referring to fig1 and 2 , there is shown a friction clutch assembly 1 which includes a first component having a rotary hub 2 , a radially outwardly extending mounting flange 3 which is integral with the hub 2 , and two disc - shaped washer - like lateral guides 4 and 5 which are non - rotatably secured to the flange 3 by an annulus of rivets 6 or other suitable fasteners . a second component of the clutch disc assembly 1 comprises an annular clutch disc 8 which is rotatable within limits relative to the fist component to both sides of a predetermined neutral angular position , and two friction coatings 7 which are disposed at the opposite sides of and rotate with the clutch disc 8 . for example , one of the coatings 7 can be engaged by the flywheel on a crankshaft forming part of an engine , and the other coating 7 can be engaged by a pressure plate forming part of a friction clutch which can couple the crankshaft to the input element of a change - speed transmission in an automotive vehicle . the maximum diameter of the mounting flange 3 is relatively small ; it can be a fraction of the maximum diameters of the guides 4 , 5 and can equal the inner diameter of the annular clutch disc 8 . the radially innermost portion of the clutch disc 8 is disposed in the annular space between the guides 4 , 5 . the assembly 1 further comprises a first friction generating unit 9 which is disposed between the clutch disc 8 and the left - hand guide 5 , as viewed in fig1 . the function of the unit 9 is to oppose each and every stage of rotation of the clutch disc 8 relative to the hub 2 . as shown , the friction generating unit 9 comprises an energy storing device in the form of a dished spring 10 , a first friction pad 11 at one side of the clutch disc 8 , and a further friction pad in the form of a sleeve 12 at the other side of and within the clutch disc 8 . the sleeve 12 has a substantially l - shaped cross - sectional outline . reference may be had to my commonly owned copending application ser . no . 396 , 137 filed july 7 , 1982 for &# 34 ; clutch disc arrangement &# 34 ; which fully discloses and shows a sleeve - like friction pad capable of being inserted into the central opening of an annular clutch disc so as to surround a first part of the first component and to be adjacent to and bear against a second part of the first component . the clutch disc 8 has a central opening 8c which receives one portion 12a of the friction pad or sleeve 12 . the portion 12a is a short cylinder which extends circumferentially of the hub 2 . a second portion 12b of the friction pad or sleeve 12 extends radially of the hub 2 and resembles a flat washer which is interposed between the clutch disc 8 and the guide 4 . as disclosed in my aforementioned copending application ser . no . 396 , 137 , the sleeve - like friction pad 12 can comprise a part which is made of steel and a part with a relatively high co - efficient of friction and constituting a coating or liner for the part which is made of steel . the friction pad 12 is a split ring so that it can be readily inserted into and withdrawn from the opening 8c of the clutch disc 8 . the liner or coating of the friction pad 12 is adjacent to the peripheral surface of the flange 3 and to the left - hand side of the guide 4 , as viewed in fig1 . the assembly 1 further comprises a so - called load friction unit 13 which is disposed outside of the annular space between the guides 4 , 5 of the first component and is adjacent to the outer side of the guide 4 . the means for supporting the friction unit 13 comprises a guide ring or supporting ring 14 which is rigidly secured to the flange 3 of the hub 2 by the aforementioned fasteners 6 . the friction unit 13 comprises a winged load friction disc 15 which is inwardly adjacent to an axially offset outer marginal portion 14a of the supporting ring 14 so that the ring 14 fixes the position of the friction disc 15 , as considered in the radial direction of the first component including the hub 2 . the friction unit 13 further comprises a friction generating device having a friction pad 16 which is interposed between the friction disc 15 and the guide 4 , and a resilient energy storing device 17 in the form of a dished spring whose radially innermost portion reacts against the marginal portion 14a of the supporting ring 14 and whose radially outermost portion bears against the adjacent portion of the friction disc 15 . in other words , the dished spring 17 urges the friction disc 15 and the friction pad 16 against the outer side of the guide 4 so that the pad 16 offers a certain resistance to rotation of the friction disc 15 relative to the guide 4 . in order to regulate the operation of the friction unit 13 via friction disc 15 , the clutch disc 8 comprises projections in the form of arms 18 extending in parallelism with the axis of the hub 2 and with clearance into cutouts or slots 19 of the friction disc 15 . the projections 18 can constitute integral parts of the clutch disc 8 , i . e ., they may constitute lugs which are bent out of the general plane of the clutch disc so as to extend toward the friction disc 15 and into the respective cutouts 19 . while extending from the clutch disc 8 into the respective cutouts 19 of the friction disc 15 , the projections 18 further extend with clearance through cutouts or slots 20 of the guide 4 . the assembly 1 further comprises a set of energy storing coil springs ( one shown at 24 in fig1 ) which spacedly surround the hub 2 . the projections 18 of the clutch disc 8 are disposed radially inwardly of the annulus which is formed by such coil springs . these coil springs are installed in openings or windows ( to be described hereinafter ) which are machined into or otherwise formed in certain parts of the assembly 1 , and the projections 18 are preferably located in the region of the innermost portions of such windows and radially inwardly of the radially innermost portions of the coil springs . the width of the cutouts 20 in the guide 4 , as considered in the circumferential direction of the hub 2 , exceeds the width of the corresponding cutouts 19 in the friction disc 15 . thus , when the clutch disc 8 rotates relative to the hub 2 , its projections 18 engage first the surfaces bounding the respective cutouts 19 before such projections engage the surfaces surrounding the respective cutouts 20 . rotation of the second component including the clutch disc 8 and its coatings 7 relative to the first component ( including the parts 2 , 3 , 4 and 5 ) is terminated when the projections 18 engage the surfaces surrounding the respective cutouts 20 , i . e ., when the guide 4 is compelled to share angular movements of the disc 8 and the rivets 6 compel the hub 2 , the flange 3 and the guide 5 to rotate with the guide 4 . the operation of the clutch disc assembly 1 is as follows : the path for transmission of torque between the hub 2 ( i . e ., the first component ) and the second component including the clutch disc 8 and its coatings 7 comprises three groups or sets of energy storing cell springs 22 , 23 and 24 ( shown schematically in fig2 ). the first group or set including the coil springs 22 is installed in windows 25 of the clutch disc 8 and in windows 26 of the guides 4 and 5 . the dimensions of the windows 25 match those of the windows 26 . the springs 22 act to oppose rotation of the clutch disc 8 from a neutral angular position through angles 27 and 28 . the magnitude of torque which is necessary to overcome the resistance of the coil springs 22 , while the clutch disc 8 rotates relative to the hub 2 through the angle 27 or 28 , can be seen in the diagram of fig3 . once the clutch disc 8 has turned through an angle exceeding that shown at 27 or 28 , the surfaces surrounding the windows 29 of the clutch disc 8 engage the coil springs 23 of the second set or group . the coil springs 23 are further installed in the windows 130 of the guides 4 and 5 . the coil springs 23 are stressed and store energy ( i . e ., they oppose rotation of the clutch disc 8 relative to the hub 2 ) while the clutch disc 8 turns through the angle 30 minus 27 or through the angle 31 minus 28 . at such time , rotation of the clutch disc 8 relative to the hub 2 is still opposed by the first friction generating unit 9 because the latter is effective during each and every stage of rotation of the clutch disc 8 from its neutral position through the angle 30 or 31 . the springs 24 of the third set or group are installed in the windows 32 of guides 4 , 5 and in the windows 33 of the friction disc 15 . the dimensions of the windows 33 ( as considered in the circumferential direction of the hub 2 ) match those of the windows 32 in the guides 4 and 5 . the springs 24 further extend into windows 34 which are provided therefor in the clutch disc 8 and whose width , as considered in the circumferential direction of the hub 2 , exceeds the width of the windows 32 or 33 by a distance corresponding to the combined difference between the angles 27 , 28 on the one hand and the angles 30 , 31 on the other hand . this can be seen in fig2 . the projections 18 of the clutch disc 8 engage the surfaces surrounding the respective cutouts 19 when the angular displacement of the clutch disc 8 relative to the hub 2 exceeds the angle 30 or 31 . from there on , and assuming that the extent of angular displacement of the clutch disc 8 from its neutral position continues to increase , the friction disc 15 rotates with the clutch disc 8 relative to the hub 2 . at such time , the surfaces surrounding the windows 34 in the clutch disc 8 engage the corresponding coil springs 24 of the third set so that the springs 24 undergo compression and store energy with the result that they also oppose rotation of the clutch disc 8 relative to the hub 2 . this also applies for the friction unit 13 which is active as soon as the friction disc 15 begins to rotate with the clutch disc 8 . when the angular displacement of the clutch disc 8 relative to the hub 2 reaches the value 35 or 36 ( see fig3 ), the projections 18 of the clutch disc 8 engage the surfaces bounding the cutouts 20 of the guide 4 and the clutch disc 8 is brought to a halt ( as concerns is angular movement relative to the first component including the hub 2 ). from there on , the hub 2 shares all angular movements of the clutch disc 8 or vice versa . the friction generating unit 9 is effective within the entire range of angular movement of the clutch disc 8 relative to the hub 2 ( i . e ., through the sum of angles 35 and 36 ). it is clear that the improved assembly is susceptible of many further modifications without departing from the sprit of the invention . for example , the assembly can comprise one or more projections 18 which are provided on the clutch disc 8 and engage the friction disc 15 after the clutch disc 8 completes an angular movement through the aforediscussed angle 30 or 31 , and one or more discrete or additional projections or arms which engage the guide 4 or another part of the first component to terminate the angular movement of the clutch disc 8 with reference to the hub 2 . an important advantage of the improved clutch disc assembly is its simplicity . this is attributable , in part , to the feature that the projections 18 of the clutch disc 8 can strike directly against one of the guides 4 , 5 when the angular movement of the clutch disc relative to the first component is to be terminated . this obviates the need for bolts or otherwise configurated stops between the guides 4 and 5 for the clutch disc 8 . moreover , the provision of projections 18 on the clutch disc 8 renders it possible to employ a very simple and inexpensive friction disc , i . e ., the disc 15 need not be formed with lugs and / or other types of protuberances in order to participate in regulation of operation of the friction generating device including the parts 16 and 17 . as explained above , the friction unit 13 need not be active or operative during the initial stage or stages of rotation of the clutch disc 8 from its neutral angular position relative to the first component including the parts 2 to 5 . the unit 13 begins to participate in the opposition to rotation of the clutch disc 8 relative to the hub 2 when the projections 18 engage the surfaces bounding the respective cutouts 19 of the friction disc 15 , i . e ., when the discs 8 and 15 rotate in unison with reference to the first component . if desired , the projections 18 can be provided close to the radially outermost part of the clutch disc 8 or close to the radially outermost portion of the guide 4 . the previously discussed positioning of the projections 18 is preferred at this time , i . e ., inwardly of the radially innermost portions of the coil springs 22 , 23 and 24 and in the region of windows ( such as 25 , 26 and 34 ) in the clutch disc 8 . this contributes to compactness of the clutch disc assembly , as considered in the radial direction of the hub 2 . it is further possible to provide two load friction units , one at the outer side of each of the two guides 4 and 5 . fig1 shows by broken lines a portion of a second load friction unit , namely , a portion of a second friction disc 215 , a portion of a friction pad 216 and a portion of an energy storing resilient device 217 which reacts against a supporting member 214 and urges the parts 215 and 216 against the outer side of the guide 5 . it will be noted that both load friction units are disposed outside of the annular space between the guides 4 and 5 . the two load friction units can operate in parallelism with one another , or each thereof can be entirely independent of the other , i . e ., the unit 13 can be operative to oppose one or more first stages of angular movement of the clutch disc 8 relative to the hub 2 , and the unit including the parts 215 to 217 can be operative to resist or oppose one or more second stages of angular movement of the clutch disc with reference to the first component . the friction pad 16 or 216 can be omitted , i . e ., the respective friction unit can rely exclusively on friction between the disc 15 or 215 and the corresponding guide ( 4 or 5 ). it has been found that , by properly selecting the friction coefficient and the dimensions of the pad 16 or 216 , the opposition of the corresponding friction unit can be enhanced at a minimal additional cost . the aforementioned parts 10 and 11 of the friction generating device 9 can be said to constitute a so - called damping device which is active during idling , namely , when the clutch disc 8 is still free to rotate relative to the friction disc 15 and / or 215 . such damping device is desirable and advantageous in many types of clutch disc assemblies . as shown , the parts 10 and 11 are disposed at that side of the clutch disc 8 which faces away from the portion 12b of the member 12 , i . e ., which faces away from the guide 4 and toward the inner side of the guide 5 . without further analysis , the foregoing will so fully reveal the gist of the present invention that others can , by applying current knowledge , readily adapt it for various applications without omitting features that , from the standpoint of prior art , fairly constitute essential characteristics of the generic and specific aspects of my contribution to the art and , therefore , such adaptations should and are intended to be comprehended within the meaning and range of equivalence of the appended claims .