although only one preferred embodiment of the invention is explained in detail , it is to be understood that the embodiment is given by way of illustration only . it is not intended that the invention be limited in its scope to the details of construction and arrangement of components set forth in the following description or illustrated in the drawings . also , in describing the preferred embodiments , specific terminology will be resorted to for the sake of clarity . it is to be understood that each specific term includes all technical equivalents which operate in a similar manner to accomplish a similar purpose . as shown in fig1 - 4 , the present invention is directed to a coupling assembly , generally designated by the reference numeral 10 , which is mounted immediately adjacent a motor 12 on a motor shaft 14 . the assembly 10 includes a worm 20 , generally designated by the reference numeral 20 , an annular thrust ring 30 , a coupling washer , generally designated by the reference numeral 40 , and o - rings 50 . as can be seen in fig3 the inner diameter of the worm 20 is larger than the outer diameter of the shaft 14 so that the worm rides on the shaft with a slip fit . the worm is held in place axially by means of the thrust ring 30 on one side , and the coupling washer 40 on the other side . each of the thrust ring 30 and the coupling washer 40 are press fit onto the motor shaft 14 . the worm 20 includes a head portion 22 and a helical geared portion 24 . the head portion 22 includes coupling elements 26 which are raised relative to an outer planar surface 28 of the head portion . the outer planar surface 28 is substantially perpendicular to the longitudinal axis of the helical geared portion 24 and generally cylindrical . the coupling elements 26 fit cooperatively with mating portions of the washer 40 , transmitting torque from the motor shaft 14 to the worm 20 . as shown in fig4 the coupling elements 26 have a generally triangular shape as viewed perpendicular to the outer surface 28 , with an inner truncated vertex 26 a and two outer vertices 26 b . the peripheral convex outside edge 26 c of each element 26 between the two outer vertices 26 b is flush with the circumference of the head portion 22 . the truncated inner vertex 26 a is concave such that the coupling element has an inner curvature that approximates that of the shaft but does not contact the motor shaft 14 . alternatively , the inner vertex 26 a may be constructed without truncation so as to have a structure like that of the outer vertices 26 b . two concave sides 26 d join the inner vertex 26 a with each of the two outer vertices 26 b , respectively . the coupling elements 26 are preferably machined into the head portion 22 of the worm . as shown in fig1 and 5 , the washer 40 has a flat outer face 44 a generally parallel with an inner face 44 b , and two straight , generally parallel , sides 40 a joined by two slightly convex sides 40 b . the outer face 44 a may meet the sides 40 a , 40 b at substantially a right angle or the edge therebetween may be beveled . protruding from each of the straight sides 40 a is a torque - transmitting element , generally designated by the reference numeral 42 , which also extends inwardly so as to project beyond the otherwise planar inner face 44 b of the washer 40 . in addition , the washer has a cylindrical central opening 46 to receive the motor shaft 14 . each of the torque - transmitting elements 42 has a substantially planar inside face 42 a , and side faces including a generally concave inner portion 42 b nearest the central opening 46 , and a generally convex portion 42 c . an angular portion 42 d joins each end of the concave portion 42 b to an adjoining end of the convex portion 42 c . the resulting structure is convexo - concave , i . e ., the convex portion 42 c of the side face has greater curvature than the concave portion 42 b . the inside face 42 a may meet the side face portions 42 b , 42 c , 42 d at substantially a right angle or the edges therebetween may be beveled . the shape of the washer enables the torque - transmitting elements 42 to fit cooperatively between the coupling elements 26 , with the inside faces 42 a against the outer surface 28 of the head portion 22 of the worm 20 . as illustrated in fig6 standard annular o - rings are fitted on the torque - transmitting elements 42 . the angular portions 42 d of the torque - transmitting elements 42 orient corresponding portions of the o - rings advantageously to complement the curvature of the concave sides 26 d of the coupling elements 26 . thus , the geometries of the torque - transmitting elements 42 and the coupling elements 26 are adapted to each other to ensure the o - rings are only compressed between flat or slightly curved faces , and thus not pinched and possibly damaged by an edge of these torque - transmitting features . during assembly , the thrust ring 30 is pressed onto the motor shaft 14 toward , but not in contact with , the motor housing . the worm 20 is then slipped onto the shaft 14 with the coupling elements 26 facing away from the thrust ring 30 . the o - rings 50 are fitted onto the torque - transmitting elements 42 of the coupling washer 40 , and the washer 40 is then pressed onto the motor shaft , leaving sufficient axial clearance to allow the worm to turn within the limits of the coupling geometry . additional wear washers ( not shown ), such as between the worm 20 and the coupling washer 40 , may be added during this assembly sequence depending upon the expected life of the product . in operation , the o - rings are compressed when torque is transmitted to the worm . in case of shock load , the o - rings are increasingly compressed as the torque becomes higher and higher . due to the forgiveness of the o - rings , the peak torque , which determines the loading of adjacent components , e . g ., the gears , bearings , motor shaft , casing and the coupling itself , is reduced . the present invention is advantageous whether the motor shaft is running against a point contact outside the motor or internally within the motor housing . if the thrust from the worm is taken up by the ends of the motor shaft thrusting against an outside housing or casing , the diameter of the thrust face can be low , virtually a point contact , and will typically be no more than the outer diameter of the motor shaft . the inventive arrangement is particularly effective with such a configuration , i . e ., with the motor is running against point contacts or small flat faces on its end , i . e ., thrusting with the motor shaft ends , rather than against an internal contact inside the motor housing , because the least amount of force ( voltage ) is necessary to effectively break free , and friction generated by the thrust forces of the worm is minimized , maximizing thrust transference . if , on the other hand , point contacts are not used and the motor takes up the thrust internally within the motor housing , a thrust ring mounted on the motor shaft is needed to transmit the force . since such a thrust ring must be larger than the diameter of the motor shaft , more friction is generated . nevertheless , the geometries of the torque - transmitting elements 42 and the coupling elements 26 still allow the motor shaft 14 to turn relative to the worm 20 for a fraction of a revolution to gain inertia and speed before the washer begins to transmit torque to drive the worm . this allowed movement , and the resulting inertia and speed gained thereby , facilitates breaking free from a stalled condition , e . g ., a jammed gear train . another advantage realized through the inventive design is reduced space requirements . with conventional worm gears , representatively depicted in fig7 the worm 20 ′ and mating helical gear 17 are at a distance from the motor 12 . the motor shaft 14 ′ holds part of the coupling 8 a , while the worm 20 ′ and a mating coupling portion 8 b are mounted on an auxiliary shaft 15 . as can be seen , the spacing of the worm 20 ′ and helical gear 17 from the motor 12 creates wasted space 55 . by contrast , the design of the present invention , shown in fig8 positions the coupling and damping arrangement on the far end of the motor shaft 14 , with the worm 20 then being as close to the motor 12 as the dimensions of the mating helical gear 17 will allow . the result is a very compact arrangement with no wasted space . the coupling washer 40 is preferably made of sintered metal which allows a large design freedom in the geometry of the torque - transmitting elements 42 that transmit the torque and hold the o - rings . the worm is machined such that the mating geometry of the coupling elements 26 that receive the torque is easily manufactured in a shape that requires only a simple milling operation from two sides to achieve such coupling elements 26 . in summary , the present invention represents a space - saving arrangement that provides safe break - free capability from a jammed gear condition with a minimal amount of power . no separate is worm bearing system is necessary , and manufacture is simplified through machining of the worm with coupling features and the use of standard o - rings which obviates the need for custom molded damping elements . the foregoing descriptions and drawings should be considered as illustrative only of the principles of the invention . the invention may be configured in a variety of shapes and sizes and is not limited by the dimensions of the preferred embodiment . numerous applications of the present invention will readily occur to those skilled in the art . therefore , it is not desired to limit the invention to the specific examples disclosed or the exact construction and operation shown and described . rather , all suitable modifications and equivalents may be resorted to , falling within the scope of the invention .