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  1. 1. * GB785864 (A) Description: GB785864 (A) ? 1957-11-06 Wedge actuated brake Description of GB785864 (A) 1 PATENFP SPE MC ATIoN I, S,$ 64 Ad Cs Dote of Application and filing Complete Specification: Feb 9, 1956. ao 4059156. t LH a 4 ' of 1 Application made in United States of America on Feb 15, 1955. Complete Specification Published: Nov 6, 1957. Index at acceptance-Class 103 ( 1), E 2 M 2 ( 1 84 C 2 C 134 F: E: E 3: F 4: X 2). International Classifici'vion:-D 362 d. COMPLETE SPECIFICATION Wedge Actuated Syake We, ROCKWELL SPRING AND AXLE COMPANY, a Corporation organised and existing under the laws of the State of Pennsylvania, United States of America, doing business in Coraoplis, Pennsylvania, United States of America, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement: - This invention relates to improvements in vehicle brakes and particularly to wedge actuated brake mechanisms. Particularly in heavy duty brakes, it has become practice to mount the unit furnishing power for braking action on the exterior of the fixed brake assembly housing chiefly to meet the space demands required for large high capacity power units Previous exterior mounted power actuator units have been mounted directly on axle housings or, for the front steerable axles, directly on the exterior side of the brake backing plate Most presently known brakes that use such exteriorly mounted actuators embody a crank arm to operate a rotatable cam shaft extending through the backing plate and carrying a brake shoe actuating cam on the interior of the plate Other known arrangements,
  2. 2. utilising an exterior power source, reciprocate a wedge member in a path substantially normal to the brake assembly backing plate, but most of these require complex power transfer mechanism between the wedge actuator and the brake shoes and usually require a special loosely mounted slidable wedge cage. All of these presently known arrangements of exterior mounted power units use extended air or vacuum chamber mounting brackets and power shafts, occupy a large amount of space, have complex parts difficult to manufacture with proper tolerances and are subject to operational difficulties due to the number of moving parts exposed on the exterior side d& the brake. This in Ven 4 i&b is primarily directed to an improved wedge actuated brake using a reciprocable wedge member movable in a path substantially normal to the brake assembly backing plate The power actuator is located 50 on the exterior side of the backing plate and rigidly mounted on a special adapter mount which in turn is rigidly fixed to the backing plate This novel mounting may be arranged with the actuator axis offset from a line nor 55 mal to the backing plate and can be used on fixed and steerable axles in the same manner. Incorporated in this novel brake is a combined brake support, actuator bracket and 60 wedge cage which may be constructed to provide a sealed wedge cage if lubrication is desired On the other hand if it be desired to provide a dry running wedge actuation, a modified novel unsealed wedge actuated 65 mechanism is available Using the inherent flexibility of a connection between a reciprocable rod and a diaphragm form of pneumatic or vacuum motor actuator, or an alternative universal connection such as a ball 70 and socket between a reciprocable wedge rod and the drive element of other forms of power actuators, this invention realises a reciprocable wedge which has an axis of reciprocation that can deviate, up to approxi 75 mately 20 degrees from perpendicular to the brake mechanism support or backing plate. This factor enables several important results, namely: the power actuator can be offset further toward the periphery of the brake 80 assembly than the wedge actuated mechanism, to obtain proper axle clearance in some installations; and a self-balancing wedging force is transmitted between the two shoes of an expanding shoe brake 85 Together with the aforementioned novel wedge cage assembly and power actuator support bracket, this invention includes several novel individual shoe adjustment mechanisms One embodiment discloses a 90 new individual worm drive anchor abutment adjustment for use with either actuating levers or directly actuated brake shoes while the second embodiment discloses a new adjustment mechanism incorporated directly in the wedge actuated mechanism In the adjustable anchor
  3. 3. abutment embodiment shoe return springs are anchored to the adjustable abutments thus permitting the return springs to maintain a substantially constant length in deactuated position regardless of the state of adjustment. Accordingly, a primary object of this invention is to provide a novel heavy duty brake construction embodying a transversely reciprocable wedge actuation. Another object resides in connecting the wedge of a wedge actuated brake to directly utilise the push motion of a power unit push rod, thereby multiplying the force of the power unit through the mechanical advantage of the wedge slope and the internal brake shoe actuating levers This is a material improvement over prior brake actuating systems which use a crank arm, rotatable shaft and cam actuator between brake shoes. A further object resides in providing a wedge actuated brake assembly with -novel structural cooperation between the power unit, the wedge and wedge actuated mechanism which permits the wedge to freely float and thus locate itself so force delivered to opposed brake shoes and brake shoe actuating linkage will always be automatically balanced. A still further object resides in the provision of a novel combined wedge actuator cage and power actuator mounting rigidly fixed to a brake assembly support wherein thrust at right angles or deviations up to approximately 20 degrees from right angles to the brake support is absorbed within the combined cage and mounting. Still another object resides in providing a novel braking assembly using wedge actuating mechanism wherein wedges of various slopes are readily interchangeable to provide different thrust load ranges as desired and required for different installations and uses. A further object resides in the provision in a power actuated expanding shoe brake assembly of novel individual adjusting mechanisms incorporated in either the anchor abutments or opposed actuating elements, for use with a brake assembly having directly actuated shoes or shoe actuating levers. A particular object in this respect resides in the provision of novel individual worm and worm gear adjustment means in the anchor abutment. Another object resides in providing a novel wedge actuated cage enclosing opposed plungers that coact with the individual brake shoe actuating means and journal wedge engaging rollers in members that guide the wedge during its reciprocation A further object in this respect resides in the provision of additional antifriction rollers within the wedge cage which cooperate with the wedge engaged rollers and the cage structure to transfer wedge cross thrust to the wedge 70 cage. Still further ancillary objects reside in providing a sealed wedge
  4. 4. cage and a sealed anchor abutment with enclosed adjustment mechanism, for retaining lubricant and pre 75 venting the escape of such lubricant to the interior of a brake assembly. Still another object resides in the novel provision, in expanding shoe brakes, of anchoring brake shoe return springs between 80 the brake shoes and the abutment end of an adjustable anchor abutment. Further novel features and objects of this invention will become apparent from the following detailed description and the appended 85 -claims taken in conjunction with the accompanying drawings showing a preferred embodiment thereof, in which: Figure 1 is a top plan view partially in section showing one embodiment of the novel 90 wedge actuated brake assembly of this invention, mounted on a rear drive axle with the axle housing and brake drum shown in phantom lines; Figure 2 is an end elevation view of the 95 brake assembly in Figure 1, with one brake shoe and actuating lever removed and with the top of the actuating boss practically broken away to show the roller and plunger structure; 100 Figure 3 is a detail section taken on line 3-3 of Figure 2 and illustrates the actuator boss, wedge and mounting adapter for the power actuator; Figure 4 is a detail section taken on line 105 4-4 of Figure 2 and illustrates the internal structure of the worm adjusting mechanism in the anchor boss; Figure 5 is a detail section taken on line 5-5 of Figure 4 and illustrates the exterior 110 of one end of the anchor boss; Figure 6 is a detail section taken on line 6-6 of Figure 2 illustrating the actuating lever guide support and brake shoe abutment on the backing plate adjacent the actuating 115 boss, Figures 7 and 8 are detail sections taken on lines 7-7 and 8-8, respectively, of Figure 2 and illustrate the integral bridge on the backing plate for retaining and guidingly 120 supporting the actuating lever and brake shoe; Figure 9 is an end view of a second brake assembly embodiment using a wedge actuator in accordance with this invention; 125 Figure 10 is a front elevation of the wedge actuator and cage of Figure 9 with the other brake elements broken away; Figure 11 is a detail section taken on line 11-11 of Figure 9 illustrating interior de 130 785,864 gagement with the shank 68 of an anchor oolt 70 The enlarged head 72 of each anchor bolt has a slot 74 formed transverse to the bolt axis to receive the adjacent abutment ends 75 and 76, respectively, of a brake 70 shoe web 71 and a relatively slidable actuating levli 40 The brake shoe actuating levers include spaced protections or tabs 77 and 78 Figure 2 at their abutment ends 76 to bracket the slotted anchor bolt heads 72 and 75 maintain said levers in aligned engagement with the respective anchor head slots 74. Each bushing 64 is rotatable within an opening 79 in boss 32 and bears at one end on annular shoulder 80 and at the other end on 80 a cover
  5. 5. plate 81 fastened to the ends of the boss by screw 82 and bolts 83 The openings 79 are reduced in diameter beyond shoulder 80, as indicated at 84, and extend to a common central oil lubricant reservoir 85 which also provides room for axial movement of the bolt shanks 68 whenever a worm gear bushing 64 is turned by its worm 46. The reservoir 85 is normally filled with oil and sealed with a disc plug 86 when the 90 brake is assembled The sides of the hexagon end portion 37 of each adjusting rod 36 may be resiliently engaged by a spring 87 fastened to the exterior surface of boss 32 by a bolt 88 to provide a detent for the worm 95 rod and thereby maintain the adjustments to the respective anchor bolts 70 0-ring seal 89 in each bushing counterbore 90 prevents loss of oil through cover plate openings 91 to the interior of the brake 100 A set of springs 92 are used at the anchor abutment ends of the brake shoes to urge that end of the shoes toward deactuated position To this end a shoe return spring anchor post 93 is fixed on the anchor head 105 72 of each anchor bolt 70 The return springs 92 extend between an anchor post 93 and a suitable bracket 94 affixed to the respective shoe lining platform Mounting of return spring anchor post 93 on the anchor 110 bolt 70 ensures that springs 92 will remain at constant length and therefore be under a constant stress at all times when the brake is deactuated, regardless of the brake shoe wear and adjustment conditions 115 Figures 1, 2 and 3 illustrate the brake acuating mechanism The actuating chamber boss 34, which projects from the interior side of the plate 22, is formed with a transverse through bore 96 defining cylinders to 120 guide the axial movement of roller assemnbly pistons 97 when the brake is actuated or deactuated Each piston 97 is provided with an annular groove 98 retaining an ",O' ring 99 to prevent loss of oil from boss 34 to the 125 interior of the brake A wedge actuating member 100 with sloped sides 101 projects into boss 34 from the exterior side of the support plate 22 and, for brake actuation, moves inward across the bore 96 moving 130 tails of the modified plunger assemblies; Figure 12 is a section view taken on line 1 '-1 of Fiaure 9 illustrating the modified anchor abutment; and Figure 13 is a detail perspective of the modified plunger. Ln the drawings, wherein like reference characters are used to indicate similar parts throughout, Figures 1 and 2 illustrate the combination of the primary braking structure of this invention Figure 1 shows the relationship of the brake to a rear drive axle and wheel drum which are shown in phantom lines The rear axle housing 20 has a brake mounting flange 21 to which is secured the rigid backing plate 22 of the brake assembly 24 as by bolts or studs passing through holes 23 Axle housing 20 extends through a central opening 25 in backing plate 22 and journailed on it is a wheel hub 26 having a flange 27
  6. 6. carrying a brake drum 28 fixed thereto. The axle shaft passing through housing 20 is secured to hub 26 in a conventional manner A ground engaging wheel assembly (not shown) is normally fastened to the hub flange 27 and rigidly fixed relative to the drum 28. Backing plate 22 is generally elliptical with an integral anchor boss 32 and an integral actuating chamber boss 34 diametrally opposed and corresponding respectively to the front and rear of the brake assembly, and both projecting interiorly of the brake mechanism assembly 24. With reference to Figures 2, 4 and 5, the anchor boss 32 projecting from the interior side of the plate 22 has rotatably mounted thereon two individual adjusting rods 36 A hexagon end portion 37 on each rod 36 extends from the interior of boss 32 to the exterior side of plate 22 and enables individual adjustment of the respective shoes 38 and shoe actuating levers 40 Only one rod 36 is shown in Figure 4, the other half of anchor boss 32 being a duplicate of that shown. Each adjusting rod 36 has a cylindrical extension 42 provided with serrations 44 by which a worm gear 46 and spacer sleeve 48 are non-rotatably mounted thereon, with the spacer sleeve 48 abutting a shoulder 50 on rod 36 The assembled worm and rod units are each mounted in the boss 32 with worm 46 rotatable within a bore 52 and confined between a shoulder 54 at the base of the bore and a button cap 56 closing the top of the bore Each spacer sleeve 48 is journalled in a reduced diameter bore 58 and provides a radial journal for the worm and rod assembly Button caps 56 are threaded 60 into boss 32 and thereby close bores 52 and properly maintain and retain worms 46 in operative position. Each worm 46 meshes with a respective worm gear 62 cut into or otherwise integrally joined to a bushing 64 that has an internally threaded bore 66 in threaded en785,864 botli pist Ons 97 To facilitate the separating movemient of pistons 97, wedge member 100 engages rollers 102 mounted for rotation on integral extended ohier pins 104 which rest in grooves 106 of roller assembly piston inserts 108 Each piston insert 108 l, has sliding fit in a blind bore 110 at one end of its piston 97, and is provided with a slot 112 transverse to groove 106 which provides a recess for roller 102 Slots 112 also receive and guide the wedge actuating member 100 and, by cooperation with the wedge member, provide rotational alignment of the inserts 108 to enable proper wedge engagement with rollers 102 The end of the actuating piston 97 that extends from the end of bore 96, receives the abutting end 116 of a lev er 40 in a slot 118 The top of boss 34 is formed as a hollow extension 120 to permit extended actuating travel of wedge member 100 inward across the brake An oil plug 119 can be
  7. 7. provided in the top of extension 120 so that boss 34 may be filled with oil The hollow interior 121 in the extension 120 is of sufficient width to provide clearance whenever wedge member 100 shifts in the direction of one actuating piston 97 or the other to balan-ce the actuating force transrmitted to both. Boss 34 has tvo integral reinforcing webs 122 extending toward the center of the backing plate The top of each web carries a spring anchor projection 124 for a second set of shoe return springs 125 which extend to brackets 95 on the brake shoe table Two more reinforcing webs 126 extend from the ends of boss 34 to backing plate lever and shoe web guide and shoe abutment bosses 128 Figure 6 A hardened metal block 127, rests in a groove 129 formed in boss 128 and is retained by a bolt 130 The metal block 127 has a plane top surface 131 that guides the lever 40 Side surface 132 of the block 127 serves as an abutment face for a curved abutment end 75 of a brake shoe web 71. Top surface 136 of boss 128, which is stepped lower than the block surface 131, guides and axially positions the shoe web 71. Inwardly extending bridge shaped bosses 140 provided at the top and bottom of the backing plate Figure 1 each have an integral top circular plane surface 142 which constitutes a central guide and support pad for a shoe web 71 and forms channel 144 Figures 7 and 8 Two angle meinbers 146 are fixed, as by welding, to each shoe lining platform at opposite sides of the shoe web 71 so that free arm 14 -8 olf each member 146 proJects inwardly from the shoe rim, parallel to aid eclually spaced from opposite sides of tre shoe web 71 When the shoe is assembled to the backing plate, arm 148 cf one angle member projects through channel 144 in the bridge boss 140 to guide and axially retain shoe 38 The arm 148 of the other angle meiiiber 146 conikiles an-d aligns the respective actuating lever 40 in axial position against the shoe web 71. Each actuating le-r 40 at its anproxirmate center, is wuipnped W lateral pro 70 jections 160, ha i dneir radiaill outer surfaces 161 curved to rochao' abut and transmit brake actuating force from the levers to radial miner curved a'iuttin edaes 132 of the shoe wvebs 71 Two s-ts of oosses each con} 75 prising a backing niate boss 165, sitioned to one side of the axial onenina and boss 166 positioned on the other side of the axial opening 25, are diametrally opposed, with all bosses located radially inward from the 80 bridge bosses 140 Tle diametral bosses 165 and 166 are used for front wheel mounting, the set used being dependent on whether it is a left or right wheel mounting. Mlounted Oil the exterior of backing plate 85 22 and aligned with interior boss 34 an adapter 170 is fastened to backing plate 22 by
  8. 8. bolts 172 A flexible sealing diaphragm 173 is Afrmed with an inner annular head 174 fitting tightly in groove 175 of the wedge 90 actuator 100 is vulcanised to a gasket 176 clamped between Jhe adapter 170 andbackina plate 22 Diaphragin 173 has an intermediate corrugated sectlon so that tlie diaphragm conforms to Do Ih volume and pressure 95 changes inside the cage and there is no breathing of air tlhrough the seals 99 This laterally flexible diaphragm assembly permits lateral shifting movement of the actuator rod while maintaining an oil tight seal to 100 retain oil within boss 34 A diaphragm type servo-motor 177 for operating the wedge actuator is mounted off center on an angled mounting flange 178 of member 170 The off center and angled disposition of the 105 mounting permits the servo-motor actuator to be located away from axle 20 to ensure ample clearance Actuators such as a vacuum cylinder or a hydraulic slave cylinder may be used in place of diaphragm servo 110 motor 177 W Vedge actuating member 100 is fixed as by being threaded to the end of reciprocable diaphragm rod 179 and locked in position by a locknut 180 Rod 179 is fixed at its other end to flexible motor diaphragm 1 15 177 ' about which the rod Ha tilt somewhat in assambly Suitable menes are provided for fluid power actuanic N of diaphragm 1771 to reciprocate rod 17) Wedee 109 which is illustrated in Fiat re 1 as be'al anguilarly off 120 set from a line Pep:1 c' l to the backina plate ma,/l be ari-en t an angle from right angles to approxinately 20 degrees from right ainles across the 'Graae Wedges 100 with different sloeat l 10 are int rchange 12 '5 ab 11 on rod 179 i or c-er to provide diilerent threts load ranaes as requ Ired for diferent applications Fexi'l of t d apilraami witii 1 the diapiliragim type actuator 177 periiits angular displaceme nts of wedge actua 13 C 785,364 785,864 5 tor 100 to balance actuating forces transmitted to both thrust rollers 102. Rear drive axle brakes 24 are installed with the diaphragm actuator 177 to the rear. The same brake, adapted for front axle steerable wheels is installed with the diaphragm actuator 177 to the front and mounted on a shorter support member 170. In operation when actuator 177 is energised, wedge 100 within cage boss 34 is pushed inward across the brake 24 Sloped sides 101 of wedge 100 progressively separate the rollers 102 during inward movement and, since wedge 100 is free to angularly float sideways, force transmitted to rollers 102 is constantly balanced Piston inserts 108 transmit the force from rollers 102 through actuating pistons 97 to the respective shoe levers 40 Actuating force transmitted to brake levers 40 operates the brake mechanisms 24 in conventional dual primary brake fashion. Figures 9-12 illustrate another novel wedge actuated brake embodiment in which adjustable actuating plunger assemblies 250 are provided in
  9. 9. place of the adjustable anchor abutments of the previous embodiment and the plunger assemblies abut in bracketing relation with the ends 252 of the respective brake shoes 254 rather than intermediate actuating levers Wedge 100 with sloped sides 101, contained within boss 256 is connected to a diaphragm actuator 177 and, for brake actuation, moves inward across the brake progressively separating both thrust rollers 258 in a manner identical to that described for the preceding embodiment. An actuating chamber 256 extends to the interior of the brake through backing plate 259 and is fastened to the backing plate by rivets 257 Chamber 256 is formed with a transverse through channel 260 along which actuating roller assemblies 262 roll during 49 brake energisation or de-energisation Each roller 258 is mounted for rotation upon a roller pin 264 which extends through tongues 266 of an actuating plunger 268 Outboard channel rollers 270, one at each end of pins 264 on the outside of tongues 266, resist thrust of wedge 100 across the brake by rolling along the inside surface of the top wall 272 of boss 256 A rectangular opening 274 in top wall 272 permits the wedge 100 to extend through the boss during travel across the brake for actuation The floating wedge can shift toward either brake shoe to continuously balance force transmitted to both actuating plungers 268 At the sides of chamber 256 where channel 260 opens, the slotted end 275 of actuating plungers 268 bracket the abutting ends 252 of respective brake shoes 254 between slot tongues 276. The wedge actuating means of this embodiment runs dry with no lubrication to contaminate brake shoe and drum surfaces. The split ends 275 of each actuating plunger 268 are externally threaded as indicated at 278 to receive adjustable threaded 70 abutment members 280 provided with serrated circumferential flanges 282 Shoe ends 252 abut concave surface 284 of abutment members 280 which are held in the adjusted positions by engagement of serrations 75 282 with a shoe return spring 286 Two shoe return springs 286, hooked through shoe openings 288, extend from one shoe 254 to the other, one of the springs being radially inward from and closely adjacent the cham 80 ber 256 and the other spring being radially inward from and closely adjacent the anchor assembly 290 Openings 292 in the backing plate 259 at each end of chamber 256 permit access to the adjustable abutment members 85 280 for individual shoe abutment adjustment Although the drawings illustrate brake shoes directly actuated by the operating abutments, the adjustable actuating abutments can operate on levers in the manner 90 described for the embodiment of Figures 1-8, and similarly, directly actuated brake shoes could be utilised in the former embodiment. Spring clamps 294, one for each shoe, are 95 fastened to the backing
  10. 10. plate 259 and help maintain shoe alignment Anchor assembly 290 has two keeper plates 295, one beneath the backing plate 259 and one above an abutment plate 296 The upper keeper plate 295 100 projects over the adjacent concave abutment ends 297 of shoes 254 The shoe ends 297 abut convex mating ends 298 of abutment plate 296 which is dowelled at 299 to the backing plate 259 Three rivets 300 fasten 105 the anchor assembly 290 together and to the top of a backing plate boss 301. From the foregoing description, it is apparent that there are hereby provided improved brakes with directly driven diaphragm (air or 110 vacuum cylinder or hydraulic slave cylinder) wedge brake actuating mechanisms This construction requires less exterior space for the actuation mechanism than required by presently known power brakes and provides 115 actuation mechanisms mounted directly to the backing plates for both front and rear axle brakes It provides a relatively fixed combination of a wedge enclosing cage, actuator mount bracket and brake support 120 assembly It provides a roller thrust actuating member assembly which may and in fact does in some embodiments run dry with no lubrication This construction also provides a freely floating wedge actuator which 125 continuously balances the brake actuating force transmitted to the respective plungers and the levers and/or shoes In addition individual lever and/or shoe adjustment incorporated into a wedge actuated plunger is pro 130 785,864 6 785,864 vided in one embodiment and in another embodiment individual lever and/or shoe worm and worm gear anchor adjustment is provided In one embodiment return spring S anchor posts are mounted on lever and/or shoe adjustable anchor bolts for maintaining a constant length and constant stress in return springs when the brake is in the deactivated state, no matter what the degree of anchor bolt adjustment and/or brake lining wear These features may be interchanged between the embodiments. While the invention herein disclosed is intended more particularly for use with expanding shoe brake assemblies it may conveniently be applied to any kind of brake through the use of proper kinematic linkage. The invention may be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The present embodiments are therefore to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein. * Sitemap
  11. 11. * Accessibility * Legal notice * Terms of use * Last updated: 08.04.2015 * Worldwide Database * 5.8.23.4; 93p * GB785865 (A) Description: GB785865 (A) ? 1957-11-06 Improvements relating to windscreen wipers Description of GB785865 (A) PATENT SPECIFICATION 785,865 o, Date of Application and filing Complete Specification March 6,1956. 2 No 7017/56. Application made in United States of America on March 23, 1955. Complete Specification Published Nov 6,1957. Index at Acceptance:-Class 138 ( 1), 51. International Classification:-A 471. COMPLETE SPECIFICATION Improvements relating to 'Windscreen Wipers We, GENERAL MOTORS CORPORATION, a Company incorporated under the laws of the State of Delaware in the United States of America, of Grand Boulevard in the City of Detroit, State of Michigan, in the United States of America (Assignees of CYRIL THORNTON WALLIS) do hereby declare the invention for which we pray that a patent may be granted to us and the method by which it is to be performed, to be particularly described in and by the following statement: This invention pertains to windscreen wipers, and in particular to a windscreen wiper assembly for cleaning windscreens of the kind having a flat or slightly curved front portion and side portions connected integrally with the front portion by sharply curved portions Such windscreens are commonly referred to as "wrap-around" windscreens. By the invention the wiper blade of a windscreen wiper can be arranged to conform effectively to both the sharply curved and the
  12. 12. substantially flat portions of a windscreen. The scope of the invention is defined by the appended claims; and how it can be performed is hereinafter particularly described with reference to the accompanying drawings, in which:Fig 1 is a plan of a wiper blade assembly according to the invention; Fig 2 is a part sectional elevation of the wiper blade assembly; Fig 3 is an inverted plan of the wiper blade assembly; Fig 4 is an enlarged detail on the line 4-4 of Fig 2; Fig 5 is an enlarged detail on the line 5-5 of Fig 2; Fig 6 is an elevation of the pressure distribution frame of the assembly showing its position when the wiper blade is curved; Fig 7 is a view similar to Fig 6, when the blade is straight; Fig 8 is a plan of the backing strip for the wiper blade; and Fig 9 is an elevation of the backing strip as originally curved. As shown in Figs 1 to 3, the wiper blade 50 assembly 10 includes a primary pressure distribution member, in the form of a channeled yoke 12 having connected thereto an arm attachment socket 14,of known kind, whereby a wiper arm, not shown, connected to' the 55 socket 14 can apply pressure to the blade assembly 10 The end 16 of the yoke 12 is inclined upwardly, as indicated in Fig 2, and carries a transverse pin 18 to which the intermediate portion of a secondary yoke 20 60 is pivotally connected. The wiper blade assembly includes a squeegee unit comprising a metallic backing strip 22 and a flexible wiper blade 30 As shown in Figs 8 and 9, the backing strip 22 65 has a longitudinal slot 24, which terminates near each end of the strip, which is freely flexible in a plane perpendicular to the surface to be wiped and substantially inflexible in a plane parallel to said surface Initially, 70 the backing strip 22 is formed with a curvature opposite to that of the windshield surface to be wiped, as shown in Fig 9, in order that it may conform to either a flat or a curved surface When the blade 30 having 75 the strip 22 is pressed against a flat surface, the blade centre will first come into contact with the surface, and as pressure is applied, the blade will progressively come into contact with the flat surface from the centre 80 toward each end. In order to increase the flexibility of the backing strip at each end thereof, the strip 22, as shown in Fig 8 tapers from the middle towards each end thereof The backing strip 85 22 is also formed with notches 26 and 28, the purpose of which will be described hereinafter. The wiper blade 30 is of elastomeric material and has a retainer portion 32 and a 90 wiper edge portion 34 The retainer portion 32 and the wiper edge portion 34 are interconnected by a reduced neck 36, the flexible backing strip 22 being disposed in the groove between the portions 34 and 32, as shown in Fig 4 Thus, the wiper blade 30 is freely tiltable relative to the backing strip 22, but restrained
  13. 13. against longitudinal movement relative thereto by the closed ends of the slot 24. Opposite ends 38 and 40 of the secondary yoke 20 are movably connected at spaced points to the flexible backing strip 22 as shown in Figs 1 to 3, each end of the member 20 being formed with inwardly extending ears 42, which are engaged about the flexible backing strip 22, the ears at the end engaging in the notches 26 so that end 40 of the member 20 is movably connected to the backing strip 22, but can only slide longitudinally relative thereto within the limits of notches 26 However, end 38 can slide longitudinally relative to the backing strip 22 The upturned end 16 of the yoke 12 constitutes a weather shield for the pivotal connection between the secondary yoke 20 and the primary yoke 12. The other end 44 of the yoke 12 is also upwardly inclined, as shown in Fig 1, and has ears 46 which are engaged about the backing strip 22 and in the notches 28 therein, as shown in Figs 1 to 3, so that the backing strip 22 is movable relative thereto but can slide longitudinally only within the limits of notches 28 A cantilever arm 48 is pivotally connected to the end 44 of the holder 12 by a pin 50, as shown in Figs 2 and 5 The upwardly inclined end 44 constitutes a weather shield for this pivotal connection The arm 48 (as are the vokes 12 and 20) is of channel cross section, and the outer end 52 of arm 48 is slidably connected to the backing strip 22 adjacent the outer end thereof, by means of ears 54, which are engaged about the backing strip and freely slidable relative thereto. As shown in Fig 2, the pressure applied to the squeegee unit when it engages a windscreen is derived from a wiper arm, not shown, connected to the socket 14 and is distributed by the yokes 12 and 20, and arm 48, the pressure being applied at points 38, 40, 46 and 54 to bend the backing strip from its reverse bend, as shown in Fig 9, to that required by the greatest curvature of the surface to be wiped The pressure applied at point 54 is controlled by a tension spring 56 which is connected at its inner end to a link 58 which is pivotally supported by a transverse pin 60 carried by the yoke 12 The pin is located below and further from the end of yoke 12 than the pin 50 and is thus nearer to the backing strip than pin 50, so that it urges the backing strip 22 from the reverse curve of Fig 9 to the curvature shown in Fig 2 The outer end of the spring 56 is hooked around a transverse pin 62 carried by the arm 48, this end of the spring being centered within the arm 48 by a pair of plastic rings 64 and 66 mounted on the pin 70 62, as shown in Fig 5. * Sitemap * Accessibility
  14. 14. * Legal notice * Terms of use * Last updated: 08.04.2015 * Worldwide Database * 5.8.23.4; 93p * GB785866 (A) Description: GB785866 (A) ? 1957-11-06 Device for distributing current alternately to different apparatus Description of GB785866 (A) A high quality text as facsimile in your desired language may be available amongst the following family members: FR1143402 (A) FR1143402 (A) less Translate this text into Tooltip [79][(1)__Select language] Translate this text into The EPO does not accept any responsibility for the accuracy of data and information originating from other authorities than the EPO; in particular, the EPO does not guarantee that they are complete, up-to-date or fit for specific purposes. PATENT SPECIFICATION 785 866 Date of Application and filing Complete Specification: March 15, 1956. No 8164/56. Complete Specification Published: Nov 6, 1957. Index at acceptance:-Classes 38 ( 4), A 2 B( 2: 3: 5); and 38 ( 5), Bl S( 1 B: 6: 10), B 2 A 5 A 4. International Classification:-HO 2 c, j. COMPLETE SPECIFICATION Device for Distributing Current Alternately to Different Apparatus I, SVERKER RYDBERG, of Gotgatan 17, Linkoping, Sweden, a Subject of the
  15. 15. King of Sweden, do hereby declare the invention, for which 1 pray that a patent may be granted to me, and the method by which it is to be pertormed, to be particularly described in and by the following statement: - The present invention relates to a device for distributing current alternately to two or more electric apparatus in which device a current conducting blade spring is brought alternately into contact with a contact arranged at either side thereof The blade spring is brought into contact with the contacts by means of snap action by the aid of a hot wire attached thereto. The invention is hereinafter described with reference to the accompanying drawings which illustrate one embodiment of the invention Fig 1 is a circuit diagram of the device, Fig 2 shows the form which the blade spring would assume under a number of conditions when located in the device. Referring to the drawings, the device contains a blade spring 1 which is mounted between two immovably mounted metal supports 3, 4 on a base plate 2 On the blade spring' there is mounted at one end a stud 5 of insulating material and in the middle of the blade spring is mounted a contact 6 of silver At the free end of the stud 5 a groove 7 is formed to receive a fastening lug 8 To this, is attached both a spirally wound wire 9 and a metal wire 10, the operation of which will be hereinafter described The wire 9 is connected at its other end to an adjustable contact pin 11 which is secured in insulated manner to the base plate 2 and is so arranged that the blade spring 1 in its one end position bears with its silver contact on the same. The metal wire is a so-called hot wire i e a wire with a comparatively high electric resistance per unit of length and a high expansion coefficient It is secured in a shiftable fastening element 12 of metal which is mounted in insulated manner in the base plate 2 so that the hot wire when it is stretched by means of a tensioning member 13 which is mounted on the fastening element 12, acts to press the silver contact 6 of 50 the blade spring 1 against the contact pin 11. The support 3 and the hot wire 10 are electrically connected with the corresponding terminals 14, 15 Opposite the contact pin 11, i e on the side of the blade spring re 55 mote from the contact pin are located at a suitable position in relation to the blade spring one or more adjustable contact pins 16 which like contact pin 11 are connected with electric conductors Beside the contact 60 pin 11, when desired, additional contact pins may be arranged and, like the contact pin 16, they may be so arranged that they either effect the closing or breaking of different electric load circuits directly or by means Of 65 a relay device. The immovable metal supports 3, 4 are first mounted on plate 2 at a
  16. 16. definite distance from one another The blade spring 1 is longer than the distance between the metal 70 supports and can be slightly arched before insertion as in Fig 2 a, or bent or formed in other suitable manner for instance to a slight S form It is then inserted between the two metal supports 3, 4 which are pro 75 vided with knife edge recesses 17, 18 serving as abutments In the particular embodiment described the two contact Dins 11, 16 are arranged somewhat un-symmetrically in relation to the connecting line S between the 80 recesses 17, 18 as a result of which the blade spring after it has been stressed by insertion between supports 3, 4 bears against the contact pin 16 farthest from the line S as shown in Fig 2 b If there were no contact pin on 85 the base plate the blade spring after being stressed in the form of an arc would project over one side of the line s By the arrangement of the adjustable contact pins in relation to the line S the result is attained that the 90 blade spring 1 with its silver contact 6 bears against the contact Din 16 The blade spring assumes after stressing the kind of S-form shown in Fig 2 B By means of a simple manipulation the blade spring on stressing can be caused to assume one of the two possible S-forms viz either that in which that half-portion of the spring on which the stud 5 is mounted comes nearest the line s, or, when desired, the other mirror symmetrical S-form. After the fastening lug 8 is fastened to the stud 5 and the hot wire 10 has been secured in its fastening element 12 and in its tensioning member 13, the hot wire can be tensioned by means of the member 13 till the Sform blade spring snaps over into its other position and the silver contact bears on the contact pin 11 When the hot wire is tensioned, the S-form of the blade spring gradually becomes deeper since during the stretching an increasing tension is exerted which acts in the direction of the metal wire 10 By reason of the particular arrangement of the fastening element 12 a component of the force acting on the blade spring comes into operation which is directed at right angles thereto This component produces a turning moment which tends to shift the stud 5 towards the line s As soon as the pin has been displaced by a certain amount the blade spring has come into such a position that its spring forces exert a turning moment which acts in the same direction as the above mentioned turning moment Both turning moments act together and the blade spring snaps over until its movement is limited by the contact pin 11 This position of the blade spring is shown in Fig 20 As the point of the contact pin 11 as above described is displaced somewhat towards the line s, the blade spring is held in a position which is stable only as long as the metal wire is tensioned If the tension in the metal wire is released the blade spring momentarily snaps back until its silver contact again contacts
  17. 17. the pin 16 When the apparatus of the above described construction is subjected to a final adjustment the metal wire 10 is so tensioned that the blade spring 1 snaps into that position in which its silver contact 6 bears against the pin 11, the contact pressure being determined by the elastic properties of the spring. In making use of the apparatus it is connected to a source of current 19 Its one pole 20 is connected through a switch 21 and terminal 14 to the metal support 3 The other pole 22 of the source of current is connected through the terminal 15 with the hot wire 10 When the switch 21 is closed current flows from the metal support 3 to the blade spring 1 and from its silver contact 6 to the contact pin 11 and from there through the wire 9 to the hot wire 10 and back to the other pole 22 of the source of current. When the hot wire is traversed by current it heats up and stretches The tension on it thereby talls and the blade spring snaps momentarily into its other stable position in which its double sided silver contact 6 bears against the contact pin 16 The electric con 70 nection between the silver contact 6 and the pin 11 is thus interrupted, current ceases to flow through the hot wire, and it cools and shrinks The tension on it comes into play and the blade spring snaps back so that the 75 silver contact 6 again bears on the pin 11. The above working cycle repeats itself with the result that the blade spring snaps to and fro between the contact pins 11 and 16 The thermal inertia of the hot wire ensures that 80 the blade spring does not merely vibrate. After the blade spring 1 is directly connected with the one pole 20 of the source of current it can be used to distribute current alternately to one or more electrical consum 85 ing devices which are connected between the pole 22 of the source of current and one of the contact pins 11 and 16, for example to two lamps 23, 24 which are intended as flashing lights The lamp 23 is connected 90 with its second pole 26 to the contact pin 11 and the lamp 24 with its second pole 27 to the cortacc 16. The time for which the silver contact 6 of the blade spring remains in contact with one 95 of the two contacts 11 or 16 can in certain applications require a subsequent adjustment When the blade spring is of steel it can be influenced by a permanent or electromagnet 28 mounted adjacent thereto This 100 is so positioned that one of the magnet poles faces the broad side of the blade spring. When a permanent magnet is used the closing time can be varied by displacement of the magnet in a direction towards or from 105 the blade spring When an electro-magnet is employed the closing time can be varied by regulating the current in the winding 29 of the electro-magnet for example by a variable resistance 30 110
  18. 18. * Sitemap * Accessibility * Legal notice * Terms of use * Last updated: 08.04.2015 * Worldwide Database * 5.8.23.4; 93p * GB785867 (A) Description: GB785867 (A) ? 1957-11-06 Improvements in or relating to laundry methods and machines Description of GB785867 (A) A high quality text as facsimile in your desired language may be available amongst the following family members: CH350631 (A) FR1148698 (A) LU34276 (A) US3128615 (A) CH350631 (A) FR1148698 (A) LU34276 (A) US3128615 (A) less Translate this text into Tooltip [85][(1)__Select language] Translate this text into The EPO does not accept any responsibility for the accuracy of data and information originating from other authorities than the EPO; in particular, the EPO does not guarantee that they are complete, up-to-date or fit for specific purposes. PATENT SPECIFICATION Dnat of A Ouiication (Ind filing Comrplete Specification March 7150 -( No 9574 56. Appi Al' ntion mlode in United States of America on March 23 1955. Com-lete Specification Published Nov 6, 1957. Index at Acceptance: Class 138 ( 2), A 1 (E: K). Iniernational C Las Sification -i 6 f. _t OP y PLETE SPECIFICATTON Improvemrenits in or relating to Laundry
  19. 19. Methods and Machines CORPECTIOM OF CLERICA ERROR SPECIFICATION m C 7 E,3 P-7 The following correction is in accordance EI the Decision of the Asslstant Coriptroller, acting for the Cocptroller-Cererer 1, dated tihe ninth day of Jerne, 1958. Page 1, lines 1 to 4, for 'We, W Ahirl Dool-Seeer Corpjoration of St Joseph, Awc hgar L, United States of Anerica, a corporation organized and existing under ant 'y virtue of the iaws or the State", read " 1 Wle, Wrhirlpool Corporation, a couolration of the State". THE PATE Xi T OFFICE, 2 ath June, 1958 DB O 5 R 4/1 ( 2)/3-C 31 150 6/52 R of washing, rinsing and extracating periods. In such machines, there is also conventionally provided means for confining the mass, of materials such as clothes or other fabrics in a restricted pool where it is agitated and thereafter the pool is drained while the clothes are rotated in a rotatable extractor for the extraction of liquid therefrom. In contemporary times, however there have been developed woven fabrics which are far more delicate than the usual cotton, linen and wool fabrics widely utilized by the users of automatic washing machines For example, the use of modern fabrics woven of nylon, Dacron (Registered Trade Mark), or acetate items of wearing apparel has frequently made it necessary, heretofore, to wash such articles by hand rather than subject the fabrics to the risks of damage in an ordinary washing machine. The risk of machine washing delicate fabrics is sometimes reduced in some degree by an attempt on the part of the user to reduce the duration of the cycle periods frequently LUZ IUI 4 Jfl L%L Lk L Wy 1 a LU Il t. Frequently, it is desirable that the temperature range of the laundry liquid be considerably modified depending upon the type of materials being washed For example, delicate fabrics usually reauire a much cooler laundry liquid than ordinary cotton, linen and wool fabrics. It is an object of the present invention, therefore to provide an improved laundry method and apparatus. According to the invention, there is provided a 'aundrv machine having a receptacle for articles to be laundered, means including an electric motor for mechanicallly agitating articles in the receptacle and presettable control means whereby the machine can be made to carry out either a first or a second programme each including successive washing, rinsing and extracting cycles, in which the motor is arranged to be operated at a higher speed to effect heavy washing during the first programme and at a lower speed to effect gentle washing during the second programme. Also according to the invention, a method of 1 1 Ibl;.
  20. 20. V", -_, 1 _r -1 ,W. c. PATENT SPECIFICATION 785,867 Date of Application and filing Complete Specification March 27 1956. 1 Pl i i No 9574/56. Application made i > Complete Specifica Index at Acceptance:=Class 138 ( 2), A 1 (E: K). n United States of America on March 28, 1955. tion Published Nov 6, 1957. International Classification: -DO 6 f. COMPLETE SPECIFICATION Improvements in or relating to Laundry Methods andl Machines We, WHIRLPOOL-SEEGER CORPORATION, of St Joseph, Michigan, United States of America, a corporation organized and existing under and by virtue of the laws of the State of Delaware, United States of America, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement:- This invention relates to laundry methods and machines It provides a method and machine wherein articles to be laundered can be mechanically agitated in a receptacle containing laundry liquid at a first,speed for heavy washing of ordinary fabrics and at a second slower speed for gentle washing of delicate fabrics. Domestic laundering equipment has been provided heretofore wherein presettable means controls the operation of an automatic washing machine through a programming schedule of washing, rinsing and extracating periods. In such machines, there is also conventionally provided means for confining the mass, of materials such as clothes or other fabrics in a restricted pool where it is agitated and there-. after the pool is drained while the clothes are rotated in a rotatable extractor for the extraction of liquid therefrom. In contemporary times, however, there have been developed woven fabrics which are far more delicate than the usual cotton, linen and wool fabrics widely utilized by the users of automatic washing machines For example, the use of modern fabrics woven of nylon, Dacron (Registered Trade Mark), or acetate items of wearing apparel has frequently made it necessary, heretofore, to wash such articles by hand rather than subject the fabrics to the risk of damage in an ordinary washing machine. The risk of machine washing delicate fabrics is sometimes reduced in some degree by an attempt on the part of the user to reduce the duration of the cycle periods frequently established in an
  21. 21. automatic-type washing machine by a sequential controller If almost continual manual intervention does not attend the operation of such a machine, however, 50 only the duration of the washing cycle can be so adjusted, whereupon the fabrics will be subjected to rinsing and extraction periods of regular duration Moreover, the rinsing and extraction operations as well as the wash 55 ing operation will be carried out under ordinary operating conditions and speeds and, consequently, the user of the machine may frequently be frustrated in attempting to modify the operation of die machine to adapt 60 to the varying laundering requirements encountered in an average household or domestic laundering practice. Furthermore, most automatic washing machines embody a mixing apparatus for 65 blending a supply of hot water and a supply of cold water and the water is delivered into the machine in distinct temperature ranges. Frequently, it is desirable that the temperature range of the laundry liquid be consider 70 ably modified depending upon the type of materials being washed For example, delicate fabrics usually require a much cooler laundry liquid than ordinary cotton, linen and wool fabrics 75 It is an object of the present invention, therefore, to provide an improved laundry method and apparatus. According to the invention, there is provided a laundry machine having a receptacle 80 for articles to be laundered, means including an electric motor for mechanicallly agitating articles in the receptacle and presettable control means whereby the machine can be made to carry out either a first or a second pro 85 gramme, each including successive washing, rinsing and extracting cycles, in which the motor is arranged to be operated at a higher speed to effect heavy washing during the first programme and at a lower speed to effect 90 gentle washing during the second programme. Also according to the invention, a method of 785,867 effecting heavy and gentle washing of fabric articles in a single laundry machine having presettable control means whereby the machine can be made to carry out either a first or a second programme, each including successive washing, rinsing and extracting cycles, includes the step of mechanically agitating the articles in a receptacle containing laundry liquid by means driven by an electric motor operated at a higher speed during the first programme to effect heavy washing and at a lower speed during the second programme to effect gentle washing. Features and advantages of the present invention will become manifest to those versed in the art upon making reference to the detailed description which follows and the accompanying drawings in which a preferred structural embodiment of a washing machine capable of practicing the steps of the method herein disclosed is shown by way of
  22. 22. illustrative example. On the drawings:Figure 1 is an elevational view of a laundry apparatus with parts broken away and with parts shown in cross-section and embodying the present invention; Figure 2 is a diagram illustrating the cycle of operation of the machine of athe present invention and specifically illustrating the two separate programme schedules which can be obtained by the actuation of presettable means provided in accordance with the present invention; and Figure 3 is an electrical circuit diagram of the machine illustrated in Figure 1 and operablle in accordance with progami ng schedules illustrated in Figure 2. For purposes of illustrating the principles of the present invention, there is shown in Figure 1 an automatic washing, rinsing and extracting machine 10 having a cabinet 11 forming an enclosure or container for a tub 12 which is adapted to contain the liquid such as water or laundry liquid. A pump is indicated at 13 for withdrawing liquid from the tub 12 or for returning liquid thereinto, if desired. A receptacle or container indicated at 14 is rotatably mounted within the tub 12. Thle tub 12 is carried on a floating base 16 suspended from the top portion of the cabinet on suspension links 17 encased in rubber at their ends and carried in sockets 19 in the base 16 and in similar sockets at the upper part of the cabinet (not shoivn) for damping oscillatable movement which may occ 1 ur between the base and the cabinet. Suspended from the base 16 on a hangar bracket 20 is an electric motor 21 which operates as the drive motor for the machine. The structural and functional characteristics of the motor 21 are important in the present invention and will be described in greater detail hereinafter. A gear casing is indicated at 22 through which an 3 scillatable drive mechanism actuates an independently operable washing element or agitator 23 located interiorly of the container or receptacle 14 and, hence, interiorly also of 70 the tub 12. The gear casing 22 is also suspended from the base 16 on a plurality of bolts 24 threaded into a corresponding plurality of studs 26 fastened in firm assembly to the base 16 as 75 by welding or the like, thereby to maintain the gear casing 22 in fixed parallel spaced relation with respect to the base 16. The gear casing 22 is in two parts, a lower part housing an oscillatable drive gearing for 80 oscillatably driving the washing element or agitator 23 and an upper part housing operating and control mechanism of the machine, the details of which are not necessary to a proper understandling of the present inven 85 tion.
  23. 23. With respect to the actuation of the washing element or agitator 23, however, there is shown an oscillatable drive shaft at 27 rotatably carried in the gear casing 22 in a boss 90 28 at the lower part of the gear casing 22 The shaft 27 is also journalled within a rotatable drive sleeve indicated at 29 which extends within a stationary sleeve 30 concentrically disposed relative to a hollow center post 31 95 The hollow center post 31 forms a closure for the central part of the bottom of the tub 12 and extends upwardly from the bottom of the tub 12. The sleeve 30 is carried in the hollow centei 100 post 31 The rotatable sleeve 29 provides a support for a hollow upright support member 32 attached in firm assembly with the container or receptacle 14 Thus, the container or receptacle 14 is supported near its upper 105 end for spinning. The washing element or agitator 23 is locked to the upper end of the shaft 27 as at 33 and will be oscillatably driven upon corresponding oscillatable movement of the shaft 110 27 The rotatable sleeve 29 is driven by a drive sheave 34 mounted on the lower portion of the sleeve 29 through a clutch indicated at 36 comprising a friction disk clutch having an 115 annular friction surface engaging an upper face portion on the sheave 34, which engagement is controlled by suitable actuating mechanism. The motor 21 has a power take-off shaft 37 to which is attached a driving pulley 38 A 120 driving belt indicated at 39 is trained over the pulley 38 and over the drive sheave 34. whereupon he container or receptacle 14 will be rotated at a speed suitable for extracting liquid from clothes contained therein upon 125 actuation of the clutch 36. The belt 39 is also trained over a drive pulley 40 fastened to a shaft 41 extending out of the oscillatable drive mechanism housed within the gear case 22 It will be understood 130 785,867 that the shaft 27 will be oscillatably driven by the motor 21 through the oscillating mechanism and a detailed description of the driving mechanism does not appear to be necessary to a proper explanation of the invention. It is contemplated according to the present invention to supply a stream of hot water from a domestic supply through a conduit 42 to a mixing zone established by a fluid mixing chamber indicated at 43 In like manner, a stream of cold water from a domestic supply is conducted to the mixing zone established by the fluid mixing chamber 43 by a conduit 44. The conduits 42 and 44 and the fluid mixing chamber 43 can conveniently comprise a temperature control valve and it will be understead that the water mixed in the fluid mixing chamber 43 is discharged though an outlet conduit 46 which extends upwardly and
  24. 24. dischages into the tub 12 through a nozzle indicated at 47. The temperature control valve unit is indicated generally by the reference numeral 48 and in addition to the elements 42, 43, 44, 46 thus far described the unit 48 also includes a pair of solenoids 49 and 50, respectively. which solenoids may be referred to as a mix water solenoid 49 and a hot water solenoid 50. As will be explained presently, the solenoids 49 and 50 are electrically connected to control switches and are mechanically connected to suitable valving elements which are not illustrated in detail herein but which are for the purpose of controlling the admission of hot and cold water from the conduits 42 and 44 into the fluid mixing chamber 43 Thus, when electric current is caused to flow through the mix water solenoid 49, a movable plunger is raised by the magnetic forces associated with the current flow and a valve in the unit 48 connects the conduits 42 and 44 to the conduit 46 through the fluid mixing chamber and the relative quantities of fluid flowing are regulated by temperature-sensitive elements in the valve 48 to a relatively low temperature to cause relatively cool water to flow into the tub 12. When the hot water solenoid 50 is energized with electric current, a movable plunger is raised by the magnetic forces associated with the current flow and the valve in the unit 48 causes hot water to flow through the outlet 46 and into the tub 12. When both the mix water solenoid 49 and the hot water solenoid 50 are energized, water of an intermediate temperature pass into the tub 12. It will be appreciated, therefore, that the steps of controlling the supply of the respective streams of hot and cold water into and through the mixing zone effects delivery of water from the mixing zone to the treatment zone prescribed by the tub 12 in three distinct temperature ranges, namely, ( 1) a hot water temperature range, ( 2) an intermediate or warm temperature range and ( 3) a cool temperature range. In ordinary automatic washing machines, a single speed motor is provided and such motor 70 operates at a constant speed in order to effect a driving of the washing element or agitator 23 as well as a selective rotation of the receptacle or container 14 when extraction action on the materials being laundered is required 75 In such a machine, operation of the motor at so-called "regular" speed results in an oscillation of the washing element or agitator 23 at a rate of approximately 68-72 oscillations per minute The container or receptacle 14 80 rotates at approximately 500 revolutions per minute at " regular " speed. According to the present invention, the machine 10 is equipped with a
  25. 25. motor 21 having improved structural and functional 85 characteristics which permits the machine to satisfactorily launder delicate fabrics as well as regular fabrics such as the usual cotton, linen and wool materials which are very satisfactorily washed at regular washing speeds 90 The motor 21 of the present invention is preferably of the induction-type with a fixed field structure and a squirrel cage armature or rotor within the field structure Windings on the field structure define a first winding con 95 nected between a terminal B and a terminal C (Figure 3) and a second winding connected between a terminal D and the terminal C the first winding being arranged to be energized to provide a first plurality of poles on such 100 field structure and the second winding being arranged to be energized to provide a second plurality of magnetic poles on such field structure so that connection of the terminals B and C to a source of alternating current will result 105 in a rotation of the armature at one speed and connection of the terminals D and C to the alternating source will result in a rotation of the armature at a slower speed. By way of illustrative example, and not by 110 way of limitation, the field structure may have four poles when the terminals B-C are connected to a source of alternating current and six poles when the terminals D-C are connected to the source of alternating current 115 With a source of 60 cycle current, the synchronous speeds will be 1800 revolutions per minute and 1200 revolutions per minute and if the motor is of the induction-type, the actual speed of the motor under load will be some 120 what less than synchronous speed, for example, 1750 revolutions per minute and 1150 revolutions per minute. Because of the provision of the motor 21, it is possible to operate the machine of the 125 present invention so that the washing element or agitator 23 will oscillate at a rate of approximately 45-48 oscillations per minute whenever delicate fabrics are being laundered in the machine 10 and at the regular rate of 130 785,867 68-72 oscillations per minute for ordinary fabrics Likewise, if a centrifuging extraction operation is to be performed on the materials contained within the container or receptacle 14, the present machine will effect a rotational speed of the container or receptacle 14 of approximately 330 revolutions per minute when delicate fabrics are being laundered and the regular speed of 500 revolutions per minute will be available for laundering of ordinary materials. It should be noted that a single speed motor could be used in c 2 onjunction with a gear changing or other speed changing mechanism. 1 S The two-speed motor, howvever is particularly advantageous not only because of the simnplicity obtained thereby, but also because the optimum load for maximum effciencv on a motor of this pole changing type decreases as the number of poles increases and hence as the speed
  26. 26. decreases Since the load on the agitator or washing element 23 decreases as its speed decreases, the motor 21 is operated at optimum load conditions for both rated speeds. The present invention further contemplates the provision of a sequential controller for automatic operation of the machine through a serks of washing, rinsing and extraction periods The sequential controller actuates the driving means of the machine at a first regular speed or at a second slow speed through a corresponding first programming schedule and a corresponding second programming schedule of washing, rinsing and extraction. Moreover, it is further contemplated according to the present invention that the washing, rinsing and extraction periods of the first programming schedule will be of a corresponding first duration and the washing, rinsing and extraction periods of the second corresponding programming schedule will be of a corresponding second shorter duration It should be understood however that, if desired, the schedules may be of equal duration, altering only the speed of the operatione This aspect of the present invention can best be understood by considering the operational schedule illustrated in Figure 2 in conjunction with the sequential controller and the electrical circuitry associated therewith illustrated in Figure 3. The diagram of Figure 2 indicates the condition of the cam actuated switches controlling the energization of the various elements identified thereon at the various times in the operating cycle, these times being identified by the indication of the " minutes " line of the diagram It will be understood, of course, that an element may be indicated as energized in the diagram of Figure 2, when in fact, some other portion of the energizing circuit is open and for that reason the element does not operate. The sequential controller or cycle control stitch, shown diagrammatically in Figure 3, for example, comprises a plurality of cams which are indicated by the reference numerals C-1 to C-8, inclusive, with the associated switches S-1 to S-8, inclusive, in co-operative engagement therewith for opening and closing movenients as the cams are rotated. The cams are mounted on a common insulated shaft 51 which is driven by a timer 75 motor 52 which, for the particular embodiment of the present invention herein described, is a synchronous alternating current motor capable of rotating the shaft 51 one revolution in 60 minutes 80 The cams C-1 to C-8 ace aligned relative to the shaft 51 to provide the desired sequence of control and a knob 53 is rrovided with suitable rmarkings to indicate the point on the operating cycle to which the shaft 51 has been Saligned or set. As eill ha clearly evident upon inspecting the diagram of Figure 2,
  27. 27. there are two distinct programming schedules identified as the norm-1 wvashing cycle and the modern fabrics 90, cycle This arrangement is afforded by providing cams C-1 to C-8 vhich have high and low and intermediate camming surfaces engageabie with the switch means S-1 to S-8 on opposite circumferentially spaced 95 portions of the shaft 51 Thus, whenever the shaft 51 is adjusted through a sector of movee nt corresponding to proximately 220 of arc, all of the electrical equipment iiil be conditioned in accordance with the 100 programinig specifications oi the normal mashin, cycle Moreover, whenever the shaft 51 is aligned and positioned in a different sector covering approximately 95 all of the e ectcical devices are conditioned in accordance 105 fith I the programm-ing schedule determined in th mnodern fabrics cycle. Before preceeding with a description of the oaeration of the sequential controller and the machine ol the present invention, several 110 adii'onal structural units should be identified. First of all, it will be noted that these is shown on Figure 3 an agiator control solenoid 54 It will be understood that the solenoid 54 controls mechanical means for selectively 115 actuating the washing element or agitator 23 through the oscillata Lle drive mechanism contained in the housing 22 There is also pro7 iled a two-way valve control solenoid 56 whnichl controls a two-way valve indicated at 120 57 in Figure 1 and associated with the pump 13 by means of a conduit 58 By effecting actuatien of the two-way valve 57 with the solenoid 56, soap suds can be numred out of the tub 12 and into a suds storage recep 125 tacle or pumped back again from the receptacle into the tub 12. There is further provided an extractor control solenoid indicated at 59 It will be understood that this solenoid controls actuation of 130 785,867 the clutch 36, thereby to selectively initiate rotational operation of the container or receptacle 14 whenever extraction is required. A pressure-type three position water level selector switch is indicated at 60, thereby making the control of the machine responsive to the water level conditions established in the tub 12. In connection with the circuitry for the mixed water solenoid 49 and the hot water solenoid 50, there are also provided water temperature switches 61 and, 62, which are manually selectively adjustable as by the means indicated at 63 to select one of the three distinct water temperature ranges described hereinbefore. It may also be noted that a separate cam C-7 a, driven by the motor 52, is provided for the so-called " spray-rinse " and a corresponding switch S-7 a is associated therewith. By means of such provision, a contact is effected for very short
  28. 28. duration several times during the cycle and coincident with extraction to assist in rinsing the materials contained within the container or receptacle 14. In view of Figure 3, the shaft 51 and the associated cams are rotated by the motor 52 in the direction indicated by the arrow 531 and the shaft is shown as rotated to the position corresponding to the beginning of the period identified in Figure 2 by the legend "suds '", this period being the preliminary period during which the used suds are returned to the tub 12 to provide wash water for a subsequent cycle of operation. Assuming that the laundering machine 10 is to be started from an unenergized condition and that the storage reservoir provided to retain used suds is empty, the knob 53 is rotated to the position corresponding to the beginning of the fill period also labeled by legend on Figure 2 and is then depressed to close the single pole switch indicated at 63. Without further manual intervention, the entire programming schedule illustrated in the " normal washing cycle " in Figure 2 will be carried out It will be noted that the duration of the wash cycle can be as long as 14 minutes and the duration of the rinse period can be as long as 8 minutes Moreover, the drying period can be as long as 8 minutes also during the normal washing cycle. Although these periods may be selectively shortened, by manual intervention during the course of the cycle, automatic operation witliout manual intervention will normally result in the full rinsing and drying periods with the washing period being selectively varied within the limits prescribed by that portion of the cycle identified by the legend "fill ") a variable amounting to approximately 7 minutes Thus, if the operator sets the dial at 6, for example, the machine starts to fill but does not begin operation until after the machine is filled with water, whereupon the switch 60, if desired, starts the machine in operation. If delicate fabrics are being laundered, a completely separate programming schedule may be effected by adjusting the knob 53 and 70 the shaft 51 to a corresponding annular alignment suitable for scheduling the modern fabrics program It will be noted that in the modern fabrics cycle, the wash period is only of 4 minutes duration and even this Period 75 can be cut down within the limits prescribed by the period of " fill " which amounts to 2 minutes Furthermore, the rinse period is of 5 minutes duration and the dry period is of 4 minutes duration, both the rinsing and drying 80 periods being considerably shorter in duration than the normal rinsing and drying periods established in the normal washing programme. Thu-, the opposite sides of the cams C-1 to C-8 are, in effect,
  29. 29. separate presettable 85 means, each of which prescribes independently of the other a complete programming schedule of different characteristics. According to the present invention, the operation of the washing and extracting means 90 and the regulation of the mixing and the hot and cold water steams are interlocked to prevent the supply of extremely hot water into the treatment zone when the washing and extracting means is operated at a slow speed 95 and during which time it is contemplated that delicate modern fabrics will be contained within the container or receptacle 14. This is effected specifically in the sequentialcontroller by means of the cam C-7 and the 100 switch S-7 which provides an electical override in circuit with the mix water solenoid 49. Thus, even if a hot water selection is indicated by adjustment of the control 63, the mix water solenoid will be energized so that only 105 relatively cool water will be supplied to the treatment zone thereby safeguarding against any damage which might be caused to delicate modem fabrics through an incorrect setting of the controls l O 1 * Sitemap * Accessibility * Legal notice * Terms of use * Last updated: 08.04.2015 * Worldwide Database * 5.8.23.4; 93p * GB785868 (A) Description: GB785868 (A) ? 1957-11-06 Air conditioning installations for rooms Description of GB785868 (A) A high quality text as facsimile in your desired language may be available amongst the following family members: BE547036 (A) CH329664 (A) DE1769156 (U) FR1149027 (A) BE547036 (A) CH329664 (A) DE1769156 (U) FR1149027 (A) less
  30. 30. Translate this text into Tooltip [85][(1)__Select language] Translate this text into The EPO does not accept any responsibility for the accuracy of data and information originating from other authorities than the EPO; in particular, the EPO does not guarantee that they are complete, up-to-date or fit for specific purposes. AMENDED SPECIFICATION Reprinted as amended in accordance with the Decision of the Superintending Examiner acting for the Comptroller-General dated the thirteenth day of September 1963, under Section 29, of the Patents Act, 1949. PATENT SPECIFICATION DRAWINGS ATTACHED 785,868 Date of Application and filing Complete Specification: April 16, 1956. No 11462156. Application made in Switzerland on April 15, 1955. Complete Specification Published: Nov 6, 1957. Index at acceptance:-Class 137, B 2 (A:B), B 4 (A:B). International Classification:-F 24 f. COMPLETE SPECIFICATION Air Conditioning Installations for Rooms We, SULZER F Rt RES, SOCIETE ANONYME, a Company organised under the Laws of Switzerland, of Winterthur, Switzerland, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement: - This invention relates to air conditioning installations for rooms, of the kind comprising a fresh air receiver which can be supplied with suitably conditioned fresh air at super atmospheric pressure and in an amount adjustable to suit requirements, expansion nozzles through which the fresh air from the receiver flows into a mixing chamber disposed above the receiver, in which mixing chamber the fresh air is mixed with air sucked in from the room by the ejector effect of the expansion nozzles, and a finned heat exchanger disposed in the path of the room air as it flows into the mixing chamber for heating or cooling the room air. Installations of the kind specified are being increasingly used in buildings where ventilating ducts would be difficult to install or are precluded by lack of space Whereas in air conditioning plants of the type most commonly employed hitherto a part of the air in an air
  31. 31. conditioned room is continuously sucked off through a ventilating duct into a central air conditioning plant and there, together with a certain amount of fresh air, it is brought to suitable temperature and humidity and is then returned to the room together with the fresh air through another ventilating duct, and an amount of room air corresponding to the supplied amount of fresh air escapes from the room through any apertures therein, the lPrice 4 s 6 d l operation of installations of the kind specified is as follows A central conditioning plant sucks in fresh air from the atmosphere and brings this air to suitable temperature and humidity. The conditioned fresh air is then supplied under increased pressure to individual installations of the kind specified distributed among the rooms of the buildings In each installation the fresh air expands in passing through the expansion nozzles, producing an ejector the rooms of the building In each installation This room air is heated or cooled, as occasion demands, by means of the heat exchanger and is mixed with the expanded fresh air, after which the mixture produced flows out into the room Here also an amount of air corresponding to the supplied amount of fresh air escapes from the room Thus no ventilating duct for returning air from the room to the central air conditioning plant is required, only a single pipe for supplying fresh air to the installation being needed This air supply pipe can be very small in comparison with the ventilating ducts in conventional air conditioning plants, because the fresh air supplied to the room is only a fraction of the mixture of room air and fresh air which is circulated by the installation in the room. Also, as the fresh air is supplied at higher pressure to the installation the flow crosssection of the air supply pipe can be still further reduced on account of the greater flow velocity thus attainable One advantage of the small air supply pipe is that even a building with a considerable number of storeys can be supplied with fresh air from a single central air conditioning plant without the air supply pipes occupying an excessively large area of the ground plan Moreover, the air conditions in the various rooms connected to the central air conditioning plant can be individually adjusted to suit requirements The installations set up in the individual rooms can serve for both cooling and heating. The present invention arose from the recognition that in hitherto known installations of the kind specified, with the mixing chamber flanked by the heat exchanger on one side, the passages through the heat exchanger that are furthest away from the expansion nozzles contribute to the heating or cooling of the circulated room air only to a negligible degree. According to the present invention the mixing chamber, which is free
  32. 32. of heat exchanger fins, is flanked by the heat exchanger over the greater part of its height on both sides This arrangement produces the result that the air from the room flows through the heat exchanger practically uniformly over its whole height so that the proportion of room air to fresh air in the mixing chamber is increased and the whole outer surface of the heat exchanger contributes effectively to the heating or cooling of the circulated room air. The known arrangement with the mixing chamber flanked on only one side by the heat exchanger has the disadvantage that the heat exchanger has to be tall in order to provide the necessary heat transfer area, because the length of the passages for the room air through the heat exchanger may not exceed a certain maximum in order that there shall not be too much resistance to air flow On the other hand, since the suction effect of the mixture of room air and fresh air rising in the mixing chamber decreases with increasing distance from the outlet apertures of the expansion nozzles, the greater part of the sucked in room air flows through the heat exchanger passages which are situated closer to the nozzles, so that the more distant passages will contribute progressively less to the heating or cooling of the circulated room air The invention reduces these disadvantages to a great extent. In one form of installation embodying the invention the heat exchanger passages for the room air are disposed at an angle of between and 900 to the direction of flow of the fresh air leaving the nozzles. It is recommended that the heat exchanger and the mixing chamber should be contained in a common housing of which the walls beside the heat exchanger have inlet apertures for the room air In such an arrangement the housing may also contain the fresh air receiver with a space between the fresh air receiver and the walls of the housing through which room air entering the housing by further inlet apertures in the bottom of the housing can flow upwardly to the heat exchanger. The pipes of the heat exchanger through which the heating or cooling medium flows preferably have a flattened cross-section and are provided with vertical fin plates Where the housing also contains the fresh air receiver and has room air inlets at the bottom, it is desirable for the edges of the fin plates nearest the housing walls to be inclined with respect to these walls, being farthest from these walls at the bottom. The invention may be performed in various ways, and one installation embodying the invention, and a modification, will now be specifically described by way of example with reference to the accompanying drawings, in which:Figure 1 is a transverse cross-section through the installation; Figure 2 is a front view of the installation shown in Figure 1, partly in section through the central longitudinal plane;
  33. 33. and Figure 3 shows a modified construction of the heat exchanger. The installation shown in Figures 1 and 2 comprises a sheet metal housing 1 which contains in its lower part a fresh air receiver 2. In the interior of the fresh air receiver there is disposed a distributing passage 3, which is connected to a fresh air supply pipe 4 Felt linings 6 for the purpose of damping noise are fitted on the inside of the sheet metal body 5 of the fresh air receiver 2, as well as on both sides of the sheet metal wall of the distributing passage 3 The fresh air supplied through the pipe 4, conditioned to suitable temperature and humidity and compressed to a super atmospheric pressure, flows through an aperture 7 of the distributing passage 3 into the receiver 2. Along the top of the receiver 2 there is a row of expansion nozzles 8 such that the fresh air flows through the nozzles 8 into a mixing chamber 9 at reduced pressure and at relatively high velocity The motion of the expanded fresh air into the mixing chamber 9 produces a suction or ejector effect which sucks air from the room through apertures 10 and 11 in the side walls ofthe housing and through an aperture 12 in the bottom of the housing into the mixing chamber where it mixes with the fresh air The mixture of fresh air and room air flows out through apertures 13 in the top of the housing 1 into the room For adjusting the heat content of the air mixture a heat exchanger 14 is disposed in the path of the room air sucked in through the apertures 10, 11 and 12 Furthermore, the pipe 4 is provided with a throttle valve 15 adjustable by hand. According to the invention the mixing chamber 9 is free from heat exchanger fins and is flanked by the heat exchanger 14 on both sides for the greater part of its height. For this purpose the heat exchanger consists of two elements 14 a and 14 b situated in the interior of the housing 1, respectively behind the apertures 10 and 11 in the side walls of the housing Each element of the heat exchanger consist of a pipe coil 16, which is provided with vertical fin plates 17 The pipe coil of the element 14 a of the heat 785,868 gives favourable deflection conditions for the room air entering through the apertures 10 and 11 and for the room air sucked in through the opening 12 and rising along the housing walls 70 The edges of the fin plates 17 situated nearest the housing walls are inclined with respect to these walls, being farthest from these walls at the bottom The free space thus left between the heat exchanger and the hous 75 ing walls affords low resistance guiding for the room air entering through the aperture 12 in the bottom of the housing and rising along the housing wall This arrangement makes it possible to maintain some circulation of the 80 room air through the installation by convection when the supply of fresh air is stopped and the heat
  34. 34. exchanger is heated, for heating the room. * Sitemap * Accessibility * Legal notice * Terms of use * Last updated: 08.04.2015 * Worldwide Database * 5.8.23.4; 93p

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