Fld-out ramp having a load dampener

Abstract

A ramp assembly is provided. The ramp assembly includes a ramp platform coupled to a frame, a reciprocating mechanism coupled to the ramp platform for reciprocating movement of the ramp platform between a stowed position and a deployed position, and a dampener coupled to the reciprocating mechanism to dampen loads associated with operation of the ramp platform.

Description

FIELD OF THE INVENTION

[0002] The present invention relates generally to power transmission devices of wheelchair ramps and, more particularly, to driveshaft assemblies of the power transmission devices of wheelchair ramps.

BACKGROUND OF THE INVENTION

[0003] The Americans with Disabilities Act (ADA) requires the removal of physical obstacles to those who are physically challenged. The stated objective of this legislation has increased public awareness and concern over the requirements of the physically challenged. Consequentially, there has been more emphasis in providing systems that assist such a person to access a motor vehicle, such as a bus or minivan.

[0004] A common manner of providing the physically challenged with access to motor vehicles is a ramp. Various ramp systems for motor vehicles are known in the art. Some slide out from underneath the floor of the vehicle and tilt down. Others are stowed in a folded position and are pivoted about a hinge. Ramps of this category are known as “fold-out ramps.”

[0005] Fold-out ramps have automatic deploy/stow mechanisms with manual operation capabilities. Current deploy/stow mechanisms include hydraulic or pneumatic motors, and cylinders or other hydraulic or pneumatic devices. Other suitable deploy/stow mechanisms are of the electric variety, and include an electric motor. Electric motors, through reduction gears, allow a small, inexpensive motor to produce large torques able to drive the fold-out ramp.

[0006] Although these previously developed electric automatic mechanisms are suitable for their intended purpose, they are not without their problems. More specifically, reduction gears have high gear reduction ratios so that small high-speed motors can move large, heavy objects, albeit at a slow speed. For example, a three stage planetary reduction gear may provide a gear reduction ratio of 1000 to 1. When being back driven, the high gear reduction ratio has the effect of increasing the “realized” inertia of the motor, at the reduction gear output shaft, by the square of the gear reduction ratio. As a result, a reduction gear ratio of 1000 to 1 creates an inertia at the reduction gear output shaft of 10002, or 1,000,000 times the actual motor inertia.

[0007] Thus, the torque exhibited upon a driveline coupling the reduction gear to the driven object can be extremely high, thereby leading to potential equipment failure.

SUMMARY OF THE INVENTION

[0008] A ramp assembly is provided. The ramp assembly includes a frame attachable to a vehicle and a platform coupled to a portion of the frame. The ramp assembly also includes a ramp having a weight and a reciprocating mechanism coupled to the ramp to reciprocate the ramp between a stowed and deployed position. A dampener is coupled to the reciprocating mechanism to dampen loads associated with moving the ramp from a static position.

[0009] In another embodiment of the present invention, a ramp assembly includes a ramp platform coupled to a frame and a reciprocating mechanism coupled to the ramp platform for reciprocating the ramp platform between a stowed position and a deployed position. The ramp assembly also includes a dampener coupled to the reciprocating mechanism to dampen loads associated with operation of the ramp platform.

[0010] A ramp assembly formed in accordance with yet another embodiment of the present invention, includes a frame attachable to a vehicle having a floor, and a ramp coupled to a portion of the frame at least in part by a reciprocating mechanism for reciprocating movement of the ramp between a stowed position and a deployed position. The ramp assembly also includes a dampener coupled to the reciprocating mechanism to dampen loads associated with moving the ramp from a static position. The ramp assembly also includes a lifting assembly disposed between the platform and the frame for reciprocating movement of the ramp into and out of a position substantially flushed with the floor as the ramp is reciprocated between the deployed and stowed positions.

[0011] In still yet another embodiment of the present invention, a ramp assembly includes a ramp platform coupled to a frame and a reciprocating mechanism extending between the ramp platform and the frame for reciprocating movement of the ramp platform from a static position. The ramp assembly also includes means for damping loads associated with reciprocating movement of the ramp platform from a static position, wherein the means for damping loads is coupled at least in part to the reciprocating mechanism.

BRIEF DESCRIPTION OF THE DRAWINGS

[0012] The foregoing aspects and many of the attendant advantages of this invention will become more readily appreciated as the same become better understood by reference to the following detailed description, when taken in conjunction with the accompanying drawings, wherein:

[0013] FIG. 1 is a perspective view of a fold-out ramp constructed in accordance with one embodiment of the present invention, with the fold-out ramp shown in the stowed position;

[0014] FIG. 2 is a perspective view of a fold-out ramp formed in accordance with one embodiment of the present invention, with the fold-out ramp shown in the deployed position;

[0015] FIG. 3 is a cross-sectional perspective view of a fold-out ramp formed in accordance with one embodiment of the present invention, with the fold-out ramp shown in the deployed position;

[0016] FIG. 4 is a cross-sectional planar view of a counterbalance assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention;

[0017] FIG. 5 is a perspective view of a fold-out ramp formed in accordance with one embodiment of the present invention, showing a fixed attachment point of the fold-out ramp to a mounting structure;

[0018] FIG. 6 is a perspective view of a fold-out ramp formed in accordance with one embodiment of the present invention, showing a rotating attachment point of the fold-out ramp to a mounting structure;

[0019] FIG. 7 is a perspective cross-sectional view of a fixed attachment end of a counterbalance assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention;

[0020] FIG. 8 is a perspective cross-sectional view of a rotating attachment end of a counterbalance assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention;

[0021] FIG. 9 is a perspective view of a ramp, drive motor assembly, and pivot link assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention with structure removed for clarity;

[0022] FIG. 10 is a perspective view of a pivot link assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention;

[0023] FIG. 11 is a cross-sectional perspective view of a pivot link assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention and showing one end of the pivot link assembly;

[0024] FIG. 12 is a cross-sectional side planar view of a fold-out ramp, formed in accordance with one embodiment of the present invention, showing the fold-out ramp in a partially deployed position;

[0025] FIG. 13 is a cross-sectional side planar view of a fold-out ramp, formed in accordance with one embodiment of the present invention, showing the fold-out ramp in a substantially neutral position;

[0026] FIG. 14 is a cross-sectional side planar view of a fold-out ramp, formed in accordance with one embodiment of the present invention and showing the fold-out ramp in the fully deployed position;

[0027] FIG. 15 is a perspective view of a fold-out ramp, formed in accordance with the present invention and showing a first alternate embodiment of the counterbalance assembly;

[0028] FIG. 16 is a partial perspective view of a fold-out ramp, formed in accordance with the present invention and showing a more detailed view of the motor drive assembly and linkage assembly of the counterbalance assembly of FIG. 15;

[0029] FIG. 17 is an exploded view of the fold-out ramp assembly of FIG. 15, showing the major components of the fold-out ramp assembly;

[0030] FIG. 18 is a perspective view of a torsion pin weldment for the counterbalance assembly;

[0031] FIG. 19 is a top planar view of the torsion pin weldment of FIG. 18;

[0032] FIG. 20 is a side planar view of the torsion pin weldment of FIG. 19, taken through Section 20-20;

[0033] FIG. 21 is an end planar view of the torsion pin weldment of FIG. 18;

[0034] FIG. 22 is a perspective view of the first alternate embodiment of the counterbalance assembly for the ramp assembly of FIG. 15, with portions of the ramp removed for clarity;

[0035] FIG. 23 is a perspective view of the counterbalance assembly of FIG. 22, wherein the counterbalance assembly is rotated 180° from the view shown in FIG. 22;

[0036] FIG. 24 is a side planar view of the counterbalance assembly of FIG. 22;

[0037] FIG. 25 is a top planar view of the counterbalance assembly of FIG. 24;

[0038] FIG. 26 is a partial cross-sectional side planar view of the counterbalance assembly of FIG. 24, taken through Section 26-26;

[0039] FIG. 27 is a cross-sectional side planar view of the counterbalance assembly of FIG. 24, taken through Section 27-27;

[0040] FIG. 28 is a top planar view of the fold-out ramp assembly, showing the fold-out ramp assembly in the fully deployed position;

[0041] FIG. 29 is a partial cross-sectional side planar view of the fold-out ramp of FIG. 28, showing the counterbalance assembly and taken through Section 29-29 of FIG. 28;

[0042] FIG. 30 is a perspective view of a fold-out ramp of FIG. 15, with the fold-out ramp shown in the stowed position;

[0043] FIG. 31 is a top planar view of the fold-out ramp of FIG. 30;

[0044] FIG. 32 is a partial cross-sectional side planar view of the fold-out ramp of FIG. 31, taken through Section 32-32;

[0045] FIG. 33 is a perspective view of the fold-out ramp of FIG. 15, with the fold-out ramp shown in a substantially 90° deployment position.

[0046] FIG. 34 is a top planar view of the fold-out ramp assembly of FIG. 33;

[0047] FIG. 35 is a partial cross-sectional side planar view of the fold-out ramp assembly of FIG. 34, taken through Section 35-35;

[0048] FIG. 36 is a perspective view of a second alternate embodiment of a counterbalance assembly for a fold-out ramp, formed in accordance with the present invention, with portions of the fold-out ramp assembly removed for clarity;

[0049] FIG. 37 is an end planar view of the counterbalance assembly of FIG. 36;

[0050] FIG. 38 is a side planar view of the counterbalance assembly of FIG. 37 and taken through Section 38-38;

[0051] FIG. 39 is a partial cross-sectional end planar view of the counterbalance assembly of FIG. 38 and taken through Section 39-39;

[0052] FIG. 40 is a cross-sectional side planar view of the counterbalance assembly of FIG. 37 and taken through Section 40-40;

[0053] FIG. 41 is a cross-sectional side planar view of the counterbalance assembly of FIG. 37 and taken through Section 41-41;

[0054] FIG. 42 is a perspective view of the counterbalance assembly of FIG. 36, where the counterbalance assembly is rotated 180° from the view shown in FIG. 36;

[0055] FIG. 43 is a partial view of the counterbalance assembly of FIG. 42, with portions thereof removed for clarity;

[0056] FIG. 44 is a perspective view of a fold-out ramp assembly, formed in accordance with the second alternate of the counterbalance assembly of FIG. 36;

[0057] FIG. 45 is a partial view of the fold-out ramp assembly of FIG. 44, showing the counterbalance assembly of FIG. 36;

[0058] FIG. 46 is a perspective view of a rear stub shaft of a ramp assembly of the present invention, with the second alternate counterbalance assembly of FIG. 36;

[0059] FIG. 47 is a perspective view of a fold-out ramp, formed in accordance with one embodiment of the present invention, showing the fold-out ramp in the closed position;

[0060] FIG. 48 is a perspective view of a counterbalance assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention;

[0061] FIG. 49 is a perspective view of a fold-out ramp, formed in accordance with one embodiment of the present invention and showing a stub shaft;

[0062] FIG. 50 is a perspective view of a fold-out ramp, formed in accordance with one embodiment of the present invention and showing an adjustment assembly to selectively preload the counterbalance assembly;

[0063] FIG. 51 is a perspective view of a drive assembly for a fold-out ramp, formed in accordance with the present invention;

[0064] FIG. 52 is a perspective view of an idler and roller assembly for a drive assembly of a fold-out ramp, formed in accordance with one embodiment of the present invention and showing a chain tension assembly;

[0065] FIG. 53 is a perspective view of an attachment arm for a fold-out ramp, formed in accordance with one embodiment of the present invention;

[0066] FIG. 54 is a perspective view of a cam and roller assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention;

[0067] FIG. 55 is a perspective view of a portion of the cam and roller assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention and showing one embodiment of a stow latch assembly in a locked position;

[0068] FIG. 56 is a perspective view of a portion of the cam and roller assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention and showing one embodiment of a stow latch assembly in an unlocked position;

[0069] FIG. 57 is a perspective view of a clutch assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention;

[0070] FIG. 58 is an exploded view of a clutch assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention;

[0071] FIG. 59 is a cross-sectional perspective view of a clutch assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention;

[0072] FIG. 60 is a partial perspective view of a handle assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention and showing the handle assembly in a down position;

[0073] FIG. 61 is a partial perspective view of a handle assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention and showing the handle assembly in an up position;

[0074] FIG. 62 is a partial perspective cutaway view of a handle assembly and stow latch assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention;

[0075] FIG. 63 is a partial side view of a handle assembly and stow latch assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention;

[0076] FIG. 64 is a partial cross-sectional perspective view of a stow latch assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention;

[0077] FIG. 65 is a partial perspective view of a handle assembly and stow latch assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention and showing the handle assembly in an up position;

[0078] FIG. 66 is a side planar view showing a handle assembly and stow latch assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention and showing the handle assembly in an up position;

[0079] FIG. 67 is a partial cross-sectional view of a handle assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention;

[0080] FIG. 68 is a partial cross-sectional view of a handle assembly for a fold-out ramp, formed in accordance with one embodiment of the present invention and showing the handle assembly in an up position;

[0081] FIG. 69 is a perspective view of a fold-out ramp assembly, formed in accordance with one embodiment of the present invention, showing the fold-out ramp in a stowed position;

[0082] FIG. 70 is a partial perspective view of a fold-out ramp assembly, formed in accordance with one embodiment of the present invention, showing an adjustment assembly for selectively preloading the counterbalance assembly, wherein the adjustment assembly is shown in a loaded condition;

[0083] FIG. 71 is a partial side planar view of the fold-out ramp assembly and adjustment assembly depicted in FIG. 70, wherein the adjustment assembly is shown in the loaded condition;

[0084] FIG. 72 is a partial side planar view of the fold-out ramp assembly and adjustment assembly depicted in FIG. 70, wherein the adjustment assembly is shown in the unloaded condition;

[0085] FIG. 73 is a partial perspective view of the fold-out ramp assembly depicted in FIG. 69, showing the adjustment assembly in the loaded condition;

[0086] FIG. 74 is a partial perspective view of the fold-out ramp assembly and adjustment assembly depicted in FIG. 73, wherein a bearing block has been removed to show the coupling of a torsion lever arm to a torsion bar;

[0087] FIG. 75 is a perspective view of a torsion lever arm assembly, formed in accordance with the present invention and suitable for use with the fold-out ramp assembly depicted in FIG. 69;

[0088] FIG. 76 is an exploded perspective view of the torsion lever arm assembly depicted in FIG. 75, wherein the bearing block has been separated from the torsion lever arm assembly to show the torsion lever arm;

[0089] FIG. 77 is a reverse perspective view of the torsion lever arm assembly depicted in FIG. 76, wherein the bearing block has been separated from the torsion lever arm assembly to show a pair of saddle bearings attached to the bearing block;

[0090] FIG. 78 is a perspective view of a torsion bar, formed in accordance with the present invention and suitable for use with the fold-out ramp assembly depicted in FIG. 69;

[0091] FIG. 79 is a partial perspective view of the torsion bar illustrated in FIG. 78, showing a lobed spline end for engaging the torsion lever arm;

[0092] FIG. 80 is a perspective view of the fold-out ramp assembly depicted in FIG. 69, wherein the fold-out ramp has been rotated 90 degrees counterclockwise from the position depicted in FIG. 69;

[0093] FIG. 81 is a partial perspective view of the fold-out ramp assembly depicted in FIG. 80, showing a counterbalance linkage assembly in a loaded condition;

[0094] FIG. 82 is a partial side planar view of the counterbalance linkage assembly depicted in FIG. 81, showing the counterbalance linkage assembly in the loaded condition;

[0095] FIG. 83 is a partial side planar view of the counterbalance linkage assembly depicted in FIG. 81, showing the counterbalance linkage assembly in an unloaded condition;

[0096] FIG. 84 is a perspective view of the fold-out ramp assembly, partially deployed in a vertical position, wherein a rising floor has been removed for clarity;

[0097] FIG. 85 is a partial perspective view of the fold-out ramp assembly depicted in FIG. 84, showing the counterbalance linkage assembly in the loaded condition and with a pin joining a torsion lever arm to a counterbalance actuating arm;

[0098] FIG. 86 is a partial perspective view of the fold-out ramp assembly depicted in FIG. 84, wherein the counterbalance linkage assembly is shown in the unloaded condition and with the counterbalance actuating arm shown in the engaged position;

[0099] FIG. 87 is a partial perspective view of the fold-out ramp assembly depicted in FIG. 84, wherein the counterbalance linkage assembly is shown in the unloaded condition and with the counterbalance actuating arm shown in the disengaged position;

[0100] FIG. 88 is a reversed partial perspective view of the fold-out ramp assembly depicted in FIG. 87, showing the counterbalance linkage assembly in the unloaded condition and with the counterbalance actuating arm shown in the disengaged position;

[0101] FIG. 89 is a partial perspective view of the fold-out ramp assembly depicted in FIG. 88, wherein the counterbalance linkage assembly is shown in the unloaded condition and with the counterbalance actuating arm shown in the disengaged position, wherein the frame side rail has been removed for clarity;

[0102] FIG. 90 is a perspective view of another fold-out ramp assembly formed in accordance with another embodiment of the present invention;

[0103] FIG. 91 is a partial perspective view of the fold-out ramp assembly of FIG. 90 focusing on an idler and roller assembly of a drive assembly of the fold-out ramp;

[0104] FIG. 92 is the partial perspective view of the fold-out ramp assembly of FIG. 91, wherein portions of the fold-out ramp, such as the ramp platform, have been removed to more clearly show portions of a flexible driveshaft assembly constructed in accordance with one embodiment of the present application;

[0105] FIG. 93 is a partial perspective view of the flexible driveshaft assembly shown in FIG. 92;

[0106] FIG. 94 is an exploded partial perspective view of the flexible driveshaft assembly shown in FIG. 93;

[0107] FIG. 95 is an exploded perspective view of a motor, reduction gear, and second coupling assembly of the drive assembly shown in FIG. 92;

[0108] FIG. 96 is a perspective view of a flexible driveshaft assembly formed in accordance with an alternate embodiment of the present application;

[0109] FIG. 97 is a perspective view of the flexible driveshaft assembly of FIG. 96 with a portion thereof removed for clarity; and

[0110] FIG. 98 is an exploded view of the flexible driveshaft assembly of FIG. 97.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

[0111] FIGS. 1 and 2 illustrate one embodiment of a fold-out ramp assembly 20 (hereinafter “ramp assembly 20”) constructed in accordance with the present invention. The ramp assembly 20 includes a drive assembly 22, a ramp 24, a moving floor 26, and a counterbalance assembly 28. The ramp assembly 20 is adapted to be mounted to frame structure 30 of a vehicle (not shown), such as a bus, by mounting bracket 32. The ramp assembly 20 is reciprocal between a stowed position, as seen in FIG. 1, and a deployed position, as seen in FIG. 2. In the stowed position, the ramp 24 and moving floor 26 are stacked upon each other in a bi-fold manner, such that the lower surface of the ramp 24 is flush with the floor (not shown) of the vehicle. In the deployed position, the ramp extends outward and contacts a surface 29, such as a curb or roadside.

[0112] As seen best by referring to FIG. 3, the ramp 24 is hingedly attached to the moving floor 26 by the counterbalance assembly 28. The ramp 24 includes side curbs 34. The side curbs 34 extend upwardly from each side of the ramp 24. Each side curb 34 enhances structural strength of the ramp 24 and provides a bumper for the sides of the ramp 24, thereby increasing the safety of the ramp assembly 20. The ramp 24 is constructed from well-known materials, such as stainless steel, and, in one embodiment, includes upper and lower panels 36a and 36b spaced by a core 38. The core 38 is suitably corrugated stainless steel extending between opposing sides of the upper and lower panels 36a and 36b. The outboard edge of the ramp 24 includes a tapered nose portion 40. The ramp 24 is wedged shape in cross-section from the nose portion 40 to the inboard portion, which is attached to the counterbalance assembly 28.

[0113] The moving floor assembly 26 is similarly constructed to the ramp 24 and includes an upper panel 42 and a corrugated panel 44 welded to the upper panel 42 to increase stiffness and reduce weight of the structure. The inboard edge of the moving floor 26 is attached to the frame structure 30 by a pivot link assembly 46. The other end of the moving floor 26 is pivotally attached to the side curb 34, as is described in greater detail below. When mounted to the vehicle frame structure 30, the vehicle floor (not shown) is substantially flush and is in close proximity with the upper panel 42 of the moving floor 26 when the ramp 24 is in the deployed position to provide smooth transition between the moving floor 26 and the vehicle floor.

[0114] As noted above, when the ramp assembly 20 is in the stowed position, the lower panel 36b of the ramp 24 is substantially co-planar with the floor (not shown) of the vehicle, thereby providing a smooth transition between the floor of the vehicle and the ramp assembly 20. Because of the wedge contour of the ramp 24 and corresponding shape of the moving floor 26, when articulated into the stowed position, the ramp 24 is nested with the moving floor 26. In particular, the upper panel 36a of the ramp 24 is adjacent the upper panel 42 of the moving floor 26, such that the floor surface (which is the lower panel 36b of the ramp 24) of the ramp 24 is flush with the vehicle floor.

[0115] Referring now to FIGS. 4-8, the counterbalance assembly 28 will be described in greater detail. The counterbalance assembly 28 includes a fixed end 48 and a rotating end 50. The fixed end 48 includes a bearing block 52, a key insert 54, and a torsion tube shaft 58. The moving floor 26 is pinned to the ramp 24 at the boss and pin structure 56. As seen best in FIG. 5, the moving floor 26 includes a lug 60 extending from one end and the lug 60 is pinned to the side curb 34 by a boss and pin structure 56. Movement of the ramp 24 is tied to the moving floor 26, such that the moving floor 26 moves with corresponding movement of the ramp 24 between stowed and deployed positions, as is described in greater detail below. Received within the key insert 54 is one end of a torsion rod 62, thereby locking the fixed end 48 of the counterbalance assembly 28 to the bearing block 52 to resist rotation of the torsion rod 62, as is described in greater detail below.

[0116] Referring now to FIG. 6, the rotating end 50 of the counterbalance assembly 28 will now be described in greater detail. The rotating end 50 includes a key insert 64, a bearing block 66, and a boss and pin structure 68. The rotating end 50 is similar to the fixed end 48 described above, with the exception that the key insert 64 of the rotating end 50 is attached to a torsion tube shaft 70, which, in turn, is attached to the ramp 24 and rotates with the ramp 24, as is described in greater detail below.

[0117] Still referring to FIGS. 4-8, the counterbalance assembly 28 includes a torsion tube 72 extending between the fixed and rotating ends 48 and 50. The rotating end 50 also includes a sprocket 74 fixed to the torsion tube shaft 70, such that when the drive assembly 22 is attached to the sprocket 74, the torsion rod 62 is twisted within the counterbalance assembly 28.

[0118] In operation, one end of the torsion rod 62 is fixed to the torsion tube shaft 70 by the key insert 64, such that as the drive assembly 22 causes the ramp 24 to rotate, the rotating end 50 of the torsion rod 62 twists to counterbalance the weight of the ramp 24. This reduces the load to drive the ramp 24 between stowed and deployed positions, thereby reducing motor drive requirements as well as improved weight and cost savings. Also, the counterbalance assembly 28 reduces the force required to manually operate the ramp 24 between stowed and deployed positions. The counterbalance assembly 28 preloads the ramp 24 in the stowed or deployed positions and is maintained in any position between the deployed and stowed positions by the combined resistance of the drive assembly 22, including the gear motor and/or system friction. The neutral position for the counterbalance assembly 28 is when the ramp 24 is nearly vertical, such that in either the stowed or deployed positions, the counterbalance assembly 28 is loaded because the torsion rod 62 is twisted from its normal shape or condition. This results in reduced load and forces required to reciprocate the ramp 24 between its stowed and deployed positions.

[0119] Referring now to FIGS. 9-11, the pivot link assembly 46 will be described in greater detail. The pivot link assembly 46 includes a bracket 76, a pivot rod 78, a spacer 80, and first and second links 82a and 82b. The bracket 76 is adapted to be fastened to frame structure 30 by well-known fasteners, such as bolts and screws. The pivot rod 78 is attached by a well-known fastener, such as a weld, to one end of the first and second pivot links 82a and 82b. The other ends of the first and second pivot links 82a and 82b are pivotably attached opposite ends of the spacer 80. The inboard end of the moving floor 26 is pivotally attached to the pivot rod 78 by a well known fastener 90, such as a pin or shoulder screw, extending through a side plate 92 of the moving floor 26 and into the pivot rod 78.

[0120] Operation of the moving floor 26 may be best understood by referring to FIGS. 12-14. As the ramp 24 begins its actuation sequence from the stowed to the deployed position, the ramp 24 pivots about the counterbalance assembly 28. The moving floor 26 pivots about the spacer 80, and it also translates slightly outboard from its stowed position. Because the moving floor 26 is attached to the pivot link assembly 46 by the links 82a and 82b and attached to side curb 34 at boss 56, the moving floor acts as a coupler of a four bar linkage. Further, as the ramp 24 continues to the deployed position, the moving floor is raised upwardly to a position substantially flush with the floor of the vehicle by the pivot link assembly 46. Thus, as the ramp assembly 20 reciprocates between its deployed and stowed position, the moving floor 26 both rotates and translates into and out of flush position with the floor of the vehicle.

[0121] Referring now to FIGS. 15-30, a first alternate embodiment of a fold-out ramp 1020, formed in accordance with the present invention, will now be described in greater detail. The fold-out ramp assembly 1020 is identical in materials and operation as the embodiment described above, with the exception that a new counterbalance assembly 1028 is included. As may be best seen by referring to FIG. 17, this embodiment of the fold-out ramp assembly 1020 includes three bearing points 1092a, 1092b, and 1092c. The counterbalance assembly 1028 includes a torsion pin weldment assembly 1094, a counterbalance linkage assembly 1096, an adjustment assembly 1098, and a torsion bar 1100.

[0122] The torsion pin weldment assembly 1094 may be best understood by referring to FIGS. 18-21. The torsion pin weldment assembly 1094 includes first and second support brackets 1110a and 1110b, first and second cam pins 1112a and 1112b, and first and second stub shafts 1114a and 1114b. The first and second cam pins 1112a and 1112b extend laterally between the first and second support brackets 1110a and 1110b. The second stub shaft 1114b may be integrally formed with and extends laterally from the second support bracket 1110b. The first stub shaft 1114a includes a hex-shaped cavity 1115 extending partially therethrough and is sized to receive a correspondingly-shaped hex stub 1116b (FIG. 17) extending laterally from the ramp 1024. As a result, the ramp 1024 is keyed to the rotation of the torsion pin weldment assembly 1094.

[0123] Referring now to FIGS. 22-26, the counterbalance linkage assembly 1096 will now be described in greater detail. The counterbalance linkage assembly 1096 includes an arm 1120, a torsion arm 1122, a motor mount plate 1124, and a support plate 1126. The first and second stub shafts 1114a and 1114b of the torsion pin weldment assembly 1094 described above extend between opposed surfaces of the motor mount plate 1124 and a portion of the support plate 1126, which also includes bearings 1092b and 1092c sized to receive corresponding stub shafts 1114a and 1114b. The cam pins 1112a and 1112b of the torsion pin weldment assembly 1094 are positioned to engage a portion of the arm 1120, as described in greater detail below.

[0124] The torsion arm 1122 includes a clevis 1128 extending upwardly from the base of the torsion arm 1122. The clevis 1128 is sized to receive one end of the arm 1120 therebetween. The arm 1120 is rotatably attached within the clevis 1128 by a pin 1130 extending laterally through the clevis 1128 and the corresponding end of the arm 1120. The free end of the arm 1120 is cammed to included first and second saddles 1132a and 1132b.

[0125] As best seen by referring to FIG. 26, the first and second saddles 1132a and 1132b are sized to selectively receive the first and second cam pins 1112a and 1112b during actuation of the ramp platform 1024. The cam pins 1112a and 1112b are orientated such that when the ramp is rotated through its range of motion, each cam pin separately engages one of the two saddles 1132a and 1132b. One cam pin functions from the stowed ramp position to the vertical position. The other cam pin functions from the vertical position to the fully deployed ramp position. Typically, only one pin at a time correspondingly engages one of the two saddles 1132a and 1132b, thereby causing the torsion arm 1122 to rotate, and thus load the torsion rod 1100. The cam pins may simultaneously engage the saddles 1132a and 1132b when the ramp angle is nearly vertical, as seen in FIG. 26.

[0126] As may be best seen by referring back to FIG. 22, one end of the torsion bar 1100 is supported by the motor mount support plate 1124 and support plate 1126, and is keyed to the torsion arm 1122. The other end of the torsion bar 1100 is supported by a support block 1134 and is keyed to a tapered lever 1138 of an adjusting assembly 1098. The adjusting assembly 1098 allows preload or deadband adjustment of the counterbalance assembly 1028.

[0127] As best seen by referring to FIG. 27, the adjustment assembly 1098 includes a set screw 1136 and the tapered lever 1138. One end of the tapered lever 1138 is keyed to the torsion bar 1100 and is adapted to limit rotation of one end of the torsion bar 1100. The other end of the tapered lever 1138 is seated against the lower end of the set screw 1136. Adjustment of the set screw 1136 controls the preload or deadband stiffness of the torsion bar 1100.

[0128] Also seen in FIG. 27 is first bearing 1092a, which is sized and adapted to receive a corresponding stub shaft 1116a (FIG. 17) extending laterally from one end of the ramp 1024.

[0129] The ramp assembly 1020 in the fully deployed position may be best understood by referring to FIGS. 28-29. As seen in FIG. 29, only one of the two cam pins (1112b) of the torsion pin weldment assembly 1094 is seated within the saddle 1132b of the arm 1120.

[0130] The ramp assembly 1020 in the fully stowed position may be best understood by referring to FIGS. 30-32. In the fully stowed position, and as may be best seen by referring to FIG. 32, cam pin 1112a is seated in the first saddle 1132a of arm 1120.

[0131] The ramp assembly 1020 in the near vertical position may be best understood by referring to FIGS. 33-35. As may be best seen by referring to FIG. 35, in the near vertical 90° position, both cam pins 1112a and 1112b are seated within the first and second saddles 1132a and 1132b of the arm 1120.

[0132] Referring now to FIGS. 36-46, another embodiment of a fold-out ramp 2020 of the current invention will now be described in greater detail. This embodiment is identical in materials and operation to the invention described above, with the exception that a counterbalance assembly 2028 constructed in accordance with this embodiment of fold-out ramp assembly 2020 includes only two bearing points 2092a and 2092b instead of three bearing points.

[0133] As may be best seen by referring to FIGS. 42-46, the counterbalance linkage assembly 2096 includes an arm 2120 and a torsion arm 2122. In this embodiment, the rear stub shaft 2140 of the ramp assembly 2024 replaces the hex stub shaft 1116b of the first alternate embodiment. The rear shaft 2140 includes a spherical surface 2142 located on one end of the rear stub shaft 2140. The outer face of the rear stub shaft 2140 includes a pair of cavities 2144a and 2144b. Each cavity 2144a and 2144b is sized to receive a corresponding cam pin 2112a and 2112b. As an alternative, each cam pin may be integral with the rear stub shaft 2140.

[0134] Each cam pin 2112a and 2112b is fixed to rear stub shaft 2140 by welding or other means. Each cam pin 2112a and 2112b supports a bearing 2512. The bearings 2512a and 2512b engage saddles 2132a and 2132b of arm 2120. Torque rod 2100 is keyed to torque arm 2122 at one end and is keyed to tapered lever 2138 at the other end. Support block 2134 supports tapered lever 2138 on surface 2138a. Motor mount plate 2124 supports bearing block 2124a. Bearing 2124b is housed in bearing block 2124a (FIG. 39). Torsion arm 2122 is pivotally supported by bearing 2124b at surface 2122a. Thus, torsion arm 2122 is pivotally attached to motor mount plate 2124.

[0135] The counterbalance assembly 2028 includes a second stub shaft 2148 extending from the first bearing member 2192a. The rear stub shaft 2140 and stub shaft 2148, located in ramp platform 2024, are sized to be received within corresponding bearings 2092b and 2092a. Operation is the same as first alternate embodiment. Corresponding numbers start with 2xxx in place of 1xxx.

[0136] Referring now to FIGS. 47-68, a third alternate embodiment of the current invention will now be described in greater detail. Like the second alternate embodiment, the third alternate embodiment has two bearing points 3092a and 3092b. The fold-out ramp 3020, formed in accordance with the third embodiment of the present invention, is similar in materials and operation to the alternate embodiments described above with the following exceptions. First, elements of the counterbalance linkage assembly 3022 have been repositioned or redesigned. Second, a new drive assembly 3024 (FIG. 52) has been provided. The moving floor 26 and 1026 of the previous embodiments has been replaced with a rising floor 3026. A clutch assembly 3028 has been added. A unitized frame 3999 has been added. Finally, a stow latch assembly 3030 has been added. For conciseness, only the foregoing exceptions will be described in greater detail.

[0137] Referring to FIGS. 47-50, the counterbalance linkage assembly 3022 will now be described in greater detail. The counterbalance linkage assembly 3022 includes a torsion bar 3034, a torsion arm 3036, an actuating arm 3038, and an adjustment assembly 3039. The torsion bar 3034 is similar in operation and materials to the torsion bar 1100 (FIG. 22) described in the previous embodiments, except that it has been moved from the outboard side (curb side) of the fold-out ramp assembly 3020 to the inboard side (roadside). Specifically, the location of the torsion bar 3034 has been moved from the side of the ramp nearest the curb to a location towards the longitudinally extending centerline of the vehicle.

[0138] The actuating arm 3038 is similar in operation and materials to the actuating arm 1120 (FIGS. 22-26) described in the previous embodiments, except that it has been lengthened. As set forth above for the arm 1120, the actuating arm 3038 is suitably rotatably attached to torsion arm 3036 by a pin 3039 extending laterally through the corresponding end of the actuating arm 3038. The free end of the actuating arm 3038 is cammed to include first and second saddles 3040a and 3040b.

[0139] The torsion arm 3036 has been moved with the repositioned torsion bar 3034. The torsion arm 3036 is similar to materials and operation to the torsion arm 1122 (FIGS. 22-26) of the first embodiment and the torsion arm 2122 (FIGS. 42-46) of the second alternate embodiment. As best seen in FIG. 48, the linkage and operation of the torsion arm 3036 and the actuating arm 3038 have not changed in this third alternate embodiment. The torsion arm 3036 extends between the torsion bar 3034 and the actuating arm 3038. One end of the torsion arm 3036 is pinned to a corresponding end of the actuating arm 3038 by a well-known pin 3039. The other end of the torsion arm 3036 is keyed to an end of the torsion bar 3034.

[0140] As best seen in FIG. 49, the free end of the actuating arm 3038 has first and second saddles 3040a and 3040b. First and second bearings 3042a and 3042b are positioned on the end of first stub shaft 3046a and engage saddles 3040a and 3040b in the same general way as described in the previous embodiments. Similar to the previous embodiments described above, rotation of first stub shaft 3046a is keyed to the rotation of the ramp platform 3044, such that when the ramp is rotated through its range of motion, the bearings 3042a and 3042b engage the first and second saddles 3040a and 3040b, stroking the actuating arm 3038 and thereby causing the torsion arm 3036 to rotate and place a load upon the torsion bar 3034. As the end of the torsion bar 3034 is rotated by the torsion arm 3036, the torsion bar 3034 twists to counterbalance the weight of the ramp.

[0141] Referring now to FIG. 50, the adjustment assembly 3039 will now be described in greater detail. The adjustment assembly 3039 includes a torsion rod assembly 4040, a torsion lever weldment 4042, and a torsion anchor assembly 4044. The torsion rod assembly 4040 includes an anchor assembly 4050, first and second retaining rings 4052a and 4052b, and an anchor eccentric 4054. The anchor assembly 4050 is a substantially oblong link having a pair of sleeve bearings 4056a and 4056b disposed within opposite ends of the anchor assembly 4050. The torsion rod assembly 4040 is fastened to the frame assembly by a pin 4060 extending through the first sleeve bearing 4056a and fastened thereto by the first retaining ring 4052a.

[0142] Rotatably disposed within the second sleeve bearing 4056b is the anchor eccentric 4054. The anchor eccentric 4054 includes a lever arm 4058 fastened to the anchor eccentric 4054 by the second retaining ring 4052b. The anchor eccentric 4054 is attached to one end of the torsion lever weldment 4042. The other end of the torsion lever weldment 4042 is keyed to an end of the torsion bar 3034.

[0143] As attached, the torsion bar 3034 extends through the torsion lever weldment 4042. The torsion lever weldment 4042 extends through the torsion anchor assembly 4044 and is seated in one end of the torsion anchor assembly 4044. As seated within the torsion anchor assembly 4044, the torsion bar 3034 is retained therein by a retaining ring 4062. The torsion rod assembly 4040 includes a pair of spring pins 4064a and 4064b and is rigidly fastened to the ramp assembly by a well-known lock nut 4066 and hex screw 4068.

[0144] To preload the torsion bar 3034, a hex wrench (not shown) is inserted through a bore 4070 located in one end of the lever arm 4058 and into hex bore 4070a of eccentric 4054. The lever arm 4058 and eccentric 4054 are rotated into the position illustrated in FIG. 50. A well-known hex-head cap screw 4072 is inserted into the other end of the lever arm 4058 and into an internally threaded bore (not shown) located substantially midway between the first and second sleeve bearings 4056a and 4056b of the anchor assembly 4050. To remove the preload from the torsion bar 3034, the hex-head cap screw 4072 is removed and the lever arm 4058 of the anchor eccentric 4054 is rotated substantially 180° from the position illustrated in FIG. 50.

[0145] Referring now to FIGS. 51 and 52, the drive assembly 3024 will be described in greater detail. The drive assembly 3024 includes a gear motor 3052 and an idler and roller chain assembly 3054. The well-known gear motor 3052 is connected to a clutch 3028, which is connected to the idler and roller chain assembly 3054. The gear motor 3052 is keyed to the rotation of the ramp platform 3044 by way of the idler and roller chain assembly 3054. A suitable gear motor 3052 is Model Number IM-15, manufactured by Globe Motor.

[0146] As best illustrated in FIG. 52, the idler and roller chain assembly 3054 includes first and second sprocket assemblies 4080a and 4080b, an idler assembly 4082, a chain tension assembly 4084, and a drive chain 3056. The first sprocket assembly 4080a is fixed to one end of the second stub shaft 3046b, which is in turn keyed to rotation of the ramp platform 3044. As an alternative, the first sprocket assembly 4080a may be integral with the second stub shaft 3046b. Rotation of the first sprocket 4080a is keyed to the rotation of the second sprocket 4080b by the drive chain 3056.

[0147] The second sprocket assembly 4080b includes a retainer 4088, a retaining ring 4090, and a sprocket 4092. The second sprocket assembly 4080b is keyed to the clutch shaft 4154 at hex key 4154a (FIG. 57).

[0148] Still referring to FIG. 52, the chain tension assembly 4084 will now be described in greater detail. The chain tension assembly includes a chain tension weldment 4100, an idler 4102, a spacer 4104, and a square head set screw 4106. The chain tension weldment 4100 is keyed to the drive chain 3056 and includes a torsion arm retainer 4108 and a retaining ring 4110. A pair of cap screws 4112a and 4112b extends through opposite ends of the spacer 4104 and is operatively coupled to the set screw 4106.

[0149] Chain tension weldment 4100 is keyed at 4100b and 4100c and moves slideably on frame 3999 at guides 3999b and 3999c, respectively. Guides 3999b and 3999c form opposite sides of slot 3999a. The head of set screw 4106 rests against the end of slot 3999a. Chain tension weldment is also slotted along the axis of set screw 4106 to allow clamping action when cap screws 4112a and 4112b are tightened.

[0150] As coupled to the set screw 4106, the tension in the drive chain 3056 may be adjusted to increase or decrease the tension in the drive chain 3056 by unclamping setscrew 4106 by loosening cap screws 4112a and 4112b, turning set screw 4106, which moves chain tension weldment 4100 and thus idler 4102 along guides 3999b and 3999c, then clamping set screw 4106 by tightening cap screws 4112a and 4112b.

[0151] Referring now to FIGS. 53-56, the rising floor 3026 will now be described in greater detail. The rising floor 3026 is similar in material and operation to the moving floor 26 and 1026 (FIGS. 2 and 15), except that when the ramp assembly is in the deployed position, the rising floor 3026 is made substantially flush to the vehicle floor by way of a cam and roller assembly 3062 (FIG. 54) instead of a pivot and link assembly 46.

[0152] The rising floor 3026 includes a floor weldment 4120, attachment arms 4122, and roller assemblies 4124. The floor weldment 4120 is substantially rectangular and forms the outside perimeter frame structure for the rising floor 3026. The attachment arms 4122 are suitably integrally formed with the floor weldment 4120 and project upwardly from the planar area of the rising floor 3026. The free ends of the attachment arms 4122 include a notch 4126 formed in the lower surface of each attachment arm 4122. The notches 4126 are sized to be slidably received on a pin 4128 projecting inwardly from each side of the ramp platform 3044 in an opposing manner. Attachment arms 4122 are similar in material and operation of lugs 60 of the first embodiment.

[0153] As seen best by referring to FIG. 54, the roller assembly 4124 includes a sleeve bearing 4130 and a retaining ring 4132. The roller assembly 4124 is coupled to the interior facing side of the frame weldment 4120 on a pin 4134. The roller assembly 4124 is fastened to the pin 4134 by the retaining ring 4132. As is described in greater detail below, the roller assembly 4124 is adapted to be received within a cam plate 4140. Although a single roller assembly 4124 is illustrated, it should be apparent that a second roller assembly identical to the first roller assembly 4124 is located on the opposite side of the frame weldment 4120, such that a pair of roller assemblies 4124 is located on opposite sides of the frame weldment 4120.

[0154] In operation, as the rising floor 3026 strokes with the rotation of the ramp platform 3044, it raises and is maintained at a level substantially flush with the adjacent vehicle floor (not shown), whether the ramp is deployed to a high curb or to ground level. To facilitate removal of the rising floor 3026, the cam plate 4140 is open above the roller and the lugs 4122 on the outboard end, which captures the trunion pins 4128 on the ramp, are open on the bottom 4126. Therefore, there are no pins or fasteners to remove in order to remove the rising floor from the ramp assembly.

[0155] As best seen by referring to FIGS. 54-56, the cam plate 4140 is suitably formed from material, such as steel. The cam plate 4140 is contoured to position the rising floor 3026, such that it is either flush with the vehicle floor when the ramp assembly is in the deployed position or in a nested position when the ramp assembly is in the stowed position. In that regard, the cam plate 4140 includes a raised flat surface 4142, a sloping surface 4144, and a lower flat surface 4146.

[0156] As noted above, the roller assembly 4124 is sized to be received within the cam plate 4140, such that when the roller assembly 4124 is positioned on the raised flat surface 4142, the rising floor 3026 is flush with the vehicle floor. When the roller assembly 4124 is seated on the lower flat surface 4146 of the cam plate 4140, the rising floor 3026 is in a position below the vehicle floor, such that the articulating portion of the ramp platform 3044 is disposed on top of the rising floor 3026. As disposed on top of the rising floor 3026, the articulating portion of the ramp platform 3044 is flush with the vehicle floor, thereby providing a level floor within the vehicle. The sloped surface 4144 extends between the raised flat surface 4142 and the lower flat surface 4146 to provide a smooth transition between the deployed and stowed positions.

[0157] Referring now to FIGS. 57-59, the clutch assembly 3028 will now be described in greater detail. The clutch assembly 3028 includes a clutch hub 4150, a clutch housing 4152, and a clutch shaft 4154. The clutch hub 4150 is suitably a cylindrical member having a centrally located bore 4156 extending through the length of the clutch hub 4150. The bore 4156 is sized and adapted to receive the output shaft of the gear motor 3052, and is fastened to the output shaft by well-known fasteners, such as a key and set screw (not shown), extending through fastener holes 4158 located in the clutch hub 4150. The clutch hub 4150 is coupled to the clutch housing 4152 by well-known pins 4160 extending through the clutch housing 4152 and into the clutch hub 4150. As attached to the clutch housing 4152, torque is transferred from the clutch hub 4150 to the clutch housing 4152. Each pinhole of the clutch housing 4152 is sized to receive pins 4160 with sufficient clearance to allow the clutch assembly to center itself.

[0158] The clutch housing 4152 is hex-shaped in cross-section and is suitably a tubular member sized to slidably receive the clutch shaft 4154 therein. The clutch shaft 4154 includes a plurality of friction disks 4162 and stainless steel shims 4164. The clutch assembly 3028 also includes a spacer 4166, a spring pad 4168, a spring washer 4170, and first and second hex jam nuts 4172 and 4174. The outside diameter of the friction discs 4162 is hex-shaped to key with the interior of the clutch housing 4152 and, therefore, rotates with the clutch hub 4150 and the clutch housing 4152. The interior diameter of each shim 4164 is hex-shaped to key with the exterior of the clutch shaft 4154.

[0159] A retaining ring 4176 is disposed at one end of the clutch shaft 4154. Alternating friction discs 4162 and shims 4164 are slidably stacked on the clutch shaft 4154. The spacer 4166 is disposed between the spring pad 4168 and the last friction disc 4162. The spring washer 4170 is then slidably disposed on the clutch shaft 4154, and then the first and second hex jam nuts 4172 and 4174 are threadably fastened to the clutch shaft 4154, thereby fastening the structure to the clutch shaft 4154. As an alternative, a suitably sized compression spring may be used in lieu of spring washer 4170. The assembled clutch shaft 4154 is then slidably received within the clutch housing 4152, such that one end of the clutch shaft 4154 is radially seated within the clutch hub 4150. The other end of the clutch shaft 4154 extends outwardly from the clutch housing 4152 and is keyed for a drive sprocket 4092 (see FIG. 52). The other end of the clutch shaft 4154 also extends through frame 3999 at bearing 3998 (see FIG. 51).

[0160] Referring now to FIGS. 55, 56, and 60-68, the stow latch assembly 3030 will now be described in greater detail. The stow latch assembly 3030 includes a locking assembly 4190 and a handle assembly 3096. As best seen by referring to FIGS. 55 and 56, the locking assembly 4190 includes a latch plate 4194, a stop block 4196, a linkage assembly 4198, and a solenoid 4200. The latch plate 4194 is formed from a substantially flat rectangular plate of a thin gauge spring steel folded over onto itself, such that a live spring hinge 4202 is formed at the bend in the plate. As formed, the spring hinge 4202 extends between an attachment portion 4204 and a latch portion 4206.

[0161] The attachment portion 4204 is fixed to the ramp frame 3999 by well-known fasteners 4208, such as screws or rivets.

[0162] The free end of the latch portion 4206 is suitably bent to form a seat 4212. The seat 4212 is adapted to receive a portion of the linkage assembly 4198, as is described in greater detail below.

[0163] The stop block 4196 is suitably formed from a material, such as steel, and is a substantially rectangular member fastened to the ramp frame 3999 at a position below the locking assembly 4190. The stop block 4196 is rigidly attached to the ramp frame 3999 by well-known fasteners, such as bolts or rivets. The stop block 4196 is adapted to support the ramp platform in the stowed position, wherein the handle block 3116 of handle assembly 3096 bears on stop block 4196 (see FIG. 64). A portion of the linkage assembly 4198 is pivotally attached to the stop block 4196.

[0164] As may be best seen by referring to FIGS. 55, 56, and 62, the linkage assembly 4198 includes a latch release lever 4220, an actuating link 4222, and a coil spring 4224. The latch release lever 4220 is a substantially rectangular member pivotally attached to the stop block 4196 by a pin 4226 extending laterally through the midsection of the latch release lever 4220. One end of the latch release lever 4220 is disposed against the seat 4212 of the latch plate 4194. The other end of the latch release lever 4220 is coupled to one end of the actuating link 4222 by a pin (not shown). As attached to the latch release lever 4220, the actuating link 4222 pivots the latch release lever 4220 about the pin 4226 to displace the latch portion 4206 into an unlocked position (FIG. 56), such that the seat 4212 of latch plate 4194 disengages handle block 3116.

[0165] The other end of the actuating link 4222 is operatively connected to the solenoid 4200 and the coil spring 4224. As best seen by referring to FIG. 62, the actuating link 4222 is bent at two right angles, such that one end of the actuating link 4222 forms a substantially reverse S-shape. The coil spring 4224 extends between an attachment bore 4228 and an attachment arm 4230. The attachment arm 4230 is rigidly attached to the ramp frame 3999 in a manner well known in the art. As attached, the coil spring 4224 biases the stow latch assembly 3030 into the locked position, as seen best by referring to FIG. 55.

[0166] Referring now to FIGS. 67 and 68, the handle assembly 3096 will now be described in greater detail. Attached to the outboard side of the ramp platform 3044, the handle assembly 3096 includes a pull handle 3112, handle bias spring 3114, and a handle block 3116.

[0167] The operation of the stow latch assembly 3030 is best seen in FIG. 64, where the latch plate 4194 engages the handle block 3116 when the ramp platform 3044 is in the stowed position. During normal powered operations, when deploy is selected, the solenoid 4200 actuates the latch release lever 4220, which in turn causes the latch plate 4194 to disengage the handle block 3116 (FIG. 66). When deploying the ramp manually from the stowed position, the operator lifts the pull handle 3112, which disengages the latch plate 4194 from the handle block 3116, enabling the operator to simply lift up the ramp platform 3044.

[0168] Referring now to FIGS. 69-89, another embodiment of a fold-out ramp assembly 5020 of the current invention will now be described. This embodiment is identical in materials and operation to the invention described above, with a few exceptions. In that regard, portions of an adjustment assembly 5039, a counterbalance linkage assembly 6000, and a torsion bar 5034 have been modified as described below. Inasmuch as the remaining elements of this embodiment are identical in materials and operation to the embodiments described above, for the sake of brevity, they will not be redundantly described below.

[0169] As may best be seen by referring to FIGS. 69-72, the adjustment assembly 5039 of the present embodiment will now be described. Generally, the adjustment assembly 5039 provides an assembly to adjust the magnitude or amount of a preload or torque applied to a ramp 5021 to counterbalance the weight of the ramp 5021 during deployment and stowage. The adjustment assembly 5039 includes a yoke 5024 adjustably coupled to a pivot block 5030. A first end of the yoke 5024 includes a clevis 5025 pivotally coupled to a torsion lever arm 5042 by a pin 5032. A second end of the yoke 5024 is adjustably coupled to the pivot block 5030 by a loading screw 5028. The loading screw 5028 is suitably an externally threaded fastener having threads sized and configured to be threadably received within a set of internal threads (not shown) disposed in the second end of the yoke 5024. Through rotation of the loading screw 5028, the spacing of the pin 5032 from the pivot block 5030 may be selectively adjusted, thereby causing a corresponding rotation of the torsion lever 5042 and a torsion bar attached thereto, as described in further detail below.

[0170] A base portion of a head 5044 of the loading screw 5028 includes a spherically-shaped mating surface 5040 sized and shaped to be received within a correspondingly spherically-shaped mating surface 5041 on the pivot block 5030. The interfacing spherically shaped mating surfaces 5040 and 5041 may be angularly displaced to accommodate misalignment of the pivot block 5030 relative to the yoke 5024, thereby accommodating changes in yoke 5024 angle as the adjustment assembly 5039 is adjusted.

[0171] Focusing now on the pivot block 5030, the pivot block 5030 includes an inner passageway to accommodate the passage of the loading screw 5028 therethrough. The pivot block 5030 suitably couples the yoke 5024 to a frame side rail 5035 of the fold-out ramp assembly 5020. As best seen by referring to FIG. 70, the pivot block 5030 includes a groove 5036 that engages a tongue 5038 in the frame side rail 5035. The tongue 5038 and groove 5036 are correspondingly sized and shaped to allow the tongue 5038 to slidingly engage the groove 5036, thereby coupling the pivot block 5030 to the frame side rail 5035.

[0172] Referring now to FIGS. 71 and 72, a guard 5026 for impeding the removal of a torsion lever arm assembly 5022 from the frame side rail 5035 when the adjustment assembly 5039 is in a loaded condition, will now be described. The guard 5026 is coupled to the yoke 5024 and includes first and second blocking prongs 5046 and 5048. The blocking prongs 5046 and 5048 are sized and positioned to impede the removal of a first mounting screw 5050 and a second mounting screw 5052 when the adjustment assembly 5039 is in a loaded condition, i.e., wherein the torsion bar 5034 (see FIG. 73) is in a twisted position. The first and second mounting screws 5050 and 5052 couple the torsion lever arm assembly 5022 to the frame side rail 5035. When the adjustment assembly 5039 is in the loaded condition, the first and second blocking prongs 5046 and 5048 are positioned on the outboard side of the first and second mounting screw 5050 and 5052. As such, the blocking prongs 5046 and 5048 selectively block access to mounting screws 5050 and 5032 and, thereby, prevent removal of the mounting screws 5050 and 5052.

[0173] Referring now to FIG. 72, the adjustment assembly 5039 may be placed in an unloaded condition by rotating the loading screw 5028. Rotating the loading screw 5028 changes the effective length of yoke 5024. From a viewpoint at the head of the unloading screw 5028, a counter-clockwise rotation increases the length of the yoke 5024. This increased length causes a rotation of torsion lever arm 5042 within torsion lever arm assembly 5022 and untwists torsion bar 5034. Thus the preload torque applied by the torsion lever arm 5042 upon the torsion bar 5034 is relieved, thereby placing the torsion bar 5034 in a non-twisted or neutral position, referred to as an unloaded condition.

[0174] In the unloaded condition, as depicted in FIG. 72, the guard 5026 has moved into a position where the first and second blocking prongs 5046 and 5048 no longer substantially impede access to the first and second mounting screws 5050 and 5052 allowing removal of the torsion lever arm assembly 5022. Thus, it should be apparent to one skilled in the art that the guard 5026 impedes the removal of the first and second mounting screws 5050 and 5052 when the torsion bar 5034 is in a twisted or loaded condition and allows access to the screws 5050 and 5052 when the torsion bar 5034 is in the unloaded condition.

[0175] Still referring to FIG. 72, the pivot block 5030 may be disengaged from the yoke 5024 by rotation of the loading screw 5028 until a point where the loading screw 5028 disengages from the yoke 5024. The pivot block 5030 may then slide, either back or forth, as shown by the arrow indicated by reference numeral 5054, to disengage the tongue 5038 (FIG. 70) from the groove 5036 in the pivot block 5030. After the tongue 5038 is disengaged from the groove 5036, the pivot block 5030 may be pulled outward free and clear of the fold-out ramp assembly 5020. As should be apparent to one skilled in the art, the removal of the pivot block 5030 may only be accomplished when the torsion bar is in the unloaded condition. Pin 5032 can now be removed through access hole 5056 in frame rail 5035. Then yoke 5024 can be removed clear of the ramp assembly 5020. Pin 5032 has a head such that when the adjustment assembly 5039 is loaded, the head of the pin is captive between the inboard surface of clevis 5025 and the frame slide rail 5035.

[0176] Referring to FIGS. 73-77, the torsion lever arm assembly 5022 will now be described in further detail. The torsion lever arm assembly 5022 includes a bracket 5062, the torsion lever arm 5042, and a bearing block 5082. Referring to FIGS. 76 and 77, the torsion lever arm bracket 5062 is generally an elongate rectangular-shaped block. A first end of the torsion lever arm bracket 5062 includes first and second mounting screw apertures 5072 and 5074. The mounting screw apertures 5072 and 5074 allow the coupling of the torsion lever arm bracket 5062 to the frame side rail 5035 through the use of the first and second mounting screws 5050 and 5052 (see FIG. 72).

[0177] The second end of the torsion lever arm bracket 5062 includes first and second fastener apertures 5086 and 5088. The fastener apertures 5086 and 5088 allow the coupling of the bearing block 5082 to the torsion lever arm bracket 5062 by first and second fasteners 5068 and 5070. The torsion lever arm bracket 5062 further includes a torsion bar access hole 5090 located between the first and second fastener apertures 5086 and 5088. The torsion bar access hole 5090 allows the torsion bar to extend through the access hole 5090 to engage the torsion lever arm 5042. Once bracket 5062 is attached to frame side rail 5035, the first and second fasteners 5068 and 5070 are not accessible. Thus, all the features of adjustment assembly 5039 form a safety assembly requiring that the torsion bar 5034 be unloaded before the removal of any mounting fasteners or pins.

[0178] Referring FIG. 76, the torsion lever arm 5042 will now be described in further detail. The torsion lever arm 5042 includes a circular base portion 5092 integrally formed with an arm 5094. Concentrically located in the circular base portion 5092 is a lobed spline receptacle 5064 for receiving a correspondingly shaped lobed spline end 5096 of the torsion bar 5034 (see FIGS. 78 and 79). The lobed spline interconnection of the torsion lever arm 5042 to the torsion bar 5034 keys the torsion lever arm 5042 to the torsion bar 5034, while also providing a large contact surface area and reduced pressure angles between mating parts to increase the strength of the coupling. Located at a distal end of the arm 5094 is a pin-receiving aperture 5098 sized and shaped to receive the pin 5032 that interconnects the yoke 5024 (see FIG. 70) to the arm 5094.

[0179] Still referring to FIGS. 76 and 77, the bearing block 5082 will now be described in greater detail. The bearing block 5082 includes a rectangular-shaped base plate 5100. Integrally formed on opposite ends of the base plate 5100 are first and second saddle bearings 5076 and 5078. Opposed ends of the first and second saddle bearings 5076 and 5078 each includes an arcuate surface 5102. The curvature of the arcuate surfaces 5102 is sized and shaped to correspond to the circular base portion 5092 of the torsion lever arm 5042. As such, the first and second saddle bearings 5076 and 5078 cradle the circumferential surface of the torsion lever arm 5042 within the arcuate surfaces 5102, thereby impeding the movement of the lever arm 5042 in a direction other than rotary.

[0180] To reduce wear and friction, and thereby assist the rotary motion of the torsion lever arm 5042, the first and second saddle bearings 5076 and 5078 each further includes a strip of bearing material 5080 having a low coefficient of friction. The bearing material 5080 is secured to the arcuate surfaces 5102 of the saddle bearings 5076 and 5078 by well-known fasteners 5084, such as rivets.

[0181] Referring now to FIGS. 80-89, the counterbalance linkage assembly 6000 of the fold-out ramp assembly 5020 will now be described in further detail. The counterbalance linkage assembly 6000 is suitably located on a side of the ramp assembly 5020 opposite the adjustment assembly 5039, shown in FIG. 69. As seen best by referring to FIGS. 81-83, the counterbalance linkage assembly 6000 includes a torsion lever assembly 6022 and a counterbalance actuating arm 6002. The torsion lever assembly 6022 is similar in design and operation as the torsion lever arm assembly 5022 shown in FIGS. 69-79, and therefore will not be discussed in further detail here. The counterbalance actuating arm 6002 is similar in design and operation to the actuating arm 3038 depicted in FIGS. 47-49. Therefore, for brevity, this detailed description will focus on the distinguishing aspects of the counterbalance actuating arm 6002 of this embodiment.

[0182] Referring to FIGS. 81-89, the counterbalance actuating arm 6002 is suitably coupled to the torsion lever arm assembly 6022 by a clevis 6020. The clevis 6020 is formed by attaching an outboard clevis plate 6004 to the outboard surface of the counterbalance actuating arm 6002 and by further placing an inboard clevis plate 6006 to the inboard surface of the counterbalance actuating arm 6002. A pin-receiving aperture 6008 is located in the outboard clevis plate 6004. Likewise, concentrically aligned with the pin-receiving aperture 6008 is a corresponding pin-receiving aperture 6010 located in the distal end of the inboard clevis plate 6006.

[0183] A pin 6009 is placed through the receiving apertures 6008 and 6010 of the clevis plates 6004 and 6006, thereby coupling the counterbalance actuating arm 6002 to the torsion lever arm assembly 6022. The pin 6009 must be aligned with a pin access hole 6012 located in the frame side rail 6024. The pin access hole 6012 is suitably located in the frame side rail 6024 in such a position so as to be concentrically aligned with the pin 6009 when the adjustment assembly 5039 is in the unloaded condition. After the adjustment assembly 5039 is placed in the unloaded condition and the pin 6009 is aligned with the pin access hole 6012, the pin 6009 may be pressed inboard and through the pin access hole 6012. The pin 6009 may then be removed, decoupling the actuating arm 6002 from the torsion lever arm assembly 6022. Pin 6009 has a head similar to pin 5032 of the adjustment assembly 5039. The head of pin 6009 is captive between the inboard clevis plate 6006 and the frame side rail 6024 when the counterbalance linkage assembly 6000 is in the loaded position.

[0184] Referring to FIGS. 81-89, integrally formed with the outboard clevis plate 6004 are first and second blocking prongs 6016 and 6018. The first and second blocking prongs 6016 and 6108 perform the same purpose and function as the guard 5026 associated with the adjustment assembly 5039 depicted in FIGS. 70-74. Specifically, the first and second blocking prongs 6016 and 6018 impede the removal of the torsion lever arm assembly 6022 when the torsion bar is in a loaded condition. For example, referring to FIG. 82, the counterbalance linkage assembly 6000 is shown in the loaded condition. As a result, the first and second blocking prongs 6016 and 6018 prevent the removal of first and second mounting screws 6026 and 6028. The first and second mounting screws 6026 and 6028 couple the torsion lever arm assembly 6022 to the frame side rail 6024. Referring to FIG. 83, the counterbalance linkage assembly 6000 is shown in the unloaded condition and the first and second blocking prongs 6016 and 6018 are displaced laterally, thereby permitting the removal of the mounting screws 6026 and 6028, and thus the removal of the torsion lever arm assembly 6022 from the frame side rail 6024.

[0185] Although the preferred embodiments of the present invention have been described above, it should be apparent that changes may be made thereto and still be within the scope of the present invention. As a nonlimiting example, the cam pins may be integrally formed with the rear stub shaft. Further, a manually operated fold-out ramp is also within the scope of the present invention. In this regard, such a fold-out ramp may be manufactured without the drive assembly and, therefore, manually reciprocated between stowed and deployed positions. As another nonlimiting example, the reciprocating mechanism could independently drive the ramp and the raising floor.

[0186] Referring now to FIGS. 90-95, a fold-out ramp assembly 7000 formed in accordance with another embodiment of the present application will now be described. This embodiment is identical in materials and operation to the embodiments described above, with the following exception. In that regard, this embodiment utilizes a flexible drive assembly or dampener 8000, as described below. Inasmuch as the remaining elements of this embodiment are identical in materials and operation to the embodiments described above, for the sake of brevity, they will not be redundantly described herein.

[0187] Referring now to FIGS. 90-92, the drive assembly 8000 includes a motor 7052 and an idler and roller chain assembly 7054. The well-known electric motor 7052 is connected to a reduction gear 7028, which is connected to the idler and roller chain assembly 7054 by a flexible driveshaft assembly 8001. Rotation of the ramp platform 7044 is actuated by the idler and roller chain assembly 7054, as described in more detail immediately following.

[0188] As best illustrated in FIG. 92, the idler and roller chain assembly 7054 includes first and second sprocket assemblies 7080a and 7080b, an idler assembly 7082, a chain tension assembly 7084, and a drive chain 7056. The first sprocket assembly 7080a is fixed to one end of a stubshaft 7046, which in turn is keyed to the rotation of the ramp platform 7044 (see FIG. 91). As connected, rotation of the first sprocket assembly 7080a causes the subsequent rotation of the ramp platform.

[0189] Rotation of the first sprocket assembly 7080a is keyed to the rotation of the second sprocket assembly 7080b by the drive chain 7056. The second sprocket assembly 7080b is coupled to one end of the flexible driveshaft assembly 8001. Thus, rotation of the flexible driveshaft assembly 8001 (through the use of the motor 7052 and accompanying reduction gear 7028) causes the rotation of the second sprocket assembly 7080b. Inasmuch as the first and second sprocket assemblies 7080a and 7080b are coupled to one another by the drive chain 7056, the rotation of the second sprocket assembly 7080b causes the first sprocket assembly 7080a to rotate, thereby actuating the ramp platform 7044 (See FIG. 91) between the stowed and deployed positions in the same manner as described for the previous embodiments.

[0190] Referring to FIGS. 92-95, the components of the flexible driveshaft assembly 8001 will now be discussed in further detail. The flexible driveshaft assembly 8001 includes a first coupling assembly 8002 for coupling the flexible driveshaft assembly 8001 to the idler and roller chain assembly 7054. The flexible driveshaft assembly 8001 also includes a second coupling assembly 8004 (FIG. 95) for coupling the flexible driveshaft assembly 8001 to the reduction gear 7028.

[0191] The flexible driveshaft assembly 8001 includes a flexible driveshaft 8006 formed by a plurality of spiders 8008 interconnected with a plurality of torque transfer members 8010 in a stacked relationship. The spiders 8008 are received upon an alignment shaft 8012 that passes axially through the center of the spiders 8008 and torque transfer members 8010. The alignment shaft 8012 supports both the spiders 8008 and torque transfer members 8010 during operation, aiding in maintaining the alignment of the spiders 8008 and absorbing side loads produced during use and radial forces produced through gravity and chain pull. In another embodiment of the present application, the torque transfer members 8010 are supported by the interlocking relationship with adjacent spiders 8008, such that the torque transfer members 8010 are not supported by the alignment shaft 8012. Accordingly, such an embodiment is also within the scope of the present application.

[0192] As best seen by referring to FIGS. 93 and 94, the first coupling assembly 8002 transfers torque generated in the flexible driveshaft 8006 to the alignment shaft 8012. The first coupling assembly 8002 includes a first coupling half 8014, a clamping collar 8018, and a thrust collar 8020. It should be noted that the previously described embodiments refer to the thrust collar 8020 as a “bearing.” (See bearing 3998).

[0193] The first coupling half 8014 includes an annular body 8022 with three dogs or jaws 8024 projecting outwardly from the annular body 8022 at spaced intervals. The jaws 8024 are configured to cooperatively interface with the spiders 8008, as will be discussed in further detail below. As noted above, the first coupling half 8014 suitably includes three jaws 8024. It should be apparent to those skilled in the art that a coupling half suitable for use with the present application may have any number of jaws, either higher or lower in number, than the illustrated number of jaws. The first coupling half 8014 further includes a bore 8026 extending through its body. The diameter of the bore 8026 selected so as to receive the alignment shaft 8012 therein.

[0194] The clamping collar 8018 is suitably an annular body having a bore 8042 sized to receive the alignment shaft 8012 therein. The clamping collar 8018 includes a well known fastener 8044, such as a screw, to selectively tighten or loosen the clamping collar 8018 along the length of the alignment shaft 8002. Although a specific manner of locking the clamping collar 8018 to the alignment shaft 8012 is illustrated, it should be apparent that other methods of retaining the collar 8018 upon the alignment shaft 8012 are equally suitable for use and within the spirit and scope of the present invention.

[0195] The thrust collar 8020 is a well known bushing having a concentrically and axially aligned bore 8048 for rotatingly receiving the alignment shaft 8012. The outer diameter of the thrust collar 8020 is sized to be received by a bore (not shown) in a frame 7999 of the fold-out ramp assembly 7000, such that the alignment shaft 8012 may rotate freely within the thrust collar 8020. The thrust collar 8020 also serves to maintain the lateral alignment of the alignment shaft 8012.

[0196] Referring to FIG. 94, the alignment shaft 8012 is suitably an elongate shaft having a reduced diameter portion 8030 and a standard diameter portion 8032, thereby creating a step or shoulder 8034 at the interface of the reduced and standard diameter portions 8030 and 8032. The distal end of the alignment shaft 8012 includes a sprocket receiving portion 8036. The sprocket receiving portion 8036 suitably includes a hexagonal shaped (in cross-section) segment 8038 for receiving the sprocket of the first sprocket assembly 7080b, and a grooved portion. The grooved portion of the alignment shaft 8012 is sized and configured to receive a sprocket retaining clip 8040 (FIG. 93) of the first sprocket assembly 7080b for retaining the sprocket 7079 upon the alignment shaft 8012 such that any rotation of the alignment shaft 8012 is transferred to the sprocket 7079.

[0197] During assembly of the first coupling assembly 8002 to the alignment shaft 8012, the first coupling half 8014 is slidably received upon the standard diameter portion 8032 of the alignment shaft 8012. A keyway 8046 formed within the interior diameter of the first coupling half 8014 lockingly engages a correspondingly shaped key 8028 received within the alignment shaft 8032 in a manner well known in the art. Engagement between the key 8028 and keyway 8046 prevents rotation of the first coupling half 8014 relative to the alignment shaft 8012. Thus, any torque exerted upon the first coupling half 8014 is transferred to the alignment shaft 8012, or vice versa, via the key 8028.

[0198] The clamping collar 8018 is slid axially along the length of the alignment shaft 8012 until the clamping collar 8018 abuts against the first coupling half 8014. The clamping collar 8018 is then locked in position by the fastener 8044, thereby limiting the axially movement of the first coupling half 8014. Next, the thrust collar 8020 is slid along the reduced diameter portion 8030 of the alignment shaft 8012 until the thrust collar 8020 engages the shoulder 8034 at the interface of the reduced diameter portion 8030 and the standard diameter portion 8032.

[0199] Referring now to FIG. 95, the second coupling assembly 8004 includes a second coupling half 8016. The second coupling half 8016 is substantially similar to the first coupling half 8014, and includes an annular body 8050 with a plurality of dogs or jaws 8052 projecting axially outward from the annular body 8050 at spaced intervals. The jaws 8052 are suitably configured to cooperatively interface with the a spider 8008, as will be discussed in further detail below. In the illustrated embodiment, the second coupling half 8016 has a total of three jaws 8052, although it should be apparent to those skilled in the art that a coupling half suitable for use with the present application may have any number of jaws, either higher or lower in number, than the illustrated number of jaws.

[0200] The second coupling half 8016 includes a bore 8054 extending therethrough. The diameter of the bore 8054 is selected so as to correspond to the diameter of an output shaft 7030 of the reduction gear 7028. During assembly, the second coupling assembly 8004 is keyed to the output shaft 7030 of the reduction gear 7028 by a well known key 8058 in a manner similar to that described above with respect to the first coupling half 8014. That is, the key 8058 lockingly engages a correspondingly shaped keyway 8059 formed within the interior diameter of the second coupling half 8016. The axial position of the second coupling assembly 8004 may be locked in position by a well known set screw 8060.

[0201] Referring back to FIG. 94, the spiders 8008 will now be described in greater detail. The spiders 8008 include an annular body 8062 having a plurality of legs 8064 protruding radially outward at spaced intervals, such as 60 degree intervals. In the illustrated embodiment, the spiders 8008 have a total of six legs 8064, although it should be apparent that spiders suitable for use with the present application may have any number of legs, either higher or lower, than the illustrated number of legs. Passing through the annular body 8062 is a bore 8066 having a diameter sized to form, for example, a friction, interference, or loose fit with the standard diameter 8032 of the alignment shaft 8012.

[0202] The spiders 8008 are suitably formed from a flexible material having a low modulus of elasticity, such as polyurethane. For instance, in one embodiment, the spiders 8008 are formed from a relatively rigid polyurethane having a Shore hardness durometer test reading of about 64 Sh D-F. This “rigid” polyurethane may sustain relatively large torques while exhibiting a small twist angle under load. In another embodiment, the spiders 8008 are formed from a relatively pliable polyurethane having a Shore hardness durometer test reading of about 98 Sh A. Although this spider may be less able to withstand extreme torques, the spider offers enhanced dampening characteristics. Although specific materials having specific hardnesses are described for use in the formation of spiders formed in accordance with the present invention, it should be apparent to those skilled in the art that other materials of other or identical hardnesses are suitable for use with and within the spirit and scope of the present application.

[0203] Still referring to FIG. 94, the torque transfer members 8010 suitably include an annular body 8068 having a plurality of protruding ears 8070. In the illustrated embodiment, each torque transfer member 8010 has a total of six ears 8070 (three ears per side) projecting outward at spaced intervals, such as 120 degree intervals, from the annular body 8068. Although a specific number of ears 8070 are shown for the torque transfer members 8010 of the illustrated embodiment, it should be apparent that torque transfer members suitable for use with the present invention may have any number of ears, either higher or lower, than six. Passing through the annular body 8068 is a bore 8072 having a diameter sized and configured to allow the torque transfer member 8010 to rotate freely about the standard diameter 8032 of the alignment shaft 8012.

[0204] The torque transfer members 8010 are preferably formed from rigid or semi-rigid materials having a low modulus of elasticity, two of many suitable materials being aluminum or plastic. For instance, in one embodiment, the torque transfer members 8010 are suitably formed from aluminum having a modulus of elasticity of 70×106 kPa. In another embodiment, the torque transfer member 8010 is suitably formed from steel, which has a modulus of elasticity of approximately 210×106 kPa, to provide some additional torque dampening affects. Although specific materials having specific moduluses of elasticity are described for use in the formation of torque transfer members formed in accordance with the present application, it should be apparent to those skilled in the art that other materials of other moduluses of elasticity are suitable for use with and within the spirit and scope of the present invention.

[0205] Referring to FIGS. 92-95, in one method of assembly, the first coupling assembly 8002 is coupled to the alignment shaft 8012 as described above. The spiders 8008 and torque transfer members 8010 are then installed upon the standard diameter portion 8032 of the alignment shaft 8012 in an alternating arrangement, such that the spiders 8008 are interlocked with adjacent torque transfer members 8010 in a stacked configuration. The alignment shaft 8012 with attached first coupling assembly 8002, spiders 8008, and torque transfer members 8010 is then placed within a housing 8074 in the frame 7999 such that the thrust collar 8020 is inserted within the frame 7999 of the fold-out ramp assembly 7000.

[0206] The second coupling assembly 8004 is then attached to the output shaft 7030 of the reduction gear 7028 as described above. The reduction gear 7028 with attached motor 7052 and second coupling assembly 8004 are then inserted within the frame housing 8074 such that the jaws 8052 of the second coupling half 8016 engage an adjacent spider 8008C. The motor 7052 is then fastened to the frame housing 8074 by a well known mounting plates 8076 and 8076a, and fasteners 8078. The axial position of the clamping collar 8018 is then selected and locked in position to provide a selected axial free play, allowing take-up of axial tolerances of the stack of spiders 8008 and torque transfer members 8010. Thus, during operation, the clamping collar 8018 controls the thrust generated during the helical like deflection of the stack when subjected to a torque and thereby acts as an adjustable thrust stop for the elements of the flexible driveshaft assembly 8001.

[0207] In operation, upon the receipt of a command to actuate the ramp platform 7044 (See FIG. 91) between the stowed and deployed positions, the motor 7052 begins rotation at a high RPM. The reduction gear 7028 converts the high RPM low torque output of the motor 7052 to a low RPM, high torque output upon the output shaft 7030 of the reduction gear 7028. The output shaft 7030 torque is then transferred to the second coupling half 8016 via the key 8058. The jaws 8052 of the second coupling half 8016 engage the adjacent spider 8008C, transferring the torque present in the second coupling half 8016 to the spider 8008C. The spider 8008C in turn engages the adjacent torque transfer member 8010C, transferring torque in the spider 8008C to the torque transfer member 8010C. This process continues, until the last spider 8008 in the chain of spiders and torque transfer members 8010 engages the jaws 8024 of the first coupling half 8014. The torque transferred to the first coupling half 8014 is then transferred to the alignment shaft 8012 via the key 8028, causing the alignment shaft 8012 to rotate, thus actuating the idler and roller chain assembly 7054 to adjust the angular disposition of the ramp platform 7044 as described for the above embodiments.

[0208] During the transfer of torque as described above, the spiders 8008, and to a lesser extent the torque transfer members 8010, deform under the strain, thus absorbing torsional shock loads and also vibrations produced by uneven operation of the motor 7052 and acceleration loads. Thus, the shock felt by the drive train is absorbed to prolong the life of the drive train and provide smooth operation. Further, the flexibility of the spiders 8008 and to a lesser extent the torque transfer members 8010, may compensate for any misalignments present in the drive assembly 8000. The benefits described above may be realized when the motor 7052 is back driven, such as when an operator manually configures the ramp platform 7044 between the stowed and deployed position, as should be apparent to those skilled in the art. An operator can exert large torque and accelerations to the motor when manually configuring the ramp between stowed and deployed positions.

[0209] Further, as described above, the spiders 8008 engage the alignment shaft 8012 in a friction fit manner. Thus, as the spiders 8008 are rotated (slightly) upon the alignment shaft when deforming under load, the friction present between the spiders 8008 and the alignment shaft 8012 aids in dissipating some of the shock load.

[0210] Referring to FIGS. 93 and 94, although the illustrated embodiment is depicted with a flexible driveshaft assembly 8001 having a specific number of spiders 8008, namely eleven, and a specific number of torque transfer members 8010, namely ten, it should be apparent to those skilled in the art that any number of spiders 8008 and torque transfer members 8010 are suitable for use with and are within the spirit and scope of the present invention. Moreover, the number of spiders 8008 and torque transfer members 8010 may be varied to adjust the amount of torsional dampening provided to absorb shock from rapid changes in torque by the flexible driveshaft assembly 8000 as should be apparent to those skilled in the art.

[0211] While the preferred embodiment of the invention has been illustrated and described, it will be appreciated that various changes can be made therein without departing from the spirit and scope of the invention. As a non-limiting example, and as best seen by referring to FIGS. 96-98, a flexible driveshaft 10006, formed in accordance with another embodiment of the present application, will now be described in greater detail. The flexible driveshaft 10006 of the present embodiment is identical in materials and operation as the embodiment described above with one exception. In that regard, the flexible driveshaft 10006 includes a single spider 10008 extending between and interlocked with first and second coupling halves 10014 and 10016. In other embodiments, the spider 10008 may be bonded to the first and second coupling halves 10014 and 10016. The spider 10008 is suitably formed from a flexible material, such as plastic or urethane.

[0212] The dampening characteristics of the spider 10008 could be tuned as a function of the length of the spider 10008. Specifically, the dampening characteristic of the spider 10008 may be increased by increasing the length of the spider 10008. Conversely, the spider dampening characteristic may be decreased by shortening the length of the spider 10008. Finally, it should be apparent that any one of the flexible driveshafts and/or driveshaft assemblies described above may also be incorporated with a variety of ramps, including ramps that do not include a counterbalance assembly. Accordingly, such embodiments are also within the scope of the present application.

[0213] While the preferred embodiment of the invention has been illustrated and described, it will be appreciated that various changes can be made therein without departing from the spirit and scope of the invention.

Claims

1. A ramp assembly, comprising: (a) a frame attachable to a vehicle; (b) a platform coupled to a portion of the frame; (c) a ramp having a weight; (d) a reciprocating mechanism coupled to the ramp and extending between the ramp and the platform to reciprocate the ramp between a stowed and deployed position; and (e) a dampener coupled to the reciprocating mechanism to dampen loads associated with moving the ramp from a static position.

2. The ramp assembly of claim 1, wherein the dampener includes a plurality of spiders and torque transfer members in interlocking relationship.

3. The ramp assembly of claim 1, wherein the dampener includes a single spider.

4. The ramp assembly of claim 3, wherein the single spider is manufactured from a flexible material.

5. The ramp assembly of claim 3, wherein the dampener may be tuned to either increase or decrease dampening characteristics of the dampener.

6. A ramp assembly, comprising: (a) a ramp platform coupled to a frame; (b) a reciprocating mechanism coupled to the ramp platform for reciprocating the ramp platform between a stowed position and a deployed position; and (c) a dampener coupled to the reciprocating mechanism to dampen loads associated with operation of the ramp platform.

7. The ramp assembly of claim 6, wherein the dampener absorbs torsional loads when the ramp platform is moved from a static position.

8. The ramp assembly of claim 6, wherein the dampener includes at least one spider for absorbing torsional loads associated with operation of the ramp assembly.

9. The ramp assembly of claim 6, wherein the dampener may be tuned to either increase or decease damping characteristics of the dampener.

10. The ramp assembly of claim 6, wherein the dampener includes a plurality of spiders and torque transfer members.

11. The ramp assembly of claim 10, wherein the plurality of spiders are manufactured from a flexible material.

12. A ramp assembly, comprising: (a) a frame attachable to a vehicle having a floor; (b) a platform coupled to a portion of the frame; (c) a ramp coupled to a portion of the frame and the platform at least in part by a reciprocating mechanism for reciprocating movement of the ramp between a stowed position and a deployed position; (d) a dampener coupled to the reciprocating mechanism to dampen loads associated with moving the ramp from a static position; and (e) a lifting assembly disposed between the platform and the frame for reciprocating movement of the ramp into and out of a position substantially flush with the floor as the ramp is reciprocated between the deployed and stowed positions.

13. The ramp assembly of claim 12, wherein the dampener absorbs torsional loads.

14. The ramp assembly of claim 12, wherein the dampener includes at least one spider.

15. The ramp assembly of claim 14, wherein the at least one spider is manufactured from a flexible material.

16. The ramp assembly of claim 14, wherein the dampener includes a plurality of spiders and torque members.

17. A ramp assembly, comprising: (a) a ramp platform coupled to a frame; (b) a reciprocating mechanism extending between the ramp platform and the frame for reciprocating movement of the ramp platform from a static position; and (c) means for damping loads associated with reciprocating movement of the ramp platform from a static position, the means for damping loads coupled at least in part to the reciprocating mechanism.