Abstract:
A vehicle-sensitive retractor is provided that can be mounted in a reclinable seat back which has a nominal position inclined to the vertical and that is actuated to a locked position in each of three mutually-perpendicular planes. The retractor has a universal acceleration sensor that compensates for different seat back inclinations so that it does not lock until a threshold vehicle acceleration condition is detected, and so that it will lock regardless of the sensed acceleration when the seat back and retractor are shifted to specified inclinations forward and rearward from the seat back nominally inclined position. The sensor preferably includes a weighted basket that supports an inertia member. At the rearward inclination position, the inertia member operates an actuating mechanism to lock the retractor. A stop engages and prevents adjustment of the support at the seat back&#39;s forwardmost inclined position so that at a predetermined angular distance forward therefrom, e.g. 22°, the inertia member causing locking of the retractor before reaching the specified forward inclination position from the design position where the retractor must be locked.

Description:
This is a continuation of prior application Ser. No. 09/181,284, filed Oct. 28, 1998, now abandoned which is hereby incorporated herein by reference in its entirety. The entire disclosure of the prior application, from which a copy of the oath or declaration is supplied under paragraph 3 below, is considered as being part of the disclosure of the accompanying application, and is hereby incorporated by reference therein. 
    
    
     FIELD OF THE INVENTION 
     The invention relates to seat belt retractors and, more particularly, to seat belt retractors having universal acceleration sensors for use in reclinable seat backs. 
     BACKGROUND OF THE INVENTION 
     There are regulations currently in place in the U.S. that mandate certain retractor locking requirements which specify that acceleration sensors must be operable to lock the retractor at either one of two conditions. The first condition requires that at threshold accelerations of 0.7 g&#39;s, the sensor should cause locking of the retractor in any of three mutually-perpendicular planes. In these planes, the retractor must also lock at the specified acceleration when tilted at 45° increments to a range of 180° in the plane. 
     Automobiles are manufactured with their seat backs at a nominal design and installed position from which they can be shifted and tilted forwardly and rearwardly to respective maximum forward and rearward inclinations of the seat backs. Accordingly, §209 specifies that if the first condition is not met by the seat back retractor, the other alternative condition that must be satisfied is that the retractor lock when tilted forward or rearward 45° from the design position of the seat back. Where the retractor has the previously-described types of inertia members that may not satisfy the first condition of §209 in properly detecting vertically aligned accelerations, the second condition where locking must be present at 45° from the design position of the seat back must be established. 
     One of the difficulties in providing a commercially successful, inclinable retractor being shifted with a changing of the seat inclination is maintaining the sensitivity of the retractor locking mechanism, which typically means keeping the gap between the pawl and ratchet teeth at a constant distance. This is difficult because the inertia weight is often carried in a pivotal support and shifts relative to the pawl, which is mounted on a stationary support. The retractor locking mechanism&#39;s sensitivity should be substantially the same when the inertia member is at the nominal seat back position or when swung through almost 45° as when closely adjacent the rearward inclination position. 
     While there have been a number of prior art acceleration universal sensors designed for use in reclinable seat backs, many of these use inertia members that will not shift properly to sense accelerations in an aligned vertical plane. Further, none of these prior art universal inertia sensors successfully meet the specifications that require locking of the retractor at specified angular range of 45° its position at installation, i.e., its designed position. 
     SUMMARY OF THE INVENTION 
     In accordance with the present invention, a retractor may be mounted on an inclinable seat back; and the retractor locks at specified forward and rearward inclinations. More specifically, the retractor incorporates a universal acceleration sensor that compensates for different seat back inclinations so that it does not lock until a threshold vehicle acceleration condition is detected, and so that it will lock regardless of the sensed acceleration when the seat back and retractor are or were shifted or specified inclinations forward and rearward from the seat back inclined designed position. In this manner, the vehicle sensitive retractor herein is particularly tailored to meet automotive specifications that require retractor locking at specified angular inclinations on either side of the seat back design position. 
     Typically, prior seat belt retractors having universal sensors typically allow for equal inclinations from one side to the other of a vertical plane such that, unlike the present retractor, they are not specifically tailored to ensure locking at specific angles forward and rearward from a designed and installed position of the seat back. The design and installed inclined position of the seat back is the inclined position at which it comes delivered from the manufacturer, e.g. 18.5° from vertical. For different manufacturers or vehicles, the retractor is designed to be operated at a specific installed position that is predetermined and known, usually vertical when mounted on a pillar or the like or inclined to the vertical when mounted on a seat. The particular specification at hand requires that the retractor be locked at 45° forward and rearward from an inclined design position such that where the design position is at 18.5°, the retractor must be locked at 63.5° inclined rearwardly from the vertical. 
     In one form of the present invention, the vehicle sensitive retractor herein includes an inertia sensor that has a pivotally mounted universal support that is biased to remain substantially vertical as the seat back is tilted forwardly and rearwardly on either side of the design position. Stops engage the support to stop pivoting of the support when engaged therewith. An actuator mechanism locks the retractor reel either by operation of the inertia member, or when the retractor is reclined to a predetermined rearward inclination position. The rearward inclination position is designed so that it is at an angular spacing from the designed and installed position of the seat back that substantially corresponds to that set forth in the previously-described retractor locking specifications. As the seat back and retractor thereon are pivoted downwardly from the inclined design position, a distal projection on the actuating mechanism locks the retractor reel either by operation of the inertia member, or when the retractor is reclined to a predetermined rearward inclination position. The rearward inclination position is designed so that it is at an angular spacing from the designed and installed position of the seat back that substantially corresponds to that set forth in the previously-described retractor locking specifications. As the seat back and retractor thereon are pivoted downwardly from the inclined design position, a distal projection on the actuating mechanism causes a locking of the retractor. 
     The support engages the other stop when the retractor and seat back are shifted forwardly of the design position to a predetermined forward inclination position. At this position, the actuator mechanism will not lock the retractor until the inertia member senses at least a 0.7 g acceleration. As previously mentioned, the relevant retractor locking specifications mandate locking at a predetermined angular spacing forward of the design position, as well. Once the support hits the other stop, upon continued pivoting of the retractor past this point towards the vertical and then inclined back on the other side of the vertical, the retractor acts like a normal retractor so that the continued pivoting causes the inertia member to become less stable and more prone to actuation as the support and inertia member now pivot with the retractor. The particular inertia member will become operable as by toppling over where a standing man kind of inertia member is utilized at a predetermined amount of pivoting thereof. The position of the forward stop is predetermined and the inertia member is chosen so that the amount of pivoting before it becomes operable will be well within the forward limit set by the retractor locking specifications. And because this limit will generally be on the side of the vertical beyond which the seat back will not be pivoted, it is acceptable to rely on the inertia member to operate the actuating mechanism for locking the retractor as sensitivity variances caused by pivoting of the inertia member and support will not be of a concern. 
     On the other hand, sensitivity is an important issue on the side of the vertical where the seat back will be used and pivoted between different positions. On this operative side, it is important that the inertia sensor used with the retractor maintain substantially the same sensitivity to accelerations throughout substantially the entire range of seat back inclinations. In this regard, preferably the stops are arranged so to correspond to the forward the rearward limits of seat back inclinations so that throughout the operative range of seat back inclinations, the universal support pivots relative to the retractor and stays substantially vertical and keeps the inertia member in its predetermined positioned supported thereby which, with a standing man, is in an upright non-pivoted position. Since the rearward inclination position is on this operative side of the vertical, instead of relying on the inertia member to lock the retractor at the mandated angular distance from the design position, the actuator mechanism is constructed so that it will lock the retractor without operation of the inertia member to keep the sensitivity of the sensor to accelerations substantially the same throughout the entire range of seat back inclinations. 
     In a preferred form of the invention, a seat belt retractor is provided having a inertia sensor for being mounted to a reclinable seat back in a vehicle. The retractor can include a rotatable reel carrying a toothed wheel for rotation therewith. An inertia sensor is provided and includes a pendulum assembly for staying in a substantially vertical orientation as the seat back is inclined through a predetermined angular range having as limits predetermined forward and rearward inclinations of the seat back. An inertia member is supported in a predetermined position by the pendulum assembly as the seat back is inclined through the predetermined angular range and shifts from the predetermined position in response to a predetermined vehicular acceleration for locking of the retractor reel. A housing support pivotally mounts the pendulum assembly and is fixed to the retractor so that as the retractor changes inclination with adjustments to the seat back, the pendulum assembly pivots relative to the housing support to maintain its vertical orientation. A primary actuator is provided for being shifted by the inertia sensor at the predetermined vehicular acceleration, and a secondary actuator is provided for being shifted by the primary actuator to lock the toothed wheel to stop rotation of the reel when the inertia member shifts from its predetermined position, and when the sat back is reclined to its rearward limit without shifting of the primary actuator or the inertia member. 
     A significant feature of the present invention lies in the provision of the aforesaid primary and secondary actuators that are constructed so that at the rearward limit of the seat back inclinations, the secondary actuator will be shifted into locking engagement with the retractor reel without shifting of the primary actuator or of the inertia member. Thus, as the seat back approaches its limit of being inclined in a rearward direction, it will be locked regardless of whether the inertia member has shifted. In this manner, the sensitivity of the inertia member is not made to vary as there is no reliance on shifting of the inertia member to cause retractor locking at the rearward limit of seat back inclinations. 
     The preferred retractor herein is designed such that the rearward inclination is at 45° from the designed inclined position of the seat back in accordance with the previously-described automotive specifications. Whereas the locking of the retractor at the rearward limit of inclination does not rely on shifting on the inertia member, e.g. toppling of the standing man, 45° forward from the design position corresponds to a tilting of the seat back that is forward from the vertical. As most American sedans do not have seat backs that tilt forwardly from the vertical and in fact have as a forward limit a small amount of inclination, e.g. 5.5°, at which the seat back is reclined back from the vertical, the shifting of the inertia member as caused by tilting of the seat back can be relied upon without concern as to creating problems as to the sensitivity of the locking of the retractor. 
     Thus, unlike the universal retractors of the prior art, the vehicle sensitive retractor preferably has a stop that is specifically provided to be operable at the forward limit of seat back inclinations. Once the stop is operable, the retractor herein works like a regular retractor that does not adjust as the seat back is inclined. Accordingly, continued inclination of the seat back after the stop becomes operable will eventually cause the inertia member to become operable which causes the actuator mechanism to lock the retractor reel. Any sensitivity variances beyond this forward limit at which the stop is operable occasioned by the lack of functioning of the universal support when engaged with the stop are not of concern, as previously described. As long as the inertia member is operable by continued tilting of the retractor before the 45° forward angular spacing from the nominal position required by the relevant automotive retractor specifications, there is no problem in meeting and satisfying these requirements. For example, with a standing man that topples when it is pivoted 22° from vertical and where the full forward position is 5.5° inclined back from the vertical and at which a stop engages the universal support, the standing man will cause locking well before the 26.5° limit on the other side of the vertical 45° forward from the 18.5° design position, and more specifically will cause locking of the retractor at approximately 16.5° on the other side of the vertical. 
     Thus, the present retractor is particularly well adapted to be utilized in reclinable seat backs while keeping the sensitivity of the inertia member substantially the same throughout the operative range of seat back inclinations from the design inclination while at the same time meeting automotive specifications in terms of locking at a predetermined angular range forward and rearward from the design position at which the seat back comes delivered from the manufacturer. 
     Another stop can also be provided at the rearward limit of seat back inclinations to stop relative pivoting between the housing and pendulum assembly thereat. 
     In a preferred form, the primary actuator has a distal projection on which the secondary actuator rides so that the predetermined rearward inclined position at which the secondary actuator locks into the tooth wheel without shifting of the primary actuator or inertia member is at approximately 63.5°. 
     The inertia member and primary actuator can include cooperating arcuate surfaces to permit relative movement therebetween without shifting of the primary actuator when the inertia member is in its predetermined position. In this manner, during tilting of the seat back and retractor, any relative movement between the inertia member and primary actuator will not cause the retractor to lock until approaching a position 45° from the design position. 
     The retractor may be installed in a seat back inclined at approximately 18.5°, and at 45° inclined forwardly and rearwardly of the design installed inclination, the secondary actuator is in locking engagement with the toothed wheel. In this manner, the vehicle sensitive retractor herein satisfies the retractor locking specification requiring that the retractor be locked at 45° on either side of the nominal position. 
     The primary actuator can include a programmed surface portion so that with the inertia member in its predetermined position and as the seat back is inclined, the secondary actuator will slide along the programmed surface portion keeping a substantially constant gap between the secondary actuator and the toothed wheel. A distal projection can be provided adjacent the programmed surface portion for shifting the secondary actuator into locking engagement with the toothed wheel as the seat back is being inclined to the predetermined, rearward, inclined, locking position. Accordingly, the primary and secondary actuators work together to keep the sensitivity of the sensor substantially constant until the secondary actuator reaches the distal projection of the primary actuator which starts to shift the secondary actuator toward the teeth of the retractor wheel, and into engagement therewith at the specified angular distance rearward from the nominal position which can correspond to the rearward limit of travel of the seat back. 
     In a preferred form of the invention, an inertia sensor for a seat belt retractor that is to be mounted in an adjustable seat back in a vehicle is provided and includes a inertia member for sensing predetermined vehicular accelerations. A pendulum support for the inertia member is provided for staying in a substantially vertical orientation at different seat back inclinations. The inertia member is supported by the support in a predetermined position and shifts from the position when the predetermined acceleration is sensed. A first actuator is pivotally mounted to the support with the first actuator pivoting in response to shifting of the inertia member during predetermined vehicle accelerations. A housing for the pendulum support is provided and is affixed to the retractor. A second actuator is pivotally mounted to the housing for pivoting into locking engagement with the retractor. A first stop of the housing engages the support at a first inclination of the seat back with the second actuator out of locking engagement with the retractor. A second stop of the housing engages the support at a second inclination of the seat back that is greater than the first seat back inclination so that with the second stop in engagement with the support, the first actuator will pivot the second actuator into locking engagement with the retractor at the second seat back inclination. 
     In a preferred form, the first and second inclinations of the seat back are the limits of the angular adjustments through which the seat back can be reclined, the inertia member is a standing man, and the pendulum support includes a weighted basket that stays vertically oriented as the seat back is adjusted between the first and second inclinations and supports the standing man in an upright predetermined position during said adjustment so that the sensitivity of the standing man to shifting in response to predetermined accelerations stays substantially the same through substantially the entire range of seat back inclinations. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     FIG. 1 is a perspective view of a vehicle sensitive retractor in accordance with the present invention showing a universal support engaged with a stop at a forwardly inclined position of the retractor; 
     FIG. 2 is a perspective view of the vehicle sensitive retractor of FIG. 1 inclined rearwardly from the FIG. 1 position so that the support engages another stop on the housing and a secondary actuator is shifted into engagement with a toothed wheel for locking the retractor; 
     FIG. 3 is a perspective view of a housing for the inertia sensor; 
     FIG. 4 is a plan view of the inertia sensor housing of FIG. 3; 
     FIG. 5 is a perspective view of a standing man inertia member and a support basket therefor; 
     FIG. 6 is a perspective view of a pendulum weight for being attached to the inertia member support of FIG. 5; 
     FIG. 7 is an end elevational view of the inertia member support of FIG. 5; 
     FIG. 8 is a side elevational view of the inertia member support of FIG. 5; 
     FIG. 9 is a perspective view of a primary actuator for resting on the inertia member and being shifted thereby; 
     FIG. 10 is a side elevational view of the primary actuator of FIG. 9 showing the programmed surface portion thereof and projection adjacent thereto upon which the secondary actuator rides as the retractor is inclined; 
     FIG. 11 is an end elevational view of the primary actuator of FIG. 9; 
     FIG. 12 is a plan view of the primary actuator of FIG. 9; 
     FIG. 13 is a perspective view of a secondary actuator including a lower foot portion for riding on the primary actuator as the retractor is inclined; and 
     FIG. 14 is a graph indicating the various inclined positions of the retractor and seat back to which it is to be mounted and showing the retractor locked positions at 45° forward and rearward from a seat back design position. 
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
     In FIGS. 1 and 2, a vehicle sensitive retractor  10  in accordance with the present invention is shown. The retractor  10  incorporates an inertia sensor  12  for sensing predetermined vehicular accelerations to lock the retractor  10  against belt payout therefrom. The inertia sensor  12  has a universal support generally designated  14  that allows the retractor  10  to have its orientation changed through a predetermined range of inclinations, as illustrated in FIG. 5, relative to the vertical without causing the retractor  10  to be locked absent sensing of the predetermined vehicle acceleration condition by the sensor  12 . The inertia sensor  12  is designed such that the retractor  10  can be inclined about arrow  16  through a predetermined angular range of inclinations from the vertical with the universal support  14  staying in a substantially vertical orientation throughout this range of inclinations. In this manner, the universal support  14  keeps an inertia member  18  (FIG. 5) in a predetermined position without shifting as the retractor  10  and seat back (not shown) to which it is mounted are adjusted through a predetermined angular range of retractor  10  and seat back inclinations. Thus, the universal support  14  allows the retractor  10  to be mounted in a reclinable seat back such that tilting of the seat back will not substantially change the sensitivity of the sensor  12  in detecting vehicle accelerations and will not cause locking of the retractor  10  against belt payout therefrom. 
     The retractor  10  herein is also specifically designed so as to meet the retractor locking specifications that mandate locking of the retractor at specified angular spacings forwardly and rearwardly from its design inclined position of the seat back as it is installed and shipped from the automobile manufacturer. To this end, the retractor  10  includes an actuator mechanism generally designated  20  that is operable by the inertia member  18  when the inertia member  18  senses the predetermined acceleration and shifts in response thereto. When the inertia member  18  shifts in response to sensing the predetermined vehicle acceleration, the actuator mechanism  20  causes the retractor  10  to become locked against rotation. In addition, the actuator mechanism  20  is constructed so that when the retractor  10  is shifted rearwardly to a predetermined angular distance from the design position as specified by the pertinent retractor regulations, the actuator mechanism  20  will cause a locking of the retractor  10  without requiring that the inertia member  18  be shifted from its predetermined position on the support  14 . In this manner, the present retractor  10  does not rely on the inertia member  18  to achieve retractor locking at the specified angular distance rearward from the nominal position so that the sensitivity of the sensor  12  remains substantially the same as the retractor  10  moves through the angular range as the seat back is adjusted and tilted. 
     The regulations also require that the retractor be locked at an angular distance forwardly from the nominal position of the seat back that is equal to the distance at which it is to be locked rearward from the nominal inclined position. As previously discussed, most vehicles do not have seat backs that tilt forwardly beyond the vertical. The present retractor  10  has a stop  22  for engaging the support  14  at a predetermined forward inclination of the retractor  10  and seat back to which it is mounted. Continued pivoting of the retractor  10  past this predetermined forward inclined position will cause the support  14  and inertia member  18  to pivot to cause the actuating mechanism to lock the retractor. When the support  14  and inertia member  18  continues to pivot with further retractor inclination, the inertia member  18  will eventually shift from its predetermined position thereby operating the actuator mechanism  20  to lock the retractor  10 . In the preferred form, the inertia member  18  is a standing man type of inertia member that topples over at a predetermined tilting or inclination from the vertical, e.g. 22°. Balls, pendulums or other inertia members could be used rather than the inertia member illustrated herein. Depending on what the design position, a stop could be provided and used to actuate and lock the retractor when shifted 45° forwardly from the design position, if such an inclination of the seat was permitted. 
     Referring to FIG. 14, one exemplary application where the retractor  10  is mounted to a seat back is depicted in graph form where the seat back design position  24  is shown as 18.5° inclined back from vertical axis  26  on side  26   a  thereof. On this side  26   a  of the vertical, the seat back can be adjusted through a predetermined range of angular inclinations from its full forward position  28  which is shown as 5.5° inclined back from the vertical  26  to its full rearward inclined position  30 . The full rearward inclined position can correspond to the position  30  at which the retractor is locked at 45° rearwardly from the design position  24  as mandated by the retractor locking specifications. The present requirements of the specification mandate that the retractor be locked at both 45° forwardly and rearwardly from the design position  24 . Assuming that the longitudinal axis  10   a  of the retractor  10  is aligned with the axis of the seat back when mounted thereto, the actuator mechanism  20  will be effective to lock the retractor  10  when the seat back is reclined to 63.5° from the vertical  26  at position  30  which can correspond to the rearward limit of seat back travel. At the rearward limit  30  of seat back inclinations, the actuator mechanism  20  is operable to lock the retractor  10  without requiring that the inertia member  18  be shifted from its predetermined position relative to the support  14 . 
     The full forward position  28  of the seat back at 5.5° inclined rearwardly from vertical  26  is only 13° forwardly from the design position  24 . When the seat back is at its full forward position  28 , the support  14  engages stop  22  of the retractor  10 . With the stop  22  engaged with the support  14  so as to prevent its pivoting relative to the retractor  10 , should there be continued inclination of the retractor  10  past the full forward position  28 , the retractor  10  will act as a normal retractor. Accordingly, continued pivoting of the retractor  10  and universal support  14  therewith past the full forward position  28  will cause the inertia member  18  to shift from its predetermined position at a predetermined angular spacing from the full forward position  27 . Where the standing man  18  of FIG. 5 is utilized as the inertia member, the standing man  18  will topple when it is tilted approximately 22°. Thus, the standing man  18  will topple well before the forward locked position  32  that is 45° angularly spaced forward from the design position  26  at which retractor locking is mandated by the relevant retractor specifications. Accordingly, in testing of the illustrated retractor  10 , once the retractor  10  reaches the full forward position  28  so that the support  14  engages stop  22 , the inertia member  18  will cause locking of the retractor  10  at 22° from that point, or in other words at −16.5° inclined back on the other side  26 B of the vertical  26 . Manifestly, the locking of the retractor can be varied from this −16.5° position to other portions so long as the locking is achieved at or before the 45° forward position  32 . As is apparent, locking of the retractor at −16.5° is well within the specification of −26.5° at position  32  that is currently required. 
     Thus, while the inertia member  18  is not relied upon to achieve the locked condition of the retractor  10  45° rearwardly from the design position  24 , operation of the inertia member  18  is used to lock the retractor  10  before the forward locked position  32  on the other side  26 B of the vertical  26 . Such reliance on operation of the inertia member  18  beyond the full forward position  28  does not impact negatively on the performance of the retractor  10  as though the operative range of seat back inclinations between positions  28  and  30  on the operative side  26   a  of the vertical, the universal support  14  is fully functioning so as to maintain consistency in terms of the sensitivity of the inertia member  18  to vehicle accelerations. Since the forward locked position  32  is well beyond the full forward position  28  of the seat back and in fact on the other side  26 B of the vertical at which the seat back is not operative, any variations in sensitivity as caused by reliance on operation of the inertia member  18  to lock the retractor  10  by the time it reaches the forward locked position  32  will not adversely affect operation of the vehicle sensitive retractor  10  herein. Further, because operation of the inertia member  18  is not relied upon for locking of the retractor  10  at the rear locked position  30 , the sensitivity of the inertia sensor  12  can be maintained substantially the same throughout the operative range of seat back inclinations between full forward position  28  and to the full rear locked position  30 . 
     The retractor  10  can take on a variety of forms including the illustrated form where the retractor  10  has sidewalls  33  and  34  that are interconnected by end wall  36 . A reel (not shown) is journaled for rotation between the walls  33  and  34  with the reel having a length of seat belt webbing wound thereon that can be protracted and retracted therefrom for use in restraining passengers in their seats in an automobile. The reel frame supports a locking mechanism in the form of ratchet wheel  38  that rotates with the reel and has a plurality of teeth  40  formed about its periphery. Locking the retractor  10  against protraction of seat belt webbing wound on the reel is achieved upon shifting of the actuator mechanism  20  into engagement with the ratchet wheel teeth  40  so as to block continued rotation of the ratchet wheel  38  and reel carrying the seat belt wound thereon. The particular locking mechanism may be changed from that described and illustrated herein as there are many forms of locking mechanism that are commercially used and which could be actuated by an actuating mechanism, such as the actuating mechanism  20 . 
     The universal support  14  is shown in FIGS. 5-8 and is preferably in the form of a basket  42  having a weight member  44  (FIG. 6) to be attached thereto to pivot the basket to the true vertical position  26 . Pivot axles or trunnions  46  extend laterally outward from either side of the basket  42  for pivotally mounting the weighted basket universal support  14  to the retractor  10 , and specifically sensor housing  48 , as will be more fully described hereinafter. The basket  42  has an interior surface  50  having various diameters as will be described herein and at the bottom of which is a substantially flat annular seat  52  for supporting the bottom of the standing man  18  thereon. The standing man  18  has a tapered lower portion  54  and an enlarged upper head portion  56 . The basket annular seat  52  supports the bottom of the standing man lower portion  54  so that the standing man  18  is maintained in a predetermined substantially upright position when the support  14  is in its vertical orientation. 
     The pivot axles  46  of the support  14  define a pivot axis  58  for the weighted basket universal support  14  when pivotally mounted to the housing  48 . The pivot axis  58  is generally aligned with the bottom of the basket portion  42  of the support  18 , and particularly the seat  52  thereof on which the standing man  18  pivots for sensing accelerations of the vehicle. As the basket  42  and attached weight member  44  form a pendulum assembly that is heavier than the small, light-weight standing man  18 , the lesser mass and inertia of the lighter standing man  18  will cause it to have more sensitivity to vehicle accelerations versus the heavier pendulum support assembly  14 . Thus, the standing man  18  will shift at a faster rate from its predetermined upright position in response to vehicle accelerations that reach a predetermined threshold level; in comparison to the heavier pendulum support assembly  14  with its greater weight and inertia which shifts first at a lower threshold, but at a much slower rate than the standing man in response to accelerations of the vehicle. 
     Spaced vertical projections  60  extend upwardly from the top of the basket  42  at its forward and rearward ends along one side of the basket  42 . The projections  60  each include an aperture  62  for pivotally mounting primary actuator  64  thereto. The primary actuator  64  is shown in FIGS. 9-12 and includes a transverse body portion  66  having a pivot shaft  68  formed along one side of the body portion  66 . The pivot shaft  68  includes reduced diameter front and a back ends  70  and  72  for pivotally mounting in the projection apertures  62 . The shaft ends  70  and  72  can be provided with a taper or chamfer similar to the apertures  62  for tightly fitting therein. 
     The primary actuator body portion  66  has a domed portion  74  which extends convexly from the top of the body  66 . Similarly, the head portion  56  of the standing man  18  has a rounded or domed portion  76  which extends convexly upward from the flat top thereof. The body  66  has a chamber  78  formed below the domed portion  74  and having a surface (not shown) that is convexly shaped to match the curvature of the domed portion  74  on the underside thereof. Thus, with the actuator  64  pivotally mounted to the inertia member support or pendulum assembly  14  as by pivot shaft  68  and projections  60  thereof and with the standing man  18  supported in its upright position in the basket  42  by the annular seat  52 , the rounded top  76  of the standing man  18  will project into the chamber  78  and into engagement with the underside of the domed portion  64  of the actuator  74 . It is preferred that the respective domed portions  74  and  76  of the actuator  64  and standing man  18  have substantially the same radium of curvature such that relative motion between the support  14  and inertia member  18  before toppling of the inertia member  18  in response to the threshold predetermined acceleration will not cause shifting or pivoting of the actuator  64  as could change the sensitivity of the actuating mechanism  20  during most of the relative travel or motion between the domed portions  74  and  76 . In this manner, there is neither a substantial change in sensitivity nor a premature locking of the retractor  10  by the actuator mechanism  20  before the threshold acceleration is sensed. 
     The primary actuator  64  has an elongated extension portion  80  (FIGS. 9-12) that extends generally parallel to the pivot shaft  68  transverse to the body portion  56  and across the domed portion  74  thereof. The extension portion  80  includes portion  81  thereof that is provided with a top contoured engagement surface section  82  for supporting secondary actuator  84  (FIG. 13) which rides thereon as the retractor  10  and seat back are tilted. The secondary actuator  84  similar to primary actuator  64  has a pivot shaft  86  extending laterally at its front end for pivotally mounting the actuator  84  to sensor housing  48 , as will be more fully described hereinafter. Extending rearwardly and transverse to the pivot shaft  86  is pick or pawl portion  88 . The pawl portion  88  extends rearwardly to a distal end or tooth  90  which is squared off to provide a flat abutment surface  90   a  for engaging in the teeth  40  of the ratchet wheel  38  when the vehicle reaches the threshold acceleration or at the specified inclination positions  30  or  32  from the design position  24 . The pawl portion  88  includes a depending foot projection  92  for resting on top of the primary actuator extension portion  80 . 
     The secondary actuator  84  rests on the primary actuator  64  and respective pivot axes of these actuators are at 90° to one another. The engagement surface section  82  on the primary actuator  64  is contoured relative to the contour of the surface  82  so that as the secondary actuator foot projection  92  is caused to slide therealong by tilting of the seat back and retractor  10 , the distal end  90  of the secondary actuator pawl portion  88  will stay consistently spaced from the ratchet wheel teeth  40 . Thus, the sensitivity of the locking mechanism is maintained as the basket pivots. That is, the contour of the surface section  82  is programmed so that a substantially constant gap  94  is maintained between the end  90  of the secondary actuator pawl portion  88  and the teeth  40  of the ratchet wheel  38  during tilting of the seat back through most of the seat back inclination. By keeping the gap  94  constant, the sensitivity of the sensor  12  to vehicular accelerations will not change despite having the seat back at different angles of inclinations to the vertical  26 . More specifically, the contoured engagement surface  82  preferably defines an arc of a circle which has a center that substantially coincides with the pivot axis  58  of the pendulum support assembly  14 . Accordingly, as the retractor  10  is caused to move through the angular range of seat back inclinations, the secondary actuator  84  will move in a circular path about the programmed surface portion  82  with its distal end  90  kept at a consistent spacing  94  from the ratchet wheel teeth  40 . 
     As previously discussed, the actuator mechanism  20  is constructed such that when the seat back and retractor  10  mounted thereto are reclined to their rearward inclination position  30 , the actuator mechanism  20 , and specifically the primary actuator  64  and secondary actuator  84  cooperate to cause the retractor  10  to be locked against belt protraction therefrom, as shown in FIG.  2 . In this regard, the extension  80  of the primary actuator  64  includes a distal portion or projection  96  extending rearwardly from the portion  81  thereof including the contoured engagement surface  82  towards the ratchet wheel teeth  40 . Thus, as the retractor  10  is tilted rearward, the foot projection  92  of the secondary actuator  84  will eventually move from the contoured engagement surface  82  onto the flatter surface  98  of the projection  96 . When the secondary actuator foot projection  92  reaches the distal projection portion  96  of the extension  80 , continued pivoting of the retractor  10  towards the rearward inclination position  30  causes the foot projection  92  to ride on the flat surface  98  so that the secondary actuator distal end  90  moves towards the ratchet teeth  40 . When the retractor  10  is tilted to the rearward inclination postion  30 , the secondary actuator foot projection  92  will be supported by the rearward end  96   a  of the projection  96  with its squared off end  90   a  moved into locking engagement with the ratchet wheel teeth  40 , as is shown in FIG.  2 . 
     In this manner, the projection  96  of the extension portion  80  of the primary actuator  64  is operable to cause the secondary actuator  84  to lock the retractor  10  at the mandated angular distance, i.e., 45°, from the design position  24  at rearward inclination position  30  without requiring that the standing man  18  shift or topple to cause the primary actuator  64  to be shifted for lifting the end  90  of the secondary actuator  84  into engagement with the teeth  40 . As previously discussed, by avoiding reliance on operation of the standing man  18  at and beyond the 45° rearward position  30 , the sensitivity of the sensor  12  can remain substantially unchanged during pivoting of the seat back and retractor  10  until they reach a point that is close to the rearward inclination position  30  at which the foot projection  92  begins to ride on the distal projection  96  of the primary actuator extension portion  80  so that the secondary actuator end  90  starts to be lifted towards the ratchet teeth  40 . Accordingly, there is only a short angular distance of seat back inclination where the foot projection  92  is riding on the primary actuator projection  96 . During this time, the sensor  12  will become more sensitive to vehicle accelerations because the secondary actuator distal end  90  will begin to move closer to the ratchet teeth  40  so that it will shift into engagement therewith more quickly due to the decreasing gap  94  therebetween. This heightened sensitivity of the sensor  12  will be of little practical consequence s it will only occur when the seat back is reclined almost all the way back to its rearmost inclination position  30  where presumably the seat back will rarely be used, particularly if on the driver side of the vehicle. 
     Referring to FIGS. 3 and 4, the stationary housing  48 , which is fixed to frame sidewall  34 , will next be more particularly described. The housing  48  has a side wall  100  mounted to the retractor side wall  34  at the bottom thereof below the toothed wheel  38 . As previously mentioned, both the pendulum universal support  14  and in particular the basket  42  thereof and the secondary actuator  84  are pivotally mounted to the housing  48 . To this end, the housing  48  has a side arm  102  parallel to side wall  100  and interconnected therewith by way of front end wall  104  which is integral with rearwardly angled portion  105  of the wall  104  that terminates at the previously described transverse stop  22 . The side wall  100  has a front, upper cylindrical boss  106  and a rear, lower cylindrical boss  108  that are aligned across from apertures  110  and  112  formed in the side arm  102 . The aperture  110  is formed at the upper end of substantially vertical portion  114  of the arm  102  and the aperture  112  is formed in rearwardly extending portion  116  of the arm  102  at the top of upturned end  118  thereof. The pendulum or weighted basket support  14  is pivotally mounted to the housing  48  with pivot axles  46  inserted into the cylindrical boss  108  and the aperture  112  aligned across therefrom so that the projections  60  are adjacent the side wall  100  of the housing  48 . 
     With the pivot shaft ends  70  and  72  pivotally mounted in the projection apertures  62 , the primary actuator body portion  66  extends transversely and away from retractor wall  34  and housing wall  100  affixed thereto. With this arrangement, the primary actuator extension portion  80  will be laterally spaced from the housing wall  100  and extend rearwardly so that portion  96  thereof projects beyond the basket  42 , as can be seen in FIGS. 1 and 2. In addition, the housing upper boss  106  and aperture  110  aligned therewith for pivotally mounting reduced chamfered ends  86   a  and  86   b  of the secondary actuator pivot shaft  86  are generally spaced above projection apertures  62 . Accordingly, the secondary actuator  84  as pivotally mounted to the housing  48  via boss  106  and aperture  110  thereof will be disposed over the primary actuator  64  pivotally mounted to the basket  42  and such that the rearwardly extending pawl portion  88  of the secondary actuator  84  will be aligned over the rearwardly extending extension portion  80  of the primary actuator  64  will the foot projection  92  supported on top surface sections  82  or  98  of the extension  80 . In this manner, toppling of standing man  18  causes the primary actuator  64  including the extension portion  80  thereof to shift and pivot about pivot shaft  68  which, in turn, lifts and pivots the secondary actuator  84  supported by the primary actuator portion  80  about its pivot shaft  86  and into engagement with the ratchet wheel teeth  40  for locking the retractor against belt protraction therefrom. 
     Referring to FIGS. 5-8, the basket  42  preferably includes an upper annular section  120  with an intermediate tapered section  122  extending downwardly therefrom to horizontal ledge wall  124  which projects radially inward from the bottom of the tapered section  122 . A lowered tapered section  106  extends from the radial inner edge of the ledge wall  124  down to the annular seat  52 . Thus, the inner surface  50  of the basket  42  generally tapers from the large diameter annular section  120  down to a smaller diameter at the bottom of the lowered tapered section  106  where the seat  52  is formed. 
     The housing side arm  102  (FIGS. 3 and 4) is spaced laterally from the side wall  100  so as to minimize the size of the housing  48 . In this regard, the basket  42  has a bracket portion  127  formed at the side of the basket annular and tapered sections  120  and  122  spaced from the housing wall  100  and which has a forward transverse abutment portion  127   a  for engaging stop  129  formed on inner edge  116   a  of the housing arm portion  116 , as best seen in FIG.  3 . In order to provide the support  14 , inertia member  18  and primary actuator  64  with clearance as the housing  48  is pivoted along with the retractor  10  towards the rearward inclination position  30 , inner edge  114   a  of housing arm vertical portion  114  is provided with a cutout area  115 . In this manner, there is no interference from the arm vertical portion  114  as the retractor  10  and housing  48  are pivoted rearward. The side wall  100  is provided with an integral flange  100   a  extending about its lower periphery for tightly receiving as by a friction fit a housing cover (not shown) thereon so that the housing  48  encloses the sensor  12  therein while taking up little space on the bottom and side of the retractor  10 . 
     With the weighted basket or pendulum support  14  pivotally attached to the housing  48 , the bracket portion  127  will extend laterally beyond the housing arm  102 . In addition, both stops  22  and  129  will be disposed forwardly on one side of the pivot axis  58 . Thus, as the seat pivots and causes the retractor  10  to be pivoted rearwardly towards the rearward inclination position, the housing  48  affixed to the retractor  10  will pivot about axis  58  bringing the arm portion  116  towards the pendulum support  14 , and more specifically bringing the stop  129  into engagement with the abutment portion  127   a  of the basket bracket portion  127  once the retractor  10  reaches the rearward inclination position  30 . At this time, the foot projection  92  of the secondary actuator  84  will be at the end  96   a  of the primary actuator extension portion  80  so that the secondary actuator end  90  is in engagement with the ratchet wheel teeth  40 , as previously described. Accordingly, at the rearward inclination position  30 , engagement of the support  14  and specifically bracket transverse portion  127   a  with the stop  129  coincides with the locking of the retractor ratchet wheel  38  by the actuator mechanism  20  and specifically by cooperation of the primary actuator  64  and the secondary actuator  84 . As the seat back preferably does not recline past rearmost inclination position  30 , engagement of the stop  129  with the basket portion  127  so that the support  14  does not adjust at inclinations of the retractor  10  that are past position  30  will have no practical significance. 
     Pivoting of the retractor  10  forwardly form the rearward inclination position  30  and towards the full forward position  28  causes the wall portion  105  to be pivoted toward the weight member  44  of the weighted basket support  14 . Once the full forward position  28  of seat back inclination has been reached at 5.5° in this instance, as shown in FIG. 1, the support  14 , and specifically the weight member  44  thereof will be in engagement with the stop  22  on the housing wall portion  105 . At this point, the actuator mechanism  20  will not be in locking engagement with the retractor  10  absent the vehicle reaching the threshold acceleration required for shifting of the inertia member  18 . If there were a continued pivoting of the retractor  10  past the full forward position of 5.5° to a −26.5° position, the retractor  10  would act as a normal retractor  10 , as the support  14  no longer adjusts, with the standing man toppling to actuate the locking mechanism  20  to lock the retractor. That is, the standing man inertia member is designed to topple at an inclination of 22° so that tilting of the retractor  10  forward 22° from the full forward position  28  of the seat back would cause the standing man  18  to topple which, in turn, would cause the actuator mechanism  20  to lock the retractor  10 . As discussed, because pivoting of the retractor  10  beyond the full forward position  28  preferably is not within the operative range of seat back inclinations, no problems arise by having the sensitivity of the inertia sensor  12  vary as is caused when the support  14  is in engagement with the stop  22  and the retractor  10  is pivoted forward past the full forward position  28 . In this regard, reliance upon toppling of the standing man  18  to cause locking of the retractor  10  at a point before the design locked position  32  is acceptable. 
     The details of construction of the illustrated weight member  44 , which acts to pivot the basket  42  relative to the seat back and the seat turns, will now be described. Preferably, a dovetail fit between the weight member and the basket is used. To this end, a trapezoidal-shaped mounting foot  128  can be provided at the bottom of the basket  42  for mounting the weight member  44  thereto. The weight member  44  has upper arms  130  and  132  including respective facing surfaces  130   a  and  132   a  that are inclined and diverge away from each other as they extend from the top toward the bottom of their respective arms  130  and  132 . The surfaces  130   a  and  132   a  define a trapezoidal space therebetween substantially matching the shape of the mounting foot  128 . The arms  130  and  132  extend upwardly form a main body portion  134  of the weight member  44  and spaced from vertical sides  136  and  138  thereof so that a shoulder top surface  140  of the body portion  136  is formed between sides of the arms  130  and  132  and body portion sides  136  and  138 . Below the inclined surfaces  130   a  and  132   a , raised abutment portion  141  extends between the arms  130  and  132  projecting above the body portion top surface  140 . A pair of small, semi-circular bump projections  142  are raised from bottom surface  144  of the trapezoidal foot portion  128  and are spaced centrally between oppositely inclined surfaces  146  and  148  thereof. The bump projections  142  are laterally spaced from each other at a distance that is slightly greater than the length of the arms  130  and  132 . 
     To attach the weight member  44  to the basket  42 , and specifically the arms  130  an  132  to the mounting foot  128 , the mounting foot  128  is oriented so that its inclined surfaces  146  and  148  are in confronting tight fitting relation with arm inclined surfaces  130   a  and  132   a  so as to prevent relative movement in a front to back or longitudinal direction between the weight member  44  and the basket  42 . With the trapezoidal mounting foot  128  received in the trapezoidal space defined between the arms  130  and  132  and specifically the oppositely inclined surface  130   a  and  132   a  thereof, the raised bumps  142  will be in tight fitting engagement with either side of the abutment portion  141  so as to keep the weight member  44  from shifting laterally with respect to the basket  42 . 
     As shown, the weight member  44  can be provided with a lower portion  148  below the body portion  136  to increase the weight and inertia of the weight member  44  to ensure that it stays substantially vertical as the seat and retractor  10  are pivoted and so that the standing man  18  reacts properly to sensed vehicle accelerations, as previously discussed. In addition, the interior surface  50  of the basket  42  tapers down to a throughpassageway formed in the basket foot portion  128  that is aligned with a similar throughpassageway  150  extending vertically through the weight member  44  so that any mixture or particulate member that gains access into the housing  48  and the weighted support basket  18  can escape therethrough. 
     With the basket  42  and weight member  44  assembled, and standing man  18  is placed in the basket  42  so that the standing man lower portion  54  is supported at its bottom  54   a  by the annular seat  52 , as previously discussed. The diameters across the lower tapered portion  126  of the basket  42  is at all points sufficiently larger than the corresponding diameters of the standing man lower portion  54  so as to provide room for lateral shifting or toppling over of the standing man  18  in the basket  42 . Standing man portion  54  has a height greater than that of the basket lower portion  146  so that the enlarged head  56  of the standing man  18  is disposed in the area defined by the annular section  120  and intermediate tapered section  122  of the basket  42 . Again, the diameters of the basket sections  120  and  122  are sized to be larger than the corresponding diameters of the standing man head  56  so as to provide sufficient room for lateral shifting and toppling over of the standing man  18  when the vehicle threshold acceleration is reached. 
     The standing man  18  includes a shoulder  152  between the lower portion  54  and enlarged upper head portion  56  thereof which engages the basket ledge wall  124  when the standing man  18  topples from its upright position. In this manner, the standing man  18  is kept from tipping too far over such that the engagement of the standing man shoulder  152  with the basket wall  124  allows the standing man  18  to right itself back to its upright position once the vehicle accelerations subsides below the threshold acceleration so that the sensor  12  is again operable to detect vehicle accelerations that exceed the threshold acceleration required for toppling of the standing man  18 . Similarly, when the retractor  10  is tilted beyond the design locked rearward and forward inclination positions  30  and  32 , the engagement between the standing man shoulder  152  and basket ledge wall  124  keeps the standing man  18  in the same toppled over position where it is ready to return to its upright position when the retractor  10  is inclined back to an inclination that is between the positions  30  and  32 . 
     While there have been illustrated and described particular embodiments of the present invention, it will be appreciated that numerous changes and modifications will occur to those skilled in the art, and it is intended in the appended claims to cover all those changes and modifications which fall within the true spirit and scope of the present invention.