with particular reference to the drawings , there is illustrated in fig1 a food processor embodying this invention and comprising a base housing 10 , a working bowl 12 removably mounted thereon for holding food material to be processed , and a removable cover 14 on the bowl . the base housing 10 comprises three basic structural elements . the first of these is a box - like enclosure , best illustrated in fig3 and including spaced , parallel sidewalls 16 , 18 , rear wall 20 , and front wall 22 , the latter including an angled portion 22a having a plurality of ventilation slots 24 therethrough . the second element of base housing 10 is a substantially rectangular base plate 26 ( fig2 ) having a vertical flange 28 positioned inside of the vertical walls and having on its bottom surface four rubber - like feet 30 conventionally mounted through holes 32 formed in bosses 34 . the third element making up base housing 10 is a top closure 36 which is essentially rectangular to conform to the shape of the housing , but includes an upwardly , extending circular turret 38 which defines a central , circular opening 40 and has molded into its outer periphery at least two spaced locking lugs 42 . extending upwardly through the opening 40 in top closure 36 is a spindle 44 having a flat 46 along one side and driven by a drive unit within the base housing 10 to be described more fully infra . the bowl 12 has a cylindrical sidewall 48 and a raised bottom 50 , thereby forming a depending skirt 52 . extending inwardly from the skirt 52 are a plurality of projections 54 positioned to lock under the lugs 42 on the base housing when the bowl is rotated thereon . the bowl base 50 defines a central opening bounded by a cylindrical socket 56 which surrounds the spindle 44 . on the outer surface of the cylindrical sidewall 48 is a vertical boss 58 defining a bore 60 having therein a sliding rod 62 spring loaded upwardly by means of spring 64 . when bowl 12 is locked into position on base housing 10 , the end of rod 62 is aligned with an opening 66 in the top closure 36 of base housing 10 . the upper rim of the cylindrical sidewall 48 carries a plurality of spaced , radially outwardly extending locking tabs 68 . the cover 14 for the bowl is substantially circular with a depending inner flange 70 which fits within the cylindrical sidewall 48 and an outer flange 72 which carries a plurality of depending locking fingers 74 positioned such that , when the cover 14 is rotated , they engage respective locking tabs 68 . also depending from the outer flange 72 is a camming member 76 positioned to engage and depress the sliding rod 62 when cover 14 is rotated to its fully closed and locked position . a vertical hopper or well 78 extends through the cover 14 for the insertion of food which may be pressed inwardly by means of a movable pusher 80 . as will be seen from fig2 the spindle 44 comprises a steel core 82 with an outer plastic sleeve 84 having a sealing flange 85 covering opening 40 . various tools may be positioned over this spindle , as shown in fig1 each comprising one or more blades 86 mounted on a hub 88 . further details of the construction of bowl 12 , cover 14 , and the tool assemblies will be found in the above - referenced u . s . pat . no . 3 , 892 , 365 of verdun . the drive unit of this invention is mounted in the base housing 10 by means of motor mount 90 shown in fig3 . it comprises front 92 and rear 94 cross members , each of which extends between , and is secured at its ends to , the sidewalls 16 , 18 . the cross members 92 , 94 are interconnected by means of an upwardly bowed bridging member 96 which has an integral stub shaft 98 extending upwardly therefrom for alignment with the opening 40 in the top closure 36 when it is mounted on the base housing 10 . the rear cross member 94 defines a central , circular opening 100 . aligned therewith , and defined by the front cross member 92 , is an opening 102 in the form of an inverted u extending through the bottom edge of cross member 92 . on either side of the opening 102 is a bolt hole 104 . the opening 100 in the rear cross member is provided with a rubber grommet 106 ( fig2 ) and the bolt holes 104 in the front cross member 92 are provided with similar but smaller grommets 108 ( fig4 ). a universal motor 110 is carried by the motor mount 90 at three support points . this universal motor 110 is positioned within the base housing 10 with its axis of rotation as defined by a rotatable motor shaft 118 extending horizontally parallel with the base plate 26 . the frame 111 of this motor includes a circular boss 112 encircling and concentric with the motor shaft 118 at one end of the motor , this boss 112 being inserted through and held snuggly by the resilient grommet 106 . a similar boss 114 at the other end of the motor fits within , but is spaced from , the opening 102 where it is retained by means of bolts 116 which extend through the grommeted holes 104 , as shown in fig4 . the resilient grommets 108 are symmetrically located on opposite sides of the axis of motor shaft 118 , and the other grommet 106 is concentric with the axis . in this manner , a rigid but vibration - absorbing three - point mounting is provided by the grommeted opening 100 and bolt holes 104 . extending horizontally toward the front of the base housing is the motor shaft 118 upon which is mounted by means of a key 120 , a bevelled pinion gear 122 . mounted atop the stub shaft 98 of the motor mount 90 is a bearing assembly 124 comprising an inner race mounted on shaft 98 and an outer race secured to the central hub 126 of a rotatable saucer - shaped , concavo - convex gear support member 128 . member 128 has a horizontal annular rim 130 from which depends a bevelled ring gear 132 whose teeth mesh with the pinion gear 122 and encircle the motor 110 . the ring gear 132 may be secured to member 128 , as shown , by any suitable means . alternatively , it may be integral therewith . the upper surface of the hub 126 has a circular recess 134 within which is fixedly secured a steel disk 136 which forms the head of the core 82 of spindle 44 . thus , it is seen that the bearing assembly 124 rotatably supports the spindle 44 with the spindle axis of rotation extending vertically and also rotatably supports the ring gear 132 for revolving in a horizontal plane . this ring gear 132 encircles the entire motor frame 111 in a compact configuration . the upwardly arched bridging member 96 and the inverted saucer - shaped ring gear support member 128 both are nested down around the motor 110 in overlapping relationship with one of them nested within the other . their nested relationship contributes to the compact configuration of the drive unit and advantageously reduces the required headroom within the base housing 10 . the gear support member 128 and its hub 126 serve for coupling the rotating ring gear 132 to the spindle 44 for rotating the spindle about its axis . formed on the inner surface of front wall 22 of base housing 10 is a boss 138 ( fig5 ) which supports the motor switch and the brake assembly which will now be described with particular reference to fig5 - 7 . mounted against the boss 138 by means of an l - shaped bracket 140 and screws 142 is a conventional electric motor switch 144 having a vertically extending actuator button 146 which is aligned with the opening 66 in top closure 36 . formed on the inner surface of top closure 36 and surrounding the opening 66 is a lip 148 defining a recess 150 within which is retained a flexible diaphragm 152 . diaphragm 152 seals the opening 66 so as to prevent the entry of food , liquid , or other deleterious substances into the base housing 10 . mounted to the boss 138 by means of a pivot pin 154 is a brake lever 156 which overlies switch button 146 and is urged into its upward position by means of a coil spring 158 seated on bracket 140 . near its distal end , the brake lever 156 defines an opening 160 therethrough . secured to the bottom of boss 138 by means of screws 162 is a brake band support arm 164 which has a slot 166 therethrough . the slot 166 is aligned substantially vertically with one edge of a brake drum 168 secured to the outer end of shaft 118 . a flexible brake band 170 is secured by one end to the support arm 164 , encircles the brake drum 168 , and its other end is releasably secured to brake lever 156 . it is illustrated in detail in fig6 . it includes a relatively wide body portion 172 having a longitudinal slot 174 , and an elongated narrow tongue 176 having a width slightly less than that of slot 174 . it is formed of a suitable plastic material and has molded into its end in the wide body portion 172 a pair of spaced ridges 178 by means of which the end is retained in the slot 166 of support arm 164 as illustrated . the band is wrapped around the brake drum 168 one and a half times , the tongue 176 being inserted through the slot 174 and lying therein along the lower half circumference of the brake drum . both sides of the end of tongue 176 are formed with serrations 180 thereon and this end extends upwardly through the opening 160 in brake lever 156 . by reference to fig7 it will be seen that the brake lever 156 carries a pair of cooperating , resilient clamp members 182 positioned on either side of the opening 160 . each of clamp members 182 is substantially z - shaped and includes a flat mounting base 184 secured to lever 156 , an outwardly biased resilient center section 186 , and an inwardly angled clamping end 188 . the normal configuration of clamp members 182 would cause them to assume the dotted line positions indicated at 182 &# 39 ;. however , extending outwardly from the inner side of the base housing 10 are a pair of clamping bars 190 . these bars are substantially rectangular in cross section , but their lower inside edges are rounded to form camming surfaces 192 . thus , when the brake lever 156 is pivoted downwardly into position 156 &# 39 ; illustrated in fig5 the clamp members 182 are in their open positions , out of engagement with the brake band 170 . when the lever 156 is raised by the action of spring 158 , the clamping ends 188 of clamp members 182 engage the camming surface 192 and are forced inwardly , thereby causing the clamping ends 188 to engage the serrations 180 in the brake band 170 for pulling the brake band snug around the drum 168 . this drum 168 is shown as being formed by an extended hub portion on the pinion gear 122 . the action of the clamping ends 188 engaging the serrations 180 each time that the brake band is pulled serves to provide compensation for wear of the brake band . fig3 illustrates the central portion of base housing 10 with its integral motor mount 90 . the rubber grommets 106 , 108 are inserted in the openings 100 , 104 , and the motor 110 is inserted through the bottom , the boss 110 being positioned in the grommeted opening 100 . the front end of the motor is then lifted into the opening 102 and screws 116 are engaged as shown in fig4 by means of a suitable tool such as a screwdriver , socket wrench , or allen wrench , which may be inserted through one of the ventilation slots 24 or through openings specially provided . the base plate 26 may thereafter be attached . the manner in which the remaining portions of the drive unit are assembled will be apparent to those skilled in the art from the foregoing description and drawings and need not be further explained . it is important to note that the gear support member 128 overlies and surrounds the universal motor 110 in such a manner that a very compact assembly is achieved . however , it is equally important to note that a very favorable gear ratio is achieved which makes possible the use of a high speed universal motor . in one actual embodiment , the pinion and ring gears are spiral bevel gears , the pinion being of steel and having 22 teeth and the ring gear being of delrin and having 130 teeth , thereby obtaining a speed reduction of nearly 6 : 1 . the operation of the brake will be most apparent from the following description taken in conjunction with the illustration of fig5 . as explained in the above referenced verdun patent , the cover 14 is rotatably secured to the bowl 12 and , in the act of rotatably locking it into position , the camming member 76 depresses the sliding rod 62 . rod 62 is forced through the opening 66 , stretching the diaphragm 152 and forcing down the button 146 of switch 144 , thereby starting the motor . in the present invention , the brake lever 156 which is interposed between the rod 62 and the switch button 146 is also depressed into position 156 &# 39 ;. the clamp members 182 spring apart when they move away from the confines of clamping bars 190 , thereby releasing the upper end of the brake band 170 . the brake band 170 thus loosens its grip around the brake drum 168 , permitting the motor 110 to operate unimpeded . upon completion of the food processing operation , the cover 14 is rotated in the opposite direction for removal . this releases the sliding rod 62 which is withdrawn into the boss 58 as shown in fig5 . simultaneously , the spring 158 forces the brake lever 156 back into the illustrated solid - line position . as the clamp members 182 make contact with the camming surfaces 192 on the clamping bars 190 , they are forced inwardly and engage the serrations 180 in the brake band 176 . this contact is made before brake lever 156 completes its upward movement . accordingly , as this movement is completed under the force of spring 158 , the end of the brake band 170 is pulled upward and tightens securely around the brake drum 168 . the 6 : 1 mechanical advantage of the gearing very rapidly brakes the drive unit and the rotating processing tool to a quick stop , even before the cover can be removed , thereby preventing injury to the user . in the alternative brake assembly as shown in fig8 there are a pair of opposed brake shoes 194 which are pivoted at 196 to a mounting bracket 198 which is attached to the motor mount 90 so that the pivot 196 is aligned with and below the motor shaft 118 . a curved friction pad 200 lines each of the brake shoes . these pads engage the brake drum 168 whenever a brake applying spring 202 is allowed to pull the brake shoes toward the drum . the tension spring 202 is attached to the opposite ends 203 of the curved brake shoes 192 from the pivot 196 . a modified motor switch 144a has a straight - through actuator plunger 146a with a wedge - shaped lower end 204 . whenever the plunger 146a is depressed for closing the circuit for energizing the motor 110 , the wedge portion 204 moves downwardly between the ends 203 of the brake shoes 194 , thereby overcoming the spring force and moving the brake shoes apart . in this way the braking pressure of pads 200 is released . conversely , whenever the cover 14 is removed from its working position on the bowl , the plunger 146a is allowed to be raised by an internal spring ( not shown ) within the switch 144a . the wedge portion 204 is withdrawn upwardly allowing the spring 202 to apply the braking pressure . in the further embodiment of this invention shown in fig9 through 18 the various elements performing functions corresponding to those in fig1 through 8 have the same reference numbers . the working bowl 12 and the turret 38 on which the bowl is mounted during operation may be identical to those components described above , and so their description will not be repeated . also , the spindle 44 and the food processing tool mounted on it are shown the same as described above . it is noted that more than one flat surface 46 may be provided on the spindle 44 , or it may have a spline configuration for providing a driving engagement with the hub 88 of the tool . it is also noted that the base housing 10a and motor mount 90a may be arranged so that the bowl 12 is mounted on the turret 38 with the vertical boss 58 and sliding push rod 62 positioned toward the front of the base housing or may be arranged so that the bowl is mounted with the boss 58 and sliding rod 62 positioned toward the rear of the base housing . from a mechanical point of view either arrangement is equally acceptible , but it is my preference to employ the latter arrangement because i think a more attractive over - all appearance for the food processor is provided when the sliding push rod 62 is located toward the rear . accordingly , in this description it is assumed that the right side of fig9 is the front of the food processor . it is also to be understood that the components in the food processor shown in fig1 - 8 can be rearranged so that the working bowl could be mounted with the push rod 62 located at the rear of the base housing 10 . the drive unit is mounted in the base housing 10a ( fig9 and 10 ) by means of a motor mount 90a , which is also shown in fig1 and 12 . the base housing 10a comprises three basic structural elements . the first of these is a box - like enclosure including spaced sidewalls 16 , 18 , rear wall 20 and front wall 22 . the second element of the base housing 10a is a substantially rectangular base plate 26 having a vertical flange 28 positioned inside of the walls . on the bottom of the base plate 26 are four feet 30 of relatively soft , resilient material , such as rubber . these resilient feet 30 are associated with a vibration isolating mounting assembly for isolating the motor mount from the housing 10a as will be described more fully infra . the third element making up the base housing 10a is a top closure 36 , which is essentially rectangular to conform to the shape of the housing , but includes the circular turret 38 . it is to be understood that ventilation openings ( not shown ) are provided in the base plate 26 or in one or more of the walls 16 , 18 , 20 , 22 for cooling of the motor 110 . another way in which ventilation may be provided is to space the vertical flange 28 away from the walls 16 , 18 , 20 , 22 in one or more places to define vertical channels adjacent to the inner surface of these walls through which air can flow . it is my present preference to provide openings in the base plate 26 and also to shape the flange 28 for defining such air flow channels to assure that the motor 110 receives adequate cooling air flow , because this motor in the drive arrangement as shown is capable of performing relatively prodigious food processing tasks in which heavy motor loads are involved . if desired , the walls 16 , 18 , 20 and 22 may be made integral with the top closure 36 . for example , the top closure and walls of the housing 10a may be injection molded as an integral structure from suitable tough , durable , injection - moldable material such as in now commercially employed for making kitchen appliance housings . the motor mount 90a includes rigid bridging members 201 , 202 , 203 and 204 ( see also fig1 ) which arch up and over the motor 110 , and they unite at a center portion 206 forming a bearing mount which they support concentric with the axis of rotation of the spindle 44 . in this bearing mount 206 is a socket 208 for holding the outer race of a bearing assembly 124 , and the inner race of this bearing assembly holds the steel shaft 82 of the spindle 44 . the lower end of this steel shaft 82 carries an enlarged head 210 having a flange 212 on which is secured the concavo - convex gear support member 128 by suitable fastening means , for example a plurality of machine screws 214 . this gear support member 128 is shown formed of tough , rigid plastic material , for example such as delrin , and it has a horizontal annular rim 130 from which depends a bevelled ring gear 132 whose teeth mesh with the pinion gear 122 and encircle the motor 110 . the ring gear 132 may be secured to the rim 130 by any suitable means . alternatively , the ring gear may be integral with the member 128 . in this example , as shown in fig1 , the ring gear is formed of delrin and is secured to the horizontal rim 130 by a plurality of machine screws 216 ( fig1 ). it is my preference that in commercial production the spiral bevel ring gear 132 and gear support member 128 be moulded as an integral member from rigid low - friction plastic material , for example such as delrin . it is seen that the bearing assembly 124 rotatably supports the spindle 44 with the axis of spindle rotation extending vertically and also supports the ring gear 132 for revolving in a horizontal plane . this ring gear 132 encircles the entire motor frame 111 in a compact assembly . the upwardly arched structure of the bridging members 201 , 202 , 203 , 204 , 206 and the inverted saucer - shaped ring gear support member 128 both are nested down around the motor in overlapping relationship with one of them nested within the other . their nested relationship contributes to the compact configuration of the drive unit and advantageously reduces the required headroom within the base housing 10a . in this embodiment the arching bridging structure 201 , 202 , 203 , 204 , 206 is nested above the ring gear support members 128 ; whereas in fig1 and 2 the ring gear support member 128 is nested above the arched bridging member 96 . the universal motor 110 shown in fig9 and 10 may be similar to the motor 110 in fig1 and 2 , except that the conventional end bell which normally supports the shaft bearing at the left end of the motor is removed . this universal motor 110 in fig9 and 12 has a no load speed of approximately 18 , 000 rpm , and the ratio of the spiral bevel ring gear 132 to the spiral bevel steel pinion gear 122 is approximately 6 to 1 . thus , the no load speed of the spindle 44 is approximately 3 , 000 rpm , and this spindle delivers a torque output which is approximately six times greater than the torque capability of the motor itself . the removed end bell of the motor is replaced by a frame member 220 , whose overall shape is seen most clearly in fig1 and 12 . the motor frame 111 is directly fastened to this frame member 220 by a pair of machine screws 218 . these screws 218 are located in the same position in the motor 110 as the screws which are usually employed for holding the left end bell in place . the shaft bearing for the left end of the motor shaft 118 in fig9 is mounted in a central boss 221 ( fig1 ) of the frame member 220 and located near the pinion gear 122 . this pinion gear 122 is secured to the motor shaft 118 by any suitable attachment , for example by a force fit key , or as shown by a set screw 223 . the outer end of the hub of the pinion gear 122 has two flat surfaces 225 ( fig1 ) for providing driving engagement with a friction disc of the brake assembly as will be explained later . in order to cool the motor 110 , the frame member 220 includes a fan casing section 222 of generally circular cylindrical configuration surrounding a bladed fan 224 ( fig1 ). as seen in fig1 there are a plurality of air discharge openings 226 in the fan casing section . these discharge openings are spaced around the motor shaft 118 and allow the fan 224 to discharge cooling air which has been drawn through the motor 110 in an axial direction between the stator and armature . the frame member 220 also includes a pair of arms 228 extending out generally horizontally from either side of the fan casing section 222 . these arms 228 each have an outer end 230 with a threaded drill hole for receiving a machine screw 232 which holds one of the resilient feet 30 . in order to isolate the motor mount 90a from the base housing 10a , there is a resilient bushing 234 positioned between the outer end 230 of each arm 228 and the base plate 26 . these resilient bushings 234 are held by the screws 232 and by openings 236 in the base plate 26 and serve as vibration absorbing pedestals for supporting the motor mount 90a vibrationally isolated from the base housing 10a . the right end of the motor 110 as shown in fig9 includes a conventional end ball structure for supporting the electrical brush assemblies 238 for the commutator and also for supporting a boss 112 which holds the shaft bearing for the right end of the motor shaft 118 . this boss 112 is mounted in a resilient grommet 106 seated in a socket portion 239 of a front frame member 240 , whose overall configuration can be seen most clearly in fig1 . this frame member 240 includes a pair of arms 248 extending out generally horizontally from either side of the socket portion 239 . each arm has an outer end 250 with a threaded drill hole for receiving a machine screw 232 which holds one of the vibration - isolating resilient pedestal bushings 234 and also holds one of the resilient feet 30 in a manner similar to screw 232 shown at the right in fig1 . the arched bridging members 201 and 202 ( fig1 ) are firmly secured to the outer ends 250 of the arms 248 of the front frame member 240 by the screws 232 and by an additional pair of screws 252 ( fig1 and 12 ). similarly , the rear arched bridging members 203 and 204 are firmly secured to the outer ends 230 of the arms 228 of the rear frame member 220 by a pair of machine screws 254 . the outer ends of these bridging members 203 and 204 include depending leg portions 256 ( fig1 ) containing threaded drill holes for receiving the attachment screws 254 . in order to adjust the engagement of the teeth of the pinion gear 122 with the teeth of the ring gear 132 there is a hollow adjustment screw 258 ( fig1 ) which concentrically surrounds each attachment screw 254 and is threaded through the outer end 230 of the arm 228 of the rear frame member 220 . the lower end of the adjustment screw 258 has a square head as seen in fig1 , and its upper end abuts up against the bottom of the depending leg 256 . thus , in effect , the adjustment screws 258 act like jacks for raising or lowering the two legs 256 of the respective bridging members 203 and 204 for raising or lowering the ring gear where it engages the pinion gear . when the inner screws 254 are tightened , they lock the adjustment screws in place . although two such adjustment screws 258 are shown , it is to be understood that only one such screw may be employed . for example , washers can be inserted between one of the legs 256 and the frame member 220 for achieving a coarse adjustment of the gear engagement , and then the adjustment screw serves to make a fine adjustment by acting against the other leg 256 . as illustrated , the bridging members 201 , 202 , 203 , 204 and the frame members 220 and 240 each include various stiffening ribs 260 for providing the desired overall stiffness for the motor mount 90a . as shown in fig9 further vibration isolation is provided by a large mounting ring 262 of soft resilient material such as sponge rubber which seats down around an annular shoulder 264 on the central portion 206 of the bridging members 201 , 202 , 203 and 204 and which seats up within an annular shoulder 266 in the turret 38 of the top closure 36 . this mounting ring 262 serves to hold the motor mount 90a accurately centered and spaced with respect to the turret 38 . the brake assembly 270 ( fig9 and also fig1 - 16 ) is mounted to the rear frame member 220 by screws 271 and is located adjacent to the pinion gear 122 at the rear of the motor . a friction disc 272 mates with the flats 225 on the hub of the pinion gear so that this disc 272 is rotated whenever the motor is running . the brake assembly 270 includes a first plate 274 which forms a frame for the brake assembly and also supports a motor energizing switch 276 . a second plate 278 is movably mounted on the screws 271 . it can move toward and away from the first plate 274 . when the brake 270 is applied , as shown in fig1 , the friction disc 272 is clamped between the first and second plates 274 , 278 . this disc 272 is formed of stiff fibrous material , and offers a high coefficient of friction . thus , when the plates 274 , 278 clamp against the disc , the motor 110 is brought to a stop immediately . a leaf spring 279 is held by the screws 271 , and the ends of this leaf spring urge the second plate 278 toward the first plate 274 for clamping against the brake disc 272 . in order to release the brake plates 274 and 278 from the disc 272 , there is a generally e - shaped actuator plate 280 having three leg portions 281 , 282 and 283 . this actuator plate 280 is movable vertically , and it resides in its upper position as shown in fig9 and 14 when the brake is applied . when the bowl 12 is mounted on the turret 38 with its cover in position and the food processor is ready for operation , then the push rod 62 ( fig9 ) is depressed through the opening 66 deflecting the stretchable diaphragm 152 and depressing the actuator plate 280 as shown by the arrow 284 in fig1 and 18 , thereby releasing the brake , as will be explained . as the actuator leg portion 283 moves down , it deflects a switch arm 286 ( fig1 ), thereby closing the switch 276 for energizing the motor 110 . the center leg portion 282 of the actuator plate serves as a guide for it extends vertically in sliding relation through slots in two vertically spaced horizontal tabs 288 which are bent over from the top and bottom edges of the first plate 274 . in order to move the first and second plates 274 and 278 away from each other to release the brake disc 272 , there are four actuator balls 290 ( fig1 ) which ride in inclined grooves or tracks 292 and which are captured by the plates 274 and 278 on opposite sides of each leg portion 281 and 283 . these inclined grooves 292 are formed in both sides of the leg portions 281 and 283 and in the opposed surfaces of the first and second plates 274 and 278 . as shown in fig1 and 18 , the inclined grooves 292 are sloped so that the balls 290 are rolled toward their shallow ends for spreading ( arrows 294 in fig1 ) the brake plates 274 and 278 further apart , when the actuator plate 280 is depressed by the push rod 62 ( fig9 ). accordingly , when the food processor is ready for operation , the actuator plate 280 is moved downwardly for releasing the brake disc 272 as illustrated in fig1 and for closing the switch 276 as shown in fig1 . conversely , when the bowl cover is removed , or the food processor is otherwise rendered unready for operation , the actuator plate 280 is allowed to move up to its normal position , thereby applying the brake and opening the switch 276 for deenergizing the motor 110 . it is believed that the many advantages of this invention will now be apparent to those skilled in the art . by means of this invention , it has become possible to employ an inexpensive ac / dc universal motor in a food processor . at the same time , the drive unit , including the motor , has been made extremely compact while still obtaining a very highly desirable gear ratio between the motor and the driven tool . in addition , there has been provided an automatic brake which substantially minimizes risk of injury to the user of the apparatus . it will also be apparent to those skilled in the art that various modifications may be made in this invention without departing from its spirit and scope . accordingly , the foregoing description is to be construed as illustrative only , rather than limiting . this invention is limited only by the scope of the following claims .
an improved drive unit for a food processor of the type wherein the drive unit is enclosed in a base housing and has a vertically extending spindle which extends into a processing bowl and carries rotary tools thereon . the drive unit comprises a horizontally mounted universal motor carrying a pinion gear at the end of its shaft . a ring gear meshes with the pinion and encircles the motor on a concavo - convex support structure . the support structure is coupled to the vertical spindle . included in the drive unit are a novel three point shock mounting for the motor and an automatic brake to prevent coasting of the tool after the motor is deenergized . in a further embodiment of the drive unit the motor and the concavo - convex ring gear are held in a motor mount which is vibrationally isolated from the base housing for providing quieter operation . this mount arches up over the dome of the ring gear which in turn arches up over the motor . a lockable adjustment is provided in the motor mount for adjusting the engagement between the pinion gear and ring gear , and another form of automatic brake is shown .