Abstract:
A seat adjustment mechanism for a vehicle seat including a seat bottom supported by the vehicle and a seatback coupled to the seat bottom is provided. The seat adjustment mechanism includes a first kneel mechanism connected to the vehicle seat and a powered motor operably connected to the first kneel mechanism. The powered motor drives the first kneel mechanism to translate the seatback and seat bottom relative the vehicle to manipulate the seat assembly into a desired configuration.

Description:
FIELD 
     The present teachings relate to a seat assembly and, more particularly, to a seat assembly with recline, fold, kneel, tumble and interlock features. 
     BACKGROUND 
     In automotive applications, it is desirable for a vehicle to accommodate various requirements, such as cargo carrying and the like. To that end, reconfiguration of a vehicle seating system plays a role. Dumping, folding flat, and/or kneeling a seating system are examples of configurations that enable a vehicle interior to accommodate cargo-carrying needs, thus improving storage capability. 
     Seat assemblies typically include a plurality of mechanisms to toggle the seat between a seating position, a reclined position, a dumped position, and a kneel position to allow an occupant to selectively configure the seat assembly as desired. For example, seat assemblies generally include a recliner mechanism for enabling pivotal motion of a seatback relative to a seat bottom. Also, to provide dumping or stowing of the seat assembly, an integrated recliner and floor-latch mechanism may be provided. The recliner mechanism serves to manipulate the seatback relative to the seat bottom. A floor-latch mechanism may extend downwardly from the seat bottom for selective engagement with a floor. After the recliner mechanism reclines the seatback to a fold-flat position, releasing the floor-latch mechanism allows the seat assembly to be rolled or tumbled forward into a dumped position. In addition, the seat assembly may include a kneel mechanism to provide the ability to further articulate a seat to increase cargo area. A kneel mechanism is provided to enable such articulation. A lever actuates the kneel mechanism to cause the seat assembly to lean or kneel forward relative to its normal operating position. 
     The recliner, floor-latch, and kneel mechanisms are typically operated through a remote actuator. The remote actuator serves to selectively actuate the particular mechanism (i.e., recliner, floor-latch, or kneel) to provide a desired seating configuration. For example, an actuation handle may be provided at a remote location from the recliner and floor-latch mechanisms to allow an occupant to manipulate the seat assembly into a desired position. The remote actuator commonly includes a cable tied to the particular mechanism at a distal end and to an actuation handle at a proximal end. The actuation handle is typically rotatably supported by one of the seatback, seat bottom, or vehicle structure such that a force applied to the handle is transmitted to the cable and associated mechanism (i.e., recliner, floor-latch, or kneel). 
     Transmission of the force from the actuation handle to the cable causes the cable to be placed under tension and thereby transmit the force to the particular mechanism. Once the force reaches the mechanism, internal components of the respective mechanism are articulated and the mechanism is toggled into an unlocked position. For example, an actuation handle tied to a recliner mechanism allows an occupant to adjust the angular position of a seatback relative to a seat bottom simply by rotating the actuation handle. The rotational force applied to the actuation handle is transmitted to the recliner mechanism by the cable and serves to disengage the seatback from engagement with the recliner mechanism, thereby placing the recliner mechanism in an unlocked condition. When the recliner mechanism is in the unlocked condition, the occupant is allowed to adjust the angular position of the seatback relative to the seat bottom. A similar actuation handle may be associated with the floor-latch and kneel mechanisms to actuate the respective mechanisms and configure the seat assembly into a desired position. 
     Traditional seat assemblies suffer from a disadvantage that even though the seat assembly may not be properly engaged with the floor or properly engaged in an upright position, the seatback is fully actuable and positionable relative to the seat. As can be appreciated, the floor latch mechanism or kneel mechanism may appear to be fully latched when returned to a usable position when in fact either may be in an unlatched condition. This is particularly true in the case of a kneeling function because the seat assembly is not drastically out of position from its fully latched and secure position. 
     Furthermore, while conventional remote actuation devices adequately provide an occupant with the ability to actuate a seat mechanism such as a recliner, floor-latch, or kneel mechanism, conventional remote actuation devices suffer from the disadvantage of requiring a force to unlock the particular mechanism. As can be appreciated, such forces may be large depending on the configuration of internal locking components of each mechanism and therefore may be difficult to operate. 
     SUMMARY 
     A seat assembly generally includes a seat bottom, a seatback pivotally supported by the seat bottom, and a seat adjustment mechanism. The seat adjustment mechanism may include a kneel mechanism connected to the vehicle seat, a powered motor operably connected to the kneel mechanism and operable to translate the seatback and seat bottom, and a latch mechanism supported by the seat bottom and operable between a locked position and an unlocked position. The latch mechanism may be operated to pivot the seat bottom in the unlocked position. 
     The seat assembly may also include a recliner mechanism pivotably connecting the seatback relative the seat bottom and cooperating with the kneel mechanism to define an angular position of the seatback relative the seat bottom. The recliner mechanism may further cooperate with the kneel mechanism to position the vehicle seat in a dump position. 
     The seat assembly may also include an interlock mechanism restricting actuation of the latch mechanism into the unlocked position until the seat assembly is in a fully kneeled position, and restricting rotation of the seatback when the latch mechanism is in the unlatched position. The interlock mechanism may include a sector plate fixedly supported by the seat bottom and an interlock pin slidably supported by the latch mechanism. The sector plate may include a recess and a cam surface, wherein the recess receives the interlock pin to permit actuation of the latch mechanism and engages the cam surface to prevent actuation of the latch mechanism. 
     The seat may include a link rotatably supported by the sector plate at a first end and rotatably supported by the latch mechanism at a second end, wherein the link is operable to rotate the seatback relative to the seat bottom in response to rotation of the latch mechanism. 
     The kneel mechanism may be a linear adjustment mechanism including a housing and a recliner rod, wherein the recliner rod is operable to reciprocate linearly relative to the housing to position the seat relative to the vehicle. The housing may include a gear assembly in meshed engagement with the recliner rod to provide linear movement of the recliner rod relative to the housing. 
     Further areas of applicability will become apparent from the detailed description provided hereinafter. It should be understood that the detailed description and specific examples are intended for purposes of illustration only and are not intended to limit the scope of the teachings. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The present teachings will become more fully understood from the detailed description and the accompanying drawings, wherein: 
         FIG. 1  is a perspective view of a recliner, floor-latch, and kneel assembly in accordance with the principles of the present teachings; 
         FIG. 2  is a side view of the a recliner, floor-latch, and kneel assembly of  FIG. 1  in a design position; 
         FIG. 3  is a side view of the a recliner, floor-latch, and kneel assembly of  FIG. 1  in a reclined position; 
         FIG. 4  is a side view of the a recliner, floor-latch, and kneel assembly of  FIG. 1  in a fold-flat position; 
         FIG. 5  is a side view of the a recliner, floor-latch, and kneel assembly of  FIG. 1  in a dumped position; 
         FIG. 6  is a perspective view of a floor-latch mechanism in accordance with the principles of the present teachings; 
         FIG. 7  is an exploded view of the floor-latch mechanism of  FIG. 6 ; 
         FIG. 8  is a plan view of the floor-latch mechanism of  FIG. 6  with part of a housing removed to show the internal workings of the latch mechanism in a latched position; 
         FIG. 9  is a plan view of the floor-latch mechanism of  FIG. 6  with part of the housing removed to show the internal workings of the latch mechanism in an unlatched position; 
         FIG. 10  is a perspective view of a kneel mechanism in accordance with the principles of the present teachings; 
         FIG. 11  is an exploded view of the kneel mechanism of  FIG. 10 ; 
         FIG. 12  is a side view of the recliner, floor-latch, and kneel assembly incorporated into a seat assembly and in a design position; 
         FIG. 13  is a side view of the seat assembly of  FIG. 12  in a reclined position; 
         FIG. 14  is a side view of the seat assembly of  FIG. 12  in a fold-flat position; and 
         FIG. 15  is a side view of the seat assembly of  FIG. 12  in a dumped position. 
     
    
    
     DETAILED DESCRIPTION 
     The following description is merely exemplary in nature and is in no way intended to limit the teachings, its application, or uses. 
     With reference to  FIGS. 1–5 , a combination recliner, floor-latch, and kneel (RFK) assembly  10  for use with a seat assembly is provided. The RFK  10  is operable in a first mode to adjust the inclination of a seatback relative to a seat bottom. The RFK  10  is operable in a second mode to enable forward folding of a seatback relative to a seat bottom. The RFK  10  is operable in a third mode to allow passenger ingress and egress by forward dumping of the seat assembly. 
     The RFK assembly  10  includes operably interconnected first and second RFK halves  12 ,  14 . The halves  12 ,  14  include first and second recliner mechanisms  16 ,  18 , first and second floor-latch mechanisms  20 ,  22 , and first and second kneel mechanisms  24 ,  26 . The floor-latch mechanisms  20 ,  22  are adopted to selectively engage a pair of strikers  28  disposed on a pair of floor brackets  30 . Such engagement serves to restrict rotation of the RFK  10  about a forward pivot  34 , as shown in  FIGS. 1–5  and  12 – 15 . The kneel mechanisms  24 ,  26  are pivotably supported by the floor brackets  30  and serve to initiate articulation of the RFK  10 , as will be described in more detail below. 
     The first and second recliner mechanisms  16 ,  18  each include a link  40  extending from the floor-latch mechanisms  20 ,  22  to one of a pair of seatback supports  36 . Each link  40  includes a first end having a seat attachment aperture  42  and a second end having a latch attachment aperture  44 . The seat attachment apertures  42  are rotatably attached to their respective seatback support  36  by a pivot  46 . Similarly, the latch attachment apertures  44  are rotatably attached to their respective floor-latch mechanism  20 ,  22  by a pivot  46 . It should be appreciated that the floor latch mechanisms  20 ,  22  are identically constructed and, therefore, only a single floor latch mechanism  20  will be described in detail herein. 
       FIG. 7  depicts pivot  46  including a central cylindrical section  48  and flanking cylindrical sections  50 . The central cylindrical section  48  includes a reaction surface  52  and is rotatably received by the latch attachment aperture  44  in the link  40 . The flanking cylindrical sections  50  are fixedly received by attachment apertures  51  in the latch mechanism  20 . Each floor latch mechanism  20 ,  22  includes a first housing plate  54 , a second housing plate  56 , a claw  58 , a cam plate  60 , and a sector plate  62 . The claw  58 , cam plate  60 , and sector plate  62  are operably supported between the first and second housing plates  54 ,  56  and cooperatively serve to toggle the floor latch mechanisms  20 ,  22  between a locked position (shown in  FIG. 8 ) and an unlocked position (shown in  FIG. 9 ). 
     The first and second housing plates  54 ,  56  include a first extension  64 , a second extension  66 , and a striker recess  68 . The first extension  64  includes an attachment aperture  70 , a slot  72 , and a pivot aperture  74 . The second extension  66  includes attachment aperture  51  for rotatably attaching the link  40  to the latch mechanisms  20 ,  22 . In addition, each housing plate  54 ,  56  includes an attachment aperture  76 , and a spring slot  78 , both disposed generally between the striker recess  68  and the second extension  66 . 
     The claw  58  includes a main body  80  having a central aperture  82 , an extension  84  having an engagement surface  86 , a striker recess  88 , and a spring aperture  90 . The central aperture  82  receives a pivot  92  having a central cylindrical section  94 , a cylindrical section  96 , and a shoulder  98 . The central cylindrical section  94  includes an outer diameter generally greater than an outer diameter of the central cylindrical section  96  and generally smaller than an outer diameter of the shoulder  98 . The pivot  92  is disposed through the attachment apertures  76  of the first and second housing plates  54 ,  56  and the central attachment aperture  82  of the claw  58 . In this manner, the claw  58  is rotatably supported between the first and second housing plates  54 ,  56  and rotates about the outer diameter of the central cylindrical section  94 . In addition to rotatably supporting the claw  58  between the first and second housing plates  54 ,  56 , the pivot  92  further serves to hold the first housing plate  54  in spaced relationship to the second housing plate  56 . 
     The shoulder  98  on the pivot  92  abuts an outer surface of the second housing plate  56  to restrict travel of the pivot  92  through the attachment aperture  76 . The cylindrical section  96  of the pivot  92 , therefore, extends through attachment aperture  76  of the first housing plate  54  such that the central cylindrical section  94  extends between inner surfaces of the first and second housing plates  54 ,  56 . In this regard, the central cylindrical section  94  is disposed generally between the first and second housing plates  54 ,  56  and serves as a spacer therebetween. 
     The extension  84  of the claw  58  is integrally formed with the main body  80  generally opposite from the striker recess  88 , as best shown in  FIG. 7 . The striker recess  88  includes an engagement surface  100  designed to matingly receive the striker  28  and lock the floor latch mechanism  20 . 
     The cam plate  60  includes a central aperture  102 , a first extension  104 , and a second extension  106 . The central aperture  102  includes a pair of flats  108  for engagement with a pivot  110 . The first extension  104  includes a first reaction surface  112  and a second reaction surface  114 . The second extension  106  includes a reaction surface  116  generally opposing the second reaction surface  114  of the first extension  104 . A recess  118  is formed generally between the second reaction surface  114  of the first extension  104  and the reaction surface  116  of the second extension  106 . The recess  118  is adapted to selectively receive extension  84  of the claw  58  when the claw  58  is in the unlocked position illustrated in  FIG. 9 . 
     As previously discussed, the central aperture  102  of the cam plate  60  receives the pivot  110  such that the cam plate  60  is rotatably supported between the first and second housing plates  54 ,  56 . The pivot  110  includes a first cylindrical section  120  having flats  122 , a second cylindrical section  124 , a third cylindrical section  126  having flats  128 , a fourth cylindrical section  130 , and a key portion  132 . The pivot  110  is rotatably received through attachment aperture  74  of the first and second housing plates  54 ,  56  such that the pivot  110  rotates about the third and fourth cylindrical sections  126 ,  130 . In this manner, the second cylindrical section  124  is disposed generally between the first housing plate and the second housing plate  54 ,  56  and matingly receives the central aperture  102  of the cam plate  60 . Specifically, the flats  128  of the third cylindrical section  126  matingly engaged flats  108  of the central aperture  102  such that the cam plate  60  is fixed for rotation with the pivot  110 . The pivot  110  rotates relative to the first and second housing plates,  54 ,  56  about the second and fourth cylindrical sections  124 ,  130 . In this manner, the first cylindrical section  120  and keyed portion  132  extend from the first and second housing plates  54 ,  56 , respectively. 
     The first cylindrical section  120  of the pivot  110  matingly receives an actuation handle  134 , while the keyed portion  132  fixably receives a cross bar  136 . The actuation handle  134  provides an occupant with the ability to apply a force directly to the cam plate  60 , pivot  110 , and cross bar  136 . The actuation handle  134  is generally L-shaped and includes a raised portion  138  and a recess portion  144 . The raised portion  138  includes an attachment aperture  140  and a spring aperture  142 . The recess portion  144  includes an attachment aperture  146 . The attachment aperture  146  includes a pair of flats  148  for matingly engaging the flats  122  of pivot  110 . In this manner, the actuation handle  134  is fixed for rotation with the cam plate  60  through interaction between flats  148  on the actuation handle  134  and the flats  122  on the pivot  110 . A spring  150  rotationally biases the actuation handle  134  in the counterclockwise direction (CCW) relative to the view shown in  FIGS. 8 and 9 . The spring  150  includes a central coiled body  152  and first and second ends  154 ,  156 . The first end  154  is received by the spring aperture  142  in the actuation handle  134 , while the second end  156  is received by a spring post  158 . 
     The spring post  158  is received in spring aperture  90  of the claw  58 , as best shown in  FIGS. 8 and 9 . In this manner, the spring  150  extends between the actuation handle  134  and the claw  58  to bias the actuation handle  134  in the counterclockwise direction relative to the view shown in  FIGS. 8 and 9 . Therefore, the spring  150  also biases the claw  58  in the clockwise direction. 
     The sector plate  62  includes a main attachment aperture  160 , a cam surface  162 , and a notch  164 . The main attachment aperture  160  receives a pivot  46  and serves to rotatably support the first and second housing plates  54 ,  56 . Specifically, the cylindrical sections  50  of the pivot  46  are received by the attachment apertures  70  in the first and second housing plates  54 ,  56  while the central cylindrical section  48  is rotatably received by the main attachment aperture  160  in the sector plate  62 . In this manner, the first and second housing plates  54 ,  56  rotate about the reaction surface  52  of the pivot  46  relative to the sector plate  62 . 
     Each floor latch mechanism  20 ,  22  further includes an interlock mechanism  166  that selectively restricts rotation of the claw  58 , cam plate  60  and actuation handle  134 . The interlock mechanism  166  includes a interlock cam  168  having a pair of guides  170  and first and second reaction surfaces  172 ,  174 . The interlock cam  168  is slidably received within slots  72  in the first and second housing plates  54 ,  56 . Specifically, the guides  170  are disposed in the respective slots  72  in the first and second housing plates  54 ,  56  to guide movement of the interlock cam  168 . In a first position, the interlock cam  168  engages the cam plate  60  such that the first reaction surface  172  contacts the first extension  104  of the cam plate  60 . In a second position, the interlock cam  168  contacts the sector plate  62  such that the second reaction surface  174  contacts the cam surface  162  thereon. 
     With particular reference to  FIGS. 8 and 9 , the operation of the first and second floor latch mechanisms  20 ,  22  will be described.  FIG. 8  depicts the floor latch mechanism  20  in a locked condition such that the claw  58  engages the striker  28 . To unlock the floor latch mechanism  20 , a clockwise force is applied to the actuation handle  134  generally proximate to attachment aperture  140 . However, because the floor latch mechanism  20  is positioned such that the interlock cam  168  is aligned with the cam surface  162  of the sector plate  62 , operation of the floor latch mechanism,  20 ,  22  from the locked condition to the unlocked condition is prohibited. 
     Specifically, when the clockwise force is applied to the actuation handle  134  causing it to rotate in the clockwise direction, the first extension  104  of cam plate  60  rotates and contacts the first reaction surface  172  of the interlock cam  168 . This causes the interlock cam  168  to slide within slots  72  of the first and second housing plates  54 ,  56 . The second reaction surface  174  of the interlock cam  168  engages the cam surface  162  of the sector plate  62 , thereby prohibiting further rotation of the cam plate  60 . 
     Because the cam plate  60  is restricted from further rotation, the first reaction surface  112  of the cam plate  60  remains in contact with the engagement surface  86  of the claw  58 . In this manner, the claw  58  is restricted from rotating in the clockwise direction relative to the view shown in  FIG. 8  and, thus, will not release from the striker  28 . 
     However, when the interlock cam  168  is co-aligned with the notch  164  in the sector plate  62  (as shown in  FIG. 9 ), further rotation of the cam plate  60  is enabled, thereby enabling rotation of the claw  58  out of engagement with the striker  28 . To co-align the interlock cam  168  with the notch  164  of the sector plate  62 , the entire floor latch mechanism  20 ,  22  is rotated about pivot  46  in the sector plate  62  to the position illustrated in  FIG. 9 . 
     Once the notch  164  is co-aligned with the interlock cam  168 , a clockwise force may be applied to the actuation handle  134  causing the cam plate  60  to rotate in the clockwise direction. Upon sufficient rotation of the actuation handle  134 , the first reaction surface  112  of the cam plate  60  disengages the engagement surface  86  of the claw  58  allowing the claw  58  to rotate to the position illustrated in  FIG. 9 . 
     Once the claw  58  is sufficiently rotated, the striker  28  disengages the striker recess  88  and the floor latch mechanisms  20 ,  22  can rotate into the unlocked position. To restrict over rotation of the claw  58 , the second extension  106  of the cam plate  60  contacts extension  84  of the claw  58 . Specifically, the engagement surface  86  of the claw  58  contacts the reaction surface  116  of the cam plate  60 , thereby holding the claw  58  in the unlocked position. 
     It should be noted, that rotation of the cam plate  60  in the clockwise direction relative to the view shown in  FIGS. 8 and 9  causes the first extension  104  of the cam plate  60  to contact the first reaction surface  172  of the interlock cam  168 , thereby causing the interlock cam  168  to slide within slot  72  of the first and second housing plates  54 ,  56 . Therefore, the second reaction surface  174  of the interlock cam  168  engages the notch  164  in the sector plate  62 . This provides enough clearance for the cam plate  60  to rotate in the clockwise direction and disengage the claw  58 , as described above. 
     To return the floor latch mechanism  20  to the locked position, it is brought into proximity with the striker  28 , such that the striker  28  is received by the striker recess  88  in the claw  58 . A force is then exerted on the floor latch mechanisms  20  such that the striker  28  engages the striker recess  88 . Once the striker  28  engages the striker recess  88 , the claw  58  rotates in the counterclockwise direction relative to the view shown in  FIGS. 8 and 9 . Once the claw is sufficiently rotated in the counterclockwise direction, the striker  28  forcingly engages the engagement surface  100  of the striker recess  88  and places the floor latch mechanism  20  in the locked position. The cam plate  60  is rotated in the counterclockwise direction relative to the view shown in  FIGS. 8 and 9  by the spring  150 . This holds the floor latch mechanism  20  in the locked position. Specifically, as the claw  58  rotates in the counterclockwise direction, the extension  84  is removed from the recess  118  in the cam plate  60  and provides a clearance for the cam plate  60  to rotate under bias of the spring  150 . 
     Once the cam plate  60  and actuation handle  134  are rotated sufficiently in the counterclockwise direction, the first reaction surface  112  of the cam plate will once again contact the engagement surface  86  of extension  84  and lock the cam plate  60  and claw  58  in the locked position, thereby holding the floor latch mechanism  20  in the locked position. 
     As previously discussed, the floor latch mechanisms  20 ,  22  must be pivoted about the floor brackets  30  such that the interlock cams  168  are co-aligned with notches  164  in the sector plates  62  to be toggled into the unlocked position. This pivoting of the floor latch mechanisms  20 ,  22  is achieved via the first and second kneel mechanisms  24 ,  26  depicted in  FIGS. 1 ,  10  and  11 . The first and second kneel mechanisms  24 ,  26  rotate the first and second floor latch mechanisms  20 ,  22  to adjust the relative rotational position between the sector plate  62  and floor latch mechanisms  20 ,  22  to thereby position the interlock cam  168  into alignment with notch  164 . Specifically, the first and second kneel mechanisms  24 ,  26  rotate the first and second latch mechanisms  20 ,  22  about strikers  28  during rotation of the seatback and seat bottom supports  36 ,  38  relative to the floor bracket  30 , as will be discussed further below. 
     The first and second kneel mechanisms  24 ,  26  adjustably control reclining movement of the seatback supports  36  relative to the seat bottom support  38  through cooperation with the first and second recliner mechanisms  16 ,  18  to provide a desired angular position of the seatback supports  36  relative to the seat bottom supports  38 . In addition, the kneel mechanisms  24 ,  26  further cooperate with the first and second recliner mechanisms  16 ,  18  to articulate the seatback supports  36  into a fold-flat position while concurrently kneeling the RFK  10  into a kneeled position relative to the floor bracket  30 , as best shown in  FIG. 4 . 
     With particular reference to FIGS.  4  and  10 – 13 , the first and second kneel mechanisms  24 ,  26  will be described. However, it should be appreciated that the first and second kneel mechanism  24 ,  26  are of identical construction and, therefore, only kneel mechanism  24  will be described in detail. 
       FIGS. 10 and 11  depict kneel mechanism  24  including a drive mechanism  190 , a driven mechanism  192 , and a transmission assembly  194  for supporting and inter-engaging the drive mechanism  190  and the driven mechanism  192 . The drive mechanism  190  includes a powered motor  186  (shown in  FIG. 1 ) drivingly connected by a drive cable (not shown) to a transmission rod  196  which is journalled for rotation in the transmission assembly  194 . The transmission rod  196  includes a worm gear  198  formed coaxially thereon adjacent a first end  200  thereof. At an opposite second end  202 , the transmission rod  196  is generally smooth. The second end  202  also includes an end face having a recess for receiving the drive cable that is rotationally driven by the drive motor. 
     The driven mechanism  192  includes an elongated threaded recliner rod  204  including a first end defining a flat surface  206  having an aperture  208 . The body of the recliner rod  204  coaxially mounts a spring  210  between a washer  212  and a sleeve  214 . The threaded recliner rod  204  is received by the transmission assembly  194  for driving inter-engagement with the worm gear  198  of the drive mechanism&#39;s transmission rod  196 . In this way, the recliner rod  204  axially moves through transmission assembly  194  upon actuation of the drive motor to provide the desired linear motion. 
     The transmission assembly  194  generally includes a mounting assembly having an outer plate  216  and an inner plate  218  that are cooperatively configured to accommodate a gear retainer assembly  220  therebetween. The outer and inner plates  216 ,  218  are preferably constructed of a high strength stamped metal or high carbon such as SAE 1050-1055 steel. When assembled, the outer and inner plates  216 ,  218  house the gear retainer assembly  220  in a high load carrying assembly having a relatively small packaging volume. As generally discussed above, the gear retainer assembly  220  interconnects the transmission rod  196  and the threaded recliner rod  204  for angularly positioning the supports  176  and floor latch mechanisms  22 ,  24  relative to the floor brackets  30 . 
     The outer plate  216  is a generally U-shaped member having a central portion  222  joining first and second opposed legs  224 ,  226 . The first and second legs  224 ,  226  have aligned apertures  228  therethrough for alignment with similar apertures to the inner plate  218 . The central portion  222  of the outer plate  216  includes an aperture  230  to allow the threaded recliner rod  204  access to the gear retainer assembly  220 . The central portion  222  also includes a pair of apertures for receiving fasteners to secure the outer and inner plates,  216 ,  218 , together. 
     The inner plate  218  is shaped similar to the outer plate  216  and includes a central portion  232  flanked by first and second opposed legs  234 ,  236 . The first and second opposed legs  234 ,  236  have aligned apertures  238  therethrough for alignment with the apertures  228  of the outer plate  216 . Also, the central portion  232  includes an aperture  240  therethrough that is alignable with aperture  230  in the outer plate  216  to accommodate axial movement of the threaded recliner rod  204  through the gear retainer assembly  220 . 
     When assembled, the first and second legs  224 ,  226  of the outer plate  216  overlap the first and second legs  234 ,  236  of the inner plate  218 , as illustrated in  FIG. 10 . The gear retainer assembly  220  is sandwiched between the central portions  222 ,  232  of the inner and outer plates,  218 ,  216 , respectively. 
     The mounting assembly also includes trunion bushings  248  mounted in the aligned apertures  228 ,  238  of the legs  224 ,  226  of the outer plate  216  and the legs  234 ,  236  of the inner plate  218 , respectively. The trunion bushings  248  help secure the outer plate  216  to the inner plate  218 , thereby securing the gear retainer assembly  220  therebetween. More specifically, the trunion bushings  248  include apertures  250  for receiving a fastener  252  for mounting the transmission assembly  194  to the floor bracket  30 . The fasteners  252  are received through apertures  254  in the floor bracket  30  and threadably engage the nuts  256 . 
     The gear retainer assembly  220  includes a gear housing  258 , a helical nut gear  246 , a thrust bearing  244 , and a doubler plate  242 . The gear housing  258  includes a drive mechanism passage  260 , a gear cavity  262 , and a driven mechanism passage  264  that each communicate with one another to allow the operative interconnection of the drive and driven mechanisms  190  and  192 . The gear cavity  262  and the driven mechanism passage  264  are coaxially aligned. The drive mechanism passage  260  is perpendicular to the gear cavity  262  and driven mechanism passage  264 . More particularly, the drive mechanism passage  260  is configured to receive and support the transmission rod  196  while the driven mechanism passage  264  is spaced from and generally perpendicular to drive mechanism passage  260  to accommodate the threaded recliner rod  204 . The gear cavity  262  extends radially outward from the axis of the driven mechanism passage  264  to communicate with the drive mechanism passage  260  and accommodate the helical nut gear  246  and the thrust bearing  244 . The gear housing  258  is preferably formed from a polymeric material and, more preferably, an injected molded plastic. Most preferably, the plastic material is nylon. However, it should be appreciated that a variety of other high compressive strength, toughness and wear-resistant materials generally known in the arm may be used to form the gear housing  258 . By forming the gear housing  258  of a polymeric material, the overall weight of the linear kneel mechanisms  24 ,  26  are significantly reduced. Moreover, the configuration of the respective passages and cavities within the gear housing, as well as the light weight yet high strength provided by the plates  216  and  218 , securely interconnect the operative components of the transmission assembly  194 . 
     Disposed through the gear retainer assembly is a recliner rod passage for accommodating the linear displacement of the recliner rod  204 . The recliner rod passage is defined by a threaded opening  266  through the helical nut gear  246 , the driven mechanism passage  264 , and the coaxially aligned apertures in the thrust bearing  244  and plates  242 ,  216  and  218 . 
     An outer surface of the helical nut gear  246  is drivingly engaged by the worm gear  198  of the transmission rod  196 . The threaded opening  266  in the helical nut gear  246  is drivingly engaged by the recliner rod  204 . The thrust bearing  244  is coaxially mounted on the helical nut gear  246 , while the nut gear  246  is received within the gear cavity  262  of the gear housing  258  such that the helical nut gear  246  is disposed in a proper position for rotation within the gear retainer assembly  220 . The thrust bearing  244  is a ring-shaped member having a tab extending diametrically from an outer diameter surface thereof. The tab is received into a notch on the gear retainer assembly  220 . Therefore, the thrust bearing prevents axial displacement of the helical nut gear  246 , but permits the helical nut gear  246  to rotate within the gear retainer assembly  220 . Furthermore, the doubler plate  242  is held in position abutting the opposite side of the helical nut gear  246  by the central portion  222  of the outer plate  216 . 
     It should be noted that the first and second kneel mechanisms  24 ,  26  are preferably constructed in a similar fashion to the linear recliner mechanisms as disclosed in assignee&#39;s commonly-owned U.S. Pat. No. 6,322,146, the disclosure of which is incorporated herein by reference. 
       FIGS. 12–15  depict a vehicle seat  268  including a seatback  270 , a seat bottom  272 , and a RFK  10 . The seatback  270  is fixedly attached to the pair of seatback supports  36 . The seat bottom  272  is fixedly attached to the seat bottom supports  38 . 
       FIG. 12  depicts the vehicle seat  268  in a design position. During operation, a passenger activates the motor  186  that is operably attached to the drive mechanism  190  of the kneel mechanisms  24 ,  26 . The transmission rod  196  including the worm gear  198  of the drive mechanism  190  rotates within the gear housing  258 . The worm gear  198  meshingly engages the helical nut gear  246 , thereby causing the helical nut gear  246  to rotate relative to the gear housing  258 . The threaded opening  266  of the helical nut gear  246  threadably engages the threaded recliner rod  204 . The rotation of the helical nut gear  246  causes the threaded recliner rod  204  to linearly displace relative to the gear housing  258  toward a kneeling position illustrated in  FIG. 14 . As illustrated in  FIG. 14 , the linear displacement of the threaded recliner rod  204  causes the front supports  176  to pivot or kneel in the counter-clockwise direction relative to the floor brackets  30 . This causes the seat bottom supports  38  to displace forward, as well as downward, relative to the floor brackets  30 . Additionally, the seat bottom supports  38  cause the first and second housing plates  54 ,  56  of the floor latch mechanisms  20 ,  22  to pivot in the counter-clockwise direction relative to the floor brackets  30 . This causes the links  40  to displace upward and to the left relative to the floor brackets  30 . The links  40  thereby apply a moment to the seatback supports  36 . The moment causes the seatback supports  36  to pivot in the counter-clockwise direction and into the fold flat position illustrated in  FIG. 14 . 
       FIG. 15  illustrates the vehicle seat  268  in a dumped position. To achieve the dumped position, the vehicle seat  268  must first be configured into the fold flat position illustrated in  FIG. 14 . Therefore, it is important to note that, as described above, the pivotal displacement of the floor latch mechanisms  20 ,  22  relative to the floor brackets  30  causes the interlock cam  168  of the interlock mechanism  166  to become co-axially aligned with the notch  164  in sector plate  62 . Therefore, a passenger may apply a counter-clockwise force relative to the view shown in  FIG. 14  to the actuation handle  134  to disengage the floor latch mechanisms  20 ,  22  from the strikers  28 . As described above with reference to  FIGS. 6–9 , such a force causes the actuation handle  134  to rotate the cam plate  60  into engagement with the interlock cam  168 , thereby displacing the interlock cam  168  within slots  72  of the first and second housing plates  54 ,  56  and into the notch  164  of the sector plate  62 . It should be appreciated that rotation of the actuation handle  134  attached to the second floor latch mechanism  22  also actuates the first floor latch mechanism  20  via the crossbar  136  illustrated in  FIG. 1 . Therefore, regardless of which floor latch mechanism  20 ,  22  the actuation handle is attached to, both actuate concurrently. Therefore, as the actuation handle  134  rotates the cam plates  60  the claws  58  are also rotated via the springs  150 . The springs  150  rotate the claws  58  out of engagement with the strikers  28 . With the claws  58  disengaged from the strikers  28 , the vehicle seat  268  is free to be pivoted about the front supports  176  and into the dumped position illustrated in  FIG. 15 . To return the vehicle seat  268  to the fold flat position illustrated in  FIG. 14 , the vehicle seat  268  is simply pivoted about the front supports  176  such that the floor latch mechanisms  20 ,  22  are in close proximity to the strikers  28 . The strikers  28  are then received in the striker recesses  68  of the claws  58  causing the floor latch mechanisms  20 ,  22  to engage the striker plate. Additionally, a passenger may activate the motor operably attached to the kneel mechanisms  24 ,  26  to transition the vehicle seat  268  from the fold flat position illustrated in  FIG. 14  to the design position illustrated in  FIG. 12 . 
     The description is merely exemplary in nature and, thus, variations are intended to be within the scope and not as a departure from the spirit and scope of the teachings.