the following description of the preferred embodiment ( s ) is merely exemplary in nature and is in no way intended to limit the invention , its application , or uses . the present invention can be obtained by providing a mechanically operated brake caliper . as shown in the figures , the invention employs a simple lever system connected to an air / spring chamber which actuate the caliper pistons , depressing the brake pads against the brake rotors . as an emergency / parking brake system , the brakes should not have enough power to “ lock up ” during emergency dynamic braking so that maximum control of the vehicle is still possible . parking brakes are not dynamic and require less application power than dynamic braking , as is evident by existing parking brake systems . the system disclosed herein is well within the scope needed for successful operation . the emergency / parking caliper utilizes mechanical input versus hydraulic input , as shown in fig2 a and 2b . to achieve this , the back of the caliper is drilled out to expose the rear surface of the pistons . service brake calipers subject the back of the pistons to hydraulic pressure , whereby the preferred embodiment of the present invention employs a bridging means which connects the pistons and allows a mechanical input to actuate them . the bridge bears the necessary force applied by the lever system , and evenly distributes the force to the pistons in a controlled and sate manner . typical hydraulic operation does not subject the pistons to lateral forces . a lever system could produce lateral forces , causing possible piston and cylinder scoring . to prevent this , the lever system makes contact with the piston bridge by means of a roller . the roller is not able to transmit any significant lateral forces to the piston bridge by design . the lever system is designed in a manner that facilitates the required “ fail to safe ” concept , in that when the actuating chamber is relieved of air or fluid pressure , a maximum braking force is developed that will stop and park the vehicle . furthermore , the system does not hinder the “ floating caliper ” design , which allows the caliper to receive input from only one side of the rotor , and apply the supplied forces evenly on both faces of the rotor to prevent warping and uneven wear . thus , the lever system is integral to the caliper , and in a preferred embodiment , dual calipers are utilized on a single brake rotor , mounted to a siamese anchor plate as shown in fig4 . this configuration provides mounting for the hydraulic service brake caliper and the mechanically actuated emergency / parking caliper , as shown in fig1 . finally , the system is suitably made to fit into the space available on light / medium duty vehicles . referring now to the figures , specifically fig1 the preferred embodiment of the invention is shown , attached to the rear axle of a vehicle , comprising the linkage system 60 attached to the caliper 50 having a spring chamber 30 for engagement / disengagement of the caliper 50 without affecting the normally employed hydraulic service brake system . best illustrated in fig3 and 4 , there is shown an example of the spring chamber 30 mechanism of the present invention . known to those skilled in the art , this provides the force of the present invention through controlled air pressure releasing a parking brake spring 35 . designed to fail to the safe mode , when there is no increased air pressure present , the brake spring 35 is engaged . the spring brake chamber 34 which is charged with air pressure to compress a heavy - duty parking brake spring 35 . the fail - to - safe mode , common on most air brake systems , provides that in the event air pressure is lost ( vented ) the spring 35 will apply longitudinal force to the actuator rod 38 through the actuator plate 77 and thus causing the emergency brake to stop the vehicle if in motion , or to park the vehicle once stationary . to disengage the braking system 10 and thereby allowing the vehicle to move , the spring chamber 30 must once again be subjected to an increase in air pressure . referring now to fig1 a and 2 b , the brake pads 53 and 54 utilized in the preferred embodiment provide a frictional surface on the rotor 26 to retard vehicle movement , and are readily obtainable and known by those skilled in the art . the caliper 50 shown , is unique in that it adapts to the means of mechanical braking utilized in the present invention . in service brake applications , the caliper 50 converts hydraulic fluid pressure to mechanical output that is directly applied to a set of brake pads , wherein the present invention , the pistons 52 of the caliper 50 are operated by the mechanical means described below . the caliper 50 is mounted to the siamese anchor plate 22 adjacent to the brake rotor 26 by an anchoring means 24 , the anchor plate 22 , attaching to the axle housing 20 . in a preferred embodiment , the anchor plate 22 has dual mounting locations 25 and 27 as mentioned , for utilizing both a normal , hydraulically operated service brake caliper 28 , and the mechanical emergency / parking brake caliper 50 of the present invention upon the same rotor 26 . the anchoring means 24 in the preferred method of attaching the caliper 50 to the anchor plate 22 comprises two floating pins 29 . the caliper 50 is machined so as to bore two holes in the back of the piston cylinders , which allow external mechanical coupling of the pistons 52 , comprising the emergency braking system . to maximize reliability and functionality , each piston 52 is subjected to forces that do not exceed those produced in hydraulic applications . to accomplish this , the force produced is applied to the entire back surface area of each piston , by designing the piston coupler 56 interface to have equal surface area to that of the piston 52 . in the preferred embodiment , the coupler 56 is then attached to the piston 52 and a bridging means 55 through the center of each coupler 56 , maintaining a solid interface with the piston 52 and bridging means 55 . the bridging means 55 delivers and distributes the force to actuate two pistons in a multiple piston caliper application , commonly know in the art . the lever system is fastened using bolts 64 and 65 at the pivot points . since large forces are generated in this system , known design methods and techniques are used to account for these forces , and determine which bolt properties and geometries are necessary for reliability . with the primary stresses observed being a shear stress , the preferred embodiment utilized bolts of ¾ inch diameter . to best illustrate the leverage linking system , fig1 is referred to , showing the various components comprising the system . the linkage 60 is comprised of three individual elements ; a mounting frame 61 , the lever linkage 62 and the yoke linkage 63 . the mounting frame 61 provides a means of attaching the spring chamber 30 to the caliper 50 . the lever linkage 62 comprises the lever for applying force to the piston couplers 56 via the bridging means 55 , and further connects to the spring actuator rod 38 via the pivotal actuator linkage 63 , so as to provide the force for engagement of the braking system 10 . the mounting frame 61 , attaching the system to the caliper 50 , is generally constructed from a pair of parallel angled , square steel arms 66 and 67 with a mounting plate 68 at one end for attaching the spring chamber 30 . the mounting plate provides a means , generally an aperture there through , allowing the actuator rod 38 to engage the lever linkage 62 . the opposite end of arms 66 and 67 in the preferred embodiment are attached to the caliper 50 body and is braced , for reinforcing the brake system components . as shown , the lever linkage 62 is pivotally attached to the mounting frame 61 at a first end positioned between the parallel arms 66 and 67 by a pivotal axis bolt 65 , shown in fig2 a . this pivotal axis provides the lever means for transferring the force applied to the second end of the lever linkage 62 by the pivotally attached actuator linkage 63 attaching to the spring chamber actuator rod 38 . a roller 51 is rotatably attached to the lever linkage 62 by bolt 59 , and in a preferred embodiment , two rollers are utilized providing a more uniform distribution of force to the bridge 55 . the roller 51 transfers force applied to the second end of lever linkage 62 to the bridging means 55 , which distributes the force evenly to the caliper piston couplers 56 , without inducing lateral force or causing binding of the pistons within the cylinders . the actuator linkage 63 provides for the pivotal attachment of the spring chamber actuator rod 38 to the lever linkage 62 , and is fabricated so as to withstand the required force necessary to actuate the braking system . the brake system 60 is normally engaged , until such time that air pressure above ambient is introduced into the spring brake chamber 34 . while engaged , the actuator arm 38 is extended creating a force on the lever linkage 62 through the actuator linkage 63 . this force is carried on to the roller 51 , and translates to a longitudinal force upon the bridging means for forcing the plurality of pistons to engage the brake pads 53 and 54 with the rotor 26 . once air pressure is introduced to the spring brake chamber 34 , the pressure creates a force upon the actuator plate 77 which compresses the parking spring 35 and retracts the actuator rod 38 into the spring chamber 30 . this results in the release of the force upon the lever linkage 62 , and in turn the force applied to the pistons 50 through the couplers 56 , thereby releasing the brake pads 53 and 54 from the rotor 26 . the description of the invention is merely exemplary in nature and , thus , variations that do not depart from the gist of the invention are intended to be within the scope of the invention . such variations are not to be regarded as a departure from the spirit and scope of the invention .