an example of a scroll - type vacuum pump suitable for incorporation of the present invention is shown in fig1 and 2 . a dry , two - stage vacuum pump is shown . a gas , typically air , is evacuated from a vacuum chamber or other equipment ( not shown ) connected to a vacuum inlet 12 of the pump . a housing 14 includes a housing portion 14b that encloses and in part defines a first pump stage 18 and a housing portion 14c that encloses and in part defines a second pump stage 30 . an outlet port 14d is formed in the second stage housing near its center . the outlet port communicates with a radially - directed , high pressure discharge passage 16 in housing portion 14c , venting to atmosphere at the outer periphery of the housing . the first scroll pump stage 18 is located within the housing with an inlet region 18a connected to vacuum inlet 12 . as shown in fig2 scroll pump stage 18 may be formed by four pairs of nested spiral shaped scroll blades . each blade pair includes a stationary blade 19 and an orbiting blade 20 . the scroll blade 19 is preferably formed integrally with housing portion 14b to facilitate heat transfer and to increase the mechanical rigidity and durability of the pump . the blade 20 is preferably formed integrally with a movable plate 22 . the blades 19 and 20 extend axially toward each other and are nested as shown in fig1 and 2 . orbital motion of plate 22 and scroll blade 20 produces a scroll - type pumping action of the gas entering the scroll blades at the inlet region 18a . the free edge of each blade 19 and 20 carries a continuous tip seal 26 as described in detail below . the blades 19 and 20 extend axially toward plate 22 and housing portion 14b , respectively , so that there is a sliding seal at the edge of each blade . gas exits scroll pump stage 18 at its outer periphery 18b , where it flows through channels 28 formed in housing portion 14b to an annular inlet region of second scroll pump stage 30 surrounded by an annular plenum chamber 29 . the second scroll pump stage 30 includes a stationary scroll blade 32 and an orbiting scroll blade 31 , each of which carries a tip seal 26 on its free edge . the tip seal establishes a sliding seal between each blade and an opposing surface . the scroll blades of the first and second pump stages may have different blade heights and different numbers of turns to achieve a desired pump performance . as scroll blade 20 orbits relative to scroll blade 19 , pockets formed between the scroll blades , such as pocket pi shown in fig2 move from the inlet of the scroll pump stage toward the outlet and pump gas from the inlet to the outlet . an eccentric drive 40 for pump stages 18 and 30 is powered by a motor 42 connected by a coupling 44 to a drive shaft 46 mounted in axially spaced bearings 48 and 50 . the eccentric drive 40 produces orbiting movement of plate 22 with respect to an axis of rotation 46a of drive shaft 46 . additional details regarding the construction and operation of the scroll - type vacuum pump of fig1 and 2 are given in u . s . pat . no . 5 , 616 , 015 , issued apr . 1 , 1997 , which is hereby incorporated by reference . it will be understood that the tip seal of the present invention may be utilized in a two - stage scroll - type vacuum pump , as shown in fig1 and 2 and described above , may be utilized in a single - stage scroll - type vacuum pump , or may be utilized in any other scroll - type apparatus . in accordance with the invention , a tip seal for a scroll - type vacuum pump includes a seal element and an energizer element . the seal element establishes a sealed , sliding contact with an opposing surface of the vacuum pump . the energizer element forces the seal element into contact with the opposing surface . the energizer element is affixed to the seal element , typically by an adhesive , to form a unitary tip seal . the energizer element is fabricated of an elastomer material with compressible voids . the durometer of the elastomer material and the size and geometry of the voids are selected such that the energizer element readily conforms to the seal groove , so that little force is required to deform the energizer element to the point where the seal groove is nearly completely filled . the compressible voids cannot present a leakage path , either across the seal or along the seal groove . the elastomer material with compressible voids has a low effective modulus of elasticity , so that a low uniform loading is achieved , even after the seal groove is completely filled . a first embodiment of the tip seal is shown in fig3 . a partial cross - sectional view of a tip of scroll blade 19 is shown . the upper edge of scroll blade 19 is provided with a tip seal groove 100 , typically having a rectangular cross section . groove 100 follows the edge of scroll blade 19 and has a spiral configuration . a tip seal 102 is positioned in groove 100 between scroll blade 19 and plate 22 . the tip seal 102 comprises a seal element 110 and an energizer element 112 affixed to seal element 110 with an adhesive 114 . a surface 116 of seal element 110 contacts plate 22 and slides with respect to plate 22 to provide a sliding seal between scroll blade 19 and plate 22 during operation of the scroll pump . referring to fig1 it will be understood that scroll blades 20 , 31 and 32 may be provided with the seal configuration shown in fig3 for enhanced performance of the scroll - type vacuum pump . in the embodiment of fig3 the energizer element 112 comprises a foam having compressible voids 120 . the foam material may be a urethane foam . a preferred material is a microcellular urethane foam manufactured by poron as part no . 4701 - 21 . the voids within the foam are connected by very small passages . the foam is initially compressed about 14 % when installed in a pump . this results in a seal loading of about 5 psi . the initial compression of the foam substantially collapses the voids and passages to allow essentially no leakage through the foam matrix . the modulus of elasticity of this material is about 40 psi . the above - identified foam can be purchased with a contact adhesive on one side , which may be used to attach the energizer element 112 to the seal element 110 . both the urethane foam and the adhesive can tolerate the maximum operating temperatures within a dry scroll pump ( about 200 ef ). whether or not a particular foam performs adequately is a matter of trial and error testing . open cell foams , such as poron 4723 , have been found to work adequately , but are not preferred due to a higher modulus of elasticity of about 70 psi . the initial seal loading of 5 psi is reduced over time by two mechanisms . first , seal element 110 will wear over time , thereby reducing the compression of the energizer element 112 . second , the urethane foam will slow creep at elevated temperatures , which also reduces seal loading . during seal break - in , both the contact pressure and operating temperature of the seal and energizer are gradually reduced . after several hundred hours of pump operation , a stable , long - wearing seal / energizer combination is produced . the seal element 110 can utilize different long - wearing seal materials , such as filled or unfilled polyimides , teflon or ultra high molecular weight polyethylene . this material is typically molded into a cylindrical billet and then skived to the desired thickness . the foam is then attached to the seal material , and the foam is ground to the desired overall seal thickness to form a seal sheet . the seal sheet is then cut into the desired spiral shape . different types of foam , adhesive and seal material can be used within the scope of the invention . for example , the energizer element 112 can be a closed - cell silicone rubber foam , such as the type sold by furon under its chr trademark . in one example , the tip seal 102 had a width parallel to seal surface 116 of 0 . 094 inch and a thickness perpendicular to seal surface 116 of 0 . 112 inch . the seal element 110 had a thickness of 0 . 045 inch , the adhesive 114 had a thickness of 0 . 002 inch and the energizer element 112 had a thickness of 0 . 065 inch . the energizer element 112 was urethane foam , and the seal element was ultra high molecular weight polyethylene . the cost of the energizer required to build a pump is about one tenth that of the unsintered teflon paste . the energizer is furthermore more capable of maintaining adequate seal loading when the pump is first started and after the seal element has worn considerably . a second embodiment of a tip seal in accordance with the invention is shown in fig4 and 5 . like elements in fig3 - 5 have the same reference numerals . a tip seal 140 includes seal element 110 and an energizer element 142 . energizer element 142 comprises a low modulus of elasticity elastomer material having molded compressible voids . commercially available low modulus silicone compounds , such as dow corning silastic , have a modulus of elasticity of about 200 psi . when voids of proper geometry are molded into the energizer element 142 , the effective modulus of the energizer element can be reduced from about 200 psi to about 100 psi . in the example of fig4 and 5 , energizer element 142 has cylindrical voids 150 extending upwardly from a bottom surface of seal groove 100 . the dimensions of the voids 150 are selected to prevent a leakage path across the seal . for an energizer element having a width w of 0 . 094 inch and a thickness t of 0 . 058 inch , the cylindrical voids 150 may have diameters of 0 . 025 inch and heights of 0 . 050 inch . a mold for the energizer element 142 can be constructed through a ram edm process . an array of small holes of proper diameter and depth is drilled into a flat graphite plate . the plate is then used in a ram edm to electrically machine a steel plate . the plate then has an array of small posts protruding from one side . the plate is incorporated into a rubber molding apparatus to mold a silicone elastomeric sheet onto a teflon - based sheet of seal material , for example . the teflon material is typically etched on the molding side for better adhesion . the molded seal assembly has cylindrical holes formed in the silicone elastomer . the seal assembly is cut into a spiral shape and is installed into the seal groove . the voids in the underside of the energizer element do not present a leakage path , either across the seal or along the seal groove . as the seal assembly is cut , voids may be exposed at the sides of the seal . however , the voids in the elastomer are small enough that a leakage path is not formed across the seal . along the seal groove , the elastomer material between voids is present to fill the width of the seal groove and thereby block leakage . it will be understood that the voids 150 are not necessarily formed at the bottom of the energizer element 142 as shown in fig4 . the voids 150 may be formed at the top or on the sides of the energizer element or may be internal to the energizer element , within the scope of the invention . in general , the voids 150 permit the energizer element 142 to be compressed , even when the energizer element fills groove 100 . while there have been shown and described what are at present considered the preferred embodiments of the present invention , it will be obvious to those skilled in the art that various changes and modifications may be made therein without departing from the scope of the invention as defined by the appended claims .