Ring latch release system for long guide rail assembly

Abstract

A guide rail drive assembly having an annular latch and an annular latch release system is assembled with a fixed long guide rail for displacing a vehicle seat along the fixed long guide rail. The annular latch has spaced-apart trigger release portions and is repositionable between a locked position and an unlocked position. The annular latch release system includes a dual plunger, a rotatable actuator cam, and a return spring. The dual plunger has spaced-apart plungers configured to engage corresponding release triggers and is repositionable between a retracted position and an extended position, in which the plungers are spaced apart from the annular latch and in which the plungers engage the release triggers and reposition the annular latch to the unlocked position. Rotation of the actuator cam repositions the dual plunger toward the extended position. The return spring biases the dual plunger toward the retracted position and toward an engagement position for engaging the actuator cam.

Description

[0001] Cross - reference to related applications

[0002] This application claims priority to U.S. Provisional Application No. 63 / 082,692, filed on September 24, 2020, the disclosure of which is hereby incorporated by reference in its entirety. Technical field

[0003] The present invention relates to a long rail assembly for supporting a vehicle seat within a motor vehicle, and the long rail assembly is configured to travel along a fixed long rail when the vehicle seat is repositioned to another position along the fixed long rail. More specifically, the present invention relates to an annular latch release system for a long rail assembly, the annular latch release system being configured to automatically unlock an annular latch that couples the long rail assembly to the fixed long rail. Background art

[0004] Various sliding mechanisms for repositioning a vehicle seat along a fixed long rail in a vehicle are known. An example of a known sliding mechanism with an annular latch release mechanism is disclosed in PCT Publication WO / 2020 / 131777, in which a vehicle seat is coupled to a sliding mechanism that is capable of sliding within a fixed long rail. The sliding mechanism includes a movable upper channel member having rollers configured to travel along the fixed long rail. The annular latch releasably couples the movable upper channel member to the fixed long rail. The annular latch typically includes metal fingers and / or wire loops operatively coupled to the movable upper channel member and capable of being repositioned between an unlocked position and a locked position that engages slots, holes, and / or notches in the fixed long rail. The annular latch release mechanism is operatively connected to the annular latch. The annular latch release mechanism is configured to reposition the annular latch between the locked position and the unlocked position. The annular latch release mechanism includes a latch motor rotatably coupled to an actuator cam. The actuator cam includes a cam groove having a cam surface. A release plunger is directly coupled to the cam groove by a rivet extending through the cam groove. The release plunger is configured to releasably engage the annular latch when the release plunger moves toward the annular latch. Rotating the actuator cam by the latch motor causes the release plunger to press against a retainer of the annular latch and causes the annular latch to be repositioned to the unlocked position. Once the annular latch is in the unlocked position, the vehicle seat can be repositioned to another position along the fixed long rail. When the vehicle seat is in the desired position, the latch motor rotates the actuator cam back to the starting rotational position, which retracts the release plunger away from the annular latch. The annular latch automatically moves back to the locked position.

[0005] Because the release plunger is directly coupled to a cam slot in the actuator cam, this known annular latch release mechanism requires a specific alignment of the actuator cam and the release plunger. Additionally, this known annular latch release mechanism has only a single point of contact between the release plunger and the retainer of the annular latch, which can cause the annular latch to rotate when the annular latch is repositioned to the unlocked position. Finally, misalignment of the release plunger, the actuator cam, and the retainer of the annular latch can negatively affect the function of the annular latch release mechanism.

[0006] Accordingly, it is desirable to have an annular latch release system that eliminates the direct coupling between the actuator cam and the release plunger. Additionally, it is desirable for the annular latch release system to have more than a single point of contact between the release plunger and the annular latch to reduce rotation of the annular latch due to engagement with the release plunger. Finally, it is desirable to accommodate misalignment of components, tolerance stack-up, and variations in component dimensions while ensuring proper function of the annular latch release system. SUMMARY OF THE INVENTION

[0007] A track drive assembly having an annular latch and an annular latch release system is provided for displacing a vehicle seat along a fixed long track. The annular latch has spaced-apart trigger release portions, and the annular latch is repositionable between a locked position where the track drive assembly is interlocked with the fixed long track and an unlocked position where the track drive assembly is displaceable along the fixed long track. The annular latch release system includes: a dual plunger repositionable between a retracted position and an extended position and having spaced-apart first and second plungers configured to frictionally engage corresponding release triggers; a return spring biasing the dual plunger toward the retracted position and toward an engagement position for engagement with an actuator cam; and an actuator cam rotated to reposition the dual plunger toward the extended position. BRIEF DESCRIPTION OF THE DRAWINGS

[0008] The advantages of the present invention will be readily understood, as the invention becomes better understood by reference to the following detailed description when considered in conjunction with the accompanying drawings, in which:

[0009] Figure 1 is a cross-sectional perspective view of a long track assembly including a track drive assembly having an annular latch and an annular latch release system according to one embodiment of the present invention;

[0010] Figure 2 is a perspective view of the interior of a vehicle having a vehicle seat coupled to the long track assembly according to one embodiment of the present invention;

[0011] Figure 3 is along Figure 1taken along the sectional line A-A of Figure 1 End view of the cross-section of the long guide rail assembly, showing the annular latch release system in the retracted position and the annular latch in the unlocked position;

[0012] Figure 4 is Figure 1 Partially enlarged perspective view of part 4 of , showing the double plungers of the annular latch release system in the retracted position, where the annular latch is in the locked position;

[0013] Figure 5 is Figure 3 Partially perspective view of part 5 of , showing the annular latch in the locked position, where the double plungers are in the initial contact position;

[0014] Figure 6 is Figure 5 Partially perspective view of , showing the annular latch in the unlocked position, where the double plungers are in the extended position;

[0015] Figure 7 is taken along Figure 6 the sectional line D-D of Figure 6 Cross-sectional view of a part of the annular latch, upper channel member and fixed long guide rail of , showing the annular portion of the annular latch and the locking protrusions in the upper channel member and the fixed long guide rail;

[0016] Figure 8 is taken along Figure 1 the sectional line B-B of Figure 1 Partially cross-sectional view of the long guide rail assembly of , showing the annular latch release system in the unactuated state;

[0017] Fig. 9 is Figure 3 End view of the cross-section of the long guide rail assembly of , showing the annular latch release system in the unactuated state and the annular latch in the locked position;

[0018] Fig.10 is taken along Figure 1 the sectional line A-A of Figure 1 Partially end view of the cross-section of a part of the long guide rail assembly of , showing the actuator cam fixedly coupled to the drive shaft;

[0019] Fig.11 is Fig. 9 Partially cross-sectional view of the long guide rail assembly of , showing the annular portion of the annular latch in the locked position relative to the locking protrusions in the fixed long guide rail and the upper channel member;

[0020] Figure 12 is a partial cross-sectional view of a known long guide rail assembly, which shows an annular latch release mechanism including a plunger having a single contact point in contact with the annular latch;

[0021] Figure 13 is an end cross-sectional view of the known long guide rail assembly of Figure 12, which shows the plunger of the annular latch release mechanism directly coupled to the actuator cam;

[0022] Fig.14 is Fig.11 a partial cross-sectional view of the long guide rail assembly of, which shows the annular latch in the locked position and the double plunger in the initial contact position;

[0023] Fig.15 is Fig.14 an end cross-sectional view of the long guide rail assembly of, which shows the annular latch in the locked position, wherein the double plunger is in the initial contact position;

[0024] Fig.16 is Fig.15 a partial cross-sectional view of the long guide rail assembly of, which shows the annular latch in the unlocked position and the double plunger in the extended position;

[0025] Fig.17 is Fig.16 an end cross-sectional view of the long guide rail assembly of, which shows the annular latch in the unlocked position and the double plunger in the extended position;

[0026] Fig.18A shows Fig.17 a partial cross-sectional view of the long guide rail assembly of, which shows the annular latch release system in the unactuated state, wherein the annular latch is in the locked position;

[0027] Fig.18B shows Fig.18A a partial cross-sectional view of the long guide rail assembly of, which shows the annular latch release system in the transitional state, wherein the annular latch is in the locked position;

[0028] Fig.18C shows Fig.18B a partial cross-sectional view of the long guide rail assembly of, which shows the annular latch release system in the actuated state, wherein the annular latch is in the unlocked position;

[0029] Fig.18D shows Fig.18C a partial cross-sectional view of the long guide rail assembly of, which shows the annular latch release system in the transitional state, wherein the annular latch is in the locked position;

[0030] Fig.18E shows Fig.18DPartial cross-sectional view of a long guide rail assembly, showing an annular latch release system in an unactuated state, where the annular latch is in the locked position;

[0031] Fig.19A Shows Fig.18E End cross-sectional view of a long guide rail assembly, showing an annular latch release system in an unactuated state, where the annular latch is in the locked position;

[0032] Fig.19B Shows Fig.19A End cross-sectional view of a long guide rail assembly, showing an annular latch release system in a transitional state, where the annular latch is in the locked position;

[0033] Fig.19C Shows Fig.19B End cross-sectional view of a long guide rail assembly, showing an annular latch release system in an actuated state, where the annular latch is in the unlocked position;

[0034] Fig.19D Shows Fig.19C End cross-sectional view of a long guide rail assembly, showing an annular latch release system in a transitional state, where the annular latch is in the locked position;

[0035] Fig.19E Shows Fig.19D End cross-sectional view of a long guide rail assembly, showing an annular latch release system in an unactuated state, where the annular latch is in the locked position;

[0036] Fig. 20 Exploded perspective view of a long guide rail assembly with an annular latch release system according to a second embodiment of the present invention;

[0037] Fig.21 Is Fig. 20 Partial perspective view of a long guide rail assembly, showing the assembled annular latch release system;

[0038] Fig. 22 Is Fig.21 Partial perspective view of a long guide rail assembly, showing a return spring operatively coupled between a double plunger and a housing bracket;

[0039] Fig.23 Shows Fig. 22 Partial cross-sectional view of a long guide rail assembly, showing an annular latch release system in an unactuated state, where the annular latch is in the locked position;

[0040] Fig.24 Shows Fig.23Partial cross-sectional end view of a long rail assembly, showing a ring latch release system in an unactuated state, where the ring latch is in the locked position;

[0041] Fig.25 showing Fig.24 Partial cross-sectional view of a long rail assembly, showing a ring latch release system in a transitional state, a double plunger in an initial contact position, and a ring latch in the locked position;

[0042] Fig.26 showing Fig.25 Partial cross-sectional end view of a long rail assembly, showing a ring latch release system in a transitional state, a double plunger in an initial contact position, and a ring latch in the locked position;

[0043] Fig. 27 showing Fig.26 Partial cross-sectional view of a long rail assembly, showing a ring latch release system in an actuated state, a double plunger in an extended position, and a ring latch in the unlocked position; and

[0044] Fig.28 showing Fig. 27 Partial cross-sectional end view of a long rail assembly, showing a ring latch release system in an actuated state, a double plunger in an extended position, and a ring latch in the unlocked position. DETAILED DESCRIPTION

[0045] Figures 1 to 11 and Figures 14 to 28 Illustrated is a long rail assembly 12 according to an embodiment described herein, the long rail assembly having a rail drive assembly 14 configured to displace a vehicle seat 18 for a motor vehicle along a fixed long rail 22 for seat position adjustment. Directional references, such as front, rear, up, down, upward, downward, longitudinal, lateral, left, right, etc., employed or shown in the specification, drawings, or claims are relative terms used for convenience of description and are not intended to limit the scope of the invention in any respect. Referring to the drawings, like reference numerals represent like or corresponding components throughout the several views.

[0046] Figure 1 Illustrated is a long rail assembly 12 according to an embodiment of the present invention, the long rail assembly having a rail drive assembly for a vehicle seat 18 (in Figure 2Shown (in the drawings) is a guide rail drive assembly 14 for adjusting a position along a fixed long guide rail 22 within a motor vehicle. The guide rail drive assembly 14 includes an annular latch 28 for interlocking the guide rail drive assembly 14 with the fixed long guide rail 22. An annular latch release system 32 is operatively coupled to the annular latch 28 and is configured to automatically disengage the annular latch 28 from the fixed long guide rail 22 to unlock the guide rail drive assembly 14. When the guide rail drive assembly 14 is unlocked, the guide rail drive assembly 14 is capable of translating along the fixed long guide rail 22. In some embodiments, the guide rail drive assembly 14 is a powered guide rail drive assembly 14 configured to be automatically repositioned along the fixed long guide rail 22. In other embodiments, the guide rail drive assembly 14 is a manual guide rail drive assembly configured to be manually repositioned along the fixed long guide rail 22.

[0047] Figure 2 Shown is the interior 36 of a motor vehicle having a plurality of vehicle seats 18. Each vehicle seat 18 is connected by a guide rail drive assembly 14 to fixed long guide rails 22, 22' that extend longitudinally along the vehicle floor 40. Each vehicle seat 18 is supported on opposite sides 18A, 18B of the vehicle seat 18 by at least one leg 42 and optionally by a rear leg 42 and a front leg 44 on opposite sides 18A, 18B of the vehicle seat 18. The legs 42, 44 are removably coupled to the guide rail drive assembly 14 by any method known in the art such as by a dowel and latch mechanism.

[0048] Referring Figure 2 , each guide rail drive assembly 14 travels in a forward direction F (“forward direction”) and a rearward direction R (“rearward direction”) along one of the fixed long guide rails 22, 22' attached to the vehicle floor 40. Each vehicle seat 18 is mounted to at least one guide rail drive assembly 14. Additionally, each vehicle seat 18 travels along a pair of fixed long guide rails 22, 22' when the vehicle seat 18 is repositioned between a first vehicle seat position 60 and a second vehicle seat position 64 (shown in dashed lines as the vehicle seat 18' attached to the guide rail drive assembly 14'). The fixed long rails 22, 22' can extend any length suitable for the intended application. Similarly, any suitable number of fixed long guide rails 22, 22' can be positioned on the vehicle floor 40 according to the needs for the intended application. Thus, since the vehicle seat 18 is coupled to at least one guide rail drive assembly 14 that is capable of repositioning to any vehicle seat position 60, 74 along at least one fixed long guide rail 22, the long rail assembly 12 allows for improved adjustment of the vehicle seat 18 position.

[0049] As Figure 1As shown, the fixed long guide rail 22 has a generally U-shaped cross-sectional profile 68, a bottom wall 72, opposite side walls 76, 84, an internal channel 90, and a top wall 94 having an elongated opening 98 extending in the longitudinal direction of the fixed long guide rail 22. Referring to Figure 3 , each side wall 76, 84 of the fixed long guide rail 22 optionally includes tracks 104, 110 having a generally C-shaped cross-sectional profile, wherein each track 104, 110 has a track bottom wall 104A, 110A, track outer side walls 76A, 84A, track top walls 94A, 94B, and retaining lips 118A, 118B extending downward from adjacent track top walls 94A, 94B and spaced apart from adjacent track outer side walls 76A, 84A. As Figure 3 illustrated, each track bottom wall 104A, 110A is optionally positioned above the bottom wall 72 of the fixed long guide rail 22. The fixed long guide rail 22 is a stamped section, a formed section, a molded section, and / or a rolled section made of a metallic material or a plastic material and has a length selected based on a particular application. It should be understood that the dimensions, shape, and length of the fixed long guide rail 22 can vary without changing the scope of the present invention.

[0050] Figure 1 and Figure 3 also shown, the guide rail drive assembly 14 includes an elongated upper channel member 130 having a generally inverted U-shaped cross-sectional profile 134 and extending in a longitudinal direction between opposite ends 130A and 130B, having opposite first side walls 144A and second side walls 144B, and a top wall 150 extending between the opposite first side walls 144A and second side walls 144B. A shaft 154 extends laterally through a hollow tube 158 extending between the opposite side walls 144A and side wall 144B. Wheels 162 are fixedly attached to the shaft 154 near each end 168 of the shaft 154. Figure 1 In the embodiment of

[0051] Additional details and alternative embodiments of exemplary guide rail drive assembly 14 and fixed long guide rail 22 are more fully described in PCT Application No. PCT / US2019 / 55835, filed on October 11, 2019, which is hereby incorporated herein by reference in its entirety.

[0052] The annular latch 28 is integral with the guide rail drive assembly 14, as Figure 1 shown. The annular latch 28 interlocks the guide rail drive assembly 14 with the fixed long guide rail 22 such that the vehicle seat 18 is held in any one of its seat positions 60, 64 during use and system loading events.

[0053] In Figure 4 is shown a Figure 1 partial enlarged view of portion 4 in, which illustrates the annular latch 28, the annular latch release system 32, a portion of the upper channel member 130 of the guide rail drive assembly 14, and a portion of the fixed long guide rail 22. Figure 3 Shows a cross-sectional end view of the annular latch release system 32 and the annular latch 28. Figure 5 And Figure 6 Shows a Figure 3 partial perspective view of portion 5 of, which illustrates the annular latch 28 in the locked position 180 and the unlocked position 182, respectively.

[0054] In the Figure 5 embodiment shown, portions 260A of the side walls 144A, 144B of the upper channel member 130 bend upward to form outer channel walls 260A spaced from the side walls 144A, 144B, and a generally U-shaped channel 260 is defined between the side walls and the outer channel walls. A plurality of first generally U-shaped grooves 266 are disposed in the side walls 144A, 144B of the upper channel member 130 and are spaced apart in the longitudinal direction of the upper channel member 130. A plurality of second U-shaped grooves 268 are formed in the outer channel wall 260A and are aligned with the plurality of first generally U-shaped grooves 266 in the side walls 144A, 144B. In Figure 7 are more clearly shown the plurality of first U-shaped grooves 266 and the plurality of second U-shaped grooves 268. Referring to Figure 7 , each of the plurality of first U-shaped grooves 266 and the plurality of second U-shaped grooves 268 includes opposite upper end surfaces 268C and lower end surfaces 266D, 268D (in Figure 5Opposite outer sidewalls 266A, 266B, 268A, 268B extending between (shown in). Locking protrusions 270, 272 extend vertically downward from the upper end surfaces 268C of each of the plurality of first U-shaped grooves 266 and the plurality of second U-shaped grooves 268. The locking protrusions 270, 272 include opposite sidewalls 270A, 270B, 272A, 272B extending between the corresponding upper end surfaces 268C and the end surfaces 272C of the locking protrusions 270, 272. The end surfaces 272C of the locking protrusions 270, 272 are spaced apart from the corresponding lower end surfaces 266D, 268D of the U-shaped grooves 266, 268, and gaps 266E, 268E are defined therebetween (see Figure 5 ).

[0055] As Figure 5 and Figure 7 shown, vertical grooves 278 are spaced along the longitudinal length of the retaining lips 118A, 118B of the fixed long guide 22. Alternatively, the vertical grooves 278 may be replaced by notches and / or holes according to the needs for specific applications and latch configurations. The vertical grooves 278 have opposite sidewalls 278A, 278B (see Figure 7 ). Figure 7 Shows a partial cross-sectional view of a portion of the annular latch 28 and the upper channel member 130 taken along the section line D-D of Figure 6 , which illustrates the alignment of the first U-shaped grooves 266 and the second U-shaped grooves 268, the locking protrusions 270, 272, and the vertical grooves 278 in the retaining lips 118A, 118B. As Figure 7 illustrated, each retaining lip portion 278C extending between the adjacent sidewalls 278A and the sidewall 278B of each vertical groove in the vertical grooves 278 forms a locking protrusion 278C in the retaining lips 118A, 118B.

[0056] Referring to Figure 3 , Figure 5 and Figure 7 , the annular latch 28 includes a latch retainer 286 having an elongated main portion 286', from which a plurality of generally U-shaped annular portions 292 extend. As Figure 7Best shown in, the U-shaped annular portion 292 has opposite annular portion side portions 292A, 292B that extend laterally away from the latch retainer 286, wherein an annular portion end portion 292C extends between the opposite annular portion side portions 292A and 292B. The annular portion side portions 292A, 292B that extend away from the latch retainer 286 and the annular portion end portion 292C cooperate to define an annular cavity 292D between the annular portion side portions and the annular portion end portion. The annular portion side portions 292A, 292B are sized and shaped to pass through the side walls 144A, 144B respectively, the outer channel walls 260A, and the gaps 266F, 268F, 278F between the adjacent locking protrusions 270, 272, 278C in the retaining lips 118A, 118B. In addition, the U-shaped annular portion 292 is sized and shaped such that the annular portion side portions 292A, 292B are spaced farther apart than the width of the locking protrusions 270, 272, 278C. When the annular latch 28 is in Figure 5 the locking position 180 shown in, the locking protrusions 270, 272, 278C extend downwardly within the respective annular cavities 292D. When the annular latch 28 is in Figure 6 the unlocking position 182 shown in, the U-shaped annular portion 292 is positioned within the gap 293 between the end surfaces 272C, 278D of the locking protrusions 270, 272, 278C and the lower end surfaces 266D, 268D of the U-shaped grooves 266, 268.

[0057] The annular latch 28 is operatively coupled to a spring 294 such that the annular latch 28 is spring-biased upwardly towards the Figure 5 locking position 180 as illustrated by arrow 300A. The spring 294 ensures that the annular latch 28 returns to the locking position 180 when the annular latch release system 32 does not actively disengage the annular latch 28.

[0058] In Figure 7 the embodiment shown in, the U-shaped annular portion 292 is part of an annular member 295 that is assembled with the latch retainer 286. Alternatively, the annular member 295 is insert-molded within the latch retainer 286 and / or formed integrally with the latch retainer 286. In addition, the annular member 295 is preferably formed of a metallic material. However, it is understood that in some embodiments, the annular member 295 may be formed of a plastic material and / or a combination of metal and plastic, and may include other materials. In addition, the latch retainer 286 is formed of a plastic material, a metallic material, and / or a combination thereof. Figure 4The embodiment shown in [FIGURE] includes four U-shaped annular portions 292 extending from the latch retainer 286. However, any suitable number of annular portions 292 may be used without changing the scope of the present invention. Optionally, the annular portions 292 may be replaced by one or more finger portions, plates, pins, etc.

[0059] Referring to Figure 4 , the elongated main portion 286' of the latch retainer 286 has opposing generally vertical side surfaces 286A, 286B extending between opposing generally vertical end surfaces 286C, 286D and between opposing generally horizontal top and bottom surfaces 286E, 286F. It will be understood that the latch retainer 286 may have an alternative shape, including a non-rectangular shape, and may include more or fewer features and surfaces depending on the needs of a particular application. For example, in Figure 5 the embodiment shown, the bottom surface 286F of the latch retainer 286 has a generally arcuate shape. As Figure 7 illustrated in [FIGURE], at least a portion of the side surface 286B that abuts the inner surface 144B' of the side wall 144B of the upper channel member 130 is preferably dimensioned and shaped to matingly engage at least a portion of the inner surface 144B' such that the latch retainer 286 will travel vertically along the side wall 144B. Alternatively, the main portion 286' of the latch retainer 286 is dimensioned and shaped such that the latch retainer 286 can be vertically repositioned closer to and / or adjacent to one of the side walls 144A, 144B of the upper channel member 130.

[0060] In Figure 5 and Figure 7 the embodiment shown, the latch retainer 286 is operatively coupled to the upper channel member 130. To guide the movement of the latch retainer 286 along the inner surface 144B' of the upper channel member 130, a T-shaped protrusion 296 projects from the side surface 286B of the latch retainer 286 (shown in Figure 7 ). As Figure 7 observed in [FIGURE], the T-shaped protrusion 296 includes a base portion 296A that projects from the side surface 286B of the latch retainer 286. A head portion 296B projects angularly from the base portion 296A, thereby forming a "T" shape. Optionally, one or more bumps 296C are extended from the head portion 296B and are configured to slide along the outer surface 144B" of the side wall 144B of the upper channel member 130.

[0061] Referring to Figure 6 and Figure 7, the upper channel member 130 includes guide slots 298 defined between opposing guide slot side surfaces 298A and 298B, and between guide slot side surfaces 298A' and 298B'. These guide slot side surfaces extend between opposite inner surface 144B' and outer surface 144B" of the side wall 144B. The guide slot 298 includes a first guide slot end wall 298C positioned on the side wall 144B and extending between the opposing guide slot side surfaces 298A and 298B (shown in Figure 6 ). A second guide slot end wall 298D (shown in Figure 6 ) is positioned on the outer channel wall 260A and also extends between the opposing guide slot side surfaces 298A' and 298B'. The guide slot 298 includes a first portion 298' sized and shaped such that the base portion 296A of the T-shaped protrusion 296 can slide along the first portion 298' of the guide slot 298 while preventing the head portion 296B from passing through the guide slot 298. Additionally, the guide slot 298 includes a second portion 298" extending between the side wall 144B of the upper channel member 130 and the outer channel wall 260A. The second portion 298" of the guide slot 298 is sized and shaped to allow the head portion 296B of the T-shaped protrusion 296 to pass through the second portion 298" of the guide slot 298 and into the U-shaped channel 260 between the side wall 144B and the outer channel wall 260A. Thus, the second portion 298" of the guide slot 298 facilitates the assembly of the latch retainer 286 with the upper channel member 130.

[0062] Referring to Figure 6 , the main portion 286' of the latch retainer 286 is positioned adjacent to the inner surface 144B' of the side wall 144B. The base portion 296A of the T-shaped protrusion 296 passes through the guide slot 298, and the head portion 296B of the T-shaped protrusion 296 is positioned adjacent to the outer surface 144B" of the side wall 144B. The guide slot 298 in combination with the T-shaped protrusion 296 projecting from the latch retainer 286 guides the vertical movement of the latch retainer 286 (arrow 300 shown in Figure 6 ) and at the same time restricts the rotational movement of the latch retainer 286 away from the side wall 144B of the upper channel member 130 (arrow 302 shown in Figure 6 ).

[0063] As Figures 7 to 9 illustrated, the latch retainer 286 further includes a release trigger 310 for disengaging the annular latch 28 from the fixed long guide rail 22. In Figure 8In the embodiment shown, the release trigger 310 includes a first release trigger 310A spaced apart from a second release trigger 310B. In an alternative embodiment, the first release trigger 310A and the second release trigger 310B are part of a single release trigger 310 that projects from the latch retainer 286. In yet another alternative embodiment, as shown in Fig.24 the first release trigger 310A and the second release trigger 310B are replaced by angled cutout portions 310A' in the top surface 286E of the latch retainer 286.

[0064] As Fig. 9 observed, each of the first release trigger 310A and the second release trigger 310B has a generally frustum - triangular shape in profile, where the upper surfaces 312A, 312B extend at a downward angle. The upper surfaces 312A, 312B of each release trigger 310A, 310B form trigger engagement pads 312A, 312B. The trigger engagement pads 312A, 312B extend between opposite end walls 314A and 314B (shown in Figure 7 of the release triggers 310A, 310B. Further, as shown in Fig.15 the trigger engagement pads 312A, 312B are inclined with respect to the vertical axis 316 of the latch retainer 286. Additionally, the trigger engagement pads 312A, 312B have a vertical inclination angle 316A of approximately sixty degrees with respect to the vertical axis 316 of the latch retainer 286. When assembled as part of the rail drive assembly 14, the horizontal inclination angle 318A of the trigger engagement pads 312A, 312B with respect to the horizontal reference line 318 is approximately thirty degrees. However, it will be understood that without changing the scope of the present invention, the vertical inclination angle 316A and the horizontal inclination angle 318A of the trigger engagement pads 312A, 312B can be selected to be greater than or less than approximately sixty degrees and greater than or less than approximately thirty degrees, respectively. Preferably, the trigger engagement pads 312A, 312B are not parallel to the horizontal reference line 318 and not parallel to the vertical axis 316 of the latch retainer 286.

[0065] Referring to Figure 3 when the rail drive assembly 14 is assembled with the fixed long rail 22, the retaining lips 118A, 118B are positioned between the side walls 144A, 144B of the upper channel member 130 and the outer channel wall 260A. The retaining lips 118A, 118B include locking protrusions 278C (shown in Figure 5 and Figure 7 ) spaced along the longitudinal length of the retaining lips 118A, 118B. Due to the annular latch 28 being biased toward the locking position 180 (shown in Figure 5is shown) upward spring biasing, such that the annular portion 292 automatically moves between an unlocked position 182 (shown in Figure 6 and a locked position 180 (shown in Figure 5 . At the unlocked position, the annular portion 292 is disengaged from the locking projection 278C, and at the locked position, the annular portion 292 frictionally engages and / or meshingly engages with the locking projection 278C in the retaining lips 118A, 118B of the fixed long guide rail 22. When the annular portion 292 engages with the locking projection 278C in the retaining lips 118A, 118B, the guide rail drive assembly 14 is locked to the fixed long guide rail 22, such that the guide rail drive assembly 14 is held in any one of the seat positions 60, 64 during a system loading event. When the annular portion 292 moves to the unlocked position 182 relative to the locking projection 278C in the retaining lips 118A, 118B, the guide rail drive assembly 14 is capable of shifting along the fixed long guide rail 22.

[0066] The annular latch release system 32 is configured to automatically reposition the annular latch 28 from a locked position 180 (shown in Figure 5 toward an unlocked position 182 (shown in Figure 6 . In Figure 8 and Fig. 9 , the annular latch release system 32 is shown in an unactuated state 340, wherein the annular latch 28 is in the locked position 180. In contrast, in Fig.16 and Fig.17 , the ring latch release system 32 is shown in an actuated state 340A, wherein the annular latch 28 is in the unlocked position 182. As illustrated in Fig.14 and Fig.15 , when the ring latch release system 32 moves between the unactuated state 340 and the actuated state 340A, the ring latch release system 32 is in a transitional state 340B.

[0067] Referring to the embodiment shown in Figure 4 , the annular latch release system 32 includes an actuator cam 350, a double plunger 358, a return spring 362, and a housing 366, and the actuator cam is fixedly coupled to a drive shaft 354. Figure 4 Also shown in Figure 4The annular latch release system 32 shown in FIG. is optionally combined with a powered long rail assembly 14 configured to automatically reposition along a fixed long rail 22.

[0068] Figure 3 and Figure 4 As shown in FIG., the housing 366 includes opposing side walls 366A, 366B extending between opposing end walls 366C and 366D ( Figure 4 ), and a bottom wall 366E extending between opposing side walls 366A, 366B and between opposing end walls 366C, 366D ( Figure 3 ), thereby defining a cavity 366F between the bottom wall and the end walls and side walls.

[0069] As Figure 4 shown in FIG., the actuator cam 350 includes a collar 370 angled out from the cam body 374. Referring to Figure 3 , the collar 370 includes a bore 370A aligned with the axis of rotation 354A, the bore sized and shaped to matingly engage with an end portion 354B of the drive shaft 354. Additionally, the collar 370 includes a passage 370B extending through the collar 370 at an angle perpendicular to the axis of rotation 354A. The actuator cam 350 is formed from one or more plastic materials. However, the actuator cam 350 may be formed from alternative materials such as metals and combinations of metals and plastics.

[0070] In Figure 4 the embodiment shown in FIG., a mechanical fastener 378 fixedly couples the collar 370 to the drive shaft 354. Referring to Fig.10 , the mechanical fastener 378 is inserted through the passage 370B in the collar 370 and through the drive shaft 354. However, it will be understood that alternative methods of attaching the collar 370 to the drive shaft 354 may be used without changing the scope of the invention, such as press fits, snap features, adhesives, retaining washers, retaining clips, pins, etc. For example, in certain embodiments, the actuator cam 350 is operatively coupled to the drive shaft 354 via one or more gears. In more embodiments, the actuator cam 350 is rotated by engagement with a rod, movement of a linkage, rotation of a gear, rotation of the drive shaft of an electric motor, actuation of a Bowden cable, etc., without changing the scope of the invention.

[0071] In Figure 8 a cross-sectional view of the annular latch release system 32 is shown, which shows additional details of the actuator cam 350 and the double plunger 358. Referring to Figure 8, the actuator cam 350 is fixedly coupled to the drive shaft 354, wherein the drive shaft 354 defines a rotational axis 354A for the actuator cam 350. The actuator cam 350 is shown in Figure 8 as being in an initial rotational position 380, wherein in Figure 8 , the double plunger 358 is in a retracted position 384 and the annular latch 28 is in a locked position 180. In contrast, in Fig.16 , the actuator cam 350 is shown as being in a latch release rotational position 380B, wherein the double plunger 358 is in an extended position 384A and the annular latch 28 is in an unlocked position 182.

[0072] As Figure 8 shown, the actuator cam 350 includes a cam surface 388 having a contact point 390 that contacts the double plunger 358. The cam surface 388 extends between a first end 388A and a second end 388B. As the actuator cam 350 is rotated by the drive shaft 354, different portions 400, 404, 408 of the cam surface 388 contact the double plunger 358. Thus, as the actuator cam 350 rotates, the contact point 390 between the cam surface 388 and the double plunger 358 is repositioned along different portions 400, 404, 408 of the cam surface 388. To describe the relative motion of the actuator cam 350 with respect to the resulting motion of the double plunger 358 and the annular latch 28, the cam surface 388 is divided into a starting position 414A, a first transition zone 400 extending between the starting position 414A and an initial contact position 414B, a second transition zone 404 extending between the initial contact position 414B and a latch release position 414C, and a dwell zone 408 extending between the latch release position 414C and an end of a dwell position 414D, the dwell zone 408 being generally aligned with or in the vicinity of the second end 388B of the cam surface. Without changing the scope of the present invention, the initial position 414A may be aligned with, adjacent to, and / or offset from the first end 388A of the cam surface 388.

[0073] As Figure 8 observed, when the actuator cam 350 is in the starting rotational position 380, the actuator cam 350 rotates in a clockwise direction 418 as the contact point 390 is moved toward the latch release position 414C of the cam surface 388. In contrast, as Figure 8As observed, when the contact point 390 aligns with the dwell area 408 and the actuator cam 350 returns to the starting rotational position 380, the actuator cam 350 rotates in the counterclockwise direction 420. It will be understood that in different embodiments, the relative clockwise and counterclockwise rotations of the actuator cam 350 may be reversed. Additionally, it will be understood that the cam surface 388 of the actuator cam 350 may be adjusted to cause the dual plunger 358 to produce a desired vertical movement in response to a predetermined condition.

[0074] In Figure 4 and Figure 8 the embodiment shown, the dual plunger 358 has a generally M-shaped cross-section in profile, the dual plunger including a first release plunger 440, an alignment boss 444, and a second release plunger 448 that projects angularly from a cross member 452. The passage 454 (shown in Figure 8 ) optionally extends longitudinally partially or completely through each of the first release plunger 440, the second release plunger 448, and the alignment boss 444. In various embodiments, by way of non-limiting example, the dual plunger 358 is formed of one or more of a plastic material, a fiber-reinforced plastic material, a metallic material, and a combination of metal and plastic.

[0075] As Figure 8 shown, the cross member 452 has an upper surface 452A and a lower surface 452B. The upper surface 452A of the cross member 452 includes a contact surface 458 sized and shaped to frictionally engage the actuator cam 350. In Figure 8 the embodiment shown, the cross member 452 includes a cutout region 460 that provides a clearance between the cross member 452 and the actuator cam 350 when the actuator cam 350 rotates past the dwell area 408.

[0076] In Fig.10 the embodiment shown, the contact surface 458 and the cutout region 460 are recessed below the upper surface 452A of the cross member 452, thereby forming a rib 468 that extends around the outer periphery of the cross member 452. Due to tolerance stack-up, component variations, etc., the actuator cam 350 may be laterally repositioned as illustrated by arrow 472. The actuator cam 350 remains in lateral contact with the cross member 452 via the rib 468. The actuator cam 350 and the dual plunger 358 may be laterally repositioned relative to each other by the amount illustrated by arrow 476 and maintain the engagement between the actuator cam 350 and the dual plunger 358.

[0077] Referring to Figure 8, the dual plunger 358 is positioned within a cavity 366F in the housing 366. Additionally, each of the first release plunger 440 and the second release plunger 448 projects through a respective hole 504 in the bottom wall 366E of the housing 366 and through a respective hole 508 in the upper channel member 130. Similarly, the alignment boss 444 is configured to pass through an alignment hole 504A in the bottom wall 366E of the housing 366 and through a hole 508A in the upper channel member 130.

[0078] As Figure 4 best shown in, each of the first release plunger 440 and the second release plunger 448 has an outer surface 512 that extends between the lateral member 452 and an end surface 514 of the respective first release plunger 440 and second release plunger 448. Each of the first release plunger 440 and the second release plunger 448 has a generally frustoconical shape, where the outer surface 512 forms a barrel wall and the end surface 514 forms the frustum portion of the barrel.

[0079] Referring Fig. 9 , the end surface 514 of each of the first release plunger 440 and the second release plunger 448 forms a plunger engagement pad 514 that is configured to frictionally engage and actuate a respective release trigger of the release triggers 310A, 310B of the latch retainer 286. As Fig.15 shown in, the plunger engagement pad 514 is inclined with respect to the longitudinal axis 516 of the first plunger 440 and the second plunger 448. In Fig.15 the embodiment shown in, the plunger engagement pad 514 has a vertical inclination angle 516A of approximately sixty degrees with respect to the longitudinal axis 516 of the first plunger 440 and the second plunger 448. Preferably, as Fig.15 shown in, when the plunger engagement pad 514 is assembled as part of the rail drive assembly 14, the horizontal inclination angle 318A of the plunger engagement pad 514 is substantially equal to the horizontal inclination angle 318A of the trigger engagement pads 312A, 312B. Preferably, when the dual plunger 358 and the latch retainer 286 are assembled as part of the rail drive assembly 14, the plunger engagement pad 514 and the trigger engagement pads 312A, 312B are sized and shaped such that at least a portion of the plunger engagement pad 514 and the trigger engagement pads 312A, 312B are substantially parallel to each other.

[0080] In Fig. 9In the embodiment shown, both the plunger engagement pad 514 and the trigger engagement pads 312A, 312B have a horizontal tilt angle 318B of approximately thirty degrees relative to the horizontal reference line 318. It will be understood that in some embodiments, one of the plunger engagement pad 514 and the trigger engagement pads 312A, 312B may have a horizontal tilt angle 318A that is greater than and / or less than the horizontal tilt angle 318A for the other of the plunger engagement pad 514 and the trigger engagement pads 312A, 312B. Further, it is understood that for a particular application, the horizontal tilt angles 318A of the plunger engagement pad 514 and the trigger engagement pads 312A, 312B may be selected to be greater than or less than thirty degrees. Additionally, the plunger engagement pad 514 and the trigger engagement pads 312A, 312B are sized and shaped such that: when the dual plunger 358 moves vertically downward, as represented by arrow 300B, the plunger engagement pad 514 will frictionally engage the corresponding trigger engagement pad of the trigger engagement pads 312A, 312B. The plunger engagement pad 514 is shown in Figure 5 as frictionally engaged with the corresponding trigger engagement pads 312A, 312B.

[0081] The relative sizes, relative shapes, and relative orientations of the plunger engagement pad 514 and the trigger engagement pads 312A, 312B are selected such that the downward vertical movement 300B of the dual plunger 358 applies a load 518 to the latch retainer 286 at an angle less than ninety degrees relative to the horizontal reference line 318, as represented by the arrow 518 shown in Fig. 9 In Fig. 9In the illustrated embodiment, the plunger engagement pad 514 and the trigger engagement pads 312A, 312B are generally oriented at approximately thirty degrees relative to the horizontal reference line 318 when assembled with the upper channel member 130, and the load 518 is applied to the latch retainer 286 at an angle of approximately sixty degrees relative to the horizontal reference line 318. It will be understood that in various embodiments, the relative angles of the plunger engagement pad 514 and the trigger engagement pads 312A, 312B and the load 518 applied to the latch retainer 286 may differ from the indicated values. Since the load 518 applied by the dual plungers 358 is applied to the latch retainer 286 at an angle less than ninety degrees relative to the horizontal reference line 318, the load 518 presses the latch retainer 286 against the sidewall 144B of the upper channel member 130, as illustrated by arrow 520. The T-shaped protrusion 296 traveling along the guide slot 298 holds the lower portion 286F' of the latch retainer 286 adjacent to the sidewall 144B of the upper channel member 130. Accordingly, the T-shaped protrusion 296 reduces the rotational movement 302 of the latch retainer 286 away from the sidewall 144B of the upper channel member 130. Additionally, the plunger engagement pad 514 has a larger surface area than the trigger engagement pads 312A, 312B. This compensates for the amount of misalignment between the dual plungers 358 and the latch retainer 286 and simultaneously ensures that the plunger engagement pad 514 contacts the respective trigger engagement pads 312A, 312B.

[0082] Referring Fig.11 , since the dual plungers 358 include the spaced-apart first release plunger 440 and second release plunger 448, the loads 518A, 518B applied by the dual plungers 358 are distributed at two locations 310A, 310B on the latch retainer 286. More specifically, the loads 518A, 518B are applied to the spaced-apart release triggers 310A, 310B. Distributing the loads 518A, 518B on the two spaced-apart release triggers 310A, 310B reduces the longitudinal rotation of the latch retainer 286 as illustrated by arrow 522.

[0083] The alignment boss 444 has an outer surface 444A extending between the lower surface 452B of the transverse member 452 and the end surface 444B of the alignment boss 444, as Fig.11 shown. The alignment boss 444 is sized and shaped to pass through the alignment hole 504A in the bottom wall 366E of the housing 366 and through the hole 508A in the upper channel member 130.

[0084] In Fig.11In the illustrated embodiment, the return spring 362 is an open-coil helical wound spring that extends between opposite first and second spring ends 362A and 362B and defines a longitudinal passage therethrough. It will be understood that alternative spring types may be used, including but not limited to leaf springs, compression springs, extension springs, leaf springs, etc., in place of the return spring 362. The alignment boss 444 is inserted through the longitudinal passage in the return spring 362. The first spring end 362A is held in an annular recess 452C in the lower surface 452B of the cross member 452. The second spring end 362B is held within an annular recess 366G in the bottom wall 366E of the housing 366. The return spring 362 biases the double plunger 358 upwardly as illustrated by arrow 300A.

[0085] As Fig.10 shown, the return spring 362 that biases the double plunger 358 upwardly (arrow 300A) also biases the double plunger 358 toward an engagement position where it engages the cam surface 388 of the actuator cam 350. Thus, the return spring 362 compensates for variations in certain dimensions of the double plunger 358 and the actuator cam 350, as well as variations in the positions of the double plunger 358 and the actuator cam 350 when assembled as part of the ring latch release system 32.

[0086] Figures 12 and 13 illustrate a known ring latch release mechanism 32P that includes an actuator cam 350P rotated by a drive shaft 354P, a plunger 358P connected to a cam slot 532P within the actuator cam 350P by a rivet 530P, and a housing 366P having an alignment passage 504P. The alignment passage 504P extends through an upper channel member 130P. Within the upper channel member 130P is a ring latch 28P having a latch retainer 286P. Referring to FIG. 13, the latch retainer 286P is configured to vertically travel the sidewall 144B of the upper channel member 130P up and down as illustrated by arrow 300. Additionally, the latch retainer 286P is biased upwardly by a spring 294P. Upon assembly, a release projection 534P projects horizontally from the latch retainer 286P. The plunger 352P is vertically positioned above the release projection 534P. As shown in FIG. 12, rotation of the actuator cam 350P under the action of the drive shaft 354P, illustrated by arrow 536P, causes the rivet 530P to travel along the cam slot 532P. The cam slot 532P is sized and shaped such that the rivet 530P vertically moves up and down as illustrated by arrow 538P, thereby causing the plunger 358P to move up and down as the actuator cam 350P rotates.

[0087] When the known plunger 358P moves downward as illustrated by arrow 538P' in FIG. 13, the lower end surface 540P of the plunger 358P frictionally engages the release projection 534P of the latch retainer 286P. Since the lower end surface 540P of the plunger 358P and the upper surface 534P' of the release projection 534P are substantially horizontal, the downward load 538 applied by the plunger 358P to the release projection 534P can cause the release projection 534P to rotate away from the side wall 144B of the upper channel member 130P, as illustrated by arrow 542P. The misalignment between the plunger 358P and the release projection 534P further exacerbates the rotation of the latch retainer 286P. As shown in FIG. 12, the load 538 applied to the latch retainer 286P causes the latch retainer 286P to move downward, as illustrated by arrow 544P. A single engagement point between the plunger 358P and the latch retainer 286P on the release projection 534P may cause longitudinal rotation of the latch retainer 286P, as illustrated by arrow 546P. In addition, since the plunger 358P is directly coupled to the actuator cam 350P, changes in component dimensions and changes in the relative positions of the plunger 358P, the housing 366P, the drive shaft 354P, the upper channel member 130P, and the latch retainer 286P may affect the operation of the known annular latch release mechanism 32P. In addition, misalignment of individual components, such as the actuator cam 350P and the plunger 358P by way of example, may cause component wear, binding, and noise during the operation of the known annular latch release mechanism 32P.

[0088] In contrast, the actuator cam 350 is decoupled from the double plunger 358 in the annular latch release system 32 shown in Figures 3 to 11 . The configuration of the actuator cam 350 and the double plunger 358 in combination with the return spring 362 that biases the double plunger 358 toward an engagement position to engage the actuator cam 350 causes the annular latch release system 32 to tolerate dimensional changes within the components and misalignment of the relative positions of the components during assembly. In addition, since the double plunger 358 includes two points of contact with the latch retainer 286, the tendency for the latch retainer 286 to rotate longitudinally ( Fig.11 arrow 522 shown in Fig. 9 ) is reduced. In addition, since the plunger engagement pad 514 and the trigger engagement pads 312A, 312B are oriented at an angle of approximately thirty degrees relative to the horizontal reference line 318 during assembly, the latch retainer 286 is less likely to rotate away from the side wall 144B of the upper channel member 130 as illustrated by arrow 302 shown in

[0089] In Fig.15 and Fig.17In the embodiment shown, the dual plunger 358 includes a second alignment boss 358A extending from the cross member 452, which is configured to slide along an alignment channel 366H in the housing 366. As the dual plunger 358 moves between the retracted position 384, the initial contact position 384B, and the extended position 384A, the alignment channel 366H engages with the second alignment boss 358A to guide the vertical movement of the dual plunger 358.

[0090] The following discusses Figures 11 to 19E the movement of the annular latch release system 32 and the annular latch 28. The actuator cam 350 is shown in the Fig.11 starting rotational position. In addition, the dual plunger 358 is shown in the retracted position 384 and the latch retainer 286 is in the locked position 180. The contact point 390 between the dual plunger 358 and the actuator cam 350 is near the first end 388A of the cam surface 388 and is aligned with the starting position 414A. As shown in Fig. 9 when the dual plunger 358 is in the retracted position 384, the plunger engagement pads 514 are spaced apart from the respective first release triggers 310A and second release triggers 310B. As illustrated in Fig. 9 when the dual plunger 358 is spaced apart from the latch retainer 286, the annular latch 28 is in the locked position 180.

[0091] When the actuator cam 350 is in the Fig.11 starting rotational position 380 shown and the latch release operation is initiated, the actuator cam 350 rotates in the direction of arrow 418. As the contact point 390 moves along the cam surface 388 towards the initial contact position 414B, the dual plunger 358 moves downward towards the latch retainer 286. In Fig.14 the actuator cam 350 is shown in the initial contact rotational position 380A, where the actuator cam 350 has rotated such that the contact point 390 is aligned with the initial contact position 414B of the cam surface 388. The first release plunger 440 and the second release plunger 448 contact the release triggers 310A, 310B, where the latch retainer 286 remains in the locked position 180, as shown in Fig.14 and Fig.15 shown.

[0092] Referring to Fig.16 as the actuator cam 350 rotates further in the clockwise direction 418, the contact point 390 moves towards the latch release position 414C on the cam surface 388. As shown in Fig.16 and Fig.17As shown, as the actuator cam 350 rotates, the dual plunger 358 is pressed downward. Since the first release plunger 440 and the second release plunger 448 are frictionally engaged with the release triggers 310A, 310B, the movement of the dual plunger 358 causes the latch retainer 286 to be repositioned downward. In Fig.16 and Fig.17 , the annular latch release system 32 is shown in the actuated state 340A, in which the actuator cam 350 is in the latch release rotational position 380B. Additionally, in Fig.16 and Fig.17 , the dual plunger 358 is shown in the extended position 384A, and the latch retainer 286 is shown in the unlocked position 182. It is also shown that the annular portion 292 is disengaged from the locking protrusions 270, 272, 270C in the upper channel member 130 and the fixed long guide 22. More specifically, the annular portion 292 is positioned in the gaps 266E, 268E between the locking protrusions 270, 272, 278C and the lower end surfaces 266D, 268D of the U-shaped grooves 266, 268, as shown in Fig.17 . With the annular portion 292 disengaged from the locking protrusions 270, 272, 278C in the upper channel member 130 and the fixed long guide 22, the upper channel member 130 can be repositioned along the fixed long guide 22.

[0093] In Fig.16 it is also shown that since the cam surface 388 includes a dwell zone 408 and the lateral member 452 includes a cutout region 460, additional rotation of the actuator cam 350 past the latch release position 414C in the clockwise direction 418 does not cause additional downward movement of the dual plunger 358. The cutout region 460 in the lateral member 452 provides clearance space for additional rotation of the actuator cam 350 past the latch release position 414C without causing additional vertical movement of the dual plunger 358. This compensates for additional variations in the dimensions and positions of the components and variations in the rotational movement, thus not affecting the operation of the annular latch release system 32 and the annular latch 28.

[0094] Fig.15 and Fig.17 illustrate another embodiment of the dual plunger 358 having an optional alignment boss 358A. Referring to Fig.15 , the alignment boss 358A projects from the lateral member 452 and is oriented generally parallel to the first plunger 440 and the second plunger 448. The housing 366 includes a channel 366H configured to matingly engage with the alignment boss 358A of the dual plunger 358. As the dual plunger 358 moves vertically in the housing 366, the alignment boss 358A travels along the channel 366H in the housing 366. Fig.15An alignment boss 358A is shown near the top portion 366K of the housing 366. In contrast, Fig.17 An alignment boss 358A is shown spaced apart from the top portion 366K of the housing 366. Since the alignment boss 358A is held in the channel 366H of the housing 366, the alignment boss 358A reduces the lateral movement of the double plunger 358 when the double plunger 358 moves vertically.

[0095] FIG. 18A to FIG. 18E And FIG. 19A to FIG. 19E Illustrated is the movement of the actuator cam 350, the double plunger 358, and the ring latch 28 when the ring latch release system 32 is actuated from the unactuated state 340 toward the actuated state 340A and returned to the unactuated state 340. More specifically, Fig.18A And Fig.19A Illustrated is the ring latch release system 32 in the unactuated state 340, wherein the actuator cam 350 is in the starting rotational position 380, the double plunger 358 is in the retracted position 384, and the ring latch 28 is in the locked position 180.

[0096] When the ring latch release system 32 is in Fig.18A And Fig.19A the unactuated state 340 shown in and the latch release operation is initiated, the actuator cam 350 rotates in the clockwise direction 418 as shown in Fig.18B Illustrated. Fig.18B And Fig.19B Illustrated is the ring latch release system 32 in the transitional state 340B, wherein the actuator cam 350 rotates to the initial contact rotational position 380A, the double plunger 358 contacts the latch retainer 286 at 384B, and the ring latch 28 is in the locked position 180.

[0097] An additional rotation of the actuator cam 350 in the clockwise direction 418 causes the ring latch 28 to be repositioned to the unlocked position 182, as shown in Fig.18C And Fig.19C Illustrated. Fig.18C And Fig.19C Illustrated is the ring latch release system 32 in the actuated state 340A, wherein the actuator cam 350 rotates to the latch release rotational position 380B, the double plunger 358 is in the extended position 384A, and the ring latch 28 is in the unlocked position 182. With the ring latch 28 in the unlocked position 182, the upper channel member 130 can be repositioned along the fixed lower guide rail 22.

[0098] When the ring latch release system 32 is in Fig.18C And 19CWhen the actuation state 340A shown in and the upper channel member 130 is in the desired position 14' along the fixed lower guide rail 22, the latch relocking operation is initiated. The latch relocking operation causes the actuator cam 350 to rotate in the counterclockwise direction 420 as shown in Fig.18D toward Fig.18D and 19D the initial contact rotation position 380A shown in. The return spring 362 biases the double plunger 358 toward the actuator cam 350 such that when the actuator cam 350 rotates, the double plunger 358 retracts toward the initial contact position 384B. When the double plunger 358 retracts, the annular latch 28 is automatically repositioned toward the locked position 180 by the spring 294. Fig.18D and Fig.19D show the annular latch release system 32 in the transitional state 340B, where the actuator cam 350 has rotated to the initial contact rotation position 380A, the double plunger 358 is in contact 384B with the latch holder 286, and the annular latch 28 is in the locked position 180.

[0099] An additional counterclockwise rotation 420 of the actuator cam 350 returns the annular latch release system 32 to Fig.18E and 19E the unactuated state 340 shown in, where the actuator cam 350 has rotated to the starting rotation position 380, the double plunger 358 is in the retracted position 384 spaced apart from the annular latch 28, and the latch is in the locked position 180. The annular latch release system 32 is held in the unactuated state 340 until another latch release operation is initiated.

[0100] In Figure 20 to Figure 26 is shown Figure 1 another embodiment 32' of the annular latch release system 32. For simplicity, Figure 20 to Figure 26 the elements in that are the same as or similar to the elements used in the embodiments shown above in Figures 1 to 11 and Figure 14 to Figure 1 9 have the same reference numerals. Only the significant differences related to Figures 1 to 11 and Figure 14 to Figure 1 the embodiment shown in 9 are highlighted below. Refer to Fig. 20, the annular latch release system 32' includes at least a housing bracket 600, an actuator cam 350, a double plunger 358, a return spring 362, and a first plunger guide 610A and a second plunger guide 610B. The annular latch release system 32' is operatively coupled to an upper channel member 130 that is part of a rail drive assembly 14. Incorporated within the rail drive assembly 14 are an annular latch 28 and a spring 294. The annular latch 28 includes a plurality of annular portions 292 extending from a latch retainer 286. Additionally, spaced-apart first release triggers 310A and second release triggers 310B are formed in a top surface 286E of the latch retainer 286. The rail drive assembly 14 is also assembled with a fixed long rail 22 to form a long rail assembly 12.

[0101] Fig.21 The assembled annular latch release system 32' is shown. Referring to Fig.21 , one difference essentially involves replacing the Figure 3 housing 366 with the housing bracket 600. Referring to Fig. 22 , a second difference essentially involves rotating the actuator cam 350 by a Bowden cable 614 that replaces the Figure 4 drive shaft 354 shown in. When the rail drive assembly 14 is a manual rail drive assembly 14 lacking the ability for automatic movement, it is preferred to rotate the actuator cam 350 by replacing the drive shaft 354 with a Bowden cable 614. Fig. 22 Also shown in, a third difference essentially involves replacing the Figure 4 compression return spring 362 shown in with an extended return spring 362.

[0102] Fig. 20 The actuator cam 350 shown in includes a cam surface 388 that projects angularly from a base portion 350B of the actuator cam 350. A pivot 618 extends through the base portion 350B and defines a rotational axis of the actuator cam 350. Additionally, a link pin 620 is fixedly coupled to the base portion 350B and projects away from the actuator cam 350.

[0103] Fig. 20 The double plunger 358 also shown in includes a spaced-apart first release plunger 440 and a second release plunger 448 that project away from a cross member 452. The cross member 452 includes a first through hole 452D and a second through hole 452E for attaching a respective one of the first plunger guide 610A and the second plunger guide 610B. As Fig.24Best shown in, the first release plunger 440 and the second release plunger 448 extend generally vertically away from the cross member 452 when assembled as part of the annular latch release system 32'. In some embodiments, the dual plunger 358 is a stamped metal bracket. However, other embodiments of the dual plunger 358 are formed of plastic, fiber-reinforced plastic, and / or a combination of metal and plastic.

[0104] As Fig.23 shown, the dual plunger 358 is generally U-shaped, wherein the first release plunger 440 and the second release plunger 448 form opposite sides of the U-shape. Referring to Fig.24 , each of the first release plunger 440 and the second release plunger 448 has a curved end portion 514A that forms a plunger engagement pad 514. In Fig.24 the embodiment shown, the plunger engagement pads 514 are oriented at an angle of approximately thirty degrees relative to the horizontal reference line 318 during assembly. More specifically, each plunger engagement pad 514 is sized and shaped such that each plunger engagement pad 514 is generally parallel to the associated first release trigger 310A or second release trigger 310B formed in the latch retainer 286.

[0105] Referring to Fig.23 and Fig.24 , each of the first release trigger 310A and the second release trigger 310B includes notches 312A, 312B formed in the top surface 286E of the latch retainer 286. The notches 312A, 312B are configured to serve as trigger engagement pads 312A, 312B for the associated first release plunger 440 and second release plunger 448. Referring to Fig.23 , each trigger engagement pad 312A, 312B in the latch retainer 286 has a longitudinal width that is greater than the longitudinal width of the associated first release plunger 440 and second release plunger 448. As Fig.24 shown, the trigger engagement pads 312A, 312B are sized and shaped to be generally parallel to the associated plunger engagement pads 514 of the first release plunger 440 and the second release plunger 448 during assembly. In Fig.24 the embodiment shown, the trigger engagement pads 312A, 312B are oriented at an angle of approximately thirty degrees with respect to the horizontal reference line 318 during assembly.

[0106] Fig.21 shown, the cross member 452 of the dual plunger 358 includes an upper surface 452A configured to frictionally engage the actuator cam 350 during assembly. Referring to Fig.24 , the protrusion 444 projects away from the cross member 452 and includes a generally horizontal end portion 444C. As Fig. 22As shown, the end portion 444C of the convex portion 444 includes opposing slots 444D configured to hold the first spring end 362A of the return spring 362.

[0107] Referring to Fig. 20 and Fig.23 , each of the first plunger guide 610A and the second plunger guide 610B includes a disc-shaped base 630, a guide 634 protruding from the disc-shaped base 630, and a stem 638 protruding from the guide 634 and terminating in a rivet head 640.

[0108] Fig. 20 The housing bracket 600 shown in

[0109] is a stamped bracket having a main portion 600A with opposing first and second side portions 600B and 600C, and spaced upper and lower surfaces 600D and 600E, spaced first and second base protrusions 600F protruding from the lower surface 600E of the main portion 600A, and a curved protrusion 600G protruding angularly from the main portion 600. Further, the main portion 600A includes spaced first and second guide slots 600H and 600H', a central slot 600J, an arcuate slot 600K, and a pivot hole 600L extending between the opposing first and second side portions 600B and 600C.

[0109] As Fig. 20 illustrated, the return spring 362 is an extension spring having a first curved spring end 362A and a second curved spring end 362B. Referring to Fig. 22 , the first curved spring end 362A and the second curved spring end 362B are sized and shaped to be held in the associated slots 444D, 600M in the convex portion 444 and the curved protrusion 600G.

[0110] Referring to Fig. 20 , the upper channel member 130 includes spaced slots 130C configured to be assembled with the spaced first and second base protrusions 600F of the housing bracket 600. Further, the upper channel member 130 includes spaced holes 508 sized and shaped to be assembled with the respective first release plunger 440 and second release plunger 448.

[0111] In Fig.21 and Fig. 22 is shown the assembled annular latch release system 32'. Referring to Fig.21 and Fig. 22 , by passing the pivot 618 and the link pin 620 respectively through the pivot hole 600L in the housing bracket 600 (in Fig. 20shown) and an arcuate groove 600K to assemble the actuator cam 350 with the housing bracket 600. By passing the shanks 638 of each of the first plunger guide 610A and the second plunger guide 610B through the associated through-holes 452D, 452E in the double plunger 358 (shown in Fig. 20 shown) to assemble the first plunger guide 610A and the second plunger guide 610B with the double plunger 358. In some embodiments, the rivet heads 640 of the first plunger guide 610A and the second plunger guide 610B are formed after the first plunger guide 610A and the second plunger guide 610B are assembled with the double plunger 358. It will be appreciated that the first plunger guide 610A and the second plunger guide 610B can be assembled with the double plunger 358 by alternative methods, including but not limited to mechanical fasteners.

[0112] As Fig. 22 shown, the double plunger 358 is assembled with the housing bracket 600 by sliding the first plunger guide 610A and the second plunger guide 610B into the associated guide slots 600H, 600H' of the housing bracket 600. More specifically, the double plunger 358 is assembled with the disc-shaped bases 630 of each of the first plunger guide 610A and the second plunger guide 610B that abut the second side 600C of the housing bracket 600 (shown in Fig. 22 shown) such that the double plunger 358 abuts the first side 600B of the housing bracket 600 (shown in Fig.21 shown). Further, as Fig.23 shown, the guides 634 of each of the first plunger guide 610A and the second plunger guide 610B are aligned within the associated guide slots 600H, 600H'. The guides 634 are sized and shaped to fit within the associated guide slots 600H, 600H' and maintain the alignment of the double plunger 358 with the guide slots 600H, 600H' in the housing bracket 600. Further, the guides 634 are configured to slide vertically along the associated guide slots 600H, 600H'.

[0113] In Fig.21 and Fig. 22 also shown, the protrusion 444 of the double plunger 358 is inserted through the central slot 600J in the housing bracket 600. Referring to Fig. 22, a return spring 362 is operatively coupled between the housing bracket 600 and the dual plunger 358. More specifically, the first spring end 362A is assembled with the lug 444 of the dual plunger 358 by passing the first spring end 362A through a slot 444D in an end portion 444C of the lug 444. The second spring end 362B is assembled with the curved lug 600G in the housing bracket 600 by sliding the second spring end 362B through a slot 600M in the curved lug 600G. It will be understood that other types, other sizes, and other shapes of springs may be used in place of the return spring 362, and alternative methods of operatively coupling the return spring 362 between the housing bracket 600 and the dual plunger 358 may be used in various embodiments. The return spring 362 spring biases the dual plunger 358 toward the actuator cam 350, as illustrated by arrow 644. Thus, while a tension spring 362 is shown in Fig. 22 , alternative spring types and attachment methods, such as Figure 4 the compression spring 362 of the embodiment shown in

[0114] may be used without changing the scope of the present invention. Fig.21 , the housing bracket 600 is assembled with the upper channel member 130 by sliding a first base lug and a second base lug 600F of the housing bracket 600 through associated slots 130C in the upper channel member 130. Additionally, a first release plunger 440 and a second release plunger 448 of the dual plunger 358 are inserted into associated through holes 508 in the upper channel member 130.

[0115] A Bowden cable, indicated by an arrow 614 shown in Fig. 22 , is fixedly coupled to a distal end portion 620' of a link pin 620. During operation, when a tensile force is applied to the Bowden cable 614, the Bowden cable 614 causes the link pin 620 to rotate upwardly toward an upper end portion 650 of an arcuate slot 600K. Movement of the link pin 620 causes the actuator cam 350 to rotate about a pivot 618, and the pivot 618 defines a rotational axis 354A of the actuator cam 350. The arcuate slot 600K defines a range of motion of the actuator cam 350. When the tensile force is removed from the Bowden cable 614, an upward spring bias 644 on the dual plunger 358 causes the actuator cam 350 to rotate about the rotational axis 354A, thereby repositioning the link pin 620 toward a lower end portion 652 of the arcuate slot 600K. When the link pin 620 abuts the lower end portion 652 of the arcuate slot 600K, the actuator cam 350 is in a starting rotational position 380.

[0116] Fig.23The annular latch release system 32' is shown in the unactuated state 340, where the actuator cam 350 is in the starting rotational position 380, the double plunger 358 is in the retracted position 384, and the annular latch 28 is in the locked position 180. Additionally, the connecting pin 620 abuts against the lower end portion 652 of the arcuate slot 600K. The guide member 634 is positioned near the upper end portion 654 of the guide slots 600H, 600H'. Referring to Fig.24 , in the unactuated state 340, the plunger engagement pads 514 of the first release plunger 440 and the second release plunger 448 are spaced apart from the associated trigger engagement pads 312A, 312B of the latch retainer 286. Fig.23 and Fig.24 also shows that the annular portion 292 protruding from the latch retainer 286 is in the locked position 180 relative to the locking protrusions 270, 272, 278C of the upper channel member 130 and the fixed long guide rail 22.

[0117] As Fig.23 shown, the actuator cam 350 includes a cam surface 388 having a contact point 390 that contacts the double plunger 358. The contact point 390 between the double plunger 358 and the cam surface 388 defines the current rotational position of the actuator cam 350. The contact point 390 is aligned with the starting position 414A of the actuator cam 350 in Fig.23 . The cam surface 388 extends between a first end 388A and a second end 388B. When the actuator cam 350 is rotated by the Bowden cable 614, different portions 400, 404 of the cam surface 388 contact the double plunger 358. Thus, when the actuator cam 350 rotates, the contact point 390 between the cam surface 388 and the double plunger 358 is repositioned along different portions 400, 404 of the cam surface 388. To describe the relative movement of the actuator cam 350 with respect to the double plunger 358 and the annular latch 28, the cam surface 388 is divided into a starting position 414A, a first transition region 400 extending between the starting contact position 414A and the initial contact position 414B, and a second transition region 404 extending between the initial contact position 414B and the latch release position 414C. The latch release position 414C is generally aligned with or near the second end 388B of the cam surface 388. Without changing the scope of the present invention, the starting position 414A can be aligned with, adjacent to, and / or offset from the first end 388A of the cam surface 388.

[0118] Referring to Fig.23, the radial distance of the cam surface 388 from the axis of rotation 354A at the latch release position 414C is greater than the radial distance from the axis of rotation 354A at the starting position 414A. When the actuator cam 350 rotates, between the starting position 414A and the latch release position 414C, the difference in the radial distance between the cam surface 388 and the axis of rotation 354A is converted into the vertical movement of the double plunger 358. Similarly, the cam surface 388 can be adjusted to produce a desired amount of vertical movement of the actuator cam 350.

[0119] When the annular latch release system 32' is in Fig.23 the unactuated state 340 shown in, the latch release operation is initiated by applying a pulling force to the Bowden cable 614. The pulling force in the Bowden cable 614 causes the link pin 620 to rotate towards the upper end 650 of the arcuate slot 600K, which causes the actuator cam 350 to rotate in the clockwise direction 418, as Fig.23 observed in. When the actuator cam 350 rotates in the clockwise direction 418, the contact point 390 between the double plunger 358 and the cam surface 388 moves along the cam surface 388 through the first transition zone 400 and the second transition zone 404.

[0120] The annular latch release system 32' is shown in Fig.25 and Fig.26 as being in a transitional state 340B, in which the actuator cam 350 is rotated such that the contact point 390 is aligned with the initial contact position 414B of the cam surface 388. The first release plunger 440 and the second release plunger 448 are shown in contact with the trigger engagement pads 312A, 312B of the latch retainer 286, where the annular latch 28 is in the locked position 180. Additionally, the link pin 620 is shown as being spaced apart from both the lower end 652 and the upper end 650 of the arcuate slot 600K. It is also shown that the guide 634 of each of the first plunger guide 610A and the second plunger guide 610B is spaced apart from the upper end 654 of the associated guide slot 600H, 600H'.

[0121] Additional rotation of the actuator cam 350 in the clockwise direction 418 by the Bowden cable 614 causes the contact point 390 between the double plunger 358 and the cam surface 388 to reposition towards Fig. 27 and Fig.28 the latch release position 414C shown in. Referring to Fig. 27, the annular latch release system 32’ is shown in the actuated state 340A, where the actuator cam 350 is in the latch release rotation position 380B, the double plunger 358 is in the extended position 384A, and the annular latch 28 is in the unlocked position 182. In addition, the connecting pin 620 abuts against the upper end 650 of the arcuate groove 600K. The contact point 390 between the double plunger 358 and the actuator cam 350 is aligned with the latch release position 414C. In addition, the guides 634 of the first plunger guide 610A and the second plunger guide 610B are spaced apart from the upper ends 654 of the guide grooves 600H, 600H’. The plunger engagement pads 514 of the first release plunger 440 and the second release plunger 448 of the double plunger 358 are in frictional contact with the corresponding trigger engagement pads 312A, 312B of the latch retainer 286. The rotational movement of the actuator cam 350 causes the double plunger 358 to apply a downward load on the latch retainer 286, thereby moving the latch retainer 286 downward.

[0122] As Fig.28 shown, the downward movement of the latch retainer 286 repositions the annular portion 292 into the gaps 266E, 268E between the locking protrusions 270, 272, 278C and the lower end surfaces 266D, 268D of the U-shaped grooves 266, 268. Accordingly, the annular portion 292 disengages from the locking protrusions 270, 272, 270C in the upper channel member 130 and the fixed long guide 22. When the annular portion 292 disengages from the locking protrusions 270, 272, 270C, the upper channel member 130 can be repositioned along the fixed long guide 22.

[0123] When the annular latch release system 32’ is in Fig. 27 and Fig.28 the actuated state 340A shown and the upper channel member 130 is in the desired position 14’ along the fixed lower guide 22, the latch relocking operation is initiated. In the case where a pulling force is applied to the Bowden cable 614, the annular latch release system 32’ remains in the actuated state 340A. Releasing the pulling force on the Bowden cable 614 initiates the latch relocking operation. The spring 294 attached to the latch retainer 286 spring-biases the latch retainer 286 from Fig.28 the unlocked position 182 shown towards Fig.24 the locked position 180 shown. Accordingly, the spring 294 automatically repositions the annular latch 28 to the locked position 180.

[0124] In addition, a return spring 362 (shown in Fig. 22 ) biases the double plunger 358 towards Fig.23 the retracted position 384 shown. The upward movement of the double plunger 358 presses on the actuator cam 350, thereby causing the actuator cam 350 to move towards Fig.23 rotates from the starting rotational position 380 shown in Fig.23 , where the connecting pin 620 abuts the lower end portion 652 of the arcuate groove 600K. A spring 294 attached to the latch retainer 286 and a return spring 362 coupled between the double plunger 358 and the housing bracket 600 hold the annular latch 28 in the locked position 180 and hold the annular latch release system 32' in the unactuated state 340 until a pulling force is applied to the Bowden cable 614.

[0125] One benefit of the annular latch release system for the long rail assembly is that the annular latch release system eliminates the direct connection between the actuator cam and the release plunger. A second benefit is that the annular latch release system has two contact points between the release plunger and the annular latch to reduce the rotation of the annular latch due to engagement with the release plunger. A third benefit is that the annular latch release system can accommodate misalignment of components, tolerance stack-up, and variations in component dimensions while ensuring proper functioning of the annular latch release system.

[0126] The present invention has been described in an illustrative manner, and it is to be understood that the terms used are of a descriptive nature rather than restrictive. Many modifications and variations of the present invention are possible in light of the above teachings. Thus, it is to be understood that within the scope of the appended claims, the invention may be practiced otherwise than as specifically described.

Claims

1. A guide rail drive assembly for a vehicle seat, the vehicle seat being configured to travel along a fixed long guide rail, the guide rail drive assembly comprising: an upper channel member configured to be displaceable along the fixed long guide rail; a ring latch coupled to the upper channel member, the ring latch including a latch retainer having a first release trigger spaced from a second release trigger, the latch retainer being repositionable between a locked position and an unlocked position, at the locked position, the guide rail drive assembly is interlocked with the fixed long guide rail to prevent movement of the guide rail drive assembly, at the unlocked position, the guide rail drive assembly is displaceable along the fixed long guide rail; and a ring latch release system operatively coupled to the upper channel member, the ring latch release system including: an actuator cam rotatable about a rotation axis between a starting rotation position and a latch release rotation position, and the actuator cam having a cam surface; a double plunger having a first plunger spaced from a second plunger, wherein the first plunger and the second plunger project from a cross member, the double plunger being repositionable between a retracted position and an extended position, at the retracted position, each of the first plunger and the second plunger is spaced from the latch retainer, at the extended position, each of the first plunger and the second plunger engages a corresponding one of the first release trigger and the second release trigger; and a return spring configured to spring bias the cross member of the double plunger toward an engagement position defining a contact point between the cross member and the cam surface of the actuator cam; wherein when the contact point aligns with the starting rotation position of the cam surface, rotating the actuator cam in a first rotation direction causes the contact point to align with the latch release rotation position of the cam surface, causing the double plunger to be repositioned between the retracted position and the extended position; and wherein when the double plunger is in the extended position, the first plunger and the second plunger engage the first release trigger and the second release trigger and actuate the first release trigger and the second release trigger, thereby moving the latch retainer to the unlocked position, and when the double plunger is in the retracted position, the ring latch automatically locks with the fixed long guide rail.

2. The guide rail drive assembly according to claim 1, wherein: the return spring repositions the double plunger from the extended position toward the retracted position when the actuator cam rotates in a second rotation direction from the latch release rotation position aligned with the contact point, wherein the second rotation direction is different from the first rotation direction.

3. The guide rail drive assembly according to claim 2, wherein: each of the first plunger and the second plunger includes a respective first plunger engagement pad and a second plunger engagement pad; Each of the first release trigger and the second release trigger includes a respective first trigger engagement pad and a second trigger engagement pad; and Each of the first plunger engagement pad and the second plunger engagement pad is configured to frictionally engage a respective one of the first trigger engagement pad and the second trigger engagement pad when the dual plungers are repositioned between the retracted position and the extended position.

4. The guide rail drive assembly according to claim 3,[[]]END]] wherein: Each of the first plunger and the second plunger defines a longitudinal axis; and Each of the first plunger engagement pad and the second plunger engagement pad is inclined relative to the respective longitudinal axis.

5. The guide rail drive assembly according to claim 4,[[]]END]] wherein: The latch retainer has a vertical axis extending between opposite top and bottom surfaces of the latch retainer; and Each of the first trigger engagement pad and the second trigger engagement pad is inclined relative to the vertical axis.

6. The guide rail drive assembly according to claim 5,[[]]END]] wherein: The cam surface includes a starting position having a first radial distance from the axis of rotation and a latch release position having a second radial distance from the axis of rotation; The starting position is spaced from the latch release position, and the first radial distance is less than the second radial distance; The contact point is aligned with and frictionally engages the starting position of the cam surface when the actuator cam is in the starting rotational position; and The contact point is aligned with and frictionally engages the latch release position of the cam surface when the actuator cam is in the latch release rotational position.

7. The guide rail drive assembly according to claim 6,[[]]END]] wherein: The dual plungers are decoupled from the actuator cam.

8. The guide rail drive assembly according to claim 7,[[]]END]] wherein: The annular latch has one or more of a plurality of U-shaped annular portions, finger portions, and pins, and one or more of the plurality of U-shaped annular portions, finger portions, and pins are configured to meshingly engage one or more of a plurality of grooves, protrusions, holes, and recesses in the fixed long guide rail when the annular latch is interlocked with the fixed long guide rail.

9. The guide rail drive assembly according to claim 8,[[]]END]] wherein: The cam surface includes a dwell zone adjacent the latch release position; The cross member includes a cutout region that provides clearance for rotation of the actuator cam in the first rotational direction when the contact point is aligned with and frictionally engages the dwell zone of the cam surface; and Rotation of the actuator cam when the contact point is aligned with and frictionally engages the dwell zone of the cam surface holds the dual plungers in the extended position.

10. The guide rail drive assembly according to claim 9,[[]]END]] wherein: The actuator cam is fixedly coupled to a drive shaft aligned with the axis of rotation of the actuator cam; and Rotation of the drive shaft rotates the actuator cam.

11. The guide rail drive assembly according to claim 10,[[]]END]] wherein: The side wall of the upper channel member includes a guiding groove that extends between opposite first and second side portions of the side wall; The latch retainer includes a T-shaped protrusion having a base portion protruding from a main portion of the latch retainer and a head portion extending from the base portion; And wherein the base portion is configured to slide along the guiding groove when the main portion of the latch retainer is adjacent to the first side portion of the side wall and the head portion is adjacent to the second side portion of the side wall.

12. The rail drive assembly according to claim 11, wherein: The double plunger includes an alignment boss; and The double plunger is received and supported by a housing that includes an alignment channel configured to matingly engage with the alignment boss.

13. The rail drive assembly according to claim 8, wherein: The rail drive assembly includes a housing bracket fixedly coupled to the upper channel member, the housing bracket including a first guiding groove and a second guiding groove; The actuator cam is rotatably coupled to the housing bracket; and The double plunger is fixedly coupled to spaced-apart first and second plunger guides that are slidably coupled to respective first and second guiding grooves in the housing bracket.

14. The rail drive assembly according to claim 13, wherein: The actuator cam is rotated by a Bowden cable.

15. The rail drive assembly according to claim 14, wherein: A return spring is operatively coupled between the housing bracket and the double plunger; and The return spring biases the double plunger toward the retracted position.

16. The rail drive assembly according to claim 15, comprising: A connecting pin that protrudes from the actuator cam and is spaced from the rotational axis of the actuator cam, the connecting pin having a distal end that passes through an arcuate slot in the housing bracket, and the Bowden cable being fixedly coupled to the distal end of the connecting pin; and wherein The arcuate slot defines a rotational range of movement of the actuator cam.

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