5456 5460.output

* 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,

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

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

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

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

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

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

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

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

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.
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* 5.8.23.4; 93p
* GB785865 (A)
Description: GB785865 (A) ? 1957-11-06
Improvements relating to windscreen wipers
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.
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

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

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.
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* 5.8.23.4; 93p
* GB785866 (A)
Description: GB785866 (A) ? 1957-11-06
Device for distributing current alternately to different apparatus
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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.
785 866 Date of Application and filing Complete Specification: March
15, 1956.
No 8164/56.
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.
Device for Distributing Current Alternately to Different Apparatus I,
SVERKER RYDBERG, of Gotgatan 17, Linkoping, Sweden, a Subject of the

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

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

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

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* Accessibility
* Legal notice
* Terms of use
* 5.8.23.4; 93p
* GB785867 (A)
Description: GB785867 (A) ? 1957-11-06
Improvements in or relating to laundry methods and machines
CH350631 (A) FR1148698 (A) LU34276 (A) US3128615 (A)
CH350631 (A) FR1148698 (A) LU34276 (A) US3128615 (A) less
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

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;.

V", -_, 1 _r -1 ,W.
c.
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.
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

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

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.

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

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

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

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,

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

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,

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
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* Accessibility
* Legal notice
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* 5.8.23.4; 93p
* GB785868 (A)
Description: GB785868 (A) ? 1957-11-06
Air conditioning installations for rooms
BE547036 (A) CH329664 (A) DE1769156 (U) FR1149027 (A)
BE547036 (A) CH329664 (A) DE1769156 (U) FR1149027 (A) less

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.
DRAWINGS ATTACHED 785,868 Date of Application and filing Complete
Specification: April 16, 1956.
No 11462156.
Application made in Switzerland on April 15, 1955.
Index at acceptance:-Class 137, B 2 (A:B), B 4 (A:B).
International Classification:-F 24 f.
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

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

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;

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

exchanger is heated, for heating the room.
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* Accessibility
* Legal notice
* Terms of use
* 5.8.23.4; 93p

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