation direction 333 and the second rotation direction 333' through a movement angle at least equal to or greater than the loss angles 332 and 332', the clamping ring 162 does not restrict the rotation of the handle spline 166 relative to the disc shaft 62. It will be understood that the size and shape of the clamping ring groove 334, the channel 106 in the disc shaft 62, and the clamping ring 162 may be varied without changing the scope of the invention.

[0071] like Figure 6AAs shown, the clamping ring groove 334 includes opposing upper surfaces 334A, lower surfaces 334B, and opposing side surfaces 334C and 334D. The disc shaft orifice 310 forms an upper opening 338 in the upper surface 334A of the clamping ring groove 334. The disc shaft orifice 310 forms a lower opening 338' in the lower surface 334B of the clamping ring groove 334.

[0072] Reference Figure 2 The handle inertia spring 170 is a helical spring having a coiled portion 346 including a central passage 348, a first spring end 350 extending from the upper side portion 346A of the handle inertia spring 170, and a second spring end 350' extending from the lower side portion 346B of the handle inertia spring 170. The handle inertia spring 170 is formed of metal.

[0073] exist Figure 2 In the illustrated embodiment, the first spring end 350 of the handle inertia spring 170 is bent into an "L" shape, having a first retaining portion 354 extending from the handle inertia spring 170 at an angle. The first spring end 350 and the first retaining portion 354 are sized and shaped such that the first spring end 350 can pass through a spring slot 214 in the spring holder 158. Figure 14 As shown, when the handle inertia spring 170 is assembled as part of the overload protection device 10, the first retaining portion 354 retains the first spring end 350 in frictional engagement with the spring bracket 158.

[0074] Also in Figure 2 As shown, the second spring end 350' of the handle inertia spring 170 includes a bent portion 358 that extends generally along the rotation axis 34 of the recliner 18 after assembly with the spring bracket 158 ​​and the recliner B bracket 44. A second retaining portion 358' extends at an angle from the bent portion 358 of the handle inertia spring 170. Figure 14 As shown, the second retaining portion 358' and the bent portion 358 of the handle inertia spring 170 are sized and shaped such that when the handle inertia spring 170 is assembled as part of the overload protection device 10, the second spring end 350' can pass through the spring retaining hole 366 in the tilter B bracket 44. More specifically, as Figure 13As shown, when the second flange 207 of the handle spline 166 and the spring support 158 ​​passes through the central passage 348 of the coiled portion 346, the second spring end 350' is configured to pass through the spring retaining hole 366 in the recliner B support 44. Furthermore, the second retaining portion 358' and the bent portion 358 are sized and shaped such that after the second spring end 350' is inserted through the spring retaining hole 366 in the recliner B support 44, the second retaining portion 358' retains the second spring end 350' through the spring retaining hole 366. It will be understood that the size and shape of the handle inertia spring 170, including the first spring end 350 and the second spring end 350', can vary without changing the scope of the invention.

[0075] Figure 2 and Figure 14 The image shows a protrusion 174 formed on the support 44 of the recliner B. (See reference...) Figure 2 The recliner B bracket 44 includes a mounting portion 44A configured to engage with bosses 46, 48 projecting from the guide plate 42A of the disc recliner assembly 42. In various embodiments, the mounting portion 44A is integrally formed with the recliner B bracket 44. In alternative embodiments, the mounting portion 44A is a separate component assembled with the recliner B bracket 44. (See also...) Figure 14 The recliner B bracket 44 and the mounting portion 44A can be formed of metal, plastic, and / or a combination thereof. Preferably, at least the mounting portion 44A of the recliner B bracket 44 is formed of metal. In some embodiments, the mounting portion 44A is a metal bracket that is fixedly connected to the recliner B bracket 44.

[0076] Reference Figure 2 and Figure 14 The protrusion 174 formed on the recliner B bracket 44 bends away from the disc-shaped portion 44B of the mounting portion 44A of the recliner B bracket 44. In an alternative embodiment, the protrusion 174 is a separate component fixedly connected to the mounting portion 44A and / or the recliner B bracket 44. The protrusion 174 includes an overload stop 174A formed by the edge surface of the protrusion 174. The overload stop 174A is offset from the disc-shaped portion 44B of the mounting portion 44A. The protrusion 174 is sized and shaped such that when the spring bracket 158 ​​and the handle spline 166 are assembled on the disc shaft 62 and the spring bracket 158 ​​is along... Figure 14 When the second rotational direction B shown rotates toward the protrusion 174, the stop surface 246 of the stop flange 208 of the spring bracket 158 ​​will frictionally engage the overload stop portion 174A of the protrusion 174. It will be understood that the size and shape of the tilter B bracket 44, the mounting portion 44A, the protrusion 174, and the overload stop portion 174A can be varied without changing the scope of the invention.

[0077] Figures 10 to 13 The diagram illustrates the process of installing the overload protection device 10 on the tilting device 18. (Refer to...) Figure 10 The recliner 18 is shown assembled with the recliner B bracket 44 and the seat back 26. The recliner 18 includes a disc recliner assembly 42, which includes a guide plate 42A, a toothed plate 42B, a disc shaft 62, and other components. Furthermore, a return spring 38 is present. Figure 10 The image shows the assembly with the disc recliner assembly 42. The lower end surface 282 of the handle spline 166 is inserted into the alignment hole 250 in the spring bracket 158, wherein a plurality of splines 286 of the handle spline 166 are aligned with a plurality of splines 254 in the alignment hole 250, as shown by... Figure 10 As illustrated by arrow D. After the handle spline 166 is assembled with the spring bracket 158, the handle spline 166 is assembled with the disc shaft 62, as shown by... Figure 10 Arrow E is shown in the diagram. Alternatively, the spring bracket 158 ​​can be assembled with the disc 62 before the handle spline 166 is inserted into the alignment hole 250 of the spring bracket 158. In both cases, a portion of the disc 62 passes through the alignment hole 250 of the spring bracket 158.

[0078] Figure 11 The diagram shows a handle spline 166 and a spring bracket 158 ​​assembled on the disc shaft 62 of the disc recliner assembly 42. A clamping ring 162 is inserted into a clamping ring groove 334 in the handle spline 166, as shown by... Figure 11 As illustrated by arrow F, the clamping ring 162 axially holds the handle spline 166 on the disc shaft 62.

[0079] Figure 12 The diagram shows a cross-sectional view of the assembly of the disc shaft 62, spring support 158, handle spline 166, and clamping ring 162. (Refer to...) Figure 12 The lower support surface 194 of the spring bracket 158 ​​abuts against the base end face 94 of the disc shaft 62. Furthermore, depending on the specific dimensions of each component, the lower end surface 282 of the handle spline 166 abuts against the base end face 94 of the disc shaft 62, or the lower end surface 282 is spaced apart from the base end face 94 of the disc shaft 62. Additionally, the lower end surface 282 of the handle spline 166 is positioned within an alignment hole 250 in the spring bracket 158. Because the plurality of splines 254 in the alignment hole 250 engage with the plurality of splines 286 of the handle spline 166, the spring bracket 158 ​​will rotate together with the handle spline 166.

[0080] Although the spring bracket 158 ​​and the handle spline 166 are in Figure 12The diagram shows the handle spline 166 assembled with the disc spindle 62, but it is not fixedly connected to the disc spindle 62. The handle spline 166 is selectively connected to the disc spindle 62 based on its rotational position relative to the disc spindle 62. Figures 7 to 9 As shown, when the handle spline 166 rotates from the neutral position 322, there is a loss motion of approximately 6 degrees between the handle spline 166 and the disc shaft 62 (illustrated by loss motion angles 332 and 332'). It is understood that the magnitudes of the loss motion angles 332 and 332' can vary without changing the scope of the invention.

[0081] Similarly, Figure 12 As shown, the lower surface 298' of the cylindrical ring 290 of the handle spline 166 abuts against the upper support surface 190 of the spring support 158. The clamping ring groove 334 in the handle spline 166 is aligned with the channel 106 of the disc shaft 62, allowing the clamping ring 162 to be inserted into the clamping ring groove 334. Preferably, a portion of the inner cylindrical surface 262 of the clamping ring 162 is positioned within the channel 106, thereby preventing the handle spline 166 from moving along the rotation axis 34.

[0082] After the spring bracket 158 ​​and the handle spline 166 are assembled with the disc shaft 62, the handle inertia spring 170 is attached to the spring bracket 158 ​​and the tilting device B bracket 44, as follows: Figure 13 As shown in the image. (Refer to...) Figure 13 The first portion 346' of the coiled portion 346 of the handle inertia spring 170 is positioned below the distal flange end portion 230 of the second flange 207 of the spring support 158, such that the upper surface 346A of the coiled portion 346 abuts against the distal flange end portion 230 of the spring support 158. The second portion 346” of the coiled portion 346 of the handle inertia spring 170 is mounted on the spring bracket 158 ​​such that the lower side portion 346B of the coiled portion 346 abuts against the upper bracket surface 190 of the main bracket portion 186 of the spring bracket 158, wherein the handle spline 166 is positioned in the central passage 348 of the handle inertia spring 170. The first spring end 350 of the handle inertia spring 170 slides through the spring groove 214 in the first flange 206 of the spring bracket 158. The second spring end 350’ of the handle inertia spring 170 passes through the spring retaining hole 366 in the recliner B bracket 44. The spring torque of the handle inertia spring 170 maintains the first retaining portion 354 of the first spring end 350 of the handle inertia spring 170 in frictional engagement with the first flange 206 of the spring bracket 158. In addition, the spring torque of the handle inertia spring 170 maintains the second retaining portion 358’ of the second spring end 350’ of the handle inertia spring 170 in frictional engagement with the recliner B bracket 44.

[0083] Reference Figure 14The spring torque within the handle inertia spring 170 causes the spring bracket 158 ​​and the handle spline 166 to be rotated and biased toward the original angular position 36A along the second rotation direction B. When the handle spline 166 is in the original angular position 36A, the stop surface 246 on the spring bracket 158 ​​frictionally engages with the overload stop portion 174A on the tilter B bracket 44. More specifically, the return spring 38, which is operatively connected between the tilter 18 and the disc shaft 62, biases the disc shaft 62 toward the original angular position 36A. Therefore, when the disc shaft 62 is unloaded from an externally applied load, the return spring 38 causes the disc shaft 62 to automatically rotate toward the original angular position 36A. Furthermore, the handle inertia spring 170 rotates and biases the spring bracket 158 ​​toward the original angular position 36A. When the stop surface 246 on the spring bracket 158 ​​frictionally engages with the overload stop portion 174A on the tilter B bracket 44 and the disc shaft 62 is in the original angular position 36A, the disc shaft hole 310 of the handle spline 166 is automatically positioned in the neutral position 322, wherein the disc shaft 62 is disengaged from the disc shaft hole 310.

[0084] Figure 15 It shows Figure 14 A cross-sectional view of the disc shaft 62 and the handle spline 166, showing the spring support 158 ​​and the handle spline 166 in their original angular position 36A, wherein the disc shaft 62 is disengaged from the disc shaft bore 310 of the handle spline 166. Figure 15 The original angular position 36A shown corresponds to Figure 7 The neutral position 322 of the disc 62 and handle spline 166 shown. (See reference...) Figure 15 When the handle spline 166 is unloaded (i.e., the externally applied load is not applied to the recliner handle 14 attached to the handle spline 166), the spring torque in the handle inertia spring 170 ensures that the spring bracket 158 ​​and the connected handle spline 166 are in their original angular position 36A. When the handle spline 166 is spaced apart from its original angular position 36A and the recliner handle 14 is not constrained, the handle inertia spring 170 causes the spring bracket 158 ​​to automatically rotate in the second rotation direction B until the stop surface 246 of the stop flange 208 frictionally engages with the overload stop portion 174A of the recliner B bracket 44.

[0085] Reference Figure 14 and Figure 15 When the disc 62 is unloaded, the return spring 38 of the tilter 18 rotates the disc 62 in the second rotation direction B toward its original angular position 36A. The return spring 38 ensures that the tilter 18 is in the locked state when no upward torque is applied to the tilter handle 14. When the tilter 18 includes a cam for locking and unlocking the tilter 18, rotating the disc 62 in the first rotation direction A is alternatively described as the cam unlocking direction A. Similarly, rotating the disc 62 in the second rotation direction B is alternatively described as the cam locking direction B.

[0086] During normal use, an upward torque (first rotation direction A) is applied to the reclining handle 14 to initiate the normal reclining operation of the vehicle seat 22, such as... Figure 1 As shown. (As in...) Figure 14 and Figure 15 As observed, the rotation of the reclining handle 14 in the first rotational direction A applies torque to the handle spline 166, causing the handle spline 166 to rotate clockwise (arrow G). Figure 7 and Figure 8 As shown, there is a loss movement of approximately 6 degrees between the handle spline 166 and the disc shaft 62. It will be understood that, without changing the scope of the invention, the loss movement between the handle spline 166 and the disc shaft 62 may be greater than or less than approximately 6 degrees. (Refer to...) Figure 7 , Figure 8 and Figure 15 Before the second side portion 328' and the third side portion 329 of the disc shaft bore 310 frictionally engage with the corresponding flat side portions 72, 74 of the disc shaft 62, the handle spline 166 rotates clockwise ( Figure 8 Arrow 333 in the middle Figure 15 Arrow G) rotates through approximately a loss motion angle of 332. This initial rotation of the handle spline 166 absorbs the looseness between the disc bore 310 and the disc 62. After the looseness between the disc bore 310 and the disc 62 is absorbed by the initial rotation of the handle spline 166, the disc recliner assembly 42 functions as a typical direct-drive disc recliner assembly.

[0087] Handle spline 166 in a clockwise direction ( Figure 8 Arrow 333 in the middle Figure 15 The additional rotation (G) exceeding the loss motion angle 332 causes the disc shaft 62 to rotate together with the handle spline 166. The tilting lever handle 14 rotates along... Figure 1 The rotation in the first rotation direction A shown causes the handle spline 166, spring bracket 158, and disc shaft 62 to be rotated to Figure 16 The release angle position 36B is shown. When the tilting handle 14 rotates along the first rotation direction A, the rotational torque ( Figure 16 Arrow G) is applied to the handle spline 166, thereby keeping the handle spline 166 in the release angle position 36B. In some embodiments, the handle spline 166 rotates beyond the release angle position 36B when the tilter handle 14 is further rotated in the first rotation direction A.

[0088] When the handle spline 166 is in Figure 16When the release angle position 36B is shown, releasing the tilting lever handle 14 causes the handle inertia spring 170 to automatically rotate the spring bracket 158 ​​counterclockwise (arrow H) toward the original angle position 36A, as shown. Figure 17 As shown in the diagram, the handle spline 166 rotates together with the spring support 158 ​​because multiple splines 286 of the handle spline 166 engage with multiple splines 254 in the alignment holes 250 of the spring support 158. The spring torque in the handle inertia spring 170 maintains the stop surface 246 on the spring support 158 ​​in frictional engagement with the overload stop portion 174A of the tilter B support 44.

[0089] Figures 18 to 20 The diagram illustrates the operation of the overload protection device 10 during abnormal use. (Refer to...) Figure 1 Abnormal use occurs when a load is applied to the tilting handle 14 in the abuse rotation direction C while it is in its original position 14A. The handle spline 166 and the disc shaft 62... Figure 18 The disc is shown in its original angular position 36A, where the disc shaft 62 is disconnected from the disc shaft orifice 310. Figure 18 The relative rotational positions of the handle spline 166 and the disc shaft 62 shown are alternatively described as neutral position 322.

[0090] Figure 18 The relative rotational positions of the handle spline 166 and the disc shaft 62 in the neutral position shown correspond to the position of the tilting handle 14. Figure 1 The original position 14A is shown. Figure 18 The relative rotational position of the disc shaft orifice 310 with respect to the disc shaft 62 also corresponds to Figure 7 The disc shaft orifice 310 shown is in a relative rotational position with respect to the disc shaft 62. Specifically, when the handle spline 166 and the disc shaft 62 are in... Figure 7 and Figure 18 In the neutral position 322 shown, the fourth side portion 329' of the disc shaft bore 310 in the handle spline 166 tapers away from the adjacent flat side portion 74 of the disc shaft 62. Therefore, when the handle spline 166 is in the neutral position 322 and no load is applied to the tilter handle 14, the disc shaft bore 310 is disengaged from the disc shaft 62.

[0091] Reference Figure 1 and Figure 19 When the tilting handle 14 is in Figure 1 When the original position 14A is shown and a load is applied to the tilt handle 14 along the abuse rotation direction C, the abuse torque J ( Figure 19 The abuse torque J applied to the handle spline 166 along the cam locking direction B is... Figure 19Arrow J in the diagram indicates that, when the recliner handle 14 is in its original position 14A, an exemplary amount of abuse torque J applied to the recliner handle 14 in the cam locking direction B is approximately 120 Nm.

[0092] Reference Figure 19 The abuse torque J applied to the handle spline 166 causes the handle spline 166 to rotate in the abuse rotation direction C beyond its original angular position 36A. For a typical disc recliner lacking overload protection device 10, the abuse torque J applied to the handle spline 166 causes the handle spline 166 to rotate in the abuse rotation direction C beyond its original angular position 36A, and causes the typical disc recliner to over-lock. However, as Figure 19 As shown, when the handle spline 166 is in the neutral position 322, the stop surface 246 on the spring bracket 158 ​​of the overload protection device 10 frictionally engages with the overload stop portion 174A on the tilter B bracket 44. Furthermore, the handle spline 166 engages with the spring bracket 158 ​​and rotates together with it. More specifically, a plurality of splines 286 of the handle spline 166 engage with a plurality of splines 254 in the alignment holes 250 of the spring bracket 158, causing the handle spline 166 to rotate together with the spring bracket 158, as... Figure 10 and Figure 12 As shown in the diagram. Therefore, the abuse torque J applied to the handle spline 166 initiates rotation of the handle spline 166 in the abuse rotation direction C, thereby causing the stop surface 246 on the stop flange 208 of the spring bracket 158 ​​to strike the overload stop portion 174A on the protrusion 174 of the tilter B bracket 44, as shown in the diagram. Figure 19 As shown in the diagram, the engagement between the stop flange 208 and the overload stop portion 174A prevents the handle spline 166 from rotating beyond its original angular position 36A in the abuse rotation direction C. (See reference...) Figure 20 The abuse torque J applied to the handle spline 166 is transferred to the spring bracket 158, and the load K (illustrated by arrow K) is applied to the overload stop 174A on the protrusion 174 of the recliner B bracket 44. This effectively transfers the abuse torque J applied to the handle spline 166 to the protrusion 174 of the recliner B bracket 44.

[0093] like Figure 7 , Figure 9 and Figure 20 As shown, the looseness between the disc shaft 62 and the disc shaft orifice 310 in the handle spline 166 prevents the abuse torque J from being transferred to the disc shaft 62. Figure 7 The handle spline 166 and the disc shaft 62 are shown in the neutral position 322, wherein the first side portion 328 and the fourth side portion 329' of the disc shaft orifice 310 taper away from the adjacent flat side portions 72, 74 of the shaft. Figure 9 It shows 333' from the counterclockwise direction. Figure 7 The neutral position 322 shown rotates through the handle spline 166 at an approximately loss motion angle 332', where the overload stop 174A is omitted from the leaner B bracket 44. Figure 20 The abuse of rotation direction C and Figure 9 The counter-clockwise direction 333' shown corresponds to this. (Refer to...) Figure 9 Before the fourth side portion 329' of the disc shaft bore 310 frictionally engages with the adjacent flat side portion 74 of the disc shaft 62, the handle spline 166 must rotate counterclockwise 333'. Figure 20 The abuse of rotation direction C) rotates through approximately the loss motion angle 332'. When the handle spline 166 rotates counterclockwise 333' through the loss motion angle 332', the disc shaft 62 rotates together with the handle spline 166 because the first side portion 328 and the fourth side portion 329' have already engaged with the corresponding adjacent shaft flat side portions 72, 74 through friction.

[0094] However, as Figure 20 As shown, the frictional engagement between the stop surface 246 on the stop flange 208 of the spring bracket 158 ​​and the overload stop portion 174A on the protrusion 174 of the recliner B bracket 44 prevents the handle spline 166 from rotating beyond its original angular position 36A in the abuse rotation direction C. The abuse torque J applied to the recliner handle 14 is transferred through the handle spline 166 and loads the spring bracket 158 ​​abutting against the protrusion 174 of the recliner B bracket 44. The looseness between the disc bore 310 in the handle spline 166 and the disc 62 prevents the abuse torque J from being transferred from the handle spline 166 to the disc 62. Because the abuse torque J is transferred to the recliner B bracket 44 instead of the disc 62, the disc 62 will not rotate beyond its original angular position 36A when a downward torque is applied to the recliner handle 14. The overload protection device 10 prevents the disc shaft 62 from rotating beyond its original angular position 36A in the abuse rotation direction C, thereby effectively preventing the recliner 18 from being over-locked. Furthermore, the internal components of the disc recliner assembly 42 are not directly loaded by the downward torque of the recliner handle 14, because the load applied by the abuse torque J is transferred between the recliner handle 14, the handle spline 166, the spring bracket 158, and the protrusion 174 of the recliner B bracket 44.

[0095] Figures 21 to 26 The figure shows a second embodiment of the tilt handle 14 with overload protection device 10'. Figure 2 The first embodiment of the overload protection device 10 shown includes a spring bracket 158 ​​having a stop flange 208 assembled with a separate handle spline 166. In contrast, Figures 21 to 26The overload protection device 10' shown has a stop flange 208' integrated with the handle spline 166'. Furthermore, as... Figure 21 As shown, Figure 2 The handle inertia spring 170 shown is replaced by a handle inertia spring 170', which is operatively connected between the handle spline 166' and the recliner B bracket 44.

[0096] Figure 22 An exploded view of the components of a second embodiment of the overload protection device 10' is shown. The handle spline 166' includes a disc bore 310' extending longitudinally through the handle spline 166'. The handle spline 166' is assembled with the tilter 18 by inserting the disc shaft 62 of the tilter 18 into the disc bore 310'. The handle inertia spring 170' of the second embodiment includes a first spring end 350A configured to frictionally engage with a first spring retaining surface 370 on the handle spline 166'. Furthermore, as... Figure 21 As shown, the second spring end 350B of the handle inertia spring 170' is configured to frictionally engage with the spring retaining flange 366B on the leaner B bracket 44.

[0097] Figure 23 The handle spline 166' assembled with the recliner B bracket 44 and disc shaft 62 of the second embodiment is shown, illustrating the integrated stop flange 208' of the handle spline 166' which is in frictional engagement with the overload stop portion 174A of the recliner B bracket 44. Figure 15 The first embodiment shown and Figure 23 The comparison of the second embodiment shown illustrates the similarity between the first and second embodiments. For example, when the handle spline 166 rotates, the stop flange 208 of the spring bracket 158 ​​rotates together with the handle spline 166, as per the description of... Figures 15 to 17 As shown and described. (Refer to...) Figure 23 In the second embodiment, the stop flange 208' rotates together with the handle spline 166' because the stop flange 208' and the handle spline 166' are integrally formed.

[0098] Furthermore, the disc shaft hole 310' of the handle spline 166' in the second embodiment is similar in shape and size to the disc shaft hole 310 of the handle spline 166 in the first embodiment, as can be seen by comparison. Figure 24 and Figure 7 As shown. Reference Figure 24In the second embodiment, the handle spline 166' has a disc shaft bore 310' with an inner bore portion 310A', which is sized and shaped to engage with the elongated shaft end portion 66 of the disc shaft 62, while maintaining a loss movement of approximately 6 degrees between the disc shaft 62 and the disc shaft bore 310'. It is understood that, without changing the scope of the invention, the amount of loss movement between the disc shaft 62 and the disc shaft bore 310' can be greater than or less than approximately 6 degrees. The inner bore portion 310A' of the disc shaft bore 310' includes opposing first sidewalls 324' and second sidewalls 325', as well as opposing first endwalls 326' and second endwalls 327'. The first sidewall 324' includes a first side portion 328D' extending at an angle from the second side portion 328D', such that the interior angle 328A' between the first side portion 328D and the second side portion 328D' is greater than 180 degrees, as measured within the disc bore 310'. Similarly, the second sidewall 325' includes a third side portion 329D extending from the fourth side portion 329D' at an interior angle 329A', such that the interior angle 329A' between the third side portion 329D and the fourth side portion 329D' is greater than 180 degrees, as measured within the disc bore 310'. Furthermore, the first side portion 328D and the fourth side portion 329D' are generally parallel and spaced apart. Likewise, the second side portion 328D' and the third side portion 329D are generally parallel and spaced apart. Furthermore, the first side portion 328D is not parallel to the second side portion 328D'. Similarly, the third side portion 329D is not parallel to the fourth side portion 329D'. In some embodiments, one or more of the first side portion 328D, the second side portion 328D', the third side portion 329D, and the fourth side portion 329D' include curved surfaces, tapered surfaces, and / or generally flat surfaces. Also as... Figure 24 As shown, a first end wall 326' extends between the ends 328B' and 329B' of the first side portion 328D and the third side portion 329D of the disc shaft aperture 310'. Similarly, a second end wall 327' extends between the ends 328C' and 329C' of the second side portion 328D' and the fourth side portion 329D'. Figure 24 In the embodiment shown, the first end wall 326' and the second end wall 327' are curved walls.

[0099] Figure 26 A cross-sectional perspective view of the handle spline 166' of the second embodiment, assembled with the disc shaft 62, is shown. Figure 26In the disc shaft 62 and handle spline 166', the disc shaft orifice 310' is positioned in a neutral position 322, wherein the disc shaft orifice 310' is disengaged from the disc shaft 62. Furthermore, the inner orifice portion 310A' of the disc shaft orifice 310' is sized and shaped such that the first joint 331D of the first side portion 328D and the second side portion 328D', and the second joint 331D' of the third side portion 329D and the fourth side portion 329D', frictionally engage with the corresponding adjacent flat side portions 72, 74 of the disc shaft 62 during assembly, such as... Figure 26 As shown in the diagram. It is understood that in some embodiments, without changing the scope of the invention, the first joint 331D and the second joint 331D' are spaced apart from the adjacent flat side portions 72, 74 of the disc shaft 62. When the disc shaft 62 is centered within the disc shaft aperture 310'... Figure 26 In the neutral position 322 shown, each of the first to fourth side portions 328D, 328D', 329D, and 329D' of the disc shaft orifice 310' tapers away from the adjacent flat side portions 72 and 74 of the disc shaft 62 with approximately loss motion angles 332 and 332'. Therefore, when the handle spline 166' and the disc shaft 62 are in... Figure 26 In the neutral position 322 shown, each of the first to fourth side portions 328D, 328D', 329D, and 329D' of the disc shaft orifice 310' is substantially disengaged from the adjacent axial flat side portions 72 and 74 of the disc shaft 62. Approximate loss motion angles 332 and 332' represent the loss motion between the handle spline 166' and the disc shaft 62 when the handle spline 166' rotates. As in the first embodiment, rotating the handle spline 166' from the neutral position 322 by less than the loss motion angle 332 results in the handle spline 166' rotating independently of the disc shaft 62. When the handle spline 166' rotates from... Figure 26 When the neutral position 322 shown is rotated by approximately a loss of motion angle 332, the disc shaft orifice 310' engages with the disc shaft 62. As long as the disc shaft orifice 310' engages with the disc shaft 62, the disc shaft 62 rotates together with the handle spline 166'.

[0100] Reference Figure 25 The handle spline 166' has a plurality of splines 286' spaced apart around the outer periphery 274A of the spline portion 270', which is configured to engage with the tilter handle 14. Furthermore, the disc bore 310' extends axially through the handle spline 166'. Similarly... Figure 25As shown, the handle spline 166' includes a spring retaining flange 370A having a first spring retaining surface 370. The first spring retaining surface 370 is configured to frictionally engage with and retain the first spring end 350A of the handle inertia spring 170'. Figure 24 As shown, the spring retaining flange 370A extends circumferentially around the handle spline 166'. Figure 24 In the illustrated embodiment, the spring retaining flange 370A extends between the stop flange 208' and the first spring retaining surface 370. It will be understood that the stop flange 208' and the first spring retaining surface 370 may vary in size, shape, positioning, and location, including being separated at the handle spline 166', without departing from the scope of the invention.

[0101] Figure 24 and Figure 25 The handle spline 166' shown is sized and shaped to be formed from a plastic material using a molding process. An exemplary suitable plastic material is nylon 6 / 6 with approximately 30% glass filler. Alternatively, the handle spline 166' can be formed from a metal, such as a zinc-aluminum alloy or similar metal. An exemplary suitable zinc-aluminum alloy is Zamak 5 (4% ​​aluminum, 1% copper, and 95% zinc). It is understood that the handle spline 166' can be formed from alternative metals and molded from alternative plastic materials without changing the scope of the invention.

[0102] One advantage of the recliner handle 14 with overload protection devices 10, 10' is that it prevents damage to the recliner 18 when a downward torque (abuse torque) is applied to the recliner handle 14 when it is in its original position 14A. A second advantage is that the abuse torque applied to the recliner handle 14 is diverted away from the recliner 18. A third advantage of the overload protection devices 10, 10' between the recliner handle 14 and the recliner 18 is that it prevents overload of the recliner 18 when a downward torque is applied to the recliner handle 14.

[0103] The present invention has been described in an illustrative manner, and it is to be understood that the terminology used is intended to be descriptive rather than restrictive. In view of the foregoing teachings, many modifications and variations of the invention can be made. Therefore, it is understood that the invention can be practiced in ways other than those specifically described within the scope of the appended claims.

Claims

1. A recliner handle with an overload protection device, the recliner handle being used in a vehicle seat having a recliner fixedly connected to a recliner B bracket, the overload protection device comprising: A handle spline is fixedly connected to the recliner handle and has a disc shaft orifice configured to engage with a disc shaft operatively connected to the recliner, wherein the disc shaft is rotatable to actuate the recliner between a locked and unlocked state, thereby enabling tilt adjustment of the vehicle seat. An overload stop is fixedly connected to the tilting device B bracket; The handle spline is rotatable along a first rotational direction from a first position associated with the locked state to a second position associated with the unlocked state. When the handle spline is in the first position, the disc shaft orifice is rotatably disengaged from the disc shaft, and when the handle spline is in the second position, the disc shaft orifice is rotatably engaged with the disc shaft. A stop flange, the stop flange being attached to the handle spline and configured to abut against the overload stop portion when the handle spline is in the first position; When the handle spline is in the first position, the engagement of the overload stop portion and the stop flange prevents the handle spline from rotating in a second rotation direction opposite to the first rotation direction and away from the second position, thereby avoiding the transmission of overload force to the tilting device.

2. The tilting handle with overload protection device according to claim 1, wherein: The first position and the second position are separated by a loss motion angle.

3. The tilting handle with overload protection device according to claim 2, wherein: A handle inertia spring is operatively connected between the handle spline and the tilting device B bracket, the handle inertia spring biasing the stop flange toward an engagement position that engages with the overload stop.

4. The tilting handle with overload protection device according to claim 3, wherein: When the disc shaft is in its original angular position, the tilting device is in the locked state; and When the disc shaft is in the release angle position, the tilting device is in the unlocked state.

5. The tilting handle with overload protection device according to claim 4, wherein: The disc shaft is capable of rotating between the initial angular position and the release angular position; Rotate the disc shaft along the first rotation direction from the original angular position to the release angular position such that the tilting device is reconstructed from the locked state to the unlocked state; and Rotating the disc shaft along the second rotation direction from the release angle position to the original angle position causes the tilting device to be reconstructed from the unlocked state to the locked state.

6. The tilting handle with overload protection device according to claim 5, wherein: The reclining handle is rotatable between its original position and the reclining release position; and When the reclining handle is in the original position, the handle spline is in the first position, and the disc shaft orifice is disengaged from the disc shaft, a torque is applied to the reclining handle along the first rotation direction, causing the reclining handle to rotate in the first rotation direction less than the loss motion angle, resulting in the handle spline rotating in the first rotation direction when the disc shaft is disengaged from the disc shaft orifice.

7. The tilting handle with overload protection device according to claim 6, wherein: When the reclining handle is spaced from its original position by at least the loss angle, a torque is applied to the reclining handle along the first rotation direction, causing the reclining handle to rotate along the first rotation direction, resulting in the handle spline rotating along the first rotation direction while the disc shaft engages with the disc shaft bore; and When the disc shaft engages with the disc shaft orifice, the disc shaft rotates together with the handle spline.

8. The tilting handle with overload protection device according to claim 7, wherein: When the handle spline is in the first position and the stop flange is in the engagement position where it is engaged with the overload stop portion, the handle spline is rotated along the first rotation direction to disengage the stop flange from the overload stop portion.

9. The tilting handle with overload protection device according to claim 8, wherein: When the reclining handle is rotated to the reclining release position along the first rotation direction, the handle spline rotates to the release angle position, the disc shaft orifice that engages with the disc shaft causes the disc shaft to rotate to the release angle position, and the disc shaft that has rotated to the release angle position reconfigures the reclining device into the unlocked state.

10. The tilting handle with overload protection device according to claim 9, wherein: When the handle spline is in the first position with the disc shaft orifice disengaged from the disc shaft, and when the stop flange is in the engagement position engaged with the overload stop, a torque is applied to the tilter handle in the second rotation direction, causing a load to be applied to the overload stop through the stop flange while keeping the disc shaft orifice disengaged from the disc shaft.

11. The tilting handle with overload protection device according to claim 10, wherein, The disc shaft orifice has an elongated orifice portion, which includes: A first sidewall, comprising a first portion and a second portion joined at a first joint, the first portion and the second portion having a first end and a second end spaced apart from the first joint, and the first portion and the second portion not parallel; The second sidewall includes a third portion and a fourth portion joined at the second joint, the third portion and the fourth portion having a third end and a fourth end spaced apart from the second joint, and the third portion and the fourth portion are not parallel; A first end wall, the first end wall being adjacent to the first end of the first side wall and the third end of the second side wall; and The second end wall is adjacent to the second end of the first side wall and the fourth end of the second side wall.

12. The tilting handle with overload protection device according to claim 11, wherein, The elongated orifice portion of the disc shaft orifice includes: The first portion of the first sidewall is opposite to the third portion of the second sidewall, and the second portion of the first sidewall is opposite to the fourth portion of the second sidewall. The first end of the first portion of the first sidewall and the third end of the third portion of the second sidewall are spaced further apart than the first joint and the second joint. The second end of the second portion of the first sidewall and the fourth end of the fourth portion of the second sidewall are further apart than the first joint and the second joint.

13. The tilting handle with overload protection device according to claim 12, wherein, The elongated orifice portion of the disc shaft orifice includes: The first interior angle between the first portion and the second portion of the first sidewall is greater than 180 degrees; and The second interior angle between the third and fourth portions of the second sidewall is greater than 180 degrees.

14. The tilting handle with overload protection device according to claim 13, wherein: The disc shaft has an elongated portion with a rounded rectangular cross-section and opposite first and second axial flat sidewalls.

15. The tilting handle with overload protection device according to claim 14, wherein: When the handle spline is in the first position and the disc shaft is in the original angular position, the first portion of the first sidewall of the disc shaft orifice extends away from the first axial flat sidewall of the disc shaft, and the fourth portion of the second sidewall of the disc shaft orifice extends away from the second axial flat sidewall of the disc shaft with the loss motion angle.

16. The tilting handle with overload protection device according to claim 15, wherein: When the handle spline is in the first position and the disc shaft is in the original angular position, the second portion of the first sidewall of the disc shaft orifice extends away from the first axial flat sidewall of the disc shaft at the loss motion angle, and the third portion of the second sidewall of the disc shaft orifice extends away from the second axial flat sidewall of the disc shaft at the loss motion angle.

17. The tilting handle with overload protection device according to claim 16, wherein: When the handle spline is in the first position, the disc shaft is in the original angular position and is disengaged from the disc shaft orifice of the handle spline, the handle spline is rotated along the first rotation direction by at least the loss motion angle, causing the second portion of the first sidewall and the third portion of the second sidewall of the disc shaft orifice to rub against the first axial flat sidewall and the second axial flat sidewall of the disc shaft, respectively.

18. The tilting handle with overload protection device according to claim 17, wherein: The stop flange is integrally formed with the spring bracket; and The spring bracket is fixedly connected to the handle spline.

19. The tilting handle with overload protection device according to claim 18, wherein: The handle inertia spring is operatively connected between the spring bracket and the tilting device B bracket.

20. The tilting handle with overload protection device according to claim 19, wherein: The handle spline has an outer contour; and The spring support has a main support portion, an alignment aperture through the main support portion, a stop flange protruding from the main support portion, and the alignment aperture has an inner contour configured to engage with the outer contour of the handle spline.

21. The tilting handle with overload protection device according to claim 20, wherein: The handle inertia spring is operatively connected between the spring bracket and the tilting device B bracket, and the handle inertia spring rotates and biases the stop flange of the spring bracket toward the engagement position that engages with the overload stop portion.

22. The tilting handle with overload protection device according to claim 21, wherein: The tilting device includes a return spring operatively connected between the tilting device and the disc shaft, the return spring biasing the disc shaft toward the original angular position; and The handle spline is fixedly connected to the spring bracket, which is biased toward the first position, and the spring bracket is biased toward the engagement position, which engages with the overload stop, via the handle inertia spring.

23. The tilting handle with overload protection device according to claim 22, wherein, When the tilting handle is unloaded by an externally applied load: The return spring causes the disc shaft to automatically rotate back to the original angular position; The handle inertia spring causes the spring bracket to automatically rotate to the engagement position where it engages with the overload stop. The handle spline automatically rotates to the first position by rotating through the spring bracket to the engagement position that engages with the overload stop; and The reclining handle is rotated to the first position via the handle spline and then automatically rotates back to the original position.

24. The tilting handle with overload protection device according to claim 23, wherein: The spring support includes a first flange and a second flange projecting from the main support portion, wherein the first flange includes a spring groove; and The handle inertia spring is a helical spring having a coiled portion, a first spring end, and a second spring end. The coiled portion has a central passage extending through the coiled portion. The first spring end is configured to pass through the spring groove in the first flange, and the second spring end is configured to pass through the spring retaining hole in the leaner B bracket. The handle spline and the second flange pass through the central passage.

25. The tilting handle with overload protection device according to claim 24, wherein: The outer contour of the handle spline includes a first alignment feature configured to engage with a second alignment feature of the inner contour of the alignment orifice of the spring bracket.

26. The tilting handle with overload protection device according to claim 17, wherein: The stop flange is integrally formed with the handle spline.

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