with further reference to the drawings , a machine tool is schematically shown in fig1 and indicated generally by the numeral 10 . the present invention entails a system and method for measuring cutting forces associated with the machine tool 10 . before describing the method and apparatus for measuring these cutting forces , a brief description of a typical machine tool that would utilize the present invention will follow . in this regard , machine tool 10 comprises a turret housing 12 and a turret disk 14 rotatively mounted with respect to the housing 12 . a detachable tool holder 16 projects from the turret disk 14 and is adapted to receive and hold a cutting tool 18 . a workpiece holder 22 is disposed adjacent tool holder 16 and is designed to receive and hold a workpiece 20 . a cross slide 24 is secured to turret housing 12 and is movably mounted on a slide 26 . the present invention entails the provision of a force transducer medium that is secured to or disposed within a machine tool such that cutting forces or loads associated with the cutting tool itself are transferred through the force transducer medium . as will be understood from subsequent portions of this disclosure , the force transducer medium may assume various forms . for example , the force transducer medium may be a plate structure that is secured within a bolted joint of the machine tool . in addition , it will be appreciated that the force transducer medium of the present invention could actually be integrally formed within the machine tool structure itself . with respect to the force transducer medium of the present invention , reference is first made to fig1 and 2 . therein the force transducer medium is in the form of a force transducer plate and is indicated generally by the numeral 28 . as shown in fig1 the force transducer plate 28 is bolted between the turret housing 12 and cross slide 24 . thus , it is appreciated that the force transducer plate 28 lies in the direct path of forces associated with the cutting tool itself as these forces are transferred through the machine tool 10 and particularly through the force transducer plate 28 . viewing force transducer plate 28 in more detail , the same is preferably constructed of steel and includes opposed sides 30 and 32 and a surrounding edge 34 . see also fig3 - 5 . formed near the perimeter of transducer plate 28 is a series of bolt openings 36 . formed around each bolt opening 36 is a raised force shunting pad 38 . as seen in the drawings , it is appreciated that the force shunting pads 38 in the embodiment disclosed are raised annular rings that are elevated with respect to opposed sides 30 and 32 of the transducer plate . transducer plate 28 further includes one or more load cell cavities . in the present embodiment force transducer plate 28 includes two load cell cavities 40 and 42 along with associated wiring cavities 44 . each load cell cavity 40 and 42 is designed to accept a load cell 46 . the number and type of load cells 46 can vary depending upon requirements and conditions . but the present invention aims at providing three axis load sensing within the plate or transducer medium itself . in a preferred embodiment of the present invention , the transducer medium would include at least one three axis load cell such as kistler 9251 . as will be appreciated , the transducer plate 28 could be provided with a series of single axis load cells of compression and shear types which would cumulatively form a load cell network that would effectively yield three axis sensing capabilities . respective load cells 46 are preferably flexibly mounted within the transducer medium or plate 28 by means of conventional sealant 41 suitable for machine tool applications . turning now to fig3 an enlarged sectional view of the transducer plate 28 is shown illustrating the section taken along the line 3 -- 3 . as can be seen , the raised force shunting pads 38 extend above both opposed sides 30 and 32 of the plate 28 . in a preferred embodiment , the raised force shunting pads 38 extend approximately 0 . 127 millimeters or 0 . 005 inches above the surface of sides 30 and 32 . this distance is not critical so long as it is sufficient to prevent the bottom surface of turret housing 12 or the upper surface of cross slide 24 from contacting the opposite sides 30 and 32 of the force transducer plate 28 in either loaded or unloaded conditions . fig4 shows an enlarged sectional view of the transducer plate taken along the line 4 -- 4 in fig2 . this sectional view illustrates the relationship between the height of the load cell 46 and the raised force shunting pads 38 . in the case of one embodiment , the relative height of the load cell or load cells 46 with respect to the raised force shunting pads 38 is such that the load cell is preloaded appropriately but yet not overloaded . for example , in the case of a kistler 9251 load cell , the height is selected such that the load placed on the respective load cells will be approximately 4500 pounds . it should be appreciated that the height of the load cell above the raised force shunting pads can and will vary depending on the specific capacity of the load cell and its location with respect to the raised force shunting pads 38 . selection of actual pre - load will vary according to plate design but in any case will have to be great enough to prevent slippage of the load cell under the influence of shear forces . however , it has been found that a difference in height of approximately 0 . 0127 millimeters or 0 . 0005 inches is usually sufficient to permit the load cell to be effectively loaded but not overloaded . there are cases where it is desirable to adjust the relative height of the load cell 46 with respect to the raised force shunting pads 38 in the field and without resorting to machining . to accomplish this , the present invention provides a preload adjuster which is indicated generally by the numeral 50 in fig5 and shown in detail in fig6 . viewing the pre - load adjuster 50 it is seen that the same includes an elongated stem 52 having a circumferential groove 54 formed in a portion thereof . groove 54 is designed to receive an elastomeric o - ring 56 . a fixed disk 58 is attached to one end of stem 52 by means of a fastener 60 . pre - load shims 62 of various selective thicknesses are provided with the pre - load adjuster 50 . each pre - load shim 62 includes a central opening having a sufficient diameter so as to permit stem 52 and the accompanying o - ring 56 to pass therethrough . fig5 shows a fragmentary cross - sectional view of the transducer plate 28 showing the pre - load adjuster 50 inserted within a load cell 46 . by selectively inserting pre - load shims 62 , the height of the load cell 46 with respect to the raised force shunting pads 38 can be varied . as has been noted above , there are certain applications where the force transducer medium will be integrally formed or pocketed in the machine tool . it is appreciated that the pre - load adjuster 50 can be provided with threads about stem 52 in order that the same can be actually anchored into associated machine tool structure . for example , by providing thread on the stem 52 of the pre - load adjuster 50 , the same can be secured in an upside down fashion within the bottom surface of turret housing 12 . in such cases , the engagement of the o - ring 56 with the central opening or bore of the load cell will generally be sufficient to support the load cell 46 and hold the same in place for assembly . turning to fig7 and 8 , an alternative design for the plate type force transducer of the present invention is shown . the alternate force transducer plate is indicated generally by the numeral 80 and is designed to be located directly behind the curvic coupling 15 of the machine tool 10 or between the curvic coupling 15 and the turret housing 12 ( see fig7 ). the annular force transducer plate 80 is similar in design and function as the force transducer plate shown in fig2 and described above . but as seen in the drawings , the annular force transducer plate is particularly designed to be disposed in a plane generally perpendicular to the plane of the force transducer plate 28 as applied in fig1 where plate 28 lies between the turret housing 12 and the cross slide 24 . in any event , it is seen that the annular force transducer plate 80 includes the same series of bolt openings 36 and raised force shunting pads 38 . likewise , the annular force transducer plate includes load cell cavities 40 and 42 along with accompanying wiring cavities 44 . a pair of load cells 46 are resiliently mounted within respective load cell cavities . the relationship between the load cells 46 , raised force shunting pads 38 and the opposite sides of the annular transducer plate 80 are essentially the same as found in the force transducer plate 28 shown in fig2 . it is seen that in the force transducer medium or plate that the respective load cells 46 are positioned as closely as possible to the raised force shunting pads . this tends to minimize hysteresis and optimizes linearity . as noted before , the force transducer medium that has been particularly shown in the form of a plate structure could be integrally formed within the machine tool itself . essentially , the force transducer medium would include the same features , namely the raised force shunting pads and the selective positioning of the load cells adjacent to the raised force shunting pads . it is appreciated that the relative height differences discussed with respect to the plate structures 28 and 80 would be applicable to an integral or pocketed force transducer medium . in operation , a principal portion of the measured force is carried by the force transducer plate or medium via the raised force shunting pads 38 while a small portion is carried by the three axis load cell 46 which in turn provides a cutting force signal which is indicative of the forces applied to the cutting tool 18 . therefore , the load passing through the transducer plate or medium is effectively divided between the plate or medium and the respective load cells housed within the plate or medium . consequently , this enables one to protect against load cell overloading . in addition , the proportionate amount of load sensed or carried by the respective load cells can be varied depending upon a number of factors including the relative area and location of the raised force shunting pads 38 as shown in fig2 . from the foregoing specification and discussion , it is appreciated that the force transducer plate or medium of the present invention is capable of accurately measuring cutting forces associated with a cutting tool . the present method and system is capable of performing without a trial or turning cut and requires a minimum amount of setup time . because of the design of the raised force shunting pads and the particular location and height spacing of the load cells with respect to the force shunting pads , hysteresis is minimized and linearity is optimized . with the design of the present invention , both compression and shear forces are actually measured within the transducer plate or medium and the design does not rely on moment arms in order to measure cutting forces associated with the tool . also , because of the design and spacing of the raised force shunting pads and the location of the respective load cells with respect to the same , the output of the force transducer plate or medium is substantially immune to load application point . the present invention may , of course , be carried out in other specific ways than those herein set forth without parting from the spirit and essential characteristics of the invention . the present embodiments are , therefore , to be considered in all respects as illustrative and not restrictive , and all changes coming within the meaning and equivalency range of the appended claims are intended to be embraced therein .