US3214529A - Washing machine timer - Google Patents

Description

1965 F. DRUSEIKIS ETAL 3,2 4,

WASHING MACHINE TIMER Filed Dec. 21. 1961 a Sheets-Sheet 1 *1) ll 6 Q 6 I a s I INVENTOR5 FREDERICK DRUSEIKIS PAUL R. LAGONEGRO THEIR ATTORNEY 26, 1965 F. DRUSEIKIS ETAL 3,

WASHING MACHINE TIMER Filed Dec. 21, 1961 8 Sheets-Sheet 2 I! 4 INVENTORS K j be FREDERICK DRUSEIKIS A? 6 PAUL R. LAGONEGRO B C? Y Mam TH EIR ATTORNEY Oct. 26, 1965 F. DRUSEIKIS ETAL WASHING MACHINE TIMER 8 Sheets-Sheet 4 Filed Dec. 21. 1961 INVENTORS FREDERICK DRUSEIKIE PAUL R. LAGON EGRO THEIR ATTORNEY Oct. 26, 1965 F, DRUSEIKIS ETAL 3,214,529

WASHING MACHINE TIMER Filed Dec. 21. 1961 8 Sheets-Sheet 5 INVENTORS FREDERICK DRUSEIKIS PAUL R. LAGONEGRO THEIR ATTORNEY 1965 F. DRUSEIKIS ETAL 3,2 4,5 9

WASHING MACHINE TIMER Filed Dec. 21, 1961 8 Sheets-Sheet 6 {:3 70 a/a a 7 2 11 u Zr 30 i i INVENTORS FREDERICK DRUSEIKIS PAUL R. LAGONEG'RO THEIR ATTORNEY 1965 F. DRUSEIKIS ETAL WASHING MACHINE TIMER QN @i 8 Sheets-Sheet 7 FREDERICK DRUSEIKIS PAUL R. LAGONEGRO Filed Dec. 21, 1961 THEIR ATTORNEY United States Patent 3,214,529 WASHING MACHINE TIMER Frederick Druseikis and Paul R. Lagonegro, both of Rochester, N.Y., assignors to General Motors Corporation, Detroit, Mich., a corporation of Delaware Filed Dec. 21, 1961, Ser. No. 161,199 Claims. (Cl. 200-38) This invention pertains to an interval timer for a washing machine, and particularly to a timer having means for selectively varying both the fill time and the agitate time.

The timer disclosed herein embodies the drive mechanism of copending application Serial No. 161,209, filed of even date herewith in the name of Druseikis et al. and assigned to the assignee of this invention. Accordingly, the interval timer is of the type wherein time is removed from the function cams and controlled by a separate time cam which is coordinated with the function cams to obtain the necessary time pulses for carrying out the requisite functions, or cycles, of the washing machine. Accordingly, among our objects are the provision of a washing machine timer including variable time interval advance means; the further provision of a washing machine timer including separate time and function cams; the further provision of a washing machine timer including means for selecting a variable fill time interval; and the still further provision of a washing machine timer including means for selecting a variable agitate time interval.

The aforementioned and other objects are accomplished in the present invention by embodying an interruptible driving connection between the interval advance mechanism and the timer motor in combination with means actuated by the time cam for controlling the driving connection between the timer motor and the ratchet advance mechanism so as to advance the function cams at variable time intervals in accordance with a predetermined program as selected by the operator. This is accomplished by embodying a segment gear as the driving member for a pulse cam that actuates the ratchet advance mechanism, in combination with restart means engageable with the segment gear as controlled by the time cam. The means for selectively varying the fill and agitate time intervals comprises a plurality of sector members which are adapted to modify, or vary, the profile of the time cam in accordance with the program selected by the operator.

Further objects and advantages of the present invention will be apparent from the following description, reference being had to the accompanying drawings, wherein a preferred embodiment is clearly shown, and wherein similar numerals depict similar parts throughout the several views.

In the drawings:

FIGURE 1 is an enlarged top view in elevation of a washing machine timer constructed according to the present invention.

FIGURE 2 is a side view of the timer, in elevation, taken in the direction of arrow 2 of FIGURE 1.

FIGURE 3 is an enlarged sectional view taken along line 3--3 of FIGURE 2.

FIGURE 4 is an enlarged sectional view taken along line 44 of FIGURE 2.

FIGURE 5 is a view similar to FIGURE 4 with part of the ratchet broken away.

FIGURE 6 is an enlarged sectional view taken along line 6-6 of FIGURE 14.

' FIGURES 7 and 8 are fragmentary sectional views similar to FIGURE 6 showing two positions of the variable agitate mechanism.

58, constituting the on off switch for the timer.

FIGURE 9 is an enlarged fragmentary sectional View taken along line 99 of FIGURE 2.

FIGURE 10 is an enlarged sectional view taken along line 1010 of FIGURE 2, with certain parts broken away.

FIGURE 11 a fragmentary sectional view taken along line 11-11 of FIGURE 10.

FIGURE 12 is a fragmentary sectional view taken along line 12--12 of FIGURE 11.

FIGURE 13 is a progressive sectional view through the drive mechanism taken along line 13-13 of FIGURE 3, with certain parts shown in phantom.

FIGURE 14 is a fragmentary sectional view taken along line 1414 of FIGURE 4.

FIGURE 15 is a fragmentary sectional view taken along line 1515 of FIGURE 14.

FIGURE 16 is a chart of the washing machine timer cycle.

With reference to FIGURES 1 and 2, the washing machine timer comprises front and rear plates 10 and 12 with three transversely extending plates 14, 16 and 18 disposed therebetween and suitably interlocked therewith. As seen particularly in FIGURE 1, the transversely eX- tending plates 14, 16 and 18 are held in assembled relation between the front and rear plates by interfitting tongues and slots, and the front and rear plates are interconnected. As seen in FIGURE 9, a pair of terminal block assemblies 22 are suitably mounted between the front and rear plates 10 and 12, the terminal block assemblies being interlocked with the transversely extending plates 14 and 16.

As seen particularly in FIGURES 2 and 11, a rotatable and axially movable control shaft 24 is journalled in the front and rear plates 10 and 12, the shaft 24 being clutchable to a bevel gear 26 coaxial with the shaft 24 and having driving engagement with a bevel gear 28 attached to a cam barrel shaft 30 for manually advancing the same. The bevel gear 26 extends through an opening in the transverse plate 14 as seen in FIGURE 11, and has an elongate hub 32; The elongate hub 32 has an annular groove 34 that connects with a pair of diametrically opposed radial slots 36. The shaft 24 has a cross pin 38 adapted to mate with the radial slots 36 so as to interconnect the shaft 24 and the gear 26 for rotation in unison when the shaft 24 is pulled upwardly, as seen in FIGURE 11, or outwardly as seen in FIGURE 1. However, when the shaft is moved downwardly as seen in FIGURE 11, or inwardly as seen in FIGURE 1, the pin 38 is aligned with the annular groove 34 so as to interrupt the driving connection between the bevel gear 26 and the shaft 24. As seen in FIGURES l and 2, the upper end of the shaft 24 is provided with a knob 40 for manually advancing the timer. In addition, the two axial positions of the shaft 24 are determined by a hairpin spring detent 42 secured to a pair of depending lugs on the front plate 10 and engageable with either of a pair of annular grooves 44 and 46 on the shaft 24. I

As seen in FIGURE 11, the shaft 24 is formed with a shoulder, or collar, 48 which is engageable by a pair of followers 50 and 52. As seen in FIGURE 10, the follower 50 constitutes one leg of a bellcrank 54 pivoted at 56 to the transverse plate 14, and the other leg of the bellcrank 54 constitutes an actuator for a movable switch plate The movable switch plate 58 carries contact 60 engageable with a stationary contact 62. The follower 52 is formed on the end of a lever 64 pivoted at 66 to the plate 14 and biased into engagement with the collar 48 by a torsion spring 68. Screws 70 are used to rigidly interconnect the transverse plate 14 with, the front and rear plates 10 and 12, respectively, as seen in FIGURE 10.

A synchronous motor 72 is attached to the transversely extending plate 18, the synchronous motor embodying an integral gear reduction unit 74 having an output pinion 76, FIGURE 3, which rotates at a constant speed. The pinion 76 is engageable with a segment pulse gear 78 rotatably supported on a stud 80 carried by the plate 18. The segment gear 78 has teeth removed from its periphery leaving toothless diametrically opposed portions 82 so that when either of the toothless portions 82 is aligned with the pinion 76, the driving connection between the segment gear 78 and the pinion 76 is interrupted. In the specifically disclosedembodiment, a reduction is effected between the pinion 76 and the segment gear 78 such that when the pinion 76 engages the toothed portion of the gear 78, the gear 78 will be rotated one-half revolution every twenty seconds, which constitutes the lowest time interval advancement limit.

A double rise pulse cam 84 is formed integral with the segment gear 78, the pulse cam 84 being engaged by a follower, pivotally mounted on a stud 88 supported by the plate 18 and having an'extension spring 90 connected between the leg 92 of the follower and an anchor lug 94 struck out from the plate 18. The drive mechanism is enclosed by the front and rear plates 10 and 12, and a pair of plates 96 and 98 which are suitably interlocked with the transverse plates 16 and 18.

The motor pinion 76 has continuous meshing engageinent with an idler gear 100 journalled on a stud 102 supported by the plate 18. A cam follower 104, in the form of a lever, is also pivotally mounted on the stud 102. An adjustment plate 106 is likewise pivotally mounted on the stud 102 and carries a stud 108 on which a restart pinion 110 is journalled. The restart pinion 110 is movable into and out of engagement with the segment gear 78 under the control of a follower portion 112 that is resiliently maintained in engagement with a time cam 114 by a hairpin torsion spring 116. As seen in FIGURE 13, the follower lever 104 has elongate holes 118 and 120 which receive the studs 102 and 108, respectively, and is interlocked for rotation about the stud 118 with the adjustment plate 106. The adjustment plate 106 carries a first screw 122 which bears against the lever 110 for adjusting the position thereof relative to the stud 118 and the time cam 114. The adjustment plate 106 carries a second screw 124 which is engageable with a lug struck out from the plate 98 and constituting a stop limiting counterclockwise pivotal movement of the cam follower lever 110 under the urge of the spring 116.

The idler gear 100 meshes with a time gear pinion 126 attached to a shaft 128 journalled on the plates 16 and 18. As seen in FIGURES 4 through 6, a worm 130 attached to the shaft 128 meshes with a worm gear 132 integral with a transversely extending worm shaft 134 suitably journalled between lugs struck out from the p ate 16. The worm shaft 134 meshes with a time gear 136, FIGURE 6, which, as seen in FIGURE 14, is attached to a sleeve 138 journalled on the cam barrel shaft 30. As seen in FIGURE 9, a plurality of axially spaced function cams 140 are mounted on a knurled portion of the cam barrel shaft 30 so as to rotate therewith. The cams 140 are adapted to sequentially operate a plurality of switches 141 carried by the terminal board assemblies 22.

A bushing 142 is journalled on the sleeve 138, and the time cam 114 is rigidly attached to the bushing 142 by staking 144. The time cam 114 has an axially extending lug 146 projecting through an elongate arcuate slot 148 in a ratchet wheel 150 staked at 152 to the cam barrel shaft 30. As seen in FIGURES 4, and 14, the elongate arcuate slot 148 permits the time cam 114 to advance relative to the ratchet wheel 150 throughout an angle greater than the arcuate distance of a tooth on the ratchet wheel. This arrangement constitutes a lost motion connection which determines the highest time interval advancement limit. In the specifically disclosed embodiment the ratchet wheel has thirty equally angularly spaced teeth 153 on its periphery, and thus the teeth are spaced 12 apart. The bushing 142, and hence the time cam 114, is drivingly connected to the time gear 136 through a spring-type friction clutch 154 which, as shown in FIGURE 15, is keyed to the bushing 142 and has a plurality of spring arms disposed in a face groove 156 of the time gear 136. The time gear 136, the sleeve 138 and the bushing 142 are biased downwardly, as viewed in FIGURE 14, relative to the plate 16 by a leaf spring 158 so as to maintain snap ring 160 in engagement with the plate 16. A second snap ring 162 engages the sleeve 138 and the bushing 142 to prevent disassembly thereof.

The friction clutch 154 between the gear 136 and the bushing 142 enables the bushing 142 and the time cam 114 to be rotated by the ratchet wheel 150 when the end 148a of the slot 148 engages the tang 146 on the time cam 114 as seen in FIGURE 4. It is to be understood that the ratchet wheel 150 is driven in the counterclockwise direction as viewed in FIGURE 4, and the time, gear 136 is also capable of driving the time cam 114 in the counterclockwise direction through the spring friction clutch 154 as will be described hereinafter.

A disc 164 is journalled on the hub 142 between the time cam 114 and the time gear 136. The disc 164 is formed with a toothed shoulder 166 constituting a gear. As seen in FIGURES 6 through 8, the disc 164 is integral with a lever arm 168 which extends radially therefrom and projects through a slot in the front plate 10 of the timer. As seen in FIGURES 6 through 8 and 14, a pinion gear 170, having an integral stud 172 journalled in an opening in the time cam 114, has continuous meshing engagement with the gear teeth 166 on the disc 164. The gear is integral with an arcuate cam segment 174 which subtends an angle of substantially the purpose of which will be pointed out more particularly hereinafter.

As seen in FIGURES 4 and 5, a pair of bellcranks 176 and 178 are also pivotally mounted on the time cam 114, each of the bellcranks 176 and 178 having an arcuate lug portion 180 and 182, respectively, the purpose of which will be pointed out hereinafter. The bellcranks 176 and 178 are normally biased in the clockwise direction against stop pins 184 and 186, respectively on the time cam 114 by torsion springs 188 and 190, respectively. An actuating lever 192 is pivotally mounted on a stud 194 supported by a struck out lug from the front plate 10, which lever is adapted to coact with the bellcrank 176 and 178 at predetermined angular positions of the time cam 114 to effect pivotal movement thereof in a manner to be described.

Referring again to FIGURE 3, the cam follower 86 carries a drive pawl 196 for advancing the ratchet wheel 150 in a step by step manner. The pawl 196 is pivotally mounted on a stud 198 and biased into engagement with the teeth 152 on the ratchet wheel by a torsion spring 200. As is apparent, during rotation of the pulse cam 84 by the gear 78, the extension spring 90 will be stressed, or energy stored therein, as the follower 86 engages a rise on the pulse cam 84 so as to effect counterclockwise pivotal movement of the follower about the stub shaft 88. When the follower engages the sharp fall on the pulse cam 84, the extension spring will immediately effect clockwise pivotal movement of the follower 86, as viewed in FIGURE 3, so as to advance the ratchet wheel 150 throughout a distance of one tooth, or in other words, 12. Angular movement of the ratchet wheel 150 will impart angular movement to the cam barrel shaft 30 and the function cams 140. If the tang 146 on the time cam 114 is in engagement with the end 14811 of the slot 148, as seen in FIGURE 4, the time earn 114 will also be \advanced throughout an angle of 12. However, if the tang 146 is not in engagement with the end 148a of the slot 148, it may be advanced less than .Referring to FIGURE 1, the agitate time interval adjustment lever 168 is engaged by one end of a torsion spring 202, the intermediate portion of which encircles a stud 204. The fill adjustment lever 192 is engaged by a spring arm 206, which is biased by a torsion spring 208 which encircles a stud 210. The other leg of the tonsion spring 208 engages the stud 204. The levers 168 and 192 are biased to their normal positions, namely, full length agitate period and full length fill period. The agitate adjustment lever 168 can be move-d to select various agitate time intervals, while the fill adjustment lever is of the two-position type and can be adjusted for regular fill or short fill.

Referring to the chart of FIGURE 16, the timer is designed to control a washing machine through a wash cycle and a soak cycle. During the wash cycle, both the initial fill time and the agitate time can be varied by manipulation of levers 192 and 168, respectively. Thus in one position of the fill lever 192, the machine will be filled for a period of three minutes, and in a second position it will be filled for a period of four minutes. On the other hand, the agitate lever 168 may be adjusted to select a period of agitation having a minimum of one minute or a maximum of nine minutes and forty seconds. Likewise, during the soak cycle, the fill time may be regulated so as to be short, i.e., three minutes or regular, i.e., four minutes. The remaining variables in the wash and soak cycles are determined by selectors other than the drive mechanism of the timer, per se.

With reference to FIGURES 3 through 8, the manner in which the timer operates in combination with the variable agitate and variable fill controls will be described. When the motor 72 is energized by pushing the knob 40 inwardly to close the switch contacts 60 and 62, the motor driven pinion 76 will be rotated in a clockwise direction at a constant speed. The pinion 76 constantly drives the time gear 136 through the gear reduction at a speed of one-third rotation per hour, for example. The time cam 114 will be driven through the spring friction clutch 154 at the same speed as the time gear 136, namely one-third revolution per hour, or two degrees per minute in the clockwise direction as seen in FIGURE 3, or the counterclockwise direction as seen in FIGURES 4 through 8. As long as the motor driven pinion 76 is aligned with a toothless section 82 of the pulse gear 78, and the restart pinion 110 is disengaged from the pulse gear 78, the pulse gear remains stationary. The restart pinion 110 is maintained disengaged from the pulse gear 78 when the follower 112 engages rise 115 on the cam 114. The rises 115 are of varying angular extent as can be seen in FIGURES 4 through 8, and are spaced apart by dwells which are likewise of varying angular extent. In FIGURE 3, the restart pinion 110 is shown in meshing engagement with the pulse gear 78, and under these conditions the cam barrel shaft 30 will be advanced by the ratchet wheel 150 at twenty-second intervals. However, when the follower 112 engages rise 115 on the time cam 114, the ratchet wheel 150 will not be advanced, and accordingly, the cam barrel shaft 30 and the function cams 140' will remain stationary.

It is to be understood that the rises and dwells on the time cam 114 are designed to carry out a specific cycle as shown on the chart in FIGURE 16. Referring particularly to FIGURES 4 and 5, when the variable fill lever 192 is pivoted in the counterclockwise direction, the inner end 193 thereof will engage one or the other of the bellcranks 176 and 178 at a predetermined angular position of the time cam 114 and effect counterclockwise pivotal movement thereof such that the lug 180 or 182 will be moved out of alignment with a rise 115 on the time cam thereby resulting in a short fill period. With 6 the fill lever 192 in the position shown in FIGURES 4 and 5, it can be seen that the sharp fall on one of the rises 115 of the time cam is extended by the lug and.

thus causing delay in the advancement of the function cams by the ratchet advance mechanism for a period of time equal to one minute.

Referring to FIGURES 6 through 8, angular movement of the variable time agitate lever 168 and its disc 164. will result in rotation of the pinion gear 170 and its, arcuate flange 174 relative to the time cam 114. The pinion 170 and the arcuate flange 174 are properly oriented relative to the time cam 114 so that in the normal position, as indicated in FIGURES 6 and 7, the flange 174 will intercept the follower 112 for controlling the restart pinion so as to interrupt the driving connection between the motor driven pinion mechanism and the pulse cam for a period of nine minutes. It will be understood that the pinion gear 170 by reason of its meshing engagement with the gear teeth 166 will continuously rotate about its axis during rotation of the time cam 114. However, upon angular movement of the agitate lever 168 and the disc 164, the angular orientation of the flange 174 can be adjusted relative to the time cam 114 so as to vary the time interval of agitation in twenty second intervals from sixty seconds to nine minutes and forty seconds.

From the foregoing it is apparent that the timer construction disclosed herein is capable of adaption to various wash and soa cycles of clothes washing machines without encountering critical switching conditions since the function cams remain stationary during the timing intervals. For this reason a greater number of functions can be performed with a fixed cam diameter, and critical tolerances can be substantially reduced since the increment of angular advance of the ratchet mechanism can be appreciably increased. In addition, the respective intervals of various functions can be manually controlled at the will of the operator in a simple manner thus increasing the versatility of the instant timer construction without increasing the complexity of the component parts.

While the embodiment of the invention as herein disclosed constitutes a preferred form, it is to be understood that other forms might be adopted.

What is claimed is as follows:

1. A washing machine timer including, a timer motor, a time gear driven by said timer motor, a time cam drivingly connected to said time gear but capable of movement relative thereto, a plurality of function cams, a pluralityof switches actuated by said earns, a pulse gear having an interruptible driving connection with said timer motor, a pulse cam driven by said pulse gear, ratchet advance means operable to impart step by step movement to said function cams and actuated by said pulse cam, said time cam having a lost motion driving connection with said ratchet advance means, and means actuated by said time cam for controlling the interruptible driving connection between said pulse gear and said timer motor to obtain time intervals each of which is inde pendently variable within predetermined lower and upper limits between the step by step advancement of said function cams in accordance with a preselected program.

2. The washing machine timer set forth in claim 1 wherein one of said function cams comprises an agitate cam, and wherein said timer includes a manually operable means to vary the interval of advancement of the agitate cam.

3. The washing machine timer set forth in claim 2 wherein said time cam comprises a disc having a plurality of circumferentially spaced rises and dwells thereon, and wherein said last recited means comprises a manually adjustable flange for varying the effective angular extent to a rise on said time cam to control the interval of advancement of the agitate cam.

7 4. The Washing machine timer'set' forth in claim 1 wherein one of said function cams constitute a fill'cam, and wherein said timer includes manually operable means for varying the interval of advancement of the fi-ll cam. 5. vThe washing machine timer set forth' in claim 4 wherein said timecam comprises a disc having a plurality of circumferentially spaced rises and dwells thereon, and wherein said last recited means comprises at least one lug pivotally mounted on said time cam and manually of a rise to control the interval of advancement of the fill cam.

5 References Cited by the Examiner UNITED STATES PATENTS v 1,542,400 6/25 Ter Meer 74 12 5.5 2,236,297 3/41 Reid 74-568 v2,555,408 6/51 Horner 74-125- X 2,959,646 11/60 Martin t 74 568 X adjustable to a position for varying the angular extent 10 BROUGHTON G DURHAM, Primary Examine}.

Claims (1)

1. A WASHING MACHINE TIMER INCLUDING, A TIMER MOTOR, A TIME GEAR DRIVEN BY SAID TIMER MOTOR, A TIME CAM DRIVINGLY CONNECTED TO SAID TIME GEAR BUT CAPABLE OF MOVEMENT RELATIVE THEREOT, A PLURALITY OF FUNCTION CAMS, A PLURALITY OF SWITCHES ACTUATED BY SAID CAMS, A PULSE GEAR HAVING AN INTERRUPTIBLE DRIVING CONNECTION WITH SAID TIMER MOTOR, A PULSE CAM DRIVEN BY SAID PULSE GEAR, RATCHET ADVANCE MEANS OPERABLE TO IMPART STEP BY STEP MOVEMENT TO SAID FUNCTION CAMS AND ACTUATED BY SAID PULSE CAM, SAID TIME CAM HAVING A LOST MOTION DRIVING CONNECTION WITH SAID RATCHET ADVANCE MEANS, AND MEANS ACTUATED BY SAID TIME CAM FOR CONTROLLING THE INTERRUPTIBLE DRIVING CONNECTION BETWEEN SAID PULSE GEAR AND SAID TIMER MOTOR TO OBTAIN TIME INTERVALS EACH OF WHICH IS INDEPENDENTLY VARIABLE WITHIN PREDETERMINED LOWER AND UPPER LIMITS BETWEEN THE STEP BY STEP ADVANCEMENT OF SAID FUNCTION CAMS IN ACCORDANCE WITH A PRESELECTED PROGRAM.

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