referring to fig1 a conventional three pad compliant gas bearing assembly is shown generally as 10 . foil gas bearing assembly 10 includes a journal sleeve or bushing 12 having a generally cylindrical shape with an outer surface 14 and an inner surface 16 . outer surface 14 can contain key ways and slots ( not shown ) to facilitate installation of the bearing assembly 10 into a turbo machine . foil gas bearing assembly 10 supports a shaft 18 mounted for rotation in the direction shown by arrow 20 . disposed inside of the sleeve 12 are three bump foil assemblies 22 , 24 , and 26 , consisting of bump foils 28 , 30 , and 32 covered by a flat foil 34 , 36 , and 38 . referring to bump foil assembly 22 , the bump foil 28 is first welded to the inner surface 16 of sleeve 12 by a series of spot welds placed transversely inside of the sleeve 12 along the first or fixed end 40 of bump foil assembly 22 as is well known in the art . as shown in fig1 a spacer ( shown as 41 with assembly 22 ) is spot welded on top of the bump foil 28 where it is welded to the shell 12 . a first or fixed end of the flat foil 34 is then spot welded to the spacer 41 at the same location . thus , the bump foil assembly 28 includes a first or fixed end 40 and a second or free end 42 . neither the bump foil 28 nor the smooth foil 30 are otherwise fixed to the sleeve 12 and are free to move from the fixed end toward the free end 42 under rotation of the shaft 18 . bump foil assembly 24 has a similar fixed end 44 and a free end 46 , and bump foil assembly 26 has a fixed end 48 and a free end 50 . as shown in fig2 a , when the bump foil assembly 22 is first installed the bumps on bump foil 28 are of a uniform cross section , each having an identical height . as shown in fig2 b , when a rotational load is placed on the shaft , which is shown by arrows 52 , the bump foil 28 deflects in the direction of the arrows 53 from the fixed end 40 to the free end 42 of the bump foil assembly 22 . at the same time the bump foil 28 elongates , the smooth foil 34 can also elongate depending upon the load . referring to fig3 a , there is shown a new bump foil assembly 60 having a bump foil 62 and a smooth foil 64 . bump foil 62 is fixed to the sleeve by a weld at the first or fixed end 66 as is known in the prior art . bump foil 62 has a first series of bumps or corrugations 70 which are of a set height . bump foil 62 includes a second series of bumps disposed between each of the first series of bumps which are of a height that is approximately 70 - 95 % of the height of the bumps or corrugations 70 . as shown in fig3 b , when a load , as shown by arrows 74 , is placed on the bump foil assembly 60 , the bump foil 62 is free to move in two directions , as shown by arrows 76 , 77 , and 78 . alternating the bump height allows the bump foil to deflect in two directions for increased damping of the bump foil . as the load increases , all of the bumps will support the load resulting in increased load capacity and stiffness . bump foils according to the present invention , can be made of conventional materials such as nickel alloys sold under the tradename inconel . prior art bump foils are made from flat stock approximately 0 . 003 inches thick . bump foils , according to the present invention , can be fabricated from similar materials but with increased thickness . the new bump foil geometry allows for thicker bump foils for higher load capacity without sacrificing compliance required for coulomb damping . for example , a prior art bearing system using a 0 . 003 inch thick bump foil can be replaced with a bump foil according to the invention that has a minimum thickness of 0 . 0035 inches . it is contemplated that , depending upon the size of the bearing , the bump foil will have a thickness between 0 . 002 and 0 . 012 inches . coulomb damping is provided by the bump foils sliding motion as the load is applied and removed as shown in fig2 b and 3b . the bump foil geometry having two different bump heights results in light loads being supported only by the taller bumps ( 70 ) or 50 % of the total bump foil structure . therefore , under light loads , the new bump foil will be more compliant . as the load increases the tall bumps 70 will deflect allowing the shorter bumps 72 to support the load for increased stiffness and load capacity . the damping characteristics of the new gas foil bearings using the new bump foil design is provided by the sliding motion of the bump foil as the load is applied and removed . the bump foil designed according to the present invention permits sliding motion in two directions and is independent of load angle . this is a significant improvement over the prior art foil designs where a load applied to the free end of the bump foil assembly could lock the bump foils in place restricting motion and damping . past designs used two bump foils having different spring constants mounted in series ( nested configuration ). the bump foil motion would still be restricted if the load is applied to the free end of the pad which in turn will reduce the damping capacity of the bearing . the bump foil of the present invention permits increased stiffness with increased load without sacrificing compliance of the gas foil bearing to provide coulomb damping . having thus described my invention what is desired to be secured by letters patent of the united states is set forth in the appended claims .