referring now to the prior art shown in fig1 , there is depicted therein a pneumatic starter 10 of the general type often utilized to start gas turbine engines , such as for example aircraft turbine engines ( not shown ). the pneumatic starter 10 , also known as an air turbine starter , includes a turbine wheel ( not shown ) which is driven by a compressed gas , most commonly compressed air from an external supply , passing therethrough so as to extract energy from the gas and convert the extracted energy to mechanical energy through a gear train ( not shown ) in a manner well known in the art . although the present invention is described herein with reference to an air turbine starter , it is to be understood that the pawl and ratchet assembly of the present invention has application on any unidirectional drive system wherein a pawl and ratchet clutch is utilized to transmit rotation from a driving shaft to a driven shaft . extending axially outwardly from the transmission ( not shown ) is an output shaft 60 which has means , such as for example splines 62 , for engaging an engine shaft ( not shown ) in the gear box of the turbine engine ( not shown ) on which the starter 10 is utilized to start the turbine engine . the output shaft 60 is rotatably supported on bearing means 66 . the aforementioned pawls 48 ( or “ body ”), of which there are typically three , are supported on a clutch carrier 70 of the pneumatic starter 10 that extends radially outward from the output shaft 60 . each of the pawls 48 is pivotally supported on a shaft 52 mounted to and extending axially from the clutch carrier 70 of the pneumatic starter 10 such that the pawls 48 are disposed in cooperation with the ratchet member 46 at equally spaced intervals about the circumference of and in radially spaced relationship from the ratchet member 46 . additionally , each of the pawls 48 is biased to pivot about its support shaft 52 to rotate the toe end 47 thereof radially inwardly towards the ratchet member 46 under the force of a bias spring 54 mounted to an axial flange portion 72 of the clutch carrier 70 . each bias spring 54 may comprise a leaf spring operatively bearing against the heel 49 of its associated pawl 48 so as to function during operation of the starter 10 to load the toe end 47 of its associated pawl 48 into engagement with the teeth of the ratchet member 46 of the pawl and ratchet clutch to ensure transmission of torque from a ring gear ( not shown ) in the pneumatic starter 10 to the output shaft 60 until the output shaft 60 has reached a relatively high desired cut - off speed , for example about 5000 rpm , at which the pawls 48 pivot away from the ratchet member 46 under the influence of centrifugal force after disengagement from the teeth 45 of the ratchet member 46 upon slowing down of the ratchet member 46 after termination of the flow of compressed air through the starter turbine ( not shown ). when the pawls 48 are engaged with the teeth of the ratchet 46 during operation of the starter 10 , the output shaft 60 , and the engine shaft of the turbine engine ( not shown ) connected therewith , are driven in rotation through the engaged pawl 48 and ratchet member 46 . after the shaft of the turbine engine engaged with the output shaft 60 of the starter 10 has reached the preselected desired engine speed , the flow of compressed air to and through the turbine wheel ( not shown ) is shut off . as a result , drive power is no longer being delivered to the ratchet member 46 . consequently , the ratchet member 46 slows down and its rotational speed rapidly decreases , while the output shaft 60 of the starter 10 and the pawls 48 mounted thereto continue to rotate at the higher engine speed , thereby causing the pawls 48 to become disengaged from the ratchet member 46 and pivot away from the ratchet member 46 . centrifugal force acting on the pawls 48 overcomes the force provided by spring 54 to cause the pawls 48 to rotate away from and disengage the ratchet member 46 . if the turbine engine is later shut down , the starter output shaft 60 begins to slow down and its rotational speed steadily decreases as the turbine engine spools down . as the output shaft 60 coasts down , the centrifugal force acting on the pawls 48 so as to urge the toe ends 47 of the pawls 48 radially outwardly , steadily decreases and the toe end 47 of each pawl 48 begins to pivot radially inwardly toward the ratchet member 46 under the bias force applied by the springs 54 on the heel 49 of the pawls 48 until the toe ends 47 of the pawls 48 re - engage with the teeth of the ratchet member 46 . a spring clamp 75 is attached by bolts 80 to the axial flange portion 72 of the clutch carrier 70 to hold the spring 54 . existing ratchet and pawl clutch designs experience spring failures and pawl heel wear . a spring fracture and pawl heel wear may alter the performance of the unit in a negative manner . the source of spring fractures and pawl heel wear is the contact forces experienced between the spring end 90 and pawl heel 49 during rotation of the pawl 48 . during faster rotation , centrifugal force may rotate the pawl 48 radially outward , here in a counter - clockwise direction against the force and sliding / rubbing of the spring 54 against the pawl heel 49 . as rotation slows , the spring forces the pawl to rotate in a clockwise direction causing the spring to slide / rub against the heel 49 . further , as rotational speed fluctuates during operation , centrifugal force changes , as does the deflection of the spring , and subsequent contact and / or sliding forces wear the parts . referring now to fig2 , a rotating member 81 , such as a wheel , pin or ball or the like , may be attached by a pin 85 to the heel 49 of the pawl 48 . the rotating member 81 rides on an unsupported spring end 90 of the spring 54 . as the pawl 48 is influenced by centrifugal force as the assembly 10 rotates , the rotating member 81 engages and rolls along the spring end 90 as the pawl 48 rotates clockwise and counter - clockwise . the rotating member 81 rotating along the spring end 90 minimizes any friction and / or sliding forces that was caused by the relative movement on the heel of the spring end 90 and the heel 49 as the pawl 48 rotate in a clockwise and counterclockwise direction . the wheel 81 extends beyond dimensions of the heel 49 and into a discontinuity 83 along the axial flange portion 72 that also receives the pawl 48 . the rotating member 81 reduces sliding / rubbing between the spring end 90 and the heel 49 thereby minimizing wear caused by such sliding / rubbing . to assemble a pawl for use herein , a user evacuates enough material in the heel 49 of the pawl 48 and creates a hole 51 in which the shaft 52 is fitted for rotation thereabout . similarly , a hole 87 is drilled in the heel 49 to insert the pin 85 therein about which the rotating member 81 rotates . alternatively , the heel 49 is cast , or the like , with an opening 95 for receiving the rotating member 81 . a pawl 48 without a rotating member ( see fig1 ) may be replaced with a pawl 48 with a rotating member 81 by separating the pawl without a rotating member from the shaft on inserting the pawl 81 with a rotating member therein while deflecting the spring end 90 . although the invention has been shown and described with respect to a best mode embodiment exemplary thereof , it should be understood by those skilled in the art that various modifications , changes , omissions and additions in the form and detail thereof may be made without departing from the spirit and scope of the invention . for example , although spring end 90 of fig2 is depicted as a leaf spring , the pawl 48 with rotating member 81 can be used in conjunction with any spring means suitably configured and disposed for biasing the toe portion 47 of the pawl 48 radially inwardly toward the ratchet member 46 . although a combination of features is shown in the illustrated examples , not all of them need to be combined to realize the benefits of various embodiments of this disclosure . in other words , a system designed according to an embodiment of this disclosure will not necessarily include all of the features shown in any one of the figures or all of the portions schematically shown in the figures . moreover , selected features of one example embodiment may be combined with selected features of other example embodiments . the preceding description is exemplary rather than limiting in nature . variations and modifications to the disclosed examples may become apparent to those skilled in the art that do not necessarily depart from the essence of this disclosure . the scope of legal protection given to this disclosure can only be determined by studying the following claims .