referring to the drawings , fig2 shows a schematic structure of a clamp apparatus according to the preferred embodiment of the present invention . clamping action of a clamping mechanism of the apparatus is effected by an actuation system , in the form of two actuator devices which are operatively coupled and which comprise a variable reluctance actuator , such as a solenoid motor 34 , and a linear induction actuator such as a cylindrical voice - coil motor (“ vcm ”) 35 acting in tandem . the force - gap characteristic of a typical solenoid is highly non - linear , with force dropping off rapidly with increase in the gap between a fixed core and a movable plunger . this steep force attenuation limits the range of leadframe thickness that the clamp can handle . the inclusion of a vcm 35 in the clamp apparatus cooperating with the solenoid motor 34 facilitates movement of the plunger regardless of the solenoid gap . in other words , the motion of the plunger is effected essentially by the vcm 35 while the actual clamping force is essentially provided by both the solenoid motor 34 ( which provides a major contribution ) and the vcm 35 . the prior art clamp apparatus according to fig1 needs to use a fairly stiff return spring 21 for quick passive de - clamping . so a substantial part of the solenoid force is consumed in overcoming the spring force . in the clamping mechanism of the invention , ideally speaking , no return spring 21 is required as the vcm 35 is adequately designed for quick response , both during clamping and de - clamping . the magnetic circuit of the clamp apparatus according to the preferred embodiment also incorporates a feature , which generates an asymmetric force characteristic with respect to the direction of an energizing current . while affording a high specific clamping force , this design concept facilitates active de - clamping using the vcm 35 . the structure and function of the actuation system will now be described with reference to fig2 and 4 . a housing 1 , typically made of soft magnetic material , houses the actuation system and forms part of a magnetic circuit . an exemplary embodiment of the linear induction actuator will first be discussed . a multiplicity of permanent magnets 2 , which may each be shaped as a circular arc is mounted on the inner cylindrical surface of the housing 1 . an annular air gap 10 formed between the inner cylindrical portion of the housing 1 and the magnets 2 , contains a radial magnetic field . disposed in the air gap 10 is a cylindrical voice coil 3 - 3 ′. the voice coil 3 - 3 ′ is mounted on a coil support 4 , which in turn , is affixed to a central shaft 5 . the shaft 5 is allowed to freely move through a certain distance in the axial direction . it is guided by a snugly fitting self - lubricating bush bearing 6 , which is affixed to the housing 1 . when the voice coil 3 - 3 ′ is energized by an electric current , the shaft 5 experiences an axial force due to electromagnetic induction between the voice coil 3 - 3 ′ and magnets 2 , whose magnitude is proportional to the current passing through the voice coil 3 - 3 ′. reversing the direction of the coil current reverses the direction of the induced force . an exemplary variable reluctance actuator is discussed next . at the bottom of the housing 1 is affixed another ring - shaped coil , called a solenoid coil 7 - 7 ′. the voice coil 3 - 3 ′ and the solenoid coil 7 - 7 ′ are connected electrically in anti - series . this means that when a current passes through the voice coil 3 - 3 ′ in a clockwise direction as seen from the top of fig2 the same current passes through the solenoid coil 7 - 7 ′ in the counter - clockwise direction , as seen from the top of fig2 and vice versa . a solenoid plate 8 , typically made of soft magnetic material is affixed to the lower end of the shaft 5 , such that when the solenoid coil 7 - 7 ′ is energized by an electric current , the solenoid plate 8 is attracted towards the lower face of the housing 1 . fig3 a , 3 b and 3 c show respectively , plan , elevation and bottom views of the housing 1 and permanent magnets 2 of the clamp actuator , all in cross section . they illustrate the housing 1 , that has a flux relay portion or section 1 * dividing compartments containing the voice coil 3 - 3 ′ and solenoid coil 7 - 7 ′ respectively . there is an annular air gap 10 between the voice coil 3 - 3 ′ and housing 1 , and a void 11 in which the solenoid coil 7 - 7 ′ is contained . fig4 a shows the flux paths 12 and 13 of the vcm magnets 2 and the solenoid coil 7 - 7 ′ respectively , during a clamping process . fig4 b shows the flux paths 12 , 13 during de - clamping . the direction of magnetic flux 12 due to the permanent magnets 2 is fixed but the direction of the magnetic flux 13 due to the solenoid coil 7 - 7 ′ reverses depending upon the reversal of the excitation current . during clamping , the current in the solenoid coil 7 - 7 ′ flows as indicated in fig4 a , and thus the magnetic flux 13 due to the solenoid coil 7 - 7 ′ flowing in section 1 * of the housing 1 has a direction opposite to the magnetic flux 12 of the permanent magnets 2 . now section 1 * of the housing 1 is so designed that it is very close to saturation solely due to the flux 12 of the permanent magnets 2 . the flux 13 formed by the current in the solenoid coil 7 - 7 ′ partially cancels out the flux 12 , thus reducing the net flux density in section 1 * and taking it away from flux saturation . due to the current flow as shown in fig4 a , the voice coil 3 - 3 ′ exerts a force on the shaft 5 in the upward direction as shown by arrow a . as the shaft 5 moves upward taking the solenoid plate 8 with it , an increasingly higher force is further exerted on the shaft 5 due to solenoid plate 8 , which is strongly attracted by solenoid flux 13 at the bottom surface of the housing 1 , as it approaches the latter . the final solenoid force is substantially higher than that of the vcm 35 . during clamping action , although both forces act in tandem , the contribution of the solenoid 34 to the total force is substantially higher than that of the vcm 35 . when the direction of the excitation current is reversed as shown in fig4 b , the magnetic flux 13 of the solenoid coil 7 - 7 ′ also reverses direction such that it now travels through section 1 *, in the same direction as the flux 12 of the permanent magnets 2 . however , as previously mentioned , section 1 * of the housing 1 is very close to saturation solely on account of the flux 12 of the permanent magnets 2 . thus it can relay virtually no more flux arising from the solenoid coil 7 - 7 ′. thus in this case , the attractive force exerted by the solenoid coil 7 - 7 ′ on the solenoid plate 8 is small and so the predominant force is generated by the voice coil 3 - 3 ′ in the downward direction as shown by arrow b . this is utilized to produce the de - clamping action . the structure and function of the entire clamp apparatus is now described with reference to fig2 which shows the structure of the whole clamp apparatus . in the unclamped state , an object such as a substrate 26 is supported by channel 33 . in the preferred embodiment , clamping of the substrate 26 by a clamping mechanism , which may comprise an upper jaw 25 ( mounted on lever 22 ) and a lower jaw 27 ( mounted on lever 28 ), is effected by generating an actuation force on a force transmission mechanism , to transfer the force from the actuation system to the clamping mechanism . the force transmission mechanism may take the form of transferring the actuation force by rotationally actuating levers 22 and 28 respectively about pivots 23 and 31 , in the directions indicated respectively by arrows g and h of fig2 . the lever 22 is connected to the clamp shaft 5 through spring means , which may comprise a helical spring 9 . the spring 9 ensures decoupling of the linear motion of the shaft from the rotary motion of the lever 22 about pivot 23 . the spring 9 also ensures that irrespective of the substrate thickness clamped , the solenoid plate 8 travels its full distance towards the solenoid housing 1 , thus enabling maximum possible force of the solenoid 7 - 7 ′ on the solenoid plate 8 . in effect , the clamp apparatus exerts its force on lever 22 through spring 9 . the presence of spring 9 also ensures that the clamping force is higher for thicker substrates and lower for thinner substrates . as described above , during clamping , the voice coil 3 - 3 ′ initiates the motion of the shaft 5 in the direction of arrow a ( fig4 a ) and subsequently , the solenoid 34 also exerts an increasingly higher force on the shaft 5 in the same direction . as the shaft 5 moves in direction a , rotating the lever 22 about the pivot 23 , a cam mechanism such as a cam plunger 30 which is preloaded against lever 22 by spring 29 , moves in direction f through support bearing 32 . in doing so , inclined surface 30 ′ of the plunger 30 rotates the lever 28 about pivot 31 , in the direction indicated by arrow h , until the lever 28 rests on the horizontal surface 30 ″ of the plunger 30 . as the lever 28 so rotates , the lower jaw 27 comes in contact with the substrate from below and lifts the substrate through a small height , from its support channel 33 . the rotation of lever 22 about pivot 23 in the direction of arrow g brings the upper jaw 25 in contact with the substrate 26 from above . this results in the substrate 26 being clamped between jaws 25 and 27 . after clamping , the substrate 26 is indexed precisely through a specified distance in a direction perpendicular to the plane of fig2 . then , de - clamping is effected by reversing the current in the voice coil 3 - 3 ′ and solenoid coil 7 - 7 ′. upon current reversal , the solenoid 34 is ineffective due to magnetic saturation effect as explained previously . so the force of the vcm 35 turns the lever 22 in the direction opposite to e , raising the upper jaw 25 in a direction opposite to arrow g . at the same time , turning of the lever 22 also pushes the cam plunger 30 in the direction opposite to direction f , thus allowing the lever 28 aided by light spring 24 , to rotate in a direction opposite to direction h , while sliding down surface 30 ′ of plunger 30 , thus de - clamping the substrate 26 . an indexing actuator ( not shown ) then returns the open clamping mechanism to the initial position for the next indexing stroke . after de - clamping , the substrate 26 lies in the support channel 33 without any contact from the clamping jaws 25 and 27 . so during the return stroke of the indexing actuator , the position of the substrate 26 is not disturbed by the jaws 25 , 27 . hence the substrate may be supported solely by the support channel 33 and its position is maintained without a need to use any other fixed clamp to maintain the precise position of the substrate 26 in the channel 33 , as the index clamp returns to its initial position for the next indexing stroke . thus , it will be appreciated that the preferred embodiment of the invention employs both a solenoid and a voice coil motor ( vcm ) for its clamping action . such hybrid actuation enables better control over the impact force during clamping . it also results in a clamp with an extended range attainable by a combination of both actuation means , as well as moderation of clamping force and can handle more types of substrate thickness . further , the presence of the voice coil motor 35 affords the clamp apparatus a greater flexibility through profiling of the actuating current . current profiling involves a stepwise increase in current leading to a gradual , smoother motion of the clamp jaws thus enabling clamping of the substrate 26 with minimal impact force . current profiling , although possible with a simple solenoid clamp of the prior art , lends limited advantage due to the highly non - linear variation of force with solenoid gap . the invention described herein is susceptible to variations , modifications and / or additions other than those specifically described and it is to be understood that the invention includes all such variations , modifications and / or additions which fall within the spirit and scope of the above description .