High latch assembly with translating carriage

Abstract

A seat assembly for use in an automotive vehicle comprises a seat cushion adapted to be coupled to a floor of the automotive vehicle, a seat back pivotably coupled to the seat cushion and a high latch (12) fixedly coupled to the seat back. The high latch (12) comprises a mounting plate assembly (40) fixedly coupled to the seat back and a carriage assembly (42) slidably coupled to the mounting plate assembly (40) and configured to be selectively coupled to a striker fixedly secured to a support wall in the automotive vehicle. The mounting plate assembly (40) selectively translates relative to the carriage assembly (42) while the carriage assembly (42) is coupled to the striker causing the seat back to pivot relative to the seat cushion between a design position, a full recline position, and an unlatched position.

Description

HIGH LATCH ASSEMBLY WITH TRANSLATING CARRIAGECROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application claims priority to U.S. Provisional Application 63 / 539,952, filed on September 22, 2023, the disclosure of which is hereby incorporated by reference in its entirety.FIELD OF THE INVENTION

[0002] The present invention relates to a seat assembly for use in an automotive vehicle. More particularly, the invention relates to a high latch assembly for use on a seat assembly having a seat back pivotably coupled to a seat cushion wherein the seat back is selectively movable between an upright design position, a reclined position, and a fold flat position overlying the seat cushion.DESCRIPTION OF RELATED ART

[0003] Automotive vehicles typically include one or more seat assemblies having a seat cushion and a seat back for supporting a passenger above a vehicle floor. In sedan type or other vehicles, rear seating assemblies are often fixedly secured to the vehicle floor and have limited adjustability due to the limited space within the rear compartment of the vehicle. It is common for these rear seat assemblies to include a seat back coupled to a seat cushion by a pivot assembly for providing selective pivotal folding of the seat back relative to the seat cushion between a use position and a fold flat position overlying the seat cushion to provide additional storage space within the vehicle rear compartment. It is also common to include a recliner assembly operatively coupled between the seat back and the seat cushion to provide selective pivotal adjustment of the seat back between the use position and a rearward reclined position to provide seat occupant comfort. Alternatively, rear seat assemblies are also known to have a seat back secured to a fixed striker on the vehicle by a high latch. The high latch is selectively decoupled from the fixed striker allowing the seat back to be rotated from an upright position towards a folded position. Certain known seat assemblies are selectively moveable between a use position and a reclined position while the high latch is engaged with the fixed striker.

[0004] However, in a sedan ty pe vehicle, the range of motion of the seat back is limited by the high latch coupled to the fixed striker. It is desirable, therefore, to improve the range of motion of the seat back while the high latch is coupled to the striker.SUMMARY OF THE INVENTION

[0005] According to one embodiment, there is provided a seat assembly for use in an automotive vehicle. The seat assembly comprises a seat cushion adapted to be coupled to a floor of the vehicle, a seat back pivotably coupled to the seat cushion, a striker adapted to be fixedly secured to a support wall in the vehicle, and a high latch fixedly coupled to the seat back. The high latch comprises a mounting plate assembly fixedly coupled to the seat back and a carriage assembly slidably coupled to the mounting plate assembly and configured to be selectively coupled to the striker. The mounting plate assembly selectively translates relative to the carriage assembly while the carriage assembly is coupled to the striker which causes the seat back to pivot relative to the seat cushion between a design position, a full recline position, and an unlatched position.

[0006] According to another embodiment, there is provided a high latch for use in a seat assembly in an automotive vehicle. The high latch includes a mounting plate assembly comprising a mounting bracket and an upper guide rod fixedly coupled to the mounting bracket. The high latch also includes a carriage assembly comprising a trolley bracket slidably coupled to the upper guide rod, a lower pivot fixedly coupled to the trolley bracket, and a lower strength hook pivotably coupled to the lower pivot and adapted to be coupled to a striker in the automotive vehicle. The mounting plate assembly selectively translates relative to the carriage assembly between a design position, a full recline position, and an unlatched position.BRIEF DESCRIPTION OF THE DRAWINGS

[0007] Advantages of the present invention will be readily appreciated as the same becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings wherein:

[0008] Figure 1 is a front perspective view of an automotive seat assembly having a high latch, according to one embodiment of the present invention;

[0009] Figure 2 is semi-transparent left side view of the high latch from the seat assembly of Figure 1;

[0010] Figure 3 is a semi-transparent right side view of the high latch of Figure 2;

[0011] Figure 4 is a perspective view of the high latch of Figure 3;

[0012] Figure 5 is a cross-sectional view of the high latch of Figure 3 taken along line 5-5 in Figure 3;

[0013] Figure 6 is an enlarged cross-sectional view of portion 6 of the high latch in Figure 5;

[0014] Figure 7 is an exploded view of the high latch of Figure 4, showing a mounting plate assembly and showing a camage assembly which includes a lower pivot shaft and a hook pin;

[0015] Figure 8 is an exploded view of the mounting plate assembly of Figure 7, which includes an upper pivot shaft;

[0016] Figure 9 is a cross-sectional view of the upper pivot shaft of Figure 8;

[0017] Figure 10 is a cross-sectional view of the lower pivot shaft of the carriage assembly of Figure 7;

[0018] Figure 11 is a cross-sectional view of the hook pin of the carriage assembly of Figure 7;

[0019] Figure 12 is an exploded view of the carriage assembly of Figure 7;

[0020] Figure 13 is a cross-sectional view of the high latch of Figure 3 taken along line 13-13;

[0021] Figure 14 is an enlarged perspective view of portion 14 of the high latch in Figure 4;

[0022] Figure 15 is an enlarged semi-transparent right side view of portion 15 of the high latch of Figure 3;

[0023] Figure 16 is an enlarged semi-transparent right side view of portion 16 of the high latch of Figure 3;

[0024] Figure 17 is a semi-transparent right side view of the high latch of Figure 3, showing the high latch in a design position coupled with a striker with the mounting plate assembly- engaged with the carriage assembly;

[0025] Figure 18 is a semi-transparent right side view of the high latch of Figure 17, showing the high latch in the design position coupled to the striker with the mounting plate assembly disengaged from the carriage assembly;

[0026] Figure 19 is a semi-transparent right side view of the high latch of Figure 18, showing the high latch in a mid-position coupled to the striker with the mounting plate assembly disengaged from the carriage assembly;

[0027] Figure 20 is a semi-transparent right side view of the high latch of Figure 19, showing the high latch in the mid-position coupled to the striker with the mounting plate assembly engaged with the carriage assembly;

[0028] Figure 21 is a semi-transparent right side view of the high latch of Figure 20, showing the high latch in the full recline position coupled to the striker with the mounting plate assembly disengaged from the carriage assembly;

[0029] Figure 22 is a semi-transparent right side view of the high latch of Figure 21, showing the high latch in the full recline position coupled to the striker with the mounting plate assembly engaged with the carriage assembly;

[0030] Figure 23 is a semi-transparent right side view of the high latch of Figure 22, showing the high latch coupled to the striker, the hook pin engaged with a hook release, and the mounting plate assembly disengaged from the carriage assembly;

[0031] Figure 24 is a semi-transparent right side view of the high latch of Figure 23, showing the high latch in an unlatched position decoupled from the striker with the mounting plate assembly disengaged from the carriage assembly;

[0032] Figure 25 is a semi-transparent right side view of the high latch of Figure 24, showing the high latch in the unlatched position decoupled from the striker with the mounting plate assembly engaged with the carriage assembly;

[0033] Figure 26 is a front perspective view of a high latch, according to a second embodiment of the present invention;

[0034] Figure 27 is a semi-transparent right side view of the high latch of Figure 26, showing the high latch in a design position coupled to a striker;

[0035] Figure 28 is a semi-transparent right side view of the high latch of Figure 27. showing the high latch in a mid-position coupled to the striker;

[0036] Figure 29 is a semi-transparent right side view of the high latch of Figure 28, showing the high latch in a full recline position coupled to the striker;

[0037] Figure 30 is a semi-transparent right side view of the high latch of Figure 29, showing the high latch coupled to the striker with the hook pin engaged with the hook release; and

[0038] Figure 31 is a semi-transparent right side view of the high latch of Figure 30, showing the high latch in an unlatched position decoupled from the striker.DETAILED DESCRIPTION OF THE INVENTION

[0039] Figures 1-31 illustrate a seat assembly 10 having a high latch assembly 12 for use in an automotive vehicle according to embodiments described herein. Directional references employed or shown in the description, figures, or claims, such as top, bottom, upper, lower, upward, downward, lengthwise, widthwise, left, right, and the like, are relative terms employed for ease of description and are not intended to limit the scope of the invention in any respect. Referring to the Figures, like numerals indicate like or corresponding parts throughout the several views.

[0040] As depicted in Figure 1, the seat assembly 10 includes a seat back 14 and a seat cushion 16. Figure 1 illustrates the seat assembly 10 in a generally upright seating position. The seat back 14 is pivotably coupled to the seat cushion 16 by opposing free pivots 18. The seat cushion 16 is adapted to be coupled to a floor of an automotive vehicle. The seat assembly 10 may include a seat back spring 20 operatively coupled between the seat back 14 and the seat cushion 16. The seat back spring 20 applies a forward-biasing force (arrow 22) to rotationally bias the seat back 14 in a forward direction (arrow 24 A) around the free pivots 18 towards a fold flat position 26 with the seat back 14 overlying the seat cushion 16. The seat assembly 10 also includes a stnker 28 adapted to be fixedly secured to a support wall 32 in the automotive vehicle. The striker 28 is generally U-shaped and includes a horizontal elongated striker portion 30. It should be appreciated that the shape and structure of the striker 28 can vary without departing from the scope of the present invention.

[0041] Referring to Figures 1-5, the seat assembly 10 further includes the high latch assembly 12 (hereinafter, “high latch”) fixedly coupled to the seat back 14 and configured to selectively couple to the striker 28. In addition, the high latch 12 allows the seat back 14 to be manually repositioned between a design position 34, a mid-position 36 with the seat back 14 reclined orangled from the design position 34, and a full recline position 38, with the seat back 14 further reclined or angled from the design position 34, while the high latch 12 is coupled to the striker 28. Further, the high latch 12 is configured so that the high latch 12 can be decoupled from the striker 28 allowing the seat back 14 to be pivoted to the fold flat position 26 when an occupant actuates the high latch 12. In one embodiment, the high latch 12 is configured to adjust an inclination angle 39 between the design position 34 and the full recline position 38 of about 6.5 degrees or about a distance of 44 mm. The high latch 12 is configured to require low effort and a low stroke distance to actuate the high latch 12. Further, the high latch 12 is configured to typically accommodate about + / - 4 mm in variation in the relative position of the striker 28. The high latch 12 is configured to include a dual strength / cinch lock mechanism, as further described below.

[0042] Referring to Figure 7, the high latch 12 includes a mounting plate assembly 40 and a carriage assembly 42. The mounting plate assembly 40 is fixedly coupled to the seat back 14. The carriage assembly 42 is slidably coupled to the mounting plate assembly 40 and configured to be coupled to the striker 28. The mounting plate assembly 40 is selectively coupled to the carriage assembly 42. The mounting plate assembly 40 can be translated relative to the carriage assembly 42 while the mounting plate assembly 40 is decoupled from the carriage assembly 42. Translating the mounting plate assembly 40 relative to the carriage assembly 42 while the carriage assembly 42 is coupled to the striker 28 causes the seat back 14 to pivot relative to the seat cushion 16 between the design position 34 and the full recline position 38. In addition, the carriage assembly 42 includes a carriage bracket 44 having a forward aperture 46, a middle aperture 48, and a rear aperture 50 corresponding to the design position 34, the mid-position 36, and the full recline position 38, respectively. The carriage assembly 42 is further described below. It will be appreciated that in alternate embodiments the carriage assembly 42 can be translated relative to the mounting plate assembly 40 without altering the scope of the present invention.

[0043] Depicted in Figure 8, the mounting plate assembly 40 includes a mounting bracket 58 configured to be fixedly coupled to the seat back 14. The mounting bracket 58 includes a back panel 60, a base flange 62, an upper flange 64, and a lower flange 66. The mounting bracket 58 includes a base sidewall 68 extending laterally from a lower portion of the back panel 60. The base flange 62 extends downward from an outboard end of the base sidewall 68 and is offset laterally from the back panel 60. In addition, the base flange 62 includes spaced apartfirst and second bolt holes 70, 72 extending laterally through the base flange 62. The mounting bracket 58 is fixedly coupled to the seat back 14 by first and second bolts 69 A. 69B (Figure 17) inserted through the respective first and second bolt holes 70, 72, as is commonly known in the art. In addition, the upper flange 64 and the lower flange 66 project from the back panel 60 in a lateral direction and are spaced apart vertically. The upper flange 64 includes an upper rear hole 74 extending longitudinally therethrough and having an inner diameter 76. The lower flange 66 includes a lower rear hole 78 extending longitudinally therethrough and having an inner diameter 80. In addition, the lower flange 66 includes an aft spring slot 82 extending longitudinally in the lower flange 66 and spaced vertically apart from the lower rear hole 78. The mounting bracket 58 also includes a front flange 84, which projects laterally from the back panel 60 and is spaced longitudinally apart from the upper and lower flanges 64, 66. Further, the front flange 84 includes an upper front hole 86 extending longitudinally through an upper portion 88 of the front flange 84 and having an inner diameter 90. The upper front hole 86 and the upper rear hole 74 have respective centerlines aligned with an upper axis 92. The front flange 84 also includes a lower front hole 94 having an inner diameter 96, which extends longitudinally through a lower portion 98 of the front flange 84. and which is spaced vertically apart from the upper front hole 86. The lower front hole 94 and the lower rear hole 78 have respective centerlines aligned with a low er axis 100. In addition, the upper axis 92 is generally parallel to the lower axis 100.

[0044] Referring to Figure 8, the mounting bracket 58 also includes an upper sidew all 102 and a handle flange 104. The upper si de wall 102 projects laterally from an upper portion of the back panel 60. The handle flange 104 extends upwardly from a distal end of the upper sidew all 102 and is offset laterally from the back panel 60. Further, the handle flange 104 is spaced longitudinally between the front flange 84 and the upper flange 64. Referring to Figure 6, the handle flange 104 includes an inboard side 106 opposing an outboard side 108. Depicted in Figure 8, the handle flange 104 includes a spring tab 110, an upper spring hole 112, a lower spring slot 114, a stop tab 116, and an upper pivot hole 118. The spring tab 110 projects upwardly from a forward portion 120 of the handle flange 104 which is adjacent the front flange 84. The upper spring hole 112 extends laterally through the spring tab 110. Further, the lower spring slot 114 extends longitudinally from a rear side 122 of the handle flange 104. The stop tab 116 projects laterally from the handle flange 104 and is spaced vertically between the lower spring slot 114 and the upper sidewall 102. The stop tab 116 includes an upper hook stop 124 extending laterally along an upper side of the stop tab 116. The upper pivot hole 118 extendslaterally through the handle flange 104 and is spaced longitudinally between the upper spring hole 112 and the upper hook stop 124. The upper pivot hole 118 has an inner diameter 126 and a centerline defining an upper pivot axis 128. The mounting bracket 58 also includes a release tab 130 projecting laterally from the back panel 60 and which is spaced vertically between the upper rear hole 74 and the lower rear hole 78. The release tab 130 includes a surface defining a hook release 132 which faces the front flange 84.

[0045] Referring to Figures 5, 7, and 8, the mounting plate assembly 40 also includes an upper guide rod 134 and a lower guide rod 136, which are fixedly coupled to the mounting bracket 58. Depicted in Figure 8, the upper guide rod 134 has a generally cylindrical shape with an upper guide surface 138 extending circumferentially around the upper guide rod 134 between an upper forward end 140 and an opposing upper rearward end 142. The upper guide rod 134 has an outer diameter 144 less than the inner diameter 90 of the upper front hole 86 and less than the inner diameter 76 of the upper rear hole 74 in the mounting bracket 58. In addition, the lower guide rod 136 has a generally cylindrical shape with a lower guide surface 146 extending circumferentially around the lower guide rod 136 between a lower forward end 148 and an opposing lower rearward end 150. The lower guide rod 136 has an outer diameter 152 less than the inner diameter 96 of the lower front hole 94 and less than the inner diameter 80 of the lower rear hole 78 in the mounting bracket 58. Referring to Figure 7, the upper forward end 140 and the upper rearward end 142 of the upper guide rod 134 are inserted into the upper front hole 86 and the upper rear hole 74, respectively, in the mounting bracket 58 with a centerline of the upper guide rod 134 aligned with the upper axis 92.

[0046] Further, the lower forward end 148 and the lower rearward end 150 of the lower guide rod 136 are inserted into the lower front hole 94 and the lower rear hole 7 , respectively, in the mounting bracket 58 with a centerline of the lower guide rod 136 aligned with the lower axis 100. The upper and lower guide rods 134, 136 are fixedly coupled to the mounting bracket 58 by respective welds 154. mechanical fasteners, or the like, as is commonly known in the art.

[0047] Referring to Figures 4-9, the mounting plate assembly 40 also includes an upper pivot 156 which is fixedly coupled to the mounting bracket 58. Depicted in Figures 8 and 9, the upper pivot 156 has a generally cylindrical shape with a pivot wall 158 which extends circumferentially around the upper pivot 156, extends between a proximal end 160 and a distal end 162, and defines an upper pivot axis 164. In addition, the upper pivot 156 includes a pivot bore 166 having an inner diameter 168 extending axially therethrough between the proximalend 160 and the distal end 162. The pivot wall 158 includes a first collar 170 extending circumferentially around the upper pivot 156 and extending axially from the proximal end 160. The pivot wall 158 also includes a first sidewall 172, a channel wall 174, a second sidewall 176, a first rim 178, a third sidewall 180, and a second rim 182. The first sidewall 172 extends radially inward from a distal end of the first collar 170. The channel wall 174 extends axially away from an inner end of the first sidewall 172 towards the second sidewall 176. The second sidewall 176 extends radially outward from a distal end of the channel wall 174. Referring to Figures 6 and 9, the first rim 178 extends axially away from an outer end of the second sidewall 176. The third sidewall 180 extends radially outward from a distal end of the first rim 178. In addition, the second rim 182 extends axially away from an outer end of the third sidewall 180. The pivot wall 158 also includes a fourth sidewall 184, a third rim 186, a fifth sidewall 188, and a fourth rim 190. The fourth sidewall 184 extends radially outward from a distal end of the second rim 182. The third rim 186 extends in an axial direction from an outer end of the fourth sidewall 184. Further, the fifth sidewall 188 extends radially inward from a distal end of the third rim 186. The fourth rim 190 extends axially between an inner end of the fifth sidewall 188 and an outer edge of the distal end 162 of the upper pivot 156. As shown in Figure 9. the fourth rim 190 has an outer diameter 192. The third rim 186 has an outer diameter 194 greater than the outer diameter 192 of the fourth rim 190. In addition, the second rim 182 has an outer diameter 196 less than the outer diameter 194 of the third rim 186. Further, the first rim 178 has an outer diameter 198 less than the outer diameter 196 of the second rim 182 and greater than the inner diameter 126 of the upper pivot hole 118 in the mounting bracket 58. Also, the channel wall 174 has an outer diameter 200 less than the outer diameter 198 of the first rim 178 and less than the inner diameter 126 of the upper pivot hole 118 in the mounting bracket 58. Referring to Figure 6, the upper pivot 156 is assembled with the mounting bracket 58 such that the channel wall 174 extends through the upper pivot hole 1 18 and the handle flange 104 is spaced axially between the first collar 170 and the second sidewall 176. The first collar 170 is formed on the upper pivot 156 after the upper pivot 156 is assembled with the mounting bracket 58, as is commonly known in the art.

[0048] Depicted in Figures 7 and 8, the mounting plate assembly 40 also includes an upper cinch hook 202, which is pivotably coupled to the upper pivot 156 to move between a home position 204A (Figure 15) engaged with an adjacent one of the forward, middle, and rear apertures 46, 48, 50 on the carriage bracket 44 and a retracted position 204B (Figure 18) spaced apart from the forward, middle, and rear apertures 46, 48, 50. Referring to Figures 6 and 8, theupper cinch hook 202 has a generally J-shape and includes an inboard side 206 and an outboard side 208 extending between a forward side 210, a rearward side 212, a lower side 214, and an upper side 216. In addition, the upper cinch hook 202 includes an upper aperture 218 extending laterally therethrough near the forward side 210 which defines a pivot axis 220 for the upper cinch hook 202. Further, the upper aperture 218 has an inner diameter 222 larger than the outer diameter 196 of the second rim 182 and smaller than the outer diameter 194 of the third rim 186 of the upper pivot 156.

[0049] Referring to Figure 8, the upper cinch hook 202 also includes a spring boss 224, a hook opening 226, and a hook end 228. The spring boss 224 projects generally upwardly and forwardly from the forward side 210 of the upper cinch hook 202. In addition, the spring boss 224 includes a boss wall 234 generally facing towards the forward side 210. The hook opening 226 is a generally C-shaped slot in the upper cinch hook 202 extending between the hook end 228 and the lower side 214. Depicted in Figures 3 and 8, the hook opening 226 includes a forward cam surface 230 extending from the hook end 228 and which is configured to engage with an adjacent one of the forward, middle, and rear apertures 46, 48, 50 with a positive pressure angle. Referring to Figure 6, the upper cinch hook 202 is positioned axially along the upper pivot 156 with the second rim 182 extending through the upper aperture 218 and the outboard side 208 of the upper cinch hook 202 adjacent the fourth sidewall 184 of the upper pivot 156.

[0050] Referring to Figures 4-8, the mounting plate assembly 40 also includes an upper strength hook 236, which is pivotably coupled to the upper pivot 156 to move between a home position 237A (Figure 15) engaged with an adjacent one of the forward, middle, and rear apertures 46, 48, 50 on the carriage bracket 44 and a retracted position 237B (Figure 18) spaced apart from the forward, middle, and rear apertures 46, 48, 50. The upper strength hook 236 includes an inboard side 240 and an outboard side 242 extending between a forward side 244, a rearward side 246, a lower side 248. and an upper side 250. Depicted in Figures 6 and 8, the upper strength hook 236 includes an upper bore 252 extending laterally therethrough near the forward side 244. The upper bore 252 defines a pivot axis 254 for the upper strength hook 236. In addition, the upper bore 252 has an inner diameter 256 larger than the outer diameter 196 of the second rim 182 and smaller than the outer diameter 194 of the third rim 186 on the upper pivot 156. Referring to Figure 8. the upper strength hook 236 also includes a handle lever 258, a rear tab 260, a hook portion 262, and a stop nub 264. The handle lever 258 projects generallyupwardly from the upper strength hook 236. In addition, the handle lever 258 includes opposing forward and rearward lever walls 266, 268 extending from the forward side 244 and the upper side 250, respectively. The rear tab 260 projects rearwardly from the rearward side 246 and includes a lower surface defining a rear stop 270. The hook portion 262 projects downwardly from the lower side 248 of the upper strength hook 236 adjacent the rearward side 246. The hook portion 262 includes a hook tip 272 which extends between a first hook wall 274 and a second hook wall 276. The stop nub 264 projects laterally from the upper strength hook 236 adjacent the lower side 248 and includes a stop surface 278 extending along an upper side.

[0051] Referring to Figures 2-4. 6, and 15, the upper strength hook 236 is positioned axially along the upper pivot 156 with the second rim 182 extending through the upper bore 252, the outboard side 242 adjacent the inboard side 206 of the upper cinch hook 202, and the inboard side 240 adjacent the outboard side 108 of the mounting bracket 58. The rear stop 270 releasably engages with the upper hook stop 124 when the upper strength hook 236 is in the home position 237A (Figure 15). In addition, the first hook wall 274 has a negative pressure angle when engaged with the adjacent one of the forward, middle, and rear apertures 46, 48, 50 in the carriage bracket 44. Further, the stop surface 278 on the upper strength hook 236 releasably engages the low er side 214 of the upper cinch hook 202 when the upper strength hook 236 is in the home position 237 A.

[0052] Depicted in Figures 7 and 8, the mounting plate assembly 40 also includes an upper hook spring 280 operatively coupled between the mounting bracket 58 and the upper cinch hook 202. The upper hook spring 280 includes a spring coil 282 having a spring passageway 284 extending axially therethrough. In addition, the upper hook spring 280 includes an upper spring end 286 and a lower spring end 288 extending from the spring coil 282. Depicted in Figure 6, the upper hook spring 280 is positioned along the upper pivot 156 outboard of the third rim 186 with the fourth rim 190 extending through the spring passageway 284. Referring to Figure 4, the upper spring end 286 is frictionally engaged with the boss wall 234 on the upper cinch hook 202. In addition, the lower spring end 288 is inserted into the upper spring hole 112 in the mounting bracket 58. As viewed in Figure 3, the upper hook spring 280 applies a rearward-biasing force (arrow7290) on the upper cinch hook 202 to rotationally bias the upper cinch hook 202 in the rearward direction around the upper pivot 156 towards the home position 204A. The rearward-biasing force (arrow 290) by the upper hook spring 280 also rotationally biases the rear stop 270 on the upper strength hook 236 in the rearward direction towards theupper hook stop 124 when the lower side 214 of the upper cinch hook 202 is frictionally engaged with the stop surface 278 on the upper strength hook 236.

[0053] Referring to Figures 7, 8, and 16, the mounting plate assembly 40 also includes a fore- aft spring 294, which applies a rearward-biasing force (arrow 296) on the carriage assembly 42 to bias the carriage assembly 42 in the rearward direction (arrow 24B). In more detail, the fore- aft spring 294 is an extension spring having a spring coil 300 extending between an aft end 302 and afore end 304. The aft end 302 is inserted into the aft spring slot 82 in the mounting bracket 58. The fore end 304 is operatively coupled to the carriage assembly 42, as further described below.

[0054] Depicted in Figures 1, 3, and 7, the high latch 12 also includes a handle 306 which pivotably coupled to the upper pivot 156 and operatively coupled to the upper strength hook 236. The handle 306 is pivotable between an unactuated position 308A (Figure 3) and an actuated position 308B (Figure 18). Pivoting the handle 306 from the actuated position 308B to the unactuated position 308A causes the upper strength hook 236 to pivot from the retracted position 237B to the home position 237A with the rear stop 270 engaged with the upper hook stop 124 on the mounting bracket 58. The upper strength hook 236 can engage with the adjacent one of the forward, middle, and rear apertures 46. 48. 50 on the carriage bracket 44 when the upper strength hook 236 is in the home position 237A. Translation of the mounting plate assembly 40 relative to the carriage assembly 42 is prevented wftile the upper strength hook 236 and the upper cinch hook 202 are in the respective home positions 237 A, 204 A engaged with the carriage assembly 42. Referring to Figure 18, pivoting the handle 306 from the unactuated position 308A to the actuated position 308B causes the upper strength hook 236 and the upper cinch hook 202 to disengage from the carriage assembly 42 and causes the rear stop 270 to disengage from the upper hook stop 124. The mounting plate assembly 40 can be selectively translated relative to the carriage assembly 42 while the upper strength hook 236 and the upper cinch hook 202 are in a disengaged condition from the carriage assembly 42. The seat back 14 can be repositioned between the design position 34, the mid position 36, and the full recline position 38 while the high latch 12 is engaged with the striker 28 and the handle 306 is in the actuated position 308B. In addition, the high latch 12 can be decoupled from the striker 28 while the handle 306 is in the actuated position 308B. as further described below. The handle 306 is typically accessible near an upper portion 312 of the seat back 14. It will beappreciated that the location and configuration of the handle 306 can vary, as is commonly known in the art.

[0055] Referring to Figure 7, the exemplary handle 306 includes a handle body 314 and a handle mount 316 fixedly coupled to the handle body 314. The handle body 314 includes a grip portion 318 for actuating the handle 306. The handle body 314 also includes a support wall 320 projecting from the handle body 314. The support wall 320 includes a handle hole 322 extending laterally therethrough. In addition, the handle body 314 includes an outboard wall 324, a first handle tab 326, a second handle tab 328, and a handle slot 330. The first handle tab 326 and the second handle tab 328 project laterally from the outboard wall 324 with the handle slot 330 extending between the first and second handle tabs 326. 328. Referring to Figures 3 and 15, the handle slot 330 is sized and shaped to matingly engage with the handle lever 258 on the upper strength hook 236. In more detail, the handle lever 258 is inserted into the handle slot 330 such that the forward lever wall 266 is adjacent the first handle tab 326 and the rearward lever wall 268 is adjacent the second handle tab 328. Referring to Figures 6 and 7, the handle mount 316 has a generally cylindrical shape with a mount wall 332 extending circumferentially around the handle mount 316 and extending between an outboard end 334 and an inboard end 336. In addition, the handle mount 316 includes a bolt passage 338 having an inner diameter 340 extending laterally therethrough and defining a bolt passage axis 342. The handle 306 is assembled with the mounting plate assembly 40 with the outboard end 334 of the handle mount 316 abutting the proximal end 1 0 of the upper pivot 156 after the upper pivot 156 has been riveted to the mounting bracket 58. In addition, the bolt passage 338 in the handle 306 is aligned with the pivot bore 166 in the upper pivot 156 such that the bolt passage axis 342 is generally aligned with the upper pivot axis 164.

[0056] Depicted in Figures 3 and 7, the high latch 12 also includes a handle spring 344, which is operatively coupled between the handle 306 and the mounting bracket 58. The handle spring 344 applies a rearward-biasing force (arrow 346) to rotationally bias the handle 306 about the upper pivot 156 in the rearward direction towards the unactuated position 308A. The handle spring 344 is an extension spring having a spring coil 348 extending between an upper spring end 350 and a lower spring end 352. Referring to Figures 2 and 3, the upper spring end 350 of the handle spring 344 is inserted into the handle hole 322 in the handle 306. Next, the lower spring end 352 is inserted into the lower spring slot 114 in the mounting bracket 58.

[0057] Depicted in Figure 5. the handle 306 is pivotably coupled to the upper pivot 156. as is commonly known in the art. In one exemplary embodiment, the high latch 12 includes a bolt 354, an inboard washer 356, an outboard washer 358, and a nut 360. The bolt 354 includes a bolt shaft 362 which extends through a first washer bore 376 in the inboard washer 356, through the bolt passage 338 in the handle 306, through the pivot bore 166 in the upper pivot 156, through a second washer bore 380 in the outboard washer 358, and fastened to the nut 360. It will be appreciated that the handle 306 might be operatively coupled to the mounting bracket 58 using alternate methods as is commonly known in the art without altering the scope of the present invention. In addition, the bolt 354, the inboard and outboard washers 356, 358, and the nut 360 are omitted from the remaining Figures for simplicity.

[0058] Referring to Figures 7 and 12, the carriage bracket 44 has a generally L-shape with a carriage wall 384 extending between a carriage leg 386, a carriage side 388, a carriage front 390, and a carriage rear 392. The forward, middle, and rear apertures 46, 48, 50 are spaced apart along the carriage wall 384 in a longitudinal direction. It will be appreciated that the carriage wall 384 might include a plurality of apertures 46, 48, 50 and may include two or more apertures 46, 48, 50 without altering the scope of the present invention. Depicted in Figure 7, the forward aperture 46 includes a forward side 394 opposing a rearward side 396 and an inboard side 398 opposing an outboard side 400. The middle aperture 48 includes a forward side 402 opposing a rearward side 404 and an inboard side 406 opposing an outboard side 408. Further, the rear aperture 50 includes a forw ard side 410 opposing a rearward side 412 and an inboard side 414 opposing an outboard side 416. Referring to Figures 2, 3, 6, and 15, the forward, middle, and rear apertures 46, 48, 50 are sized and shaped so that the hook tip 272 of the upper strength hook 236 and the hook end 228 of the upper cinch hook 202 can be inserted into the adjacent one of the forward, middle, and rear apertures 46, 48, 50.

[0059] Depicted in Figure 12, the carriage leg 386 includes a fore sidewall 418, a fore slot 420, and a carriage bore 422. The fore sidewall 418 extends along a forward portion of the carriage leg 386. In addition, the fore slot 420 extends rearward from the fore sidewall 418. The carriage bore 422 extends laterally through a lower portion of the carriage leg 386 spaced apart from the fore slot 420. The carriage bore 422 has an inner diameter 424 and defines a lower pivot axis 426. Also shown in Figures 12 and 13. the carriage side 388 includes an attachment portion 428 extending along a lower edge.

[0060] Depicted in Figures 7, 12, and 13, the carriage assembly 42 also includes a trolley bracket 430 fixedly coupled to the carriage bracket 44. The trolley bracket 430 is a generally U-shaped bracket having a back wall 432 extending between a top wall 434, a bottom wall 436, a rear wall 438, and a front wall 440. The back wall 432 includes an inboard surface 442 opposing an outboard surface 444. Depicted in Figure 13, the attachment portion 428 of the carriage side 388 is fixedly coupled to the outboard surface 444 of the back wall 432 of the trolley bracket 430 by a weld 446 or other mechanical fastener, as is commonly known in the art. It will be appreciated that the carriage bracket 44 and the trolley bracket 430 might be formed as a single component without altering the scope of the present invention. Referring to Figure 12, the trolley bracket 430 also includes a pivot hole 448 having an inner diameter 450 extending laterally through the back wall 432. The pivot hole 448 has a longitudinal axis 452 which aligns with the lower pivot axis 426 in the carriage bore 422 when assembled as part of the carriage assembly 42. The trolley bracket 430 also includes a pin slot 454 extending laterally through the back wall 432 and spaced between the pivot hole 448 and the bottom wall 436. The pin slot 454 has a generally arcuate shape with a curved top slot wall 456 opposing a curved bottom slot wall 458 and a rear slot wall 460 generally opposing a front slot wall 462. The top slot wall 456 is spaced apart from the bottom slot wall 458 by a slot width 464. In addition, the trolley bracket 430 includes a striker tab 466 projecting rearward from the rear wall 438. The striker tab 466 includes a top bore 468 and a bottom bore 470 extending laterally through the striker tab 466 and spaced vertically apart.

[0061] Depicted in Figure 12, the trolley bracket 430 also includes an upper rear flange 472, a lower rear flange 474, an upper front flange 476, and a lower front flange 478. The upper rear flange 472 and the lower rear flange 474 project laterally from the rear wall 438 adjacent the top wall 434 and the bottom wall 436, respectively. The upper front flange 476 and the lower front flange 478 project laterally from the front wall 440 adjacent the top wall 434 and the bottom wall 436, respectively. Further, the trolley bracket 430 includes an upper rear bore 480, a lower rear bore 482, an upper front bore 484. and a lower front bore 486. The upper rear bore 480 and the upper front bore 484 extend longitudinally through the upper rear flange 472 and the upper front flange 476, respectively. The upper rear bore 480 and the upper front bore 484 are aligned to define a top axis 488. The upper rear bore 480 and the upper front bore 484 have an inner bore diameter 490 which is larger than the outer diameter 144 of the upper guide rod 134. The lower rear bore 482 and the lower front bore 486 extend longitudinally through the lower rear flange 474 and the lower front flange 478, respectively. The lower rear bore 482 andthe lower front bore 486 are aligned to define a bottom axis 492. In addition, the lower rear bore 482 and the lower front bore 486 have an inner bore diameter 494 which is larger than the outer diameter 152 of the lower guide rod 136. Referring to Figures 3 and 4, the top axis 488 and the bottom axis 492 of the trolley bracket 430 generally align with the upper axis 92 and the lower axis 100, respectively, of the mounting bracket 58. Depicted in Figure 12, the trolley bracket 430 also includes a spring bore 496 and a fore spring slot 498. The spring bore 496 extends laterally through the lower front flange 478 adjacent the bottom wall 436 and adjacent the back wall 432. The fore spring slot 498 extends generally vertically from the bottom wall 436 with the spring bore 496 spaced between the fore spring slot 498 and the back wall 432. Referring to Figure 5, the fore end 304 of the fore-aft spring 294 is inserted into the spring bore 496.

[0062] Depicted in Figure 12, the carriage assembly 42 also includes a plurality of bushings 500. Each bushing 500 is generally cylindrical in shape with a bushing wall 502 extending circumferentially around the bushing 500 and having a bushing outer diameter 504 less than the inner bore diameters 490, 494 in the trolley bracket 430. In addition, each bushing 500 includes a bushing passage 506 extending axially therethrough and having a bushing inner diameter 508 greater than the outer diameter 144, 152 of the upper and lower guide rods 134, 136. Referring to Figures 4, 5, and 13, the bushings 500 are inserted into the upper rear bore 480, the lower rear bore 482, the upper front bore 484, and the lower front bore 486, respectively, and fixedly coupled to the trolley bracket 430, as is commonly known in the art.

[0063] Depicted in Figure 12, the carriage assembly 42 also includes a striker bumper 510 configured to frictionally engage with the striker 28. The striker bumper 510 is a U-shaped piece which includes a bumper end wall 512, an outboard bumper wall 514, an inboard bumper wall 516, and a bumper channel 518. The outboard bumper wall 514 and the inboard bumper wall 516 project from the bumper end wall 512. The bumper channel 518 extends between the outboard and inboard bumper walls 514. 516. The bumper channel 518 is configured such that the striker tab 466 can be inserted into the bumper channel 518 during assembly. Referring to Figure 2, the striker bumper 510 is assembled with the striker tab 466 with the bumper end wall 512 facing rearward. The striker bumper 510 is fixedly coupled to the striker tab 466 by insertmolding, rivets, mechanical fasteners, or the like extending through the top bore 468 and the bottom bore 470. as is commonly known in the art. Depicted in Figure 16. the bumper end wall 512 frictionally engages with the striker 28 when the high latch 12 is latched to the striker 28.In addition, the striker bumper 510 disengages from the striker 28 when the high latch 12 is unlatched, as illustrated in Figure 24.

[0064] Depicted in Figures 7, 10 and 12, the carriage assembly 42 also includes a lower pivot 520, which is fixedly coupled to the trolley bracket 430 and the carriage bracket 44. Referring to Figures 10 and 12, the lower pivot 520 is generally cylindrically -shaped with a pivot sidewall 522 extending circumferentially around the lower pivot 520 defining a lower pivot axis 524 and extending between an outboard surface 526 and an opposing inboard surface 528. The lower pivot 520 includes a proximal collar 530, a spring shaft 532, a middle collar 534, a hook pivot 536, a carriage shoulder 538, a carriage shaft 540, and a distal collar 542 which are spaced axially along the lower pivot 520. The proximal collar 530 extends axially from an outer end of the inboard surface 528. The lower pivot 520 includes a first ledge 544 extending radially inward from an outboard end of the proximal collar 530 and terminating at an inboard end of the spring shaft 532. In addition, the lower pivot 520 includes a second ledge 546 extending radially outward from an outboard end of the spring shaft 532 and terminating at an inboard end of the middle collar 534. The lower pivot 520 also includes a third ledge 548 extending radially inward from an outboard end of the middle collar 534 and terminating at an inboard end of the hook pivot 536. The lower pivot 520 also includes a fourth ledge 550 extending radially inward from an outboard end of the hook pivot 536 and terminating at an inboard end of the carriage shoulder 538. The lower pivot 520 also includes a fifth ledge 552 extending radially inward from an outboard end of the carriage shoulder 538 and terminating at an inboard end of the carriage shaft 540. In addition, the lower pivot 520 includes a sixth ledge 554 extending radially outward from an outboard end of the carriage shaft 540 and terminating at an inboard end of the distal collar 542. Further, the outboard end of the distal collar 542 extends from the outer end of the outboard surface 526. The distal collar 542 has an outer diameter 556 larger than an outer diameter 558 of the carriage shaft 540 and larger than the inner diameter 424 of the carriage bore 422 in the carriage bracket 44. In addition, the outer diameter 558 of the carriage shaft 540 is smaller than the inner diameter 424 of the carriage bore 422. The carriage shoulder 538 has an outer diameter 560 larger than the outer diameter 558 of the carriage shaft 540. Further, the hook pivot 536 has an outer diameter 562 larger than the outer diameter 560 of the carriage shoulder 538. The middle collar 534 has an outer diameter 564 larger than the outer diameter 562 of the hook pivot 536. In addition, the spring shaft 532 has an outer diameter 566 which is smaller than the outer diameter 564 of the middle collar 534 and smaller than the inner diameter 450 of the pivot hole 448 in the trolley bracket 430. Theproximal collar 530 has an outer diameter 568 which is larger than the outer diameter 566 of the spring shaft 532 and larger than the inner diameter 450 of the pivot hole 448 in the trolley bracket 430. In addition, the proximal collar 530 and the distal collar 542 are formed on the lower pivot 520 after the lower pivot 520 is assembled with the trolley bracket 430 and the carriage bracket 44, as is commonly known in the art.

[0065] Depicted in Figures 7 and 16. the carriage assembly 42 also includes a lower strength hook 570 pivotably coupled to the lower pivot 520 to move between a latched position 572A (Figure 16) configured to engage with the striker 28 and an unlatched position 572B (Figure 24) retracted from the striker 28. In addition, the lower strength hook 570 is spring-biased towards the latched position 572A. Referring to Figures 12, 13, and 16, the lower strength hook 570 is generally J-shaped and includes a proximal surface 574, a distal surface 576, a hook peripheral surface 578, a hook slot 580, a pivot aperture 582, and a pin bore 584. The proximal surface 574 opposes the distal surface 576 and the hook peripheral surface 578 extends circumferentially around the lower strength hook 570 between the proximal and distal surfaces 574, 576. The hook slot 580 is a generally C-shaped slot in the lower strength hook 570 extending between a hook tip 586 and a top portion 588 of the low er strength hook 570. In addition, the hook slot 580 includes a strength cam surface 590 extending from the hook tip 586 along the hook slot 580, which is configured to frictionally engage with the striker 28 with a negative pressure angle. In addition, the lower strength hook 570 includes a rear cam surface 589 extending from the hook tip 586 along a rearward portion of the lower strength hook 570. The rear cam surface 589 is configured frictionally engage with the striker 28 and pivot the lower strength hook 570 towards the unlatched position 572B as the striker 28 approaches the hook tip 586. The lower strength hook 570 also includes a lower cam surface 592 extending along a lower portion of the hook peripheral surface 578. The pivot aperture 582 extends laterally through the low er strength hook 570 near the top portion 588 and defines a pivot axis 594 for the lower strength hook 570. The pivot aperture 582 has an inner diameter 596 larger than the outer diameter 562 of the hook pivot 536 and smaller than the outer diameter 564 of the middle collar 534 on the lower pivot 520. The pin bore 584 extends laterally through the lower strength hook 570 and has an inner diameter 598. The pin bore 584 is spaced generally between the pivot aperture 582 and the low er cam surface 592. Referring to Figure 13, the lower strength hook 570 is positioned axially along the lower pivot 520 with the hook pivot 536 extending through the pivot aperture 582 and the proximal surface 574 of the lower strength hook 570 adjacent the third ledge 548 on the lower pivot 520.

[0066] Depicted in Figures 4, 7, and 12, the carriage assembly 42 also includes a hook pin 600 fixedly coupled to the lower strength hook 570 and extending through the pin slot 454 in the trolley bracket 430. Referring to Figure 23, the hook pin 600 is transposed in a forward direction (arrow 601A) along the pin slot 454 by the hook release 132 as the seat back 14 is rotated forward (arrow 24A) past the design position 34. In addition, the lower strength hook 570 pivots from the latched position 572A (Figure 23) to the unlatched position 572B (Figure 24) in response to the hook release 132 transposing the hook pin 600 in the forward direction (arrow 601 A) along the pin slot 454. Referring to Figures 1 1 and 12, the hook pin 600 has a generally cylindrical shape and includes a tail end 602, a pin shaft 604, a pin collar 606, a hook shaft 608, a pin flange 610, and a head end 612 extending along a pin axis 614. The pin shaft 604 extends in an axial direction from the tail end 602. The hook pin 600 also includes a first side 616 extending radially outward from an outboard end of the pin shaft 604. In addition, the pin collar 606 extends axially from an outer end of the first side 616. The hook pin 600 also includes a second side 618 extending radially inward from an outboard end of the pin collar 606. The hook shaft 608 extends in an axial direction from an inner end of the second side 618. The hook pin 600 also includes a third side 620 extending radially outward from an outboard end of the hook shaft 608. The pin flange 610 extends axially between an outer end of the third side 620 and the head end 612. The pin shaft 604 has an outer diameter 622 smaller than the slot width 464 of the pin slot 454. The pin collar 606 has an outer diameter 624 larger than the outer diameter 622 of the pin shaft 604 and larger than the inner diameter 598 of the pin bore 584 in the lower strength hook 570. In addition, the hook shaft 608 has an outer diameter 626 smaller than the inner diameter 598 of the pin bore 584 and smaller than the outer diameter 624 of the pin collar 606. Further, the pin flange 610 has an outer diameter 628 larger than the outer diameter 626 of the hook shaft 608 and larger than the inner diameter 598 of the pin bore 584. Referring to Figure 13, the hook pin 600 is assembled with the lower strength hook 570 with the hook shaft 608 extending laterally through the pin bore 584. In addition, the second side 618 and the third side 620 are fictionally engaged with the proximal surface 574 and the distal surface 576, respectively, of the lower strength hook 570. It will be appreciated that pin flange 610 is optionally formed on the hook pin 600 after the hook pin 600 is assembled with the lower strength hook 570.

[0067] Referring to Figures 7 and 16, the carriage assembly 42 also includes a lower cinch hook 630 pivotably coupled to the lower pivot 520 to move between a latched position 631 A (Figure 16) configured to engage with the striker 28 and an unlatched position 63 IB (Figure24) retracted from the striker 28. Referring to Figures 12, 13, and 16, the lower cinch hook 630 is generally J-shaped and includes a proximal surface 632, a distal surface 634, a hook peripheral surface 636, a hook slot 638, a hook tab 640, a center passage 642, a spring tab 644, and an upper spring slot 646. The proximal surface 632 opposes the distal surface 634 and the hook peripheral surface 636 extends circumferentially around the lower cinch hook 630 between the proximal and distal surfaces 632, 634. The hook slot 638 is a generally C-shaped slot in the lower cinch hook 630 and extends between a hook end 648 and a top portion 650 of the lower cinch hook 630. In addition, the hook slot 638 includes a cinch cam surface 652 which extends from the hook end 648 along the hook slot 638. The cinch cam surface 652 is configured to frictionally engage with the striker 28 with a positive pressure angle. In addition, the lower cinch hook 630 includes a rearward cam surface 653 extending from the hook end 648 along a rearward portion of the lower cinch hook 630. The rearward cam surface 653 is configured to frictionally engage with the striker 28 and pivot the lower cinch hook 630 towards the unlatched position 63 IB as the striker 28 approaches the hook end 648. Further, the lower cinch hook 630 includes a backside portion 654 extending from the top portion 650 along the hook peripheral surface 636 which opposes the hook slot 638. The hook tab 640 projects laterally away from the proximal surface 632 along the backside portion 654 of the lower cinch hook 630. The hook tab 640 includes a lever surface 656 facing toward the hook slot 638. The center passage 642 extends laterally through the lower cinch hook 630 near the top portion 650 and defines a pivot axis 658 for the lower cinch hook 630. The center passage 642 has an inner diameter 660 larger than the outer diameter 560 of the carriage shoulder 538 and smaller than the outer diameter 562 of the hook pivot 536 on the lower pivot 520. The spring tab 644 proj ects from the backside portion 654 of the lower cinch hook 630. The spring tab 644 includes the upper spring slot 646 along an upper side 662 of the spring tab 644.

[0068] Referring to Figure 13, the lower cinch hook 630 is positioned axially along the lower pivot 520 with the carriage shoulder 538 extending through the center passage 642 and with the distal surface 634 of the lower cinch hook 630 adjacent the carriage leg 386 on the carriage bracket 44. In addition, the proximal surface 632 of the lower cinch hook 630 is adjacent the fourth ledge 550 on the lower pivot 520 and adjacent the distal surface 576 of the lower strength hook 570. Referring to Figure 16, the lever surface 656 on the lower cinch hook 630 is spaced apart from the lower cam surface 592 on the lower strength hook 570 when the lower cinch hook 630 and the lower strength hook 570 are engaged with the striker 28. Depicted in Figure 24, the lower cam surface 592 on the lower strength hook 570 engages with the lever surface656 on the lower cinch hook 630 as the hook release 132 transposes the hook pin 600 in a forward direction (arrow 601 A) along the pin slot 454. The lower cam surface 592 causes the lower cinch hook 630 to rotate with the lower strength hook 570 in a clockwise direction (arrow 664A), which allows the striker 28 to bypass the hook tip 586.

[0069] Depicted in Figures 12-14 and 16, the carriage assembly 42 also includes a lower hook spring 666 operatively coupled between the camage bracket 44 and the hook pin 600. As viewed in Figure 16, the lower hook spring 666 applies an upward-biasing force (arrow 668) on the lower strength hook 570 to rotationally bias the lower strength hook 570 in a counterclockwise direction (arrow 664B) about the lower pivot 520 and towards the latched position 572A. The lower hook spring 666 includes an upper spring end 670 and a lower spring end 672 extending from a spring coil 674. In addition, the spring coil 674 includes a spring aperture 676 extending axially therethrough. The spring aperture 676 has an inner diameter 678 larger than the outer diameter 566 of the spring shaft 532 and smaller than the outer diameter 564 of the middle collar 534 on the lower pivot 520. The spring coil 674 is positioned axially along the lower pivot 520 between the trolley bracket 430 and the middle collar 534 with the spring shaft 532 extending axially through the spring aperture 676. The upper spring end 670 is inserted into the fore slot 420 in the carriage bracket 44. Further, the lower spring end 672 is operatively coupled to the pin shaft 604 on the hook pin 600.

[0070] Referring to Figures 12, 14, and 16, the carriage assembly 42 also includes a lower cinch spring 680, which is operatively coupled between the lower cinch hook 630 and the trolley bracket 430. Depicted in Figure 16, the lower cinch spring 680 applies a downwardbiasing force (arrow 682) on the lower cinch hook 630 to rotationally bias the lower cinch hook 630 in the counterclockwise direction (arrow- 664B) about the lower pivot 520 towards the latched position 631 A. The lower cinch spring 680 is an extension spring having an upper spring end 684 and a low er spring end 686 extending from a spring coil 688. The upper spring end 684 is inserted into the upper spring slot 646 in the lower cinch hook 630. In addition, the lo er spring end 686 is inserted into the fore spring slot 498 in the trolley bracket 430.

[0071] Referring to Figure 1, the seat assembly 10 can be repositioned upon demand by the occupant between generally upright positions including the design position 34, the midposition 36, and the full recline position 38 by adjusting the high latch 12 while the carriage assembly 42 is latched to the striker 28. In one embodiment, the high latch 12 is configured to allow the inclination angle 39 of the seat back 14 to be adjusted about 6.5 degrees of recline,or a distance of about 44 mm, between the design position 34 and the full recline position 38. It will be appreciated that the high latch 12 may be configured to allow more or less than 6.5 degrees of recline without altering the scope of the present invention. In addition, the seat assembly 10 can be repositioned upon demand by the occupant from any one of the upright positions to the fold flat position 26 when the high latch 12 is decoupled from the striker 28. Further, the seat assembly 10 can be repositioned upon demand by the occupant from the fold flat position 26 back to the design position 34.

[0072] Referring to Figure 17, the seat back 14 is initially in the design position 34 with the high latch 12 latched to the striker 28. The mounting bracket 58 is fixedly coupled to the seat back 14. The handle 306 is unactuated and under a spring-loaded condition due to the handle spring 344 which biases the handle 306 towards the unactuated position 308A. The handle spring 344 also biases the upper strength hook 236 towards the home position 204A with the rear stop 270 frictionally engaging the upper hook stop 124 on the mounting bracket 58. In addition, the upper cinch hook 202 and the upper strength hook 236 are in the respective home positions 204A, 237A and in an engaged condition with the forw ard aperture 46 on the carriage assembly 42. The upper cinch hook 202 is under a spring-loaded condition due to the upper hook spring 280, which biases the upper cinch hook 202 tow ards the home position 204A w ith the forward cam surface 230 of the upper cinch hook 202 engaged with the forward side 394 of the forward aperture 46. The carriage assembly 42 is slidably coupled to the upper and lower guide rods 134, 136, which are fixedly coupled to the mounting bracket 58. In addition, the carriage assembly 42 is under a spring-loaded condition due to the fore-aft spring 294, which biases the carriage assembly 42 along the upper and lower guide rods 134, 136 in the rearward direction (arrow 24B). The carriage assembly 42 is spaced apart from the lower rear flange 474 on the mounting bracket 58 by a first distance 690. The lower cinch hook 630 and the lower strength hook 570 are in the respective latched positions 631 A, 572A and coupled with the striker 28 under a spring-loaded condition due to the lower cinch spring 680 and the lower hook spring 666. respectively. Further, the hook pin 600 is spaced apart from the hook release 132 on the mounting bracket 58. Forward rotation of the seat back 14 is restricted by the high latch 12 since the lower cinch hook 630 and the lower strength hook 570 are coupled to the striker 28 in combination with the upper cinch hook 202 and the upper strength hook 236 being coupled to the carriage assembly 42.

[0073] Referring to Figure 18, to move the seat back 14 from the design position 34 to the midposition 36, the occupant actuates the handle 306 to the actuated position 308B, which causes the handle 306 to pivot about the upper pivot 156 in a counterclockwise direction (arrow 694 A). The rotation of the handle 306 to the actuated position 308B causes the upper strength hook 236 to rotate upward (arrow 694A) about the upper pivot 156 to the retracted position 237B, which decouples the upper strength hook 236 from the carriage assembly 42. As the upper strength hook 236 rotates upward (arrow 694A). the stop surface 278 on the upper strength hook 236 engages with the lower side 214 of the upper cinch hook 202 and causes the upper cinch hook 202 to rotate upward (arrow 694A) about the upper pivot 156 to the retracted position 204B decoupled from the carriage assembly 42. Referring to Figures 18 and 19, the carriage assembly 42 is allowed to freely slide along the upper and lower guide rods 134, 136 while the upper strength hook 236 and the upper cinch hook 202 are in the respective retracted positions 237B, 204B with the lower strength hook 570 and the lower cinch hook 630 coupled to the striker 28. The seat back 14 is allowed to recline due to the upper strength hook 236 and the upper cinch hook 202 being in the retracted positions 237B, 204B. Next, the occupant applies rearward loading (arrow 696 in Figure 1) on the seat back 14 while the handle 306 is actuated with the upper cinch hook 202 and the upper strength hook 236 in the retracted positions 204B, 237B. The occupant may apply rearward loading (arrow 696) onto the seat back 14 using the occupant's torso or hand, as non-limiting examples. The rearward loading (arrow 696) overcomes the forward-biasing force (arrow 22) in the forward direction (arrow 24 A) of the optional seat back spring 20 and rotates the seat back 14 rearwards (arrow 24B) about the free pivots 18. In addition, the rearward loading (arrow 696) causes the mounting plate assembly 40 to be repositioned rearward (arrow' 24B) relative to the carriage assembly 42, until the carriage assembly 42 is spaced apart from the lower rear flange 474 a second distance 700 greater than the first distance 690.

[0074] Next in Figure 20, the occupant releases the handle 306 when the seat back 14 is in the mid-position 36. In response, the handle spring 344 causes the handle 306 to rotate clockwise (arrow 694B) about the upper pivot 156 to the unactuated position 308A, which causes the upper strength hook 236 to rotate downward to the home position 237A (arrow 694B) with the rear stop 270 engaged with the upper hook stop 124. Next, the upper hook spring 280 causes the upper cinch hook 202 to rotate downward (arrow 694B) about the upper pivot 156 to the home position 204A with the forward cam surface 230 of the upper cinch hook 202 engaged with the forward side 402 of the middle aperture 48. Further, the hook end 228 of the upperstrength hook 236 and the hook tip 272 of the upper cinch hook 202 are inserted into the middle aperture 48 and engaged with middle aperture 48. causing the mounting plate assembly 40 to engage with the carriage assembly 42 and lock the seat back 14 in mid-position 36. The seat back 14 is retained in the mid-position 36 until the occupant actuates the handle 306.

[0075] Referring to Figures 20 and 21, to move the seat back 14 from the mid-position 36 to the full recline position 38, the occupant actuates the handle 306. causing the handle 306 to pivot counterclockwise (arrow 694A) about the upper pivot 156. The rotation of the handle 306 to the actuated position 308B causes the upper strength hook 236 to rotate upward (arrow 694A) about the upper pivot 156 to the retracted position 237B which decouples the upper strength hook 236 from the carriage assembly 42. As the upper strength hook 236 rotates upward (arrow 694A), the stop surface 278 on the upper strength hook 236 engages with the lower side 214 of the upper cinch hook 202 and causes the upper cinch hook 202 to rotate upward (arrow 694A) about the upper pivot 156 to the retracted position 204B decoupled from the carriage assembly 42. Next, the occupant applies rearward loading (arrow 696 in Figure 1) on the seat back 14 while the handle 306 is actuated with the upper cinch hook 202 and the upper strength hook 236 in the respective retracted positions 204B, 237B. The rearward loading (arrow 696) causes the mounting plate assembly 40 to be repositioned rearward (arrow724B) relative to the carriage assembly 42, until the carriage assembly 42 is spaced apart from the lower rear flange 474 a third distance 702 greater than the second distance 700. Next, the occupant releases the handle 306 when the seat back 14 is in the full recline position 38. In response, the handle spring 344 causes the handle 306 to rotate clockwise (arrow 694B) about the upper pivot 156 to the unactuated position 308 A, causing the upper strength hook 236 to rotate downward (arrow 694B) about the upper pivot 156 to the home position 237A with the rear stop 270 engaged with the upper hook stop 124. Next, the upper hook spring 280 rotates the upper cinch hook 202 downward (arrow 694B) about the upper pivot 156 to the home position 204A with the forward cam surface 230 of the upper cinch hook 202 engaged with the forward side 410 of the rear aperture 50. Next, the hook tip 272 of the upper strength hook 236 and the hook end 228 of the upper cinch hook 202 are inserted into the rear aperture 50 and engaged with the rear aperture 50, which causes the mounting plate assembly 40 to engage with the carriage assembly 42. The seat back 14 is retained in the full recline position 38 until the occupant actuates the handle 306.

[0076] Referring to Figure 22, to return the seat back 14 to the design position 34 from the full recline position 38, the occupant actuates the handle 306 to the actuated position 308B, which causes the upper strength hook 236 and the upper cinch hook 202 to rotate upward (arrow 694A) to the respective retracted positions 237B, 204B decoupled from the carriage assembly 42, as shown in Figure 21. Next in Figure 21 , the occupant pivots the seat back 14 in the forward direction (arrow 24A) towards the design position 34 while the handle 306 is actuated. Next, the occupant releases the handle 306 when the seat back 14 is in the design position 34. In response, the handle spring 344 causes the handle 306 to rotate clockwise (arow 694B) about the upper pivot 156 to the unactuated position 308A, as shown in Figure 17. In addition, the upper strength hook 236 rotates downw ard (arrow 694B) about the upper pivot 156 to the home position 237A with the rear stop 270 engaged with the upper hook stop 124. Next, the upper hook spring 280 rotates the upper cinch hook 202 downward (arrow 694B) about the upper pivot 156 to the home position 204A with the forw ard cam surface 230 of the upper cinch hook 202 engaged with the forw ard side 394 of the forward aperture 46. Next, the hook tip 272 of the upper strength hook 236 and the hook end 228 of the upper cinch hook 202 are inserted into the forward aperture 46 and engaged with the forward aperture 46, causing the mounting plate assembly 40 to engage with the carriage assembly 42. The seat back 14 is retained in the design position 34 until the occupant actuates the handle 306.

[0077] Referring to Figures 17 and 18, to move the seat back 14 from one of the upright positions (i.e., the design position 34, the mid-position 36, and the full recline position 38) to the fold flat position 26, the occupant actuates the handle 306 to the actuated position 308B (arrow 694A) which causes the upper strength hook 236 and the upper cinch hook 202 to rotate upward (arrow 694A) about the upper pivot 156 to the respective retracted positions 237B, 204B decoupled from the carriage assembly 42. Next in Figure 18, the occupant pivots the seat back 14 in the forward direction (arrow 24A) past the design position 34 while the handle 306 is actuated. The forw ard rotation (arrow' 24A) of the seat back 14 causes the mounting plate assembly 40 to be transposed forward (arrow 24A) relative to the carriage assembly 42. until the camage assembly 42 is spaced apart from the lower rear flange 474 a fourth distance 704 less than the first distance 690 and the hook pin 600 engages with the hook release 132 on the mounting bracket 58. Referring to Figures 23 and 24, additional forward rotation of the seat back 14 (arrow 24A) causes the mounting plate assembly 40 to be transposed further forward (arrow 24A) relative to the carriage assembly 42, until the carriage assembly 42 is spaced apart from the lower rear flange 474 a fifth distance 706 less than the fourth distance 704. Theadditional forw ard movement (arrow 24A) of the mounting plate assembly 40 relative to the carriage assembly 42 causes the hook pin 600 to be transposed forward along the pin slot 454 (arrow 601 A) towards the front slot wall 462. The movement of the hook pin 600 along the pin slot 454 towards the front slot wall 462 causes the lower strength hook 570 to pivot downward (arrow 664A) about the lower pivot 520 until the lower cam surface 592 on the low er strength hook 570 engages with the hook tab 640 on the lower cinch hook 630. Referring to Figure 24, additional forward rotation (arrow 24A) of the seat back 14 after the lower cam surface 592 engages the hook tab 640 causes the lower cinch hook 630 to rotate downward (arrow7664A) with the lower strength hook 570 to the respective unlatched positions 631B, 572B, which allows the striker 28 to exit the hook slots 580, 638.

[0078] Referring to Figures 24 and 25, after the striker 28 disengages from the low er strength hook 570 and the low7er cinch hook 630, the lower cinch spring 680 and the low7er hook spring 666 cause the lower cinch hook 630 and the lower strength hook 570, respectively, to rotate upward (arrow 664B) about the lower pivot 520 towards the respective latched positions 631 A, 572A. In addition, the hook pin 600 is transposed rearward along the pin slot 454 (arrow7601B) as the lower strength hook 570 rotates upward (arrow7664B). The high latch 12 positions the lower strength hook 570 and the lower cinch hook 630 in such a w ay that the lower strength hook 570 and the low er cinch hook 630 will cam / ramp off the striker 28 allowing the high latch 12 to re-engage with the striker 28 when returning from the fold flat position 26. Next, the occupant releases the handle 306 after the striker 28 has disengaged from the high latch 12. After the occupant pivots the seat back 14 in the forward direction (arrow 24A) past vertical, gravity rotates the seat back 14 toward the fold flat position 26. The seat back 14 rotates forward (arrow 24 A) until the seat back 14 overlies the seat cushion 16. After the occupant releases the handle 306, the handle spring 344 rotates the handle 306 about the upper pivot 156 in the clockwise direction (arrow 694B) towards the unactuated position 308A, causing the upper strength hook 236 to rotate downward (arrow 694B) towards the home position 237A. Next, the upper hook spring 280 rotates the upper cinch hook 202 about the upper pivot 156 downward (arrow 694B) towards the home position 204A with the forward cam surface 230 of the upper cinch hook 202 engaged w ith the forward side 394 of the forward aperture 46. Next, the hook tip 272 of the upper strength hook 236 and the hook end 228 of the upper cinch hook 202 engage with the forward aperture 46, causing the mounting plate assembly 40 to engage with the carriage assembly 42. The seat back 14 is retained in the fold flat position 26 until the occupant rotates the seat back 14 towards the design position 34.

[0079] Referring to Figure 25, to return the seat back 14 to the design position 34 from the fold flat position 26, the occupant rotates the seat back 14 rearwards (arrow 24B) about the free pivots 18. As the high latch 12 moves rearward towards the striker 28, the striker 28 engages the rear cam surface 589 on the lower strength hook 570 and / or the rearward cam surface 653 on the lower cinch hook 630. As the high latch 12 moves further rearward, the striker 28 rides on the rear cam surface 589 and the rearward cam surface 653, causing the lower strength hook 570 and the lower cinch hook 630 to rotate downward (arrow 664 A) about the lower pivot 520. The lower cam surface 592 on the lower strength hook 570 optionally engages with the lever surface 656 on the lower cinch hook 630 as the lower strength hook 570 rotates downward (arrow 664A) about the lower pivot 520. After the low er strength hook 570 engages the lower cinch hook 630, the lower cinch hook 630 rotates downward (arrow 664A) with the lower strength hook 570 and ensures that both the lower cinch hook 630 and the lower strength hook 570 open enough concurrently to allow the striker 28 to enter the hook slots 580, 638, as depicted in Figure 24. Referring to Figure 24, after the striker 28 enters the hook slots 580, 638 in the lower strength hook 570 and the lower cinch hook 630, the lower cinch spring 680 and the lower hook spring 666 cause the lower cinch hook 630 and the lower strength hook 570, respectively, to rotate upward (arrow 664B) about the lower pivot 520 towards the respective latched positions 631 A, 572A and couples the high latch 12 to the striker 28 with the seat back 14 in the design position 34 (Figure 17).

[0080] A second embodiment of the high latch 12' is shown in Figures 26-31, where like primed reference numerals represent similar elements as those described above. The second embodiment shown in Figures 26-31 depicts a power mechanism 708 fixedly coupled to the mounting bracket 58' in place of the upper cinch hook 202, the upper strength hook 236, the handle 306, the upper pivot 156, the handle spring 344, and the upper hook spring 280 in the prior high latch 12. Only significant differences between the tw o embodiments are reflected in the Figures and the description below. Referring to Figure 1, the first embodiment of the high latch 12 is configured to allow manual adjustment of the seat back 14 between the fold flat position 26, the design position 34. the mid-position 36. and the full recline position 38. In contrast, the high latch 12' of the second embodiment includes a plurality of intermediate positions between the design position 34' and the full recline position 38'. In addition, the high latch 12' includes an unlatched position 710 with the seat back 14' angled forward of the design position 34' and the high latch 12' decoupled from the striker 28'.

[0081] The high latch 12' is shown in the design position 34' in Figures 26 and 27. The high latch 12' includes a mounting plate assembly 40'. a carriage assembly 42', and the power mechanism 708. The mounting plate assembly 40' includes a mounting bracket 58' having a handle flange 104' and a hook release 132'. In addition, the mounting plate assembly 40' includes upper and lower guide rods 134', 136' fixedly coupled to the mounting bracket 58'. The carriage assembly 42' includes a carriage bracket 44' fixedly coupled to a trolley bracket 430', a lower pivot 520' fixedly coupled to the trolley bracket 430' and the carriage bracket 44', a lower cinch hook 630' and a lower strength hook 570' pivotably coupled to the lower pivot 520', a lower cinch spring 680' operatively coupled between the lower cinch hook 630' and the trolley bracket 430', a lower hook spring 666' operatively coupled between the carriage bracket 44' and the lower strength hook 570', and a fore-aft spring 294' operatively coupled between the trolley bracket 430' and the mounting bracket 58'. Further, the camage assembly 42' includes a hook pin 600' fixedly coupled to the lower strength hook 570' and extending through a pin slot 454' in the trolley bracket 430'. In addition, the carriage assembly 42' includes a striker bumper 510' fixedly coupled to the trolley bracket 430'.

[0082] Depicted in Figures 26 and 27, the power mechanism 708 includes an electric motor 712, a drive shaft 714, a drive gear 716, a driven gear 718, a driven shaft 720, and a lead screw 722. The electric motor 712 is fixedly coupled to the mounting bracket 58' and operatively coupled to the drive shaft 714. The drive gear 716 is fixedly coupled to the drive shaft 714. The electric motor 712 is configured to selectively rotate the drive shaft 714 and the drive gear 716 in a first rotational direction (arrow 724A) and a second rotational direction (arrow 724B) opposing the first rotational direction (arrow 724A), as is commonly known in the art. The driven gear 718 is meshingly engaged with the drive gear 716 and fixedly coupled to a proximal end 726 of the lead screw 722. The lead screw 722 includes a shaft portion 728 adjacent the proximal end 726 and a threaded portion 730 extending longitudinally between the shaft portion 728 and a distal end 732 of the lead screw 722. The driven gear 718 and the lead screw 722 rotate about a screw rotational axis 734 in a forward rotational direction (arrow 736A) and an opposing rearward rotational direction (arrow 736B) in response to the drive gear 716 rotating in the first rotational direction (arrow 724A) and the second rotational direction (arrow 724B), respectively.

[0083] Depicted in Figure 27, the power mechanism 708 also includes an end block 738 fixedly coupled to the handle flange 104' on the mounting bracket 58'. The end block 738 rotationallysupports the lead screw 722. The end block 738 includes a shaft passageway 740 extending therethrough and having a longitudinal axis aligned with the screw rotational axis 734. The shaft passageway 740 has an inner diameter larger than the outer diameter of the shaft portion 728. In addition, the end block 738 includes a bearing recess 742 having a cylindrical shape and a longitudinal axis aligned with the longitudinal axis of the shaft passageway 740. The end block 738 also includes a bolt hole 744 extending laterally therethrough and configured to align with the upper pivot hole 118' in the mounting bracket 58' after the end block 738 is attached to the mounting bracket 58'.

[0084] The power mechanism 708 also includes a front collar 746, a rear collar 748, and a bearing 750 configured to rotationally support the shaft portion 728 of the lead screw 722. The front and rear collars 746, 748 have a cylindrical shape and include the respective first and second shaft apertures 752, 754 extending axially therethrough configured to matingly engage with an outer circumferential surface of the shaft portion 728 of the lead screw 722. The front collar 746 is fixedly coupled to a proximal side of the end block 738 with the centerline of the first shaft aperture 752 aligned with the screw rotational axis 734. In addition, the rear collar 748 is fixedly coupled to a distal side of the end block 738 with the centerline of the second shaft aperture 754 aligned with the screw rotational axis 734. The bearing 750 is inserted into the bearing recess 742 in the end block 738. In more detail, the bearing 750 is cylindrically- shaped with a bearing sidewall 756 extending circumferentially around the bearing 750 and configured to matingly engage with the bearing recess 742 in the end block 738. The bearing 750 also includes a bearing aperture 758 extending axially therethrough and configured to matingly engage with the outer circumferential surface of the shaft portion 728 of the lead screw 722.

[0085] Referring to Figure 27, the power mechanism 708 also includes an adapter block 760, first and second studs 762, 764, a threaded nut 766, and a nut bracket 768. The adapter block 760 is fixedly coupled to the carriage bracket 44' by the first and second studs 762. 764 and supports the threaded nut 766 in meshing engagement with the threaded portion 730 of the lead screw 722. In more detail, the adapter block 760 has a generally rectangular shape with a channel 770 extending laterally therethrough and including opposing first and second channel walls 772, 774 extending from a channel base 776. In addition, the adapter block 760 includes an adapter bore 778 extending longitudinally therethrough and extending through the channel 770. The adapter bore 778 has an inner diameter larger than the outer diameter of the lead screw722. Further, the adapter block 760 includes spaced apart first and second threaded holes 780, 782 extending upward from a lower end of the adapter block 760. The carriage wall 384' of the carriage bracket 44' includes first and second clearance holes 784, 786 extending vertically through the carriage wall 384' and configured to align with the first and second threaded holes 780, 782 on the adapter block 760. The first and second studs 762, 764 have respective first and second threaded ends 788, 790 configured to meshingly engage with the first and second threaded holes 780, 782. respectively. The first and second threaded ends 788, 790 of the first and second studs 762, 764 are inserted through the respective first and second clearance holes 784, 786 in the carriage wall 384' of the carriage bracket 44' and meshingly engaged with the respective first and second threaded holes 780, 782 in the adapter block 760, fixedly coupling the adapter block 760 to the carriage bracket 44'. The threaded nut 766 has a generally cuboidshape with a threaded passage 792 extending longitudinally therethrough configured to meshingly engage with the threaded portion 730 on the lead screw 722. The nut bracket 768 is a generally U-shaped bracket and including opposing first and second bracket walls 794, 796 projecting from a bracket base 798. In addition, the nut bracket 768 includes a clearance bore 800 extending longitudinally through the first and second bracket walls 794, 796 and having an inner diameter larger than the outer diameter of the lead screw 722. The threaded nut 766 is inserted into the nut bracket 768 between the first and second bracket walls 794, 796 with the longitudinal axis of the threaded passage 792 aligned with the longitudinal axis of the clearance bore 800. Next, the assembly of the threaded nut 766 and the nut bracket 768 is inserted into the channel 770 in the adapter block 760 such that the longitudinal axis of the adapter bore 778 in the adapter block 760 generally aligns with the longitudinal axis of the threaded passage 792 in the threaded nut 766.

[0086] Referring to Figures 1, 26, and 27, the carriage assembly 42' is coupled to the striker 28' and slidably coupled to the mounting plate assembly 40'. In addition, the mounting plate assembly 40' is fixedly coupled to the seat back 14'. The electric motor 712 is electrically connected by an electrical cable 801 to an input module 802 located on or near the seat assembly 10. as is commonly known in the art. In one exemplary embodiment, the input module 802 includes a first switch 804 and a second switch 806 configured to provide power to the electric motor 712 causing the electric motor 712 to rotate the drive shaft 714 in the first rotational direction (arrow 724A) and the second rotational direction (arrow- 724B), respectively.

[0087] Referring to Figure 27, the seat back 14' is initially in the design position 34' with the high latch 12' latched to the striker 28' and the carriage assembly 42' spaced apart from the lower rear flange 474' by a first distance 690'. Forward rotation (arrow 24A') of the seat back 14' is restricted by the high latch 12' since the lower cinch hook 630' and the lower strength hook 570' are coupled to the striker 28'. In addition, rearw ard rotation (arrow 24B') of the seat back 14' is restricted while the electric motor 712 is unpowered since the lead screw 722 engaged with the threaded nut 766 maintains the relative position between the mounting plate assembly 40' and the carriage assembly 42'.

[0088] Referring to Figures 27- 29. to move the seat back 14' from the design position 34' towards the full recline position 38', the occupant actuates the second switch 806 which causes the electric motor 712 to rotate the drive shaft 714 and the drive gear 716 in the second rotational direction (arrow 724B). The driven gear 718 and the lead screw 722 are rotated in the rearward rotational direction (arrow 736B) in response to the drive gear 716 rotating in the second rotational direction (arrow 724B). The mounting plate assembly 40' is transposed rearward (arrow 24B') relative to the carriage assembly 42' since the carriage assembly 42' is coupled to the striker 28' and slidably coupled to the mounting plate assembly 40'. Figure 28 shows the mounting plate assembly 40' translated rearward (arrow 24B') relative to the carriage assembly 42' with the carriage assembly 42' spaced apart from the lower rear flange 474' a second distance 700' greater than the first distance 690' with the seat back 14' in a mid-position 36', which generally corresponds to the mid position 36 of the seat back 14 in the first embodiment. To increase the inclination angle 39' to the full recline position 38' the occupant actuates the second switch 806 again, which causes the mounting plate assembly 40' to be translated further rearward (arrow 24B') relative to the carriage assembly 42' to the full recline position 38' depicted in Figure 29. Figure 29 shows the mounting plate assembly 40' translated rearward (arrow 24B') relative to the carriage assembly 42' with the carriage assembly 42' spaced apart from the lower rear flange 474' a third distance 702' greater than the second distance 700' with the seat back 14' in a full recline position 38’, which generally corresponds to the full recline position 38 of the seat back 14 in the first embodiment.

[0089] Referring to Figure 29, to return the seat back 14' to the design position 34' from the full recline position 38', the occupant actuates the first switch 804 which causes the electric motor 712 to rotate the drive shaft 714 and the drive gear 716 in the first rotational direction (arrow 724A). The driven gear 718 and the lead screw 722 are rotated in the forward rotationaldirection (arrow 736A) in response to the drive gear 716 rotating in the first rotational direction (arrow 724A). The mounting plate assembly 40' is transposed forward (arrow 24A') relative to the carriage assembly 42' since the carriage assembly 42' is coupled to the striker 28' and slidably coupled to the mounting plate assembly 40'. Figure 28 shows the mounting plate assembly 40' translated forward (arrow 24A’) from Figure 29 relative to the carriage assembly 42' with the carriage assembly 42' spaced apart from the lower rear flange 474' a second distance 700' less than the third distance 702', which generally corresponds to the mid-position 36 of the seat back 14 in the first embodiment. Additional forward translation (arrow' 24A') of the mounting plate assembly 40' relative to the carriage assembly 42' reduces the distance between the carriage assembly 42' and the lower rear flange 474' to the first distance 690', which returns the seat back 14' to the design position 34'. It will be appreciated that the inclination angle 39' of the seat back 14' is infinitely adjustable betw een the design position 34' and the full recline position 38'.

[0090] Referring to Figure 27, the move the seat back 14' from one of the upright positions (i.e., the design position 34', the full recline position 38', or any position between the design position 34' and the full recline position 38'), the occupant actuates the first switch 804 which causes the electric motor 712 to rotate the drive gear 716 in the first rotational direction (arrow7724A), causing the lead screw 722 to rotate in the forward rotational direction (arrow 736A). Referring to Figure 30. the forward rotation (arrow 736A) of the lead screw 722 transposes the mounting plate assembly 40' forward (arrow 24A') relative to the carriage assembly 42' such that the carriage assembly 42' is spaced apart from the lower rear flange 474' a fourth distance 704' less than the first distance 690' and the hook pin 600' engages with the hook release 132' on the mounting bracket 58'. Referring to Figure 31, additional forward rotation (arrow 736A) of the lead screw 722 causes the mounting plate assembly 40' to be transposed forward (arrow 24A') relative to the carriage assembly 42' until the carriage assembly 42' is spaced apart from the lower rear flange 474' a fifth distance 706' less than the fourth distance 704'. The additional forward translation (arrow 24A') of the mounting plate assembly 40' relative to the carriage assembly 42' causes the hook release 132' to slide the hook pin 600' forward along the pin slot 454', which causes the lower strength hook 570' to rotate downward (arrow 664B') about the lower pivot 520' to an unlatched position 572B'. The lower cam surface 592' on the lower strength hook 570' engages with the lever surface 656’ on the lower cinch hook 630’ as the lower strength hook 570' rotates downward (arrow 664B'), causing the lower cinch hook 630' to pivot downward (arrow 664B') to the unlatched position 63 IB', which places the seat back14 in the unlatched position 710 shown in Figure 1. The striker 28' can be exit the high latch 12' after the lower strength hook 570' and the lower cinch hook 630' are in the unlatched positions 572B', 631B'. After the striker 28' is decoupled from the high latch 12', the occupant rotates the seat back 14' forward (arrow 24A') past vertical and releases the seat back 14'. Next, gravity rotates the seat back 14' to the fold flat position 26'. After the high latch 12' is decoupled from the striker 28', the high latch 12' positions the lower strength hook 570' and the lower cinch hook 630' in such a way that the lower strength hook 570' and the lower cinch hook 630' will cam / ramp off the striker 28' allowing the high latch 12' to re-engage with the striker 28' when returning from the fold flat position 26'. In one embodiment, power is provided to the electric motor 712 to cause the electric motor 712 to rotate the drive gear 716 in the second rotational direction (arrow 724B), causing the lead screw 722 to rotate in the rearward rotational direction (arrow 736B), returning the relative position between the carriage assembly 42' and the mounting plate assembly 40' to the design position 34'. In more detail, the high latch 12' is repositioned such that the carriage assembly 42' is the first distance 690' away from the lower rear flange 474' with the hook release 132’ disengaged from the hook pin 600'. After the hook release 132' disengages from the hook pin 600'. the low er cinch spring 680' and the lower hook spring 666' cause the lower cinch hook 630' and the lower strength hook 570', respectively, to rotate upward (arrow' 664A') about the lower pivot 520' towards the respective latched positions 631 A', 572A'. In addition, the hook pin 600' is transposed rearward along the pin slot 454' as the lower strength hook 570' rotates upward (arrow 664A'). The seat back 14' is returned to the design position 34' from the fold flat position 26' in a similar manner as previously described with the first embodiment of the high latch 12.

[0091] As discussed above, the seat assembly 10 of the present invention includes a high latch 12, 12' having a mounting plate assembly 40, 40' and a carriage assembly 42, 42'. The seat assembly 10 is repositionable between the full recline and design positions while the high latch 12, 12' is coupled to the striker 28. 28'. Further, the high latch 12, 12' can be decoupled from the striker 28, 28' allowing the seat assembly 10 to be repositioned from any of the upright positions to a fold flat position 26. 26'.

[0092] The invention has been described in an illustrative manner, and it is to be understood that the terminology, which has been used, is intended to be in the nature of words of description rather than of limitation. Many modifications and variations of the present invention are possible in lamp of the above teachings. It is, therefore, to be understood thatwithin the scope of the appended claims, the invention may be practiced other than as specifically described.

Claims

What is claimed is:

1. A seat assembly for use in an automotive vehicle, the seat assembly comprising: a seat cushion adapted to be coupled to a floor of the automotive vehicle; a seat back pivotably coupled to the seat cushion; a striker adapted to be fixedly secured to a support wall in the automotive vehicle; and a high latch fixedly coupled to the seat back, the high latch comprising: a mounting plate assembly fixedly coupled to the seat back; and a carriage assembly slidably coupled to the mounting plate assembly and configured to be selectively coupled to the striker, wherein the mounting plate assembly can selectively translate relative to the carriage assembly; wherein translating the mounting plate assembly relative to the carriage assembly while the carriage assembly is coupled to the striker causes the seat back to pivot relative to the seat cushion between a design position, a full recline position, and an unlatched position.

2. The seat assembly as set forth in claim 1, wherein: the mounting plate assembly further comprises a mounting bracket fixedly coupled to the seat back and an upper guide rod fixedly coupled to the mounting bracket; and the carriage assembly further comprises a trolley bracket slidably coupled to the upper guide rod, a carnage bracket fixedly coupled to the trolley bracket, a lower pivot fixedly coupled to the trolley bracket, a lower strength hook pivotably coupled to the lower pivot and spring-biased towards the striker.

3. The seat assembly as set forth in claim 2, wherein: the mounting bracket further comprises a hook release; and the carriage assembly further comprises a hook pin fixedly coupled to the lower strength hook which releasably engages with the hook release as the mounting plate assembly is translated relative to the carriage assembly toward the unlatched position which causes the lower strength hook to pivot about the lower pivot away from the striker.

4. The seat assembly as set forth in claim 3. further comprising a lower cinch hook pivotably coupled to the lower pivot and spring-biased towards the striker.

5. The seat assembly as set forth in claim 4, further comprising a fore-aft spring operatively coupled between the carriage assembly and the mounting plate assembly.

6. The seat assembly as set forth in claim 5, further comprising: an upper pivot fixedly coupled to the mounting bracket; an upper strength hook pivotably coupled to the upper pivot and pivotable between an engaged condition with the carriage assembly and a disengaged condition spaced apart from the carriage assembly; and a handle operatively coupled to the upper strength hook and configured to rotate the upper strength hook between the engaged condition and the disengaged condition; wherein translating the mounting plate assembly relative to the carriage assembly is prevented while the upper strength hook is engaged with the carriage assembly; and wherein the mounting plate assembly can selectively translate relative to the carriage assembly between the design position and the full recline position while the upper strength hook is disengaged from the carriage assembly.

7. The seat assembly as set forth in claim 6, wherein: the carriage bracket further comprises a forward aperture, a middle aperture, and a rear aperture; and the high latch is retained in the design position when the upper strength hook is engaged with the forw ard aperture, the high latch is retained in a mid-position when the upper strength hook is engaged with the middle aperture, the high latch is retained in the full recline position when the upper strength hook is engaged with the rear aperture, and the high latch is repositionable between the design position, the mid-position, , and the full recline position while the upper strength hook is spaced apart from the carriage bracket.

8. The seat assembly as set forth in claim 5, further comprising: a threaded nut fixedly coupled to the carriage assembly; an end block fixedly coupled to the mounting bracket; a lead screw- meshingly engaged with the threaded nut and rotationally supported by the end block; and an electric motor operatively coupled to the lead screw' and configured to selectively rotate the lead screw in a forward rotational direction and a rearward rotational direction causing translation of the mounting plate assembly relative to the carriage assembly in a forward direction and a rearward direction, respectively.

9. The seat assembly as set forth in claim 8, wherein the high latch is selectively repositionable between the design position, the full recline position, and the unlatched position in response to the electric motor rotating the lead screw.

10. The seat assembly as set forth in claim 9, wherein the high latch is selectively repositionable to a plurality of intermediate positions between the design position and the full recline position while the high latch is coupled to the striker.

11. A high latch for use in a seat assembly in an automotive vehicle, the high latch comprising: a mounting plate assembly comprising a mounting bracket and an upper guide rod fixedly coupled to the mounting bracket; and a carriage assembly comprising a trolley bracket slidably coupled to the upper guide rod, a lower pivot fixedly coupled to the trolley bracket, a lower strength hook pivotably coupled to the lower pivot and adapted to be coupled to a striker in the automotive vehicle: wherein the mounting plate assembly can selectively translate relative to the carriage assembly between a design position, a full recline position, and an unlatched position.

12. The high latch as set forth in claim 11, further comprising a fore-aft spring operatively coupled between the trolley bracket and the mounting bracket.

13. The high latch as set forth in claim 12, further comprising a lower hook spring operatively coupled between the trolley bracket and the lower strength hook.

14. The high latch as set forth in claim 13, further comprising: a hook release fixedly coupled to the mounting bracket; and a hook pin fixedly coupled to the lower strength hook and configured to frictionally engage with the hook release when the high latch is in the unlatched position; wherein when the mounting plate assembly is translated relative to the carriage assembly towards the unlatched position, the hook release frictionally engages with the hook pin and causes the low er strength hook to rotate about the lower pivot.

15. The high latch as set forth in claim 14. further comprising: an upper pivot fixedly coupled to the mounting bracket; an upper strength hook pivotably coupled to the upper pivot and pivotable between a home position engaged with the carriage assembly and a retracted position disengaged from the carriage assembly; anda handle operatively coupled to the upper strength hook and configured to rotate the upper strength hook between an engaged condition with the carriage assembly and a disengaged condition from the carriage assembly; wherein translating the mounting plate assembly relative to the carriage assembly is prevented while the upper strength hook is in the engaged condition with the carriage assembly; and wherein the mounting plate assembly can selectively translate relative to the carriage assembly between the design position and the full recline position while the upper strength hook is in the disengaged condition spaced apart from the carriage assembly.

16. The high latch as set forth in claim 15. the camage assembly further comprising a carriage bracket fixedly coupled to the trolley bracket and including a forward aperture, a middle aperture, and a rear aperture; wherein the high latch is retained in the design position when the upper strength hook is engaged with the forward aperture, the high latch is retained in a mid-position when the upper strength hook is engaged with the middle aperture, the high latch is retained in the full recline position when the upper strength hook is engaged with the rear aperture, and the high latch is repositionable between the design position, the mid-position, and the full recline position while the upper strength hook is spaced apart from the carriage bracket.

17. The high latch as set forth in claim 14, further comprising: a threaded nut fixedly coupled to the carriage assembly; an end block fixedly coupled to the mounting bracket; a lead screw meshingly engaged with the threaded nut and rotationally supported by the end block; and an electric motor operatively coupled to the lead screw and configured to selectively rotate the lead screw in a forward rotational direction and a rearward rotational direction causing translation of the mounting plate assembly relative to the carriage assembly in a forward direction and a rearward direction, respectively.

18. The high latch as set forth in claim 17. wherein the high latch is selectively repositionable between the design position, the full recline position, and the unlatched position in response to the electric motor rotating the lead screw.

19. The high latch as set forth in claim 18. wherein the high latch is selectively repositionable to a plurality of intermediate positions between the design position and the full recline position while the high latch is coupled to the striker.

Images