Centering and stabilizing apparatus for a combined washing machine and extractor (original) (raw)
y 10, 1962 J. A. CASTRICONE 3,043,435
CENTERING AND STABILIZING APPARATUS FOR A COMBINED WASHING MACHINE AND
EXTRACTOR
5 Sheets-Sheet 1 Filed July 10, 1957 lNVEfl/TOR JOHN A. C145 TR/C ONE ATTORNEYS Z'Fi .1
ly 1962 J. A. CASTRICONE ,0 3,
V CENTERING AND STABILIZING APPARATUS FOR A COMBINED WASHING MACHINE AND
EXTRACTOR
5 Sheets-
Sheet
3 Filed July 10, 1957 r-IO I IV VE N TOR JOHN A' cAs'm/colvs ATTORNEYS y 0, 1962 J. A. CASTRICONE 3,
CENTERING AND STABILIZING APPARATUS FOR A COMBINED WASHING MACHINE AND EXTRACTOR Filed July 10, 1957 5 Sheets-
Sheet
4 H8 1 3 INVENTOR //2 I44 JOHN A. CASTR/CO/VE 1* BY WW,
I46 I42 ATTORNEYS y 5 .1. A. CASTRICONE CENTERING AND STABILIZING APPARATUS FOR A COMBINED WASHING MACHINE AND
EXTRACTOR
5
SheetsSheet
5 Filed July 10, 1957 INVENTOR JOHN A. CASTR/CO/VE ATTORNEYS United States Patent CENTERING AND STABILIZING APPARATUS FOR A CGENED WASHIPJG MACHINE AND EX- TRACTGR John A. Castricone, Peoria, 111.,
signments, to American Motors Corporation, Detroit,
Micln, a corporation of Maryland Filed. July 10, 1957, Ser. No. 670,974 6 Claims. (Cl. 210363) The present invention relates generally to washing machines and more particularly to a combined washing machine and extractor of the type utilizing a bottom supported tiltable spin assembly incorporating improved means for centering and stabilizing the operation of the machine. This application is a continuation-in-part of my copending application Serial No. 488,359, filed February 15, 1955 (now abandoned) and assigned to the assignee of this aplication.
Bottom supported tiltable spinning assemblies have been employed in washing machines and extractors and such devices have utilized damping and centering means consisting primarily of a rounded surface formed on the bottom of a stationary tub and a complementary shaped rounded surface on a journal member surrounding the shaft means of the spinner assembly. In this particular form of device, it is customary to provide a plurality of circumferentially spaced centering springs which are connected between the journal member and the bottom of the stationary tub. It is usually intended in such a structure that the springs develop a centering function. In other words, at least a substantial component of force exerted by the springs will be directed in such a fashion and the springs will be so angularly aligned as to assist in retaining the shaft in upright vertical position.
Being of the bottom support type, such a spinning assembly partakes of a spinning action which is gyratory in nature. For example, if the spin assembly is rotated with an uneven load located therein, an eccentric wobbling occurs which results in changes in tension in the centering springs. If the spin assembly is displaced in one lateral direction, one spring is collapsed and the spring assignor, by mesne asdiametrically opposite it is placed under increased tension.
It has been observed that under such circumstances the wobbling action is apparently aggravated by the springs since the springs appear to have the effect of storing energy which, when released, actually forces the spinning assembly laterally away from the vertical spin axis.
According to the principles of the present invention, a combined washing machine and extractor has been provided wherein the centering and damping apparatus completely eliminates the utilization of the conventionally provided centering springs.
Briefly described, according to the present invention, the entire spin assembly is supported at a bottom bearing to facilitate rotation ofthe shaft on its end support. A journaling bearing means or journal member is located at an intermediate portion of the shaft means. However the journal member does not support the spin shaft. It is merely relatively stationary with respect thereto.
Between the basket of the spin assembly and the bot tom support, there is provided a means for resisting the tilting movement of the tub which, more particularly, comprises three vertically stacked annular disc members which are arranged concentrically outwardly of the shaft means. The upper and lower disc members form a first friction unit and the intermediate disc member forms a second friction unit to frictionally engage the disc members of the first friction unit. The journaling bearing means around the shaft means is connected to the inner "ice edges of one of the friction units, thereby to tilt the friction unit in unison with the tilting action of the spin assembly. Fastening means are also provided to connect the outer edges of the other of the friction units to the bottom wall of an outer stationary tub provided for the washing machine.
To enhance the friction snubbing action of the disc members a plurality of circumferentially spaced friction pads mays be employed between the disc members. Moreover, means are provided for retaining the upper and lower disc members in frictional engagement and in this connection a plurality of circumferentially spaced bolts are located between the friction pads and extend between the upper and lower disc-members. Coil springs can be utilized in connection with each of the bolts and a threaded nut means bottoms against each corresponding coil spring, thereby continuously to spring bias the upper and lower disc members into frictional engagement with the intermediate disc member. 7
Further to enhance the operation of the apparatus, the upper and lower disc units of the one disc unit are structurally tied together to form a unit moving at the same time and means are also provided to prevent the bolts from deflecting angularly relative to each other. This construction results in one in which the spring pressures remain substantially constant and uniform whereby there is provided a more uniform snubbing action and one which is more effective than prior art devices.
The disc members preferably have a spherical contour prescribed by a radius extending approximately to the fulcrum point of the tiltable spin assembly thereby facilitating tilting action of the spin assembly and efficient frictionsnubbing action of the centering and stabilizing means.
More precisely, the radius of the spherical friction surfaces is approximately 10% less than the distance from the movably engaged surfaces of the disc members to the fulcrum point of the til-table spin assembly. By virtue of such provision, the entire spin assembly will tend to be self-centering even though no centering springs are employed.
The centering and damping arrangement thus described permits the friction surfaces to be spaced below the bottom of the tub so that an appreciable air space insulates the friction surfaces and the friction pads from the high temperatures existing at the bottom of the tub and imparted thereto by hot water contained in the stationary tub.
It is an object of the present invention, therefore, to provide an improved washing machine and extractor wherein eccentric wobbling is minimized even when unevenly distributed loads are in the machine. v
Another object of the present invention is to provide an improved centering and damping means for a bottom supported tiltable spinning assembly.
Yet another object of the present invention is to provide improved sealing means between a tiltable bottom supported spin assembly and the bot-tom wall of a stationary tub wherein resistance to lateral displacement of the spin assembly will be minimized while resistance to torque forces will be maximized.
Many other features, advantages and additional objects of the present invention will become manifest .to those versed in the art upon making reference tothe detailed description which follows and the accompanying sheets of drawings in which preferred structural embodiments of a combined washing machine and extractor are shown by way of illustrative examples.
FIG. 1 is a cross-sectional view, with parts broken away and with the parts shown in elevation, illustrating a combined washing machine and extractor provided in accordance with the principles of the presentinvention;
FIG. 2 is an enlarged fragmentary cross-sectional view with parts shown in elevation, taken substantial-1y on line 2-2 of FIG. 1;
FIG. 3 is a cross-sectional view, with parts shown in elevation and with parts removed for the sake of clarity, taken substantially on the plane of line 3-3 of FIG. 1;
FIG. 4 is a fragmentary cross-sectional view taken substantially on the
broken line
44 of FIG. 2.;
FIG. 5 is a fragmentary cross-sectional view taken sub-. stantially on line 5-5 of FIG. 3;
FIG. 6 is a fragmentary view similar to FIG. 2 of a further and improved embodiment of the invention; and
FIG. 7 is a horizontal cross-sectional view taken along the line 7-7 of FIG. 6.
As shown on the drawings, the combined washing machine and extractor of the present invention is indicated generally by the
reference numeral
10 and comprises a stationary outer tub indicated generally at 11 comprising an
upper receptacle
12 having a
bottom wall
13 and also having a
lower support section
14 forming a support frame and including a
cross arm
16.
A two directional
electric motor
17 is fastened by means of
brackets
18 to the side walls of the
support section
14 of the stationary tub 11 and has a power takeoff shaft .19 carrying a pair of driving pulleys indicated at 20 and 21, respectively, which are driven by the motor through a slip clutch, not shown.
The connection between the
motor
17 and the
brackets
18 is preferably pivotal in nature, thereby permitting slack to be taken out of
pulley belts
22 and 23, respectively, by pivotal movement of the
motor
17 with respect to the
brackets
18. Such pivotal movement is conveniently effected by means of a continuous biasing means taking the form of a
coilspring
24 hooked at one
end
26 to the lower base portion or frame of the stationary tub 11 and hooked at the
other end
27 to a
bracket arm
28 associated with the electric motor 17 (FIG. 3).
As is clearly shown in FIGS. 1 and 2, the
cross arm
16 has a centrally disposed
aperture
28 receiving a generally cup-
shaped retainer
29 carrying at the bottom thereof a
fiat strip
30 providing a
bearing surface
31 for a ball bearing 32.
A rotatable
inner shaft
33 has a comically-
shaped recess
34 formed in the end thereof to provide a seating surface for receiving the ball bearing 32. The bottom end of the
inner shaft
33 is surrounded by a sleeve member 36'wl1ich, in turn, is resiliently retained within the generally cup-
shaped member
29 by means of an annular
resilient ring
37, which may. be conveniently made of rubher or a similar resilient material. Thus, the lower shaft 33' is bottom supported for tilting movement relative to the outer stationary tub 11.
The
inner shaft
33 projects upwardly from the
cross arm
16 and projects through the
bottom wall
13 into the
receptacle
12 of the outer stationary tub 11. As is shown in FIG. 1, the
inner shaft
33 is connected to an
agitator
38 by means of a crank arm connection indicated generally at 39. The crank arm 39 is journaled with respect to the
agitator
38 by a
sleeve bearing
46 whereupon rotation of the
inner shaft
33 will produce a bodily eccentric or orbital agitating movement of the
agitator
38, such as disclosed in Patent No. 2,416,611. This movement resulting from the eccentricity between the
inner shaft
33 and the crank arm 39 results in a constantly changing center of mass. To rotate the
inner shaft
33, there is provided a
pulley wheel
40 keyed to the
inner shaft
33 by the
pin
41 and cooperating with the
pulley belt
22 driven by the
drive pulley
29 on the power take-
01f shaft
19 of the
electric motor
17.
A spin basket is provided for the combined washing machine and
extractor
10 and is indicated at 42. At the bottom of the
spin basket
42 there is provided a support bracket 43 which is locked in firm assembly to an
outershaft
44 by means of a key 46 and a lock nut 47. The
outer shaft
44 depends from the support bracket 43 and extends through the
bottom wall
13 of the outer sta-. tionary tub 11 to a point adjacent the
pulley wheel
4%) on the
inner shaft
33. A unidirectional clutching device indicated generally at 48 interconnects the
outer shaft
44 and a
pulley wheel
49 driven by the
pulley belt
23 associated with the
drive pulley
21 on the power take-off
shaft
19 of the
electric motor
17. Thus, whenever the two directional
electric motor
17 is operated in a given direction, the
outer shaft
44 will be rotated and the spin basket will be rotated in unison therewith to extract liquid from the material contained in the
spin basket
42.
A deflector or baffle 56 is attached by means of a retaining
ring
51 to the
outer shaft
44 immediately superjacent the unidirectional clutching
device
48, thereby to deflect any leaking fluid finding its Way along the
shaft
44 radially outwardly of the clutching
device
48.
It may be noted that the
pulley wheel
49 is considerably smaller than the
pulley wheel
40. Accordingly, even when the motor is operated in such a direction as to rotate both the inner shaft and the
outer shaft
33 and 44, a difference in relative rotational speeds will occur. There is provided, therefore, between the
inner shaft
33 and the
outer shaft
44 upper and
lower bearing sleeves
52 and 53, respectively.
The
bottom wall
13 of the outer stationary tub 11 is provided with a center opening to accommodate the shaft means of the spin assembly. In the region of this opening and at a medial or intermediate portion of the shaft means, there is provided a journaling bearing means indicated generally at 60. The journaling bearing means includes an
upper sleeve
61 and a
lower sleeve
62 connected in firm assembly with one another by a plurality of
fasteners
63. The
lower sleeve
62 is in journaling relationship relative to the
outer shaft
44 by virtue of hearing sleeve means indicated at 64 which are interposed between the
outer shaft
44 and the
lower sleeve
62. A slip clutch indicated generally at 66 at the lower end of the
lower member
62 insures that slippage will occur between the journaling bearing means 66 and the
outer shaft
44.
Since a tension is maintained on the
pulley belts
22 and 23, the force exerted by the belt pull will tend to tip the spin assembly to one side. To counteract this belt pull, a compensating means is provided which takes the form of a turnbuckle and spring device indicated generally at 67. The
lower sleeve
62 has a
boss
68 apertured at 69 to receive one
end
70 of a
wire
71 connected at its
other end
72 to a C-shaped
body
73 of a turnbuckle. One leg of the c-shaped
body
73 has a threaded
aperture
74 receiving a threaded
book
76. A
coil spring
77 has one
end
78 engaged with the
hook
76 and the opposite 4 end of the
coil spring
77 is indicated at 79 in engagement with a connecting
bracket
81 carried in firm assembly with the
lower support frame
14. The connecting bracket has a plurality of hook openings 82 (FIG. 3), thereby facilitating selective alignment of the turnbuckle and
spring device
67. In other words, the compensating force exerted by the turnbuckle and
spring device
67 may be adjusted relative to the alignment of the forces exerted by the belt pull.
A sealing device is provided between the support bracket 43 on the bottom of the
spin basket
42 and'the
upper sleeve
61 of the journaling bearing means 60. The sealing device is indicated generally at 83 and comprises a
flexible rubber sleeve
84 having its upper end clamped into firm assembly with the lower end of the support bracket 43 by a clamping
hand
87. A
nose ring
88 carried at the lower end of the
sleeve
84 is urged into sealing engagement with a
seal ring
90 carried 'at the upper end of the
upper sleeve
61. The engagement between the
nose ring
88 and the
seal ring
90 not only facilitates relative rotational movement therebetween but insures an effective seal against leakage into the interior of the journaling bearingmeans. This isparticularly desirable in the environment of a combined washing machine and extractor since it will be appreciated that detergents and other cleansing agents utilized in washing machines would have an adverse effecton the successful operation of bearing surfaces.
To effect a seal between the journaling bearing means 60 and the
bottom wall
13 of the outer stationary tub 11, there is provided a flexible sealing boot indicated generally at 92. The
boot
92 may conveniently comprise a flexible material such as rubber or the like and includes an
upper portion
93 which may be clamped into firm sealing assembly with the outer peripheral surface of the
upper sleeve
61 by means of a
clamping ring
94. Extending downwardly and outwardly from the
ring portion
93 is an angularly inclined rib 96 which terminates in an acutely turned upwardly and outwardly extending
rib
97. The
rib
97, in turn, terminates in an acutely turned downwardly depending outer
peripheral wall
98.
As will be noted upon inspecting the cross-sectional contour of the
boot
92, as shown in FIG. 1, the
actual rib portions
96, 97 and 98 are of relatively thin cross section, however, the apical portions indicated by the reference numeral 99 between the
rib portions
96 and 97 and by the reference numeral 100' between the
rib portion
97 and the
wall portion
98 have considerable body. There is thus provided vertically extending corrugations consisting of a plurality of concentrically pleated portions which insure minimum resistance to lateral displacement of the tiltable spin assembly but which likewise insure maximum resistance to torque displacement forces.
The downwardly depending
wall
98 terminates in an enlarged annular boss 101 (see FIG. 2) suitably recessed to receive a
flange
102 formed at the edges of the opening provided by the
bottom wall
13. A
clamping ring
103 is further provided to insure firm assembly between the
boss
101 of the sealing
boot
92 and the
bottom wall
13.
To further protect the bearing surfaces against the'possible leakage of fluid handled by the washer, a rubber sealing ring 104 (FIG. 2) snugly embraces the
outer shaft
44 and carries a
metal insert ring
106 which overlies and embraces a
tongue
107 formed at the upper end of the bearing means 64 interposed between the journaling bearing means 60 and the
outer shaft
44. Moreover, it will be noted that the
lower sleeve
62 is provided with an upwardly extending annular ring 108 chamfered as at 109 to provide a recess in which any fluid deflected by the
seal ring
104 will be directed between the upper and
lower sleeve members
61 and 62 of the journaling bearing means 60.
Positioned between the
bottom wall
13 and the bottom support of the spin assembly is a centering and damping means indicated as a whole by reference character 110A. Referring particularly to FIGS. 2 and 5, it will be noted that an
annular ring
110 is fastened in firm assembly with the
bottom wall
13 by means of spot welding or the like and is provided with a downwardly extending dependent flange 111.
An annular disc-shaped
member
112 having a vertically
bent flange
113 at the outer peripheral edge thereof is fastened in firm assembly to the flange 111 by a plurality of circumferentially spaced fastening means 114.
Between the upper and
lower sleeve members
61 and 62 of the journaling bearing means 60, there is provided an
annular disc member
116 vertically bent to' provide a downwardly extending ring portion 117 and generally radially outwardly bent to provide a
surface
118.
The
lower sleeve
62 is provided with an
annular boss
119 to which are attached guide keys which may take the form of a plurality of
screws
120. A
lower ring
121 having a radiallyoutwardly bent
annular disc member
122 forming a part thereof is confined for limited movement by the guide keys or screws 120 having portions slidably received in the
vertical slots
121A in
ring
121. This limited movement is desirable for the better adjustment of the frictional damping force by
springs
132, to be described hereinafter. I
The
upper disc member
118 is upwardly flared as at 123 and the
lower disc member
122 is downwardly flared as at 124, thereby leaving the space between the upper and lower disc members unobstructed.
By virtue of such provision, there are provided a plurality of friction units comprising three vertically stacked annular disc members which are concentrically outwardly of thev shaft means so that the upper and
lower disc members
118 and 122 comprise a first friction unit, and the
intermediate disc member
112 constitutes a second friction unit. Moreover, it will be noted that the journaling bearing means around the shaft are connected to the inner edges of one of the friction units thereby to afford unison tilting thereof with the shaft means of the spin assembly, whereas the outer edges of the other .of the friction units is stationarily connected to the outer stationary tub. The frictional interrelationship of the three annular disc members insures adequately damping of any eccentric wobbling action which might result from an unevenly loaded spin assembly.
To enhance the operation of the damping mechanism, a
plurality of circumferentially spaced friction pads indicated at 126- are interposed between the upper and
lower disc members
118 and 122 and the intermediate disc member 11 2. The
friction pads
126 conveniently comprise such material as leather, cork or some other material similar to a brake lining composition.
To facilitate tilting action of the spin assembly, each of the disc members 11?, 112 and 122 preferably have a spherical contour which is described by a radius extending approximately from the relatively movable surfaces of the disc members to the fulcrum point of the tiltable spin assembly. 1
In accordance with a particular feature of the present invention, the spherical contour of the disc surfaces is described by a radius approximately 10% less than the distance from the movably engaged surfaces of the disc niembers to the fulcrum point of the tiltable spin assemb y. f It will be appreciated that lengthening the radius of the spherical disc surfaces to a greater length than the fulcrum arm would also tend to give a corrective action and would be Within the scope of this invention.
In FIG. 2 there is shown by the legend Radius Arm to Fulcrum the distance from the spherical disc surfaces to the fulcrum point of the spin assembly. There is also shown by the legend Foreshortened Radius Arm the radius of the spherical disc surfaces, which radius is approximately 10% shorter than the distance from the disc surfaces to-the fulcrum point. Particularly good results have been obtained by employing a disc surface radius which is foreshortened approximately 10% of the distance from the disc surfaces to the fulcrum point of the tiltable spin assembly. It is contemplated in accordance with the principles of the present invention, however, that the amount of foreshortening could be varied from approxi- .mately 5% to an upper limit of approximately 15%.
The upper and
lower disc members
118 and 122 are clamped together by a plurality of "cincumferentially spaced resiliently biased clamping
bolts
130. Each bolt has a
head
131 engaged by the
upper disc member
118 and each bolt extends completely through the
intermediate disc member
112 and through the lower '
disc member
122. A coiled
compression spring
132 surrounds each
bolt
130 and is bottomed against the
lower disc member
122. Retainer caps 133 may be provided for the
springs
132 and the
nuts
134 are threaded on the ends of the
bolts
130 to adjust the amount of continuous and substantially constant force exerted by the
springs
132 to hold the friction limits in cooperative frictional engagement.
As is shown in FIG. 4, the
bolts
130 are circumferen- 6 tially spaced in alternate relation relative to, the
friction pads
126. Thus, the bolts 1%- are disposed intermediate the friction pads. Moreover, the
intermediate disc member
112 is provided with a corresponding plurality of
openings
136 to accommodate the
bolts
13% upon relative movement of the friction units.
Under all normal conditions of operation, it is contemplated that the centering and damping mechanism will adequately control any wobbling action of the spin assembly, however, to insure against unforeseen conditions of operation, a safety cutout is provided to deenergize the
electric drive motor
17 upon excessive eccentric wobble of the spin assembly. It will be understood that the washer is provided with the usual electric circuitry for effecting an automatic washing and extracting cycle and in this circuitry will be incorporated suitable switching means (not shown) for controlling the energization of the
motor
17. In FIG. 3 in shown a linkage to actuate the switching means, the linkage being indicated generally at 14%) and including a pivoted lever arm 141 actuated by a bar or
rod
142 normally spring biased by a
spring
143 into a position in proximity to the friction unit carried by the journaling bearing means 60. More specifically, as shown in FIG. 5, the bar or
rod
142 is slidably supported in a
bracket
144 carried by the flange 111. An
abutment
146 is carried on the end of the
rod
142 and lies in predetermined spaced relationship to the
flange
124 formed on the
lower disc member
122. Thus, if excessive gyration or wobbling of the spin assembly occurs, the
flange
124 will strike the
abutment
146 and will move the
rod
142 outwardly to pivot the pivot lever arm 141 and actuate the switching means to deenergize the
motor
17.
As shown in FIGS. 3 and 4, the
intermediate disc member
112 is provided with a plurality of circumferentially spaced
openings
150 which function as drain holes, thereby further facilitating the removal of any leakage fluid interiorly of the
rubber sealing boot
92.
In operation, the friction snubber action provided by the centering and damping apparatus herein described retains the spin assembly in a substantially stationary relation relative to the outer stationary tub. To displace the spin assembly requires a considerable displacing force even when such force is applied to the shaft near the top of the
spin basket
42 and when the spin assembly is stationary as it would be during a washing portion of the cycle of operation of the
machine
10. As soon as the spin assembly is set in rotation, however, the force required to displace the spin asesmbly is considerably reduced. These forces may be in the range of about twelve pounds and about one and one-half to two pounds.
This phenomenon is exploited in accordance with the principles of the present invention to obtain a centering action without the use of springs. 7
It would appear that the reduction in lateral reaction force resulting when the spin assembly is rotated and the curvature provided on the friction surfaces foreshortened from the actual radius arm to the fulcrum by approximately 10% results in a tendency of the spin assembly to move towards a vertical center position. Since no centering springs or continuous biasing means are substantially effective, there is no appreciable store-up of energy, and consequently, any eccentric wobbling will tend to be checked by the friction surfaces without being aggravated by a release of stored up energy. The present invention is particularly advantageous in a washing machine utilizing an agitator having a bodily eccentric or gyratory movement and in which the agitator is so moved during both the washing and spinning operations.
It has been found that the operation of the centering and stabilizing means can be improved even further by insuring that the so-called first friction unit including the upper and lower disc members are constrained to move as a unit and in such manner that the bolts will not be deflected when such movement occurs. An embodiment of this kind results in a more uniform frictional damping and which, as mentioned heretofore, has been found to be very eflicient in operation. This embodiment of the invention is illustrated in FIGS. 6 and 7, to which reference will now be had.
Referring now to FIGS. 6 and 7, it will be noted that only a part of the apparatus has been shown and parts like those in the embodiment already described have been indicated by like reference characters. The
friction disc member
112 remains the same in construction as that already described. The friction discs of the other friction units are, however, different and have been indicated by the
reference characters
200 and 202. The upper friction disc 200 is secured in what might be called a floating manner to the journal bearing means by the securing screws or
bolts
163. The floating mounting is provided by providing the central
inner portion
204 of the disc with
apertures
206 through which the
bolts
163 pass and which are provided also to receive with some slight
clearance silencing washers
208 which may be made of suitable material such as leather or rubber. The
central portion
204 of the disc 260 also has some clearance of vertical movement between the laterally extending
portions
210 and 212 of the bearing journal means 61 and 62.
The
lower friction disc
202 has a downturned
outer portion
212 and a downturned
inner portion
214, the latter of which somewhat loosely surrounds the intermediate enlarged
circular portion
216 of the journal means. The
portion
214 is free to move downwardly and around the
portion
216 and it is prevented from making too close a contact with the
portion
216 by a rubber ring 218 located in an annular groove 220' provided on the
portion
216.
The friction assemblies are separated by the
friction pads
126 as in the previously described embodiment of the invention. The
friction discs
200 and 202, however, in accordance with the present invention are tied together to move as a unit with the
bolts
130 and an annular plate indicated as a whole by
reference character
224 which ties together for unitary movement the lower ends of the
bolts
130.
The upper ends of the
bolts
130 are secured to the upper friction disc 200 by the squared
bolt portions
226. The bolts are tied to the
lower friction disc
202 by a rubber or other somewhat resilient mounting washers 223 having one end projecting through an
aperture
230 in the
disc
202. The
disc
224 is tied to the bolt by the
nuts
232 at the threaded ends of the bolts and between which the
disc
224 is securely held.
The friction disc assemblies are biased toward each other by the
springs
132, the opposite ends of which are located in the
spring receiving cups
234 and 236.
The operation of the apparatus of the second embodiment is substantially the same as that of the first described embodiment except that there is an improvement in operation. The improved operation results from the fact that the
bolts
130 are prevented from deflecting and thus compressing or alternately releasing the
springs
132. There is thus provided a substantially uniform damping force which is effective throughout the range of operation of the apparatus. In fact, the operation has been found to be so efficient that out-of-balance loads of five or six pounds will not produce excessive vibration of the washing machine.
While it will be appreciated by those versed in the art that various minor structure modifications might be suggested in connection with the preferred structural embodiments herein described, it should be understood that I wish to embody Within the scope of the patent warranted hereon all suoh modifications as reasonably and properly come within the scope of my contribution to the art.
What I desire to secure by Letters Patent of the United States is as follows:
1. In a washing machine having a bottom supported a sence gyratory tiltable spin assembly including a rotatable shaft means, means for resisting tilting of the shaft means and comprising three vertically stacked annular spherical segmental disc members concentrically outwardly of the shaft means, the upper and lower disc members forming a first friction unit and the intermediate disc member forming a second friction unit frictionally engaging the disc members of the first friction unit, journaling means around said shaft means connected to the inner edges of one of said friction units to tilt said one of said friction units in unison with the shaft means, and fastening means adapted to connect the outer edges of the other of said friction units to a stationary support, the friction unit connected to said journaling unit having a floating connection therewith.
2. In a washing machine having a bottom supported gyratory tiltable spin assembly including a rotatable shaft means, means for resisting tilting of the shaft means and consisting of three vertically stacked annular spherical segmental surface disc members concentrically outwardly of the shaft means, the upper and lower disc members forming a first friction unit and the intermediate disc member forming a second friction unit frictionally engaging the disc members of the first friction unit, journaling means around said shaft means connected to the inner edges of one of said friction units to tilt said one of said friction units in unison with the shaft means, fastening means adapted to connect the outer edges of the other of said friction units to a stationary support, and means resiliently urging said friction units into engagement with each other, said last mentioned means including a plurality of bolts passing through all the disc members in a direction substantially normal to the disc surfaces and being connected to said upper and lower disc members and spaced from the intermediate disc member, a spring surrounding each bolts and having one end acting against the outer surface of one of said upper and lower disc members and the other end against a bolt, and said bolt acting against the outer surface of the other of said upper and lower disc members, and an annular disc connected to the ends of all said bolts.
3. In a washing machine, the combination of a rotatable tub adapted to receive a liquid and material to be washed, means including shaft means for rotating said tub to extract liquid from the material contained therein, means for supporting said tub for gyratory tiliting movement about a fulcrum point adjacent the end of said shaft means, means comprising cooperating movably engaged spherical friction surfaces disposed between said tub and said supporting means adapted to resist tilting movement of said tub, said spherical friction surfaces being described by a
radius
5% to 15% less than the distance from the movably en aged surfaces to said fulcrum point.
4. In a washing machine, the combination of a rotatable tub adapted to receive liquid and material to be washed, means including shaft means for rotating said tub to extract liquid from the material contained therein, means for supporting said tub for gyratory tilting movement about a point adjacent the lower end of said shaft means, a plurality of friction units having spherical surfaces and respectively connected to the tub supporting means and stationary supporting means, bolts passing through said units engaged with only one of said units, spring means surrounding said bolts and pressing said units into frictional engagement with each other, one end of each said bolt being connected to one of said friction units, and means for tying together the other ends of said bolts to prevent deflection of them.
5. In a Washing machine, the combination of a rotatable tub adapted to receive a liquid and material to be washed, means including shaft means for rotating said tub to extract liquid from the material contained therein, means for supporting said tub for gyratory tilting movement about a point, means comprising cooperating stationary and movably engaged spherical friction surfaces and spring means acting substantially normally to said surfaces for resisting til-ting movement of said tub, said spherical friction surfaces being described by a radius of about 5% to 15% different from the distance from the movably engaged surfaces to said point.
6. In a washing machine, the combination of a rotatable tub adapted to receive a liquid and material to be washed, means including shaft means for rotating said tub to extract liquid from the material contained therein, means for supporting said tub for gyratory tilting movement about a point, means comprising cooperating stationary and movably engaged spherical friction surfaces for resisting tilting movement of said tub, said spherical friction surfaces being described by a radius substantially different from the distance from the relatively movable surfaces to said point.
References Cited in the file of this patent UNITED STATES PATENTS 1,633,039 Schenck June 21, 1927 2,035,481 Hume Mar. 31, 1936 2,161,604 Watts June 6, 1939 2,513,844 Castner et al. July 4, 1950 2,645,108 Smith July 14, 1953 2,652,710 De Remer Sept. 22, 1953 2,709,908 Altorfer June 7, 1955 2,793,757 McWethy May 28, 1957