Abstract:
A stabilizing apparatus and method that replaces the existing shock absorber of a road vehicle that works to resist the initiation of body roll during cornering. It seeks to counter act the forces being generated by the vehicle suspension springs that exacerbate the rollover propensity of vehicles during certain steering maneuvers.

Description:
CROSS REFERENCE TO RELATED APPLICATIONS 
     This application is related to: 
     U.S. Ser. No. 09/803,505 filed on Mar. 9, 2001 entitled Opposing Spring Resilient Tension Suspension System. 
     U.S. Ser. No. 10/033,016 filed on Oct. 26, 2001 entitled Opposing Spring Rebound Tension Suspension System. 
    
    
     STATEMENT REGARDING FEDERALLY SPONSORED RESEARCH OR DEVELOPMENT 
     Not Applicable 
     REFERENCE TO A “MICROFICHE APPENDIX” 
     Not Applicable 
     BACKGROUND OF THE INVENTION 
     1. Field of the Invention 
     The present invention relates to and, in particular, to improvements in the methods and apparatus for using a rebound spring carried on a shock absorber that is intended to utilize the unsprung weight of the wheel/axle system during rebound. More particularly, it is to resist rollover, sway, yaw and other chassis motion. 
     2. Description of Related Art Including Information Disclosed Under 37 CFR 1.97 and 1.98 
     In the past ten years the numbers of sport utility vehicles “SUV” and pickup trucks have increased dramatically to the point where those vehicles are more popular than the millions of passenger cars on the road. The SUV and trucks inherently have a higher center of gravity (CG) than normal passenger cars due to the need for higher ground clearance for bad weather travel (snow and ice), off-road use and/or for pickup truck payloads. Vehicles with a higher CG have a greater propensity to sway or even rollover during abrupt lane changes and evasive steering maneuvers than the lower normal passenger cars. 
     One important arrangement of all these vehicles is the method of suspension used. Except for the use of hydraulic shock absorber damping resistance to rebound, all vehicle chassis and body loads are supported on the vehicle axles with various types of suspensions that have springs that resist primarily load and jounce of each wheel axle. No existing suspensions using coil springs, load leaf springs, air springs, torsion bars or rubber blocks suspensions have any other provision for rebound control of the forces due to inertia or gravity type negative suspension loads. Particularly, those rebound forces occurring at the inside wheel during hard cornering or if a wheel drops into a pothole. 
     Typically, changes in suspension loads while driving straight along a road are caused generally by reactions to bumps, potholes, and roughness encountered by the vehicle wheels during their interaction with the road surface. Thus the suspension springs and associated shock absorbers quell the harshness and movements being transmitted to the body/chassis. 
     The sway or side to side rolling motions that vehicles experience due to cornering forces, also cause vehicle springs to be loaded or unloaded, depending which way the vehicle is rolling during cornering. Many vehicles have an anti-sway/roll bar installed to help the vehicle body resist the rolling actions. These devices help the vehicle partially resist roll but only as it relates to the body lean, because they are fixed to the sprung mass and leaning with the body. Thus, they can actually reduce the load on the unloaded side of the vehicle. They use the body as a structure to support the torsion bar of the anti sway system transferring wheel jounce motion across to the opposite side. The disclosure herein will obviate the need for anti-sway bars, saving the cost of providing and installing them. Shock absorbers only dampen the bouncing movement of the vehicle wheels and suspension caused by the reaction to road surface, cornering and braking. Thus, the rate of sway may be affected only to a minor degree. 
     A floating aluminum piston is placed between the fluid moving piston and the end of the shock body. The floating piston has nitrogen gas behind it that is at a preset pressure. This piston is used in racing shocks and other lift type shocks to do two things, first to pressurize the fluid at all times and second to raise the vehicle ride height. It is not practical to fill the entire shock body with fluid on both sides of the fluid piston. This ensures that as the fluid moving piston moves away from the end of the cavity as it would during extension or “rebound” travel, it does not permit a vacuum to form behind the fluid piston and sucking against the shock travel. It maintains a pressure front against the fluid to ensure that it is induced to pass the fluid piston during jounce travel. The fluid piston has holes in it to allow the fluid to pass by it and flexible shims on both sides of the fluid piston are adjusted in strength to set the resistance to flow through the piston during normal movement. Stiffer shims result in higher resistance to the fluid being compressed against them. 
     All this and the use of nitrogen pressure against the piston are typical of existing shock absorber design. The basic tubular shock absorber is well known to skilled artisans, and is a commodity and is disclosed in numerous patents. The typical shock absorber is designed to dampen motion and with coil over springs adjust the ride height and/or spring stiffness. 
     U.S. Pat. No. 2,160,541 has a paired spring suspension connected in series to only support load and jounce with the added spring coupled in line with the main spring for increasing the effective spring constant at the extremes of suspension travel. The techniques disclosed in the various embodiments of &#39;541 are in the nature of an overload spring that engages and changes the spring constant at the extremes of wheel travel. There is no spring in &#39;541 connected to specifically resist rebound forces due to diverging motion of the sprung weight to unsprung weight. The disclosure of &#39;541 specifically states that the higher spring constant results in less flex (on page 2 column 1 at lines 6 to 8), “ . . . which opposes any tendency of the vehicle to overturn laterally when negotiating a curve.” In each embodiment of &#39;541 the springs act in unison to control primarily load and jounce and there is no teaching of a particular connection to directly apply rebound reaction of unsprung weight to one of the springs. The graph in &#39;541 showing wheel travel verses spring forces verifies these conclusions. U.S. Pat. No. 5,263,695 discloses a refinement of the &#39;541 teaching that includes a shock absorber for damping motion and an elastic block to ameliorate the transition between first and second springs for carrying the load. In addition to many disclosures in &#39;695 of prior paired spring configurations there is a specific explanation in column 5, lines 1 through 5 as follows: 
     “The suspension according to the invention produces a comfort level which is higher the more the transition from one stiffness to the other takes place progressively (see the patents cited in the state of the art).” 
     The state of the art referred to includes prior patents of the same inventor and the acknowledgements of those prior patents clearly identifies the teachings as merely two springs of different stiffness in series. Even in FIG. 7 of &#39;695 the springs are concentrically mounted but act in series, see column 4, lines 8 through 12. At best the structures for multiple springs shown in these patents have differing spring rates to give an allegedly more comfortable ride but do not specifically disclose rebound control. 
     U.S. Pat. No. 3,830,517 is a motorcycle rear wheel spring suspension wherein a top spring is longer and absorbs upward road shock and a bottom spring absorbs the rider&#39;s weight. Nothing is disclosed about resisting rebound with either the top or bottom spring and no attachment of the springs is shown or described that would operate to control rebound of the sprung weight. 
     U.S. Pat. No. 3,049,359 has a pair of coaxial coil springs designed to maintain ride height by automatic screw adjustment of the smaller and lighter inner tension coil spring. No disclosure of rebound control of sprung weight is made and the inner tension coil spring loadings are varied only in so far as the ride height is less or more than required as such the size and strength of the inner tension spring would be insufficient to transfer the unsprung weight to the chassis and resist rebound. Moreover the working travel of both springs appears to be the same; thus, no rebound control is possible. 
     No existing suspension system suspends the chassis and/or body between opposing springs to counter load and jounce and reaction and rebound along different portions of the axle and wheel travel. An opposing spring suspension as disclosed herein can have little effect on the ride stiffness, but stabilizes cornering and evasive maneuvering sway by utilizing the unsprung weight of the axle system thus helping the vehicle to resist roll while maintaining the general ride quality. 
     U.S. Pat. No. 3,297,312 has a combination shock absorber and spring for automobile suspensions. Close examination reveals that a main rod connects between a top cap and a nut to bottom tube. It appears that the rod will bottom out against the tube end when the springs are compressed because rod  52  is of set length and incompressible. The four springs stacked, as a unit, abut each other to act as one continuous variable rate spring. Specifically, the upper two springs have a disc that separates them that shifts up and down with the movement of the springs. The disc has valve holes in it to permit the movement of fluid to each side of the disc to act as a shock absorber. This appears to have minimal effect or use. 
     U.S. Pat. No. 5,183,285 has a suspension of a stiffness that is greater between the operating load position and the suspended wheels position than between the operating load position and the collapsed position. It is a suspension and a suspension process that uses a greater stiffness in the region of “rebound” than in the region of “bump” with means for smoothing the stiffness from the passage of one region to the other, and means for varying the reference position for “operating load” as a function of the number of persons and the load in the vehicle. A suspension wherein the stiffness is greater in the region between the position “operating load” and a position “suspended wheels” than in the range between the position “operating load” and a position “collapsed suspension” up to shock abutment. The suspension has stiffness greater in the region of “rebound” than in the region of “bump”; if these are graphically represented, a change of thickness represented by a break in the slope appears. FIGS. 13, 14 and 16 in U.S. Pat. No. 5,183,285 have a rebound spring around a shock positioned by a jack for varying the reference position for “operating load” as a function of the number of persons and the load in the vehicle. The jack varies the preload position so there is no gap between rebound and bump. 
     U.S. Pat. No. 6,273,441 has a load leaf spring suspension system with an elongated stabilizing spring mounted there above the axle. The added spring communicates roll resistance to the vehicle axle at its top center section. Force is concurrently applied at the ends of the stabilizing spring to the leaf spring of the vehicle by shackles. Adjustment of the device is achieved by use of a plurality of mounting apertures for the shackles located at varying distances from the center of the stabilizing spring thereby allowing for adjustment by the user for desired performance characteristics. Further force adjustment is achieved with one or a combination of an optional axle spacer located at the center section of the stabilizing spring to communicate with the axle. This stabilizer system does not employ opposing spring technology. 
     An influence is delivered on the vehicle center of gravity by opposing spring. The center of gravity of the unsprung mass relative to the center of gravity of the sprung mass is affected during the cornering maneuvers. Without a tension or opposing spring to “tether” the sprung mass to the unsprung mass the unsprung mass does not initially help resist the movement upwards of the sprung mass. This resistance is best appreciated in a vehicle with very heavy unsprung mass relative to a lighter sprung mass during corn ring versus a vehicle with light unsprung mass relative to a heavy sprung mass. The former is recognized as undesirable and the latter is greatly preferred and sought after in design of vehicles. Often the physical limits of the vehicle components determine the practical boundaries of the sprung weight to unsprung weight ratio. The disclosure herein has an approach to ameliorate the dynamics of that relationship. 
     U.S. Pat. No. 6,017,044 has as it&#39;s main thrust regulation of spring rebound and bound. Vertical downward jacking-force characteristics of the front suspension is set to be stronger relatively with respect to vertical downward jacking-force characteristics of the rear suspension during cornering. This is achieved by two means. The first is the use of a very strong bump rubber in FIG. 3 of U.S. Pat. No. 6,017,044 that comes into play at the extreme end of the front jounce travel. This bump rubber is not needed in our disclosure. Second, a short “spring” item in FIG. 4 of U.S. Pat. No. 6,017,044 is intended to help control “jack up” of the rear suspension occurring near the extreme end of the roll. The working distance traveled is very short. 
     U.S. Pat. No. 6,220,406 discloses a damper for reducing sway. It discloses background on various types of shock absorbers used in connection with motor vehicle suspension systems to absorb unwanted vibrations that occur during various driving conditions. To dampen the unwanted vibrations, shock absorbers are generally connected between the sprung portion (i.e., the vehicle body) and the unsprung portion (i.e., the suspension) of the vehicle. A piston assembly is located within the working chamber of the shock absorber and is connected to the body of the motor vehicle through a piston rod. Generally, the piston assembly includes a primary valve arranged to limit the flow of damping fluid within the working chamber when the shock absorber is compressed or extended. As such, the shock absorber is able to generate a damping force to smooth or dampen the vibrations transmitted from the suspension to the vehicle body. Typically, these vibrations occur from forces generated in a vertical direction between the vehicle body and the driving surface. 
     The greater the degree to which the flow of damping fluid within the working chamber is restricted across the piston assembly, the greater the damping forces that are generated by the shock absorber. It is also possible to implement a primary valve arrangement that produces one magnitude of damping on the compression stroke, and a second magnitude of damping on the rebound stroke. These different damping rates are typically constant as varying the sizes of the compression and rebound bypass orifices produces them. 
     While these shock absorbers produce ride comfort levels ranging from “soft” to “firm,” few, if any, of the known shock absorbers produce varying degrees of damping in a passive manner. The shock absorber systems in use are capable of producing varying degrees of damping force; typically achieve this through the use of active control systems. These systems generally react to the vertically generated forces placed upon the vehicle suspension. 
     Accordingly, in &#39;406 a shock absorber that includes a primary damping mechanism for counteracting the vertical forces placed upon the vehicle, and a secondary damping mechanism which is capable of providing varying damping in response to horizontal and lateral forces that are placed upon the vehicle suspension. Secondary and variable damping is provided in proportion to the lateral force encountered by a passive control or valves arranged to implement a passive anti-roll system for enhancing the control to the vehicle provided by the vehicle suspension. While such a passive damping system also eliminates the need for complicated and expensive controls to actively provide the varying degrees of damping, it is not easily adapted to the large variety of vehicles and their suspensions. 
     The problem of the lateral forces placed upon the vehicle suspension is they are generated during high-speed cornering. As the suspension and tires counteract these lateral forces, a rolling action on the vehicle body is produced. When these rolling forces exceed the limit for the vehicle, a rollover condition may be created wherein the vehicle is literally flipped over on its side. Accordingly, it is desirable to provide a shock absorber that provides increased resistance in response to these lateral and horizontal forces for counteracting or at least minimizing these rolling forces and the lift associated therewith. 
     BRIEF SUMMARY OF THE INVENTION 
     In the disclosed device and method, a rebound spring is placed to resist the lengthening of the shock absorber from a position that starts one inch into jounce travel from normal ride height to the full rebound suspension travel position. This rebound spring is opposing and resisting the forces that are generated when the suspension is unloading as for example during cornering. Namely the forces caused by the vehicle suspension spring trying to return to its free position and the centrifugal forces naturally resulting during cornering. 
     Using an additional coil spring mounted about the shock absorber to resist the rebound motion of the sprung weight applied by movement thereof away from the design height reduces chassis roll. The shock absorber thus reduces the initiation of rebound travel between the sprung and unsprung weights as the vehicle becomes lighter due to dynamic forces inducing roll or lift of the chassis and vehicle body. 
     The transitory effects of body roll during cornering flex the load springs on the side of the vehicle following the outside of the turn due to increased transfer weight to that side. Meanwhile the springs on the side of the vehicle, following the inside of the turn, unload extending toward their free position using the axle as a location for inducing lift of the sprung weight on that side resulting in increased body roll. Roll or sway during sudden cornering or evasive maneuvers rotates the vehicle and its center of gravity “CG” around the Roll Center axis. 
     The Roll Center axis is a function of the particular vehicle&#39;s suspension geometry. Roll or sway is increased if the vehicle center of gravity is raised as in a SUV, four-wheel drive vehicle or truck. A sudden turn opposite the direction of vehicle travel can cause momentum to continue the sway of the vehicle forcing its center of gravity to move laterally past its maximum upright position, and so the vehicle continues on rolling and overturns. 
     The solution, as disclosed herein, may include an added rebound spring mounted coaxial about the shock absorber tube to act primarily to resist rebound of the suspension from the design height position and thereby apply resistive force to the chassis via the shock absorber to reduce lift. The coil rebound spring can also be added to a strut type suspension for exactly the same purpose. It is an advantage of the present invention that it can be easily and inexpensively added as an after market supplement to either the front or rear of an existing vehicle suspension with tubular shock absorbers. It is a further advantage of the present invention that the coil rebound spring has very little influence on ride height and/or ride stiffness. 
     The coil rebound spring works from one inch of jounce travel all the way to full rebound travel of the shock absorber. It works to prevent the onset of roll from the design height, rather than limiting the roll to a certain amount after it has rolled a certain amount. Limiting the roll from the design height position serves to reduce the momentum or inertial weight gain that occurs at the initiation of roll and continues after roll has begun. In other words, we seek to eliminate as much roll as possible from the outset. Rebound control overlaps the jounce control; therefore the disclosed system is truly bi-linear, a preferred embodiment. 
    
    
     BRIEF DESCRIPTION OF THE DRAWING 
     FIG. 1 is a side view in cross section of a shock absorber having a coil rebound spring thereabout. 
     FIG. 2 is a schematic perspective view of a vehicle rounding a corner with roll depicted about its longitudinal axis A—A. 
     FIG. 3 is a side view in cross section of a typical combined shock absorber and strut type suspension unit, having a load spring but with the addition of the disclosed coil rebound spring thereabout. 
     FIG. 4 is a graph showing the travel relative to the jounce and rebound loads of the combined shock absorber and strut depicted in FIG.  3 . 
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     FIG. 1 shows a cross section view of a vehicle rebound control shock absorber  10  with a special suspension coil rebound spring  11  arrangement. It is to be used to replace a standard shock absorber installation independent of the vehicle spring system, as is commonly found in both vehicles with leaf type and coil type suspension spring systems. Commonly a shock absorber connects the sprung mass to the un-sprung mass and is used only to dampen unsprung mass oscillations induced by bumpy roads and sometimes with helper load springs for preloaded height and jounce improvement. The sprung mass is carried on vehicle chassis and body and herein after will be referred to structurally as chassis  16 . The unsprung weight is that which is not supported by the vehicle suspension spring system, i.e. axles  15 , wheels, tires, brake assemblies and suspension components that hang downwardly if the body is lifted. Typically, the passenger vehicle has four wheels with associated suspension with two at the front and two at the rear. The disclosure herein is to cover any number of axle  15  and wheel combinations so long as there is roll to be restrained. 
     FIG. 1 shows a coil spring mounted about a rebound control shock absorber  10  for exerting force to resist upper rebound control shock absorber  10  movement from the normal design height or preloaded ride position of chassis  16 . When both ends of the rebound control shock absorber  10  are pulled apart, as experienced by chassis  16  when it lifts during rebound of the axle  15 . It is called coil rebound spring  11  because it is intended to counter the lifting action of the vehicle suspension during roll due to cornering maneuvers. When a vehicle corners, its chassis  16  rolls about its longitudinal axis A—A in FIG. 2 relative to axles  15 . Load carrying coil springs  14  on the outside of chassis  16  become compressed as they assume jounce and the coil load springs  14  located on the inside of the turning chassis  16  during cornering become extended while experiencing rebound see FIG.  2 . Coil load springs  14  on the unloading inside side of the cornering vehicle are trying to return to their free state as they extend. Thus coil load springs  14  as they extend exert a lifting force to chassis  16  which is exacerbating the roll angle of the body mass. The lifting force is exactly what is not desired and is resisted by the coil rebound springs  11  herein disclosed. The whole purpose of using coil rebound springs  11  is to reduce chassis  16  roll at initiation of and during cornering because rebound movement at any axle  15  will likewise be resisted. 
     FIG. 3 shows another rebound control shock absorber  10  having coil rebound spring  11  thereabout, but with the addition of a compression type suspension coil load spring  14 . The additional compression coil load spring  14  carries the sprung weight and is intended to replace or supplement chassis  16  existing original equipment manufacturer suspension load spring  14 , if any. If load spring  14  is carried on the rebound control shock absorber  10  and no separate load spring  14  is used the vehicle suspension would be fully self-contained. Thus the rebound control shock absorber  10  with an integral coil load spring  14  as per FIG. 3 would be able to serve as a replacement assembly providing that the vehicle mounting points for such an assembly is sufficient to respond and carry the loadings expected. Typically, strut mountings that are prevalent on modern cars and trucks are adequate for operation with the assembly shown in FIG.  3 . It is important to note that coil rebound spring  11  seeks to control the sprung weight and the coil load spring  14  if original equipment manufacturer and/or on the rebound control shock absorber  10  as in FIG. 3 supports the sprung weight. 
     A rebound control shock absorber  10  for placement between axle  15  and chassis  16  is shown in FIGS. 1,  2  and  3 . The rebound control shock absorber  10  is for additionally controlling the vehicle dynamics with increasing resistance under motion between a preloaded vehicle ride height position to a fully extended position of rebound control shock absorber  10  during rebound movement of chassis  16  away from axle  15  along an axis B—B through the rebound control shock absorber  10 . It is rebound control shock absorber  10  that applies the unsprung weight of the wheels, brake and axle  15  to chassis  16  through coil rebound spring  11 . The goal is not to lift the axle, wheel and its tire from the ground, if possible, during cornering but to apply the unsprung weight of those components at the lifting side of chassis  16  to resist roll of the chassis and body. 
     An axle mount  17  on axle  15  is provided to connect to rebound control shock absorber  10 . A chassis attachment  18  on chassis  16  of the vehicle connects to the depending rebound control shock absorber  10  so that it may operate along axis B—B between axle mount  17  and chassis attachment  18 . An elongated rod  19  has opposite ends  20  and  21  carried and aligned along the axis B—B. End  20  connects to chassis attachment  18  in FIG. 1 or  3 . While rebound control shock absorber  10  is shown with elongated rod  19  and end  20  at the top in FIGS. 1 and 3, skilled artisans will understand that it can be inverted so that elongated rod  19  connects to axle mount  17 . A fluid displacement piston  22  is located on end  21 . If rebound control shock absorber  10  is inverted (not shown) then attention to how coil rebound spring  11  carries the unsprung weight must be addressed; again this is within the skill of artisans. Fluid displacement piston  22  is carried on the elongated rod  19  opposite its connection end  20 . Likewise a tube  23  is aligned along the axis B—B and connects to the axle mount  17  when the end  20  is connected to the chassis attachment  18 ; alternatively, the tube  23  connects to chassis attachment  18  when the end  20  is connected to the axle mount  17 . 
     Tube  23  has inside and outside cylindrical surfaces  24  and  25 . Inside cylindrical surface  24  is sized diametrically for surrounding the fluid displacement piston  22  for sliding sealing circumferential engagement there between with reciprocation along the axis B—B. A chamber  26  is defined by the inside cylindrical surface  24  and chamber  26  carries damping fluid (not shown) about fluid displacement piston  22  for controlled resistance to sliding reciprocal movement of the fluid displacement piston  22  within tube  23  against the inside cylindrical surface  24  and along the axis B—B. 
     Coil rebound spring  11  is carried about outside cylindrical surface  25  of tube  23  coaxial thereto and for expansion and contraction along the axis B—B as in FIGS. 1 and 3. Coil rebound spring  11  is mounted to restrain expansion along the axis B—B of the rebound control shock absorber  10  between axle  15  and chassis  16  of the vehicle. Restraint is from at least the preloaded vehicle ride height position to the coil rebound spring  11  fully extended position during rebound motion of the axle  15  away from the chassis  16  as in FIG.  2 . 
     Tub  23  is elongated along the axis B—B with a top  27  and a bottom  28  separated from each other. A flanged retainer  29  affixes about the outside cylindrical surface  25  of tube  23 . Flanged retainer  29  is located between the top  27  and bottom  28  for applying axial rebound loads to tube  23  from rebound spring  11  during motion along axis B—B of the axle  15  away from chassis  16 . A tube cap  30  mounts in the top  27  and extends from tube  23  to a seat  31  overhanging tube cap radially from the outside cylindrical surface  25  as shown in FIGS. 1 and 3. 
     A bore  32  positioned in and passing through tube cap  30  is coaxial with axis B—B and bore  32  allows elongated rod  19  to pass there through and reciprocate therein. Tube cap  30  connects axially to tube top  27  to capture coil rebound spring  11  between flanged retainer  29  and seat  31 . The coil rebound spring is thereby supported for coaxially circumscribing tube  23  between top  27  and bottom  28  thereof. Rebound is resisted during expansion of rebound control shock absorber  10  from its preloaded height to full extension along the axis B—B with motion of axle  15  away from chassis  16 . 
     A cylindrical housing  33  in FIGS. 1 and 3 is affixed to the end  20  connected to either chassis  16  or axle  15  depending on the orientation of rebound control shock absorber  10 . Cylindrical housing  33  extends from its affixed connection along the axis B—B to engage flanged retainer  29 . Cylindrical housing  33  has a circular cross section sized diametrically for surrounding coil rebound spring  11  with a clearance there between. In FIG. 3 the cylindrical housing  33  is shown with external threads. A fastener  34  on tube cap  30  adjacent seat  31  is shaped to retain coil rebound spring  11  to seat  31  during movement of coil rebound spring  11  along the axis B—B with motion of axle  15  away from chassis  16 . The coil rebound spring  11  is preloaded by the flanged retainer when the coil rebound spring is captured between flanged retainer  29  and seat  31 . During expansion of the rebound control shock absorber  10  from its preloaded position, the coil rebound spring resists expansion under motion of axle  15  away from chassis  16 . 
     Coil load spring  14  mounts co-axially about cylindrical housing  33  for carrying chassis  16  of the vehicle from the preloaded ride height position to a full jounce position compressing the coil load spring  14  as shown graphically in FIG.  2 . An upper collar  35  about cylindrical housing  33  is near connection end  20  and a lower collar  36  at tube bottom  28  capture coil load spring  14  so rebound spring  11  substantially resists expansion after coil load spring  14  substantially resists compression during rebound and jounce, respectively. The term, “after” is used in the preceding sentence because rebound spring  11  and coil load spring  14  operate independently to control (resist) different loads. 
     A method for rebound control by rebound control shock absorber  10  placed between axle  15  and chassis  16  of a vehicle is operable at least between a preloaded vehicle ride height position to a fully extended position during rebound movement of axle  15  away from chassis  16  along axis B—B. The method of rebound control has the steps of mounting rebound control shock absorber  10  to axle mount  17 , and attaching rebound control shock absorber  10  to chassis attachment  18  along axis B—B there between. Another step connects elongated rod  19  having opposite ends  20  and  21  so end  20  connects to either axle mount  17  or chassis attachment  18 . Locating piston  22  at the opposite end and connecting tube  23  to axle mount  17  if the elongated rod  19  is connected to chassis attachment  18  or connecting tube  23  to chassis attachment  18  if the elongated rod  19  is connected to the axle mount  17  are steps. The step of sizing tube  23  with a cross section to surround piston  22  for sliding sealing circumferential engagement within tube  23  due to motion of axle  15  away from chassis  16  is performed. Carrying damping fluid about piston  22  in chamber  26  defined by tube  23  is a step. The steps of controlling resistance to sliding reciprocal movement of piston  22  in tube  23  with the damping fluid, and carrying rebound spring  11  about tube  23  for restraining expansion of the rebound control shock absorber  10 . Restraining is between axle  15  and chassis  16  of the vehicle from the preloaded vehicle ride height position to the fully extend position along the axis B—B during rebound movement of axle  15  away from chassis  16  are followed. 
     The step of supporting rebound spring  11  coaxially circumscribing tube  23  so that rebound is resisted during expansion of rebound control shock absorber  10  from its preloaded height to full extension along the axis B—B with motion of axle  15  away from chassis  16  is done. The step of supporting load spring  14  relative to rebound spring  11  coaxial to one another and along the axis B—B with a clearance there between occurs. During expansion of rebound control shock absorber  10  from its preloaded vehicle height to full extension along the axis B—B there is motion of axle  15  away from chassis  16  load spring  14  and the rebound spring  11  operate substantially independent of one another to resist jounce and rebound, respectively. The method for rebound control by rebound control shock absorber  10  with the step of supporting rebound spring  11  and load spring  14  at the preloaded vehicle height so that the working force application travel there between is overlapping. Thus, about one inch of travel overlap during movement of the rebound spring  11  along the axis B—B with motion of axle  15  away from chassis  16  from the preloaded vehicle height is thus preformed. FIG. 4 shows in graphic form the resultant of overlap for rebound spring  11  and the load spring  14  combined. In the graph of FIG. 4 the load paths at a rate of 320 pound per inch compression jounce spring and a rate of 160 pounds per inch rebound counter spring are shown. The affect on the rebound travel spring of the suspension if engaged at one inch of jounce is no curve at the transition point. 
     The step of having the ratio of the spring constants of coil rebound spring  11  to the spring constant of load spring  14  be less than one. So that during expansion of rebound control shock absorber  10  from its preloaded position coil rebound spring  11  happens to resist expansion under motion of axle  15  away from chassis  16  to a lesser extent than load spring  14  resists jounce. The step of coil rebound spring  11  applying force to resist rebound of the axle  15  occurs. 
     The method for rebound control by rebound control shock absorber  10  has the step of locating coil rebound spring  11  to substantially resist expansion of rebound control shock absorber  10 . The step of co-axially positioning coil load spring  14  to substantially resist compression of rebound control shock absorber  10  during rebound and jounce is performed independently. 
     While the examples illustrating rebound control shock absorber  10  and rebound spring  11  are disclosed and described, skilled artisans will appreciate that many variations for the addition of rebound spring  11  will be possible. The specific examples should not be considered limiting and the particular arrangements shown in FIGS. 1 and 2 are merely for depiction of but some examples of form. In that regard, in the claims that follow the orientation of rebound control shock absorber  10  is either up or down and angled mounting thereof is also within the scope of the claims.