US3142641A

US3142641A - Zero locking system for centrifugal apparatus

Info

Publication number: US3142641A
Application number: US81571A
Authority: US
Inventors: Remy J Lachat
Original assignee: Whirlpool Corp
Current assignee: Whirlpool Corp
Priority date: 1961-01-09
Filing date: 1961-01-09
Publication date: 1964-07-28
Anticipated expiration: 1981-07-28

Description

3 Sheets-Sheet 1 R. J. LACHAT ZERO LOCKING SYSTEM FOR CENTRIF'UGAL APPARATUS July 28, 1964 Filed Jan. 9, 1961 INVENTOR. REMY J* LACHAT ATTORNEYS R. J. LAcHAT 3,142,641 zERo LOCKING SYSTEM FOR CENTRIFUGAL APPARATUS July 28, 1964 5 Sheets-Sheet 2 Filed Jan. 9, 1961 INVENTOR. REMY J. LACHAT @y QL* ATTORN EYS 3,142,641 ZERO LOCKING SYSTEM FoR CENTRIFUGAL APPARATUS Filed Jan. 9, 1961 l R. J. LACHAT July 28, 1964 3 Sheets-Sheet 3 l' |l h Il Ll INVENTOR. REMY J. LACHAT Y* ATTORNEYS www United States Patent O Filed Jan. 9, 1961, Ser. No. 81,571 7 Claims. (Cl. 21o-144) The present invention relates broadly to apparatus for counterbalancing unsymmetrically distributed centrifugal forces in a rotating body as exemplified by a substantially horizontal axis type laundry drum, and is more particularly concerned with novel means for assuring that the counter-balancing system is accurately indexed prior to initiation of drum high speed rotation and before and after any bodily movements of the laundry appliance.

Various ways have been proposed to shorten the drying time of the washing and drying cycles of a domestic laundry appliance as exemplified by an automatic washer or combination washer-dryer. One approach is to increase the drying heat input to the dryer, however, this is disadvantageous in View of the power requirements, as well as from the standpoint of engineering design considerations which are required because of the increased power input to the drying means.

A second and preferred approach is to increase the rotative cylinder speed used during the extraction part of the wash cycle, thereby removing larger amounts of water from the load prior to the beginning of the tumble drying in the machine or line drying of the load. This accomplishes a power consumption savings of the order of approximately eight to fteen times as compared with the high power input drying process. However, it frequently occurs that when a load is introduced into a laundry receiving cylinder or drum and the drum rotated at relatively high speeds, the load distributes itself in such a manner that the center of mass of the loaded cylinder does not coincide with the cylinder bearing axis. As a result, there is produced an unbalanced centrifugal force which is directly proportional to the mass of the unbalanced portion of the total rotating mass, the square of the angular velocity of such unbalanced mass, and to the radius of the unbalanced mass from the axis of rotation of the cylinder.

To overcome the unbalancing problem, it has been proposed to limit the spin speed of the horizontal axis type drum so that unbalanced loads encountered during normal operation do not produce a suicient amount of centrifugal force to cause serious machine vibrations, which at times may be suicient to actually lift the machine frorn its supporting surface and produce a violent movement colloquially referred to as walking Other solutions to the problem which have been proposed include control means which deactivates a spin mechanism in response to the excessive motion in the apparatus, so that the drum or cylinder decelerates to a tumbling speed for redistribution of the contents thereof. Such an arrangement can readily be appreciated to be disadvantageous since less liquid is centrifugally extracted from the contents of the drum or cylinder than is desired, and in consequence, a longer drying period is required, whether or not machine or line-drying is utilized.

There is also within the prior art disclosures suggestions of the use of suspension systems to suspend the entire laundry machine along with an additional mass producing dead weight within an enclosing cabinet on a complex spring system. Quite clearly when this approach is used there is required an enclosing cabinet of greatly increased size to allow for the violent gyratory motions of such a system during operation of the machine or if the cabinet size is limited the machine drum or cylinder must be reduced in size to the extent that the drum capacity is too small to accomplish quality Washing and drying operations on normal loads.

In one construction wherein markedly improved results are obtained a casing is rigidly supported upon a base frame and a drum is mounted within the casing for rotation and vibratory movements relative to the base frame. In such a machine, a plurality of liquid balance compartments are disposed on the periphery of the drum, and the vibratory movements of the drum or cylinder are sensed by a movable deflector member or by a movable iuid introduction nozzle to control the addition of counterbalancing liquid to a particular liquid balance pocket or pockets.

The counterbalancing control means for such a machine must be indexed or coordinated with respect to the pockets and their respective collector segments to assure addition of counterbalancing fluid to the proper pocket or pockets during the counterbalancing of the drum at precisely the correct time. Usually, any machine movements either by shipment from the factory or by change of location of the machine by the user have tended to destroy the original critical adjustment of either the pivoting deflector or the pivoting nozzle. The services of a technician at the site of installation of the machine were then usually required, necessitating a partial dismantling of the machine in order to restore the control means to a proper or zero indexed position.

In accordance with this invention there is provided what may be termed a self compensating or zero locking system, This zero locking system functions to assure that whenever the drum is to be rotated at high spin speeds, the correct dimensional relationship will always exist between the balance fluid collector segments and the balance liuid deiiector or pivoting nozzle even if the machine is moved from one location to another between machine operating cycles. This system desirably embodies pivotal stop means carried upon a common shaft with the deiector or nozzle, the stop means originally being adjusted to a zero position at the factory or similar situs. The stop means in an illustrative embodiment of this invention is normally contacted by a friction detent or brake member which is released when the access door to the drum is opened, or when other suitable release means is actuated. The friction detent is pivotally supported by casing structure, and when released, moves suiciently to restore the stop means to its original zero or indexed position. Closing of the access door or actuation of other release means applies a braking or holding force to the friction detent, and thereby assures that when the counterbalancing action is initiated, the deiiector or nozzle is in its original zero or indexed position with respect to the water balance pockets on the drum periphery.

It is accordingly an important 'aim of the present invention to provide improved counterbalance control means for ia rotating receptacle.

Another object of the instant invention is to provide a balancing system for a laundry apparatus wherein the laundry liquid may be effective-ly utilized as a balancing fluid.

Still another object of this invention lies in the provision of a balancing system for `a rotatable receptacle provided with fluid receiving counterbalancing pockets thereon, and wherein there is provided means in control of the addition of fluid to the pockets to effect counterbalancing, as well as means controlled by movements of the access door to the receptacle and interconnected between the receptacle mounting means and the fluid addition control means for automatically indexing Ithe control means with respect to the pockets tto assure addition of counter-balancing fluid to the proper pockets during the counte-rbalancing of the receptacle. v

A further object of the present invention is to provide an automatically self compensating indexing or zero locking system of the foregoing character, which has utility with balancing systems of various types, and which is constructed of relatively few comparatively simple parts of high reliability.

Other objects `and advantages of the invention will become more apparent during the course of the following description, particularly when taken in connection with the accompanying drawings.

In the drawings, wherein like numerals designate like parts throughout the same:

FIGURE l is a side elevational View, with parts removed yand with parts taken in section, to more clearly illustrate the self compensating indexing or zero locking system of this invention;

FIGURE 2 is a rear elevational view from which parts have been removed to show in further detail a laundry machine embodying the control means and indexing means of this invention;

FIGURE 3 is an enlarged elevational view of the control and indexing structure;

FIGURE 4 is an enlarged elevational View, with parts thereof taken in section and with other parts eliminated, showing more fully the locking system as it appears in FIGURE l;

FIGURE 5 is a bottom plan view of the friction detent and release means therefor constituting a part of the control means and indexing means herein provided',

FIGURE 6 is a detail view of the access door hinge structure and the brake release structure associated therewith;

FIGURE 7 is a sectional View, with parts thereof in elevation, illustrating further details of the access door latch means and the cam and cable structure employed in connection therewith; and

FIGURE 8 is a sectional view taken along the line VIII-VIII of FIGURE 2 with some parts eliminated to more clearly show a second embodiment incorporating a pivoting nozzle.

Referring now iirst to FIGURES l and 2, there is shown and designated generally by the numeral 1t? a domestic laundry appliance which may take the form of a so-called combination washer-dryer. Certain structural portions of the laundry appliance have been omitted in the interest of clarity of illustration and since such portions are not essential to the present invention.

In the exemplary structural organization shown, the machine 10 is provided with a base plate or support structure indicated at 11. The exterior cabinet members are mounted on the support structure 11 to form a complete aesthetically appealing enclosure for the machine 10. The front wall provides access such -as at 12 by means of which a batch of materials to be laundered may be placed in or withdrawn from a treatment zone formed within the machine 10.

The support structure 11 is supported upon front and

rear legs

13 and 14, and upon the base portion there is lixedly but resiliently mounted a supporting structure or pylon member designated at 15, and which may take the form of a pair of spaced

uprights

15a and 15b having a cross member 21. The base portion of the cabinet 11 further ixedly supports a casing 16 spaced within the enclosure cabinet, and shaped along its lower portion as indicated in FIGURE 2 to provide a sump 16a.

Mounted for rotation within the casing 16 and for vibratory movement relative to the supporting structure 11 and casing 16 is a perforated drum or cylinder I7 having a passaged front wall 17a and closed rear wall 1'7b connecting generally centrally thereof with shaft means 18 received at its opposite end in xed bearing means 19 encased in a bearing Ahousing 2t). The bearing housing 2t) is attached in any suitable manner to the generally horizontal pylon cross member 21 connected at its opposite ends to the

upright members

15a and 15b, and constituting the herein provided means for mounting the drum 17 for rotation within the casing 16 and for vibratory movement relative to the casing 16 and support structure 11. As will be later described in further detail, rotation of the drum 17 with an unbalanced load therein causes the pylori member 21 to vibrate in opposed horizontal directions as indicated by the arrows 22, and in the absence of the application of counterbalancing forces, such vibration may be suiicient to cause the machine 10 to actually walk upon the floor. This situation can exist whether or not a supporting structure of the character indicated at 15 is employed, and it can accordingly be appreciated that the supporting means 15 can take the form of :an A-frame or other basket or drum mounting arrangements,

The drum or basket 17 is further provided with recess means at a plurality of circumferentially spaced points on its periphery' to accommodate mounting in such recesses a liquid balancing receptacle, of which three are provided in the illustrative embodiment shown and designated therein by the numerals 23a-c. Each balancing receptacle is of essentially identical construction and comprises a generally trough-shaped tray member having a wall 2d spaced radially outwardly of an imperforate wall portion 25 formed on the drum 17 at the recessed area. Each receptacle 23a-c further includes side walls 26, and in the generally diagrammatic showing of FIGURE l, front and rear walls 27 and 28.

Illustratively, the receptacles 23a-c and injection intake structure therefor may be constructed in the mam ner indicated in FIGURES l and 2. The rear Wall 28 of each receptacle 23 and rear wall 17h of the drum 17 may be passaged to receive a connector member 29 in lluid receiving communication with an inlet assembly generally designated by the numeral 32 having an inner diameter 32d, and desirably provided by a generally U-shaped ring member divided as at 33 to provide three inlet segments 32a-c extending through 120 of arc on the rear wall 17b ofthe drum 17.

The drum 17 is rotatably driven within the casing 16 1n any desired manner, and illustratively there may be provided motor means 39 provided with a shaft 40 mounting pulley means 41 about which is trained a belt 42 also wrapping a pulley 43 on the drum drive shaft 18. Desirably the motor means 39 connects with transmission means having low and high speed capabilities, and shifting or clutching means preferably form a part of the transmission means in order that continued acceleration of the basket or drum 17 can be terminated during counter-balancing. This, however, forms no part of the instant invention and the details thereof are accordingly not illustrated.

FIGURES 1 and 2 show a first embodiment of a water or fluid balance system used with this self compensating or indexing zero locking system which incorporates a pivoting detlector. In this system a nozzle assembly 45 having a nozzle outlet 45a is firmly mounted in the rear wall 16h of the casing 16 and is targeted or directed to deliver a stream of balancing Huid to the collector segments 32a-c on the rear wall 17 b of the drum 17 Whenever this stream is not interrupted. A pivoting control member 46, which pivots as a result of vibrations or deiiections of the drum 17 and pylon cross member 21 due to the spinning of an unbalanced load in the drum 17, includes an enlarged end portion 46a. This end portion when in its neutral position will interrupt the stream of balancing fluid emanating from the nozzle outlet 45a and deflect it back into the sump 16a from Where a pump (not shown) will return the uid back to the nozzle assembly 45 during the extraction of high speed spin cycle.

During the extraction cycle with an unbalanced load present, the control member 46 will pivot, as later eX- plained in detail, up and down with deflections of the pylon cross member 21 such that when deliections of the cross member 21 are to the left of the vertical centerline as shown in FIGURE 2 the control member 46 will move upwardly to move end portion 46a above the fluid stream emanating from the nozzle outlet 45a and allow this fluid to pass into the proper inlet segment or segments from where it will pass into the proper balance pocket or pockets to counterbalance the unbalanced load, causing the forced oscillation of cross member 21.

FIGURE 8 shows a second embodiment of a iiuid balance system very similar to the rst embodiment of FIG- URES l and 2 except that in this embodiment the nozzle assembly 45 is iirmly mounted in the end portion 46a of the control member 46. A predetermined deflection to the left of the pylon cross member 21 will allow the end portion 46a to carry the nozzle outlet 45a so that the balancing uid will pass over the top of the inner diameter 32d of the collector segments and into the proper collector segment or segments for delivery to the proper balance pocket or pockets. Clearance is provided in the rear Wall 1612 of the casing 16 to allow for the movements of the nozzle assembly 45. Both embodiments respond identically to the deflections of the drum and pylon cross member.

For either of the fluid balance system embodiments to function properly, it is vitally important that precise relationships exist at all times between the deilections of the drum 17 and pylon cross member 21 and the pivotal movement of the control member 46. Adjustment of the control member 46 must be such that in the iirst embodiment, that is, the pivoting deilector or interrupter system, the end portion 46a of the control member 46 will move upward out of the path of the balancing fluid emanating from the nozzle outlet 45a at a predetermined deflection or amplitude of vibration of the drum and pylon cross member to the left of the machine vertical centerline. This illustrative adjustment, which was determined and veriiied under test conditions, will allow the balancing uid to enter the proper balance pocket or pockets to counterbalance the unbalanced load producing the deflections while using a minimum volume of balancing uid. The adjustment for the second embodiment, that is, the pivoting nozzle uid balance system, is the same as for the rst embodiment except that in this case the end portion 46a must lift the iiuid stream emanating from the pivoting nozzle outlet 45a above the inner diameter 32d of the collector segments 32a-c at the precise predetermined amplitude of vibration to the left of the vertical centerline of the machine of the drum and pylon cross member.

The aforementioned adjustment is so important that if means are not built into the machine to assure this proper adjustment at all times, the fluid balance system may become much less effective or even compeltely inoperative when this adjustment is upset either by moving the machine or by a poor original adjustment,

Such problems are herein effectively eliminated by the provision of a zero locking system embodying means controlled by movements of the access door 12 and interconnected between the casing rear wall 16h and con trol member 46 for automatically indexing the control means to the proper adjustment with respect to the inner diameter 32d of the collector segments 32a-c to assure addition of counterbalancing uid to the proper balance pockets during the counterbalancing of the receptacle 17.

The zero locking system of this invention is designated generally in the drawings (FIGURES 1 and 2) by the legend S, and may be seen to comprise a generally channel-shaped bracket member 5t) having outwardly turned ange portions 51 (FIGURE 3) secured by a fastening means 52 to a wall portion 21a of the `plyon cross member 21. The pylon cross member 21 may be seen to be further formed with upright wall portions 2lb and 21C, the later wall portion extending a relatively short distance downwardly between casing rear Wall 1Gb and rear Evallstla of the generally channel-shaped bracket mem- The bracket member 5t) is shaped to provide outwardly extending

wall portions

50b and 50c, and secured to the rear wall 50a of this bracket member by adjustable fastening means 53 is a generally U-shaped plate member 54. The plate member 54 is formed with a relatively flat wall portion 54a lyng flush against the bracket member rear wall 50a, and the plate member rear wall 54a is slotted at 55 to receive the fastening means 53 for a purpose to be shortly described. The plate member 54 is further constituted by a pair of spaced wall portions 5412 and 54C extending outwardly at generally right angles to the rear wall portion 54a, and the end walls 54h and 54C are apertured to receive control member 46 adjusting means 56, the purpose of which will also shortly be described.

The control member 46 is nonrotatably carried upon shaft means 57 extending through an apertured embossment 5S formed in the rear wall 16h of the casing 16. The shaft means 57 may be observed to be provided with a stepped outer diameter, and this shaft is mounted for rotation in a collar member 5g having a ange portion 59a thereon bearing against the front surface of the rear wall 50a of the bracket means 56. The flange 59a of the collar member 59 is securely attached by any convenient method to the rear wall Sila of the bracket member 5t). The opposite end of the collar member 59 forms a thrust bearing surface for the body portion 60a of stop or driven means 66, and it is to be noted that the stop means 60 is connected to the shaft 57 by fastening means 61 which may take the form of a screw threadably received in the shaft 57.

The body portion 60a of the stop means 60 is of generally flat configuration and extending forwardly from the body portion is a pair of spaced ear portions 60h and 60e, the latter ear portion being in contact with the end wall 54e of the plate member 54 when the control member 46 is in a zero indexed or neutral position with respect to the balancing receptacles 23 and their collector segments. It may accordingly be observed at this point that positioning of the plate member 54 through the adjusting means 56 and locking means 53 determines the proper position or adjustment of the control member 46, with regard to the inner diameter 32d of the collector segments.

The stop member 60 is maintained in abutment with the plate member 54 after the original zero adjustment, and returned to abutting contact therewith during swinging of the deflector member 46 by provision of spring means 62 connected to the body portion of the stop member 60 and to the end wall Stb of the bracket member 50. As a further structural feature of the stop member 6) the body portion 66a thereof is downwardly extended to provide an end portion 60d against which bears a rearwardly extending lange portion 63a formed on a tab por-tion 63b of a lever member 63.

The lever member 63 is pivotally connected at 64 to a more or less channel-shaped bracket member 65 (FIG- URE 5) having a wall portion 65a welded or otherwise secured to the casing rear wall 1617 which in turn is rigidly connected to base plate 11. Spring means 66 connected between the lever member tab portion 63b and the end wall Stic on the bracket member 50 resiliently automatically takes up any lost motion between

members

60 and 63 by maintaining the lever member 63 in abutting contact with the end portion 66d on the stop member 60. As will be more fully noted later, the spring force applied by the spring means 62 is greater than the force of the spring means 66, so that the stop member 60 is returned to abutting contact with the plate member 54,

27 thereby automatically maintaining the indexed position of the deflector member 46.

The lever member 63 is shaped to provide an extended main body portion 63C, and one end of the body portion of the lever member is elampingly engaged during the entire high spin speed extraction cycle by a brake or friction detent means generally designated by the numeral 67. The friction detent means 67 may be provided by 0pposed friction shoe members 67a and 6711, the friction shoe member 67a being stationarily mounted by a wall portion 65h formed on the bracket means 65. The friction shoe member 67b, on the other hand, is movably carried by leg portion 63a of a lever arm 63 pivotally supported at 69 upon a tab portion 70 forming a part of or attached to wall portion 65e of the bracket member 65. The means attaching the brake or shoe member 67h to the lever leg portion 68a may of course take various forms, and illustratively the fastening means 71 may be a cotter pin.

As appears in FIGURE 5, the lever arm 68 is shaped to provide a second leg portion 68h and connected to one side of this leg portion is firs-t spring means 72, also attached to Wall portion 65d on the more or less channel-shaped bracket means 65. The lever arm leg portion 6817 further has attached thereto second sring means 73 connected at its opposite end to a coupling member 74. As will be later described, the first spring means 72 is effective when the tension in cable 75 is reduced by opening access door 12 so as to allow lever arm 68y to swing clockwise as shown in FIGURE to release the brake means 67, thereby permitting the lever arm 63 to pivot about its connection 64 to the bracket means 65, so that the spring means 62 can always restore the stop member 60 and connecting control member 46 to a zero or properly pre-adjusted indexed position with respect to the inner diameter 32d of the collector segments. The second spring means 73, on the other hand, functions to take up slack in cable means 75 connected to the access door hinge in a manner to be later fully described. Accordingly, the spring means 73 normally is characterized by a relatively greater spring force than the spring means 72.

The cable means 75 is shown in FIGURE 5 as connected to the coupling member 74, and substantially entirely along its length the cable 75 is received in a stationary conduit 76. The conduit 76 extends along the casing rear wall 16b and along casing side wall 16e (FIG- URE l) to the casing front wall 16a, and along said wall to the access door hinge. Of course, the path taken by the conduit 76 may be dilferent from that indicated, however, in the illustrative embodiment shown, the conduit 76 is supported by the casing structure by grommets or the like 77 (FIGURE 5) attached by fastening means 78 to bracket means 79 suitably attached to the casing walls or other appropriate structure.

The access door 12 in FIGURE l is indicated as of the vertically opening type, however, the instant invention is of course of equal utility with a horizontal opening type door. Referring now to FIGURES 6 and 7, the cable means 75 is connected to a cam follower lever member 80 mounted by a shaft member 81 received at opposite ends in

wall portions

82a and 82b of bracket means 82, which may be formed as a part of the casing front wall structure or may be a separate member welded or otherwise attached thereto.

The access door 12 is supported from two of the bracket means 82. It is necessary that only one of the bracket means 82 contain the cam follower lever member 8). The bottom wall 82C of the bracket 82 is pierced to provide a tab 82d to anchor the end of the cable guide conduit 76 as by means of the grommet 77 and fastening means.

Each of the two mounting brackets 82 also mount access door hinge means 86 on shaft means extending between bracket end or side walls 82a and 82h. When the door is in the closed position, the outside aesthetic surface E of the door lies in the plane of the frontaesthetic panel of the machine which extends upwardly from the support structure 11 as previously explained. The hinge means S6 further includes a cam portion 86a which serves to drive the cam member Si) about the pin 81 against Vthe bias of spring 72 when the access door 12 is closed.

As was indicated hereinabove, the control member 46 is originally adjusted to a zero or indexed position with respect to the collector segments 32a-c and the balancing pockets 23 when the brake or friction detent 67 is released by utilization of the adjusting means 56 connecting with the plate member 54 and bracket member 50. Once the desired position of control member 46 relative to collector segments 32a-c is established by threadable movement of the adjusting means 56, the locking means 53 is tightened. Accordingly, when so adjusted the stop member 60 and particularly the wall portion 60e thereof is in abutting contact with the wall portion 54C on the plate member 54, and is resiliently held or maintained in this position by the spring means 62, the spring action being abetted by the weight of the detlector arm 46.

Opening of the access door 12 for the insertion or removal of the fabrics to be laundered causes swinging action of the hinge means 86 from the full line to dotted line position in FIGURE 6, and by action of the spring means 72 (FIGURE 5) the cam follower lever member 80 is shifted by the cable 75 from the full line to dotted line position of FIGURE 6, The spring means 72 at the same time exerts sufficient spring force on the lever arm leg portion 68h to pivot the lever arm 68 about the point 69, releasing the holding or braking force of the brake or detent means 67b. This permits the lever member 63 to be pivoted about the point 64 by the spring 62, and since the spring force of the spring means 62 is greater than the force exerted by the spring means 66, the stop member 60 is drawn or pivoted clockwise by the spring means 62 to bring the surfaces 60C and 54C again into abutting engagement. Engagement of these surfaces assures that the control member 46 is again in its zero or indexed position.

Closing of the access door for initiation of the laundering cycle essentially reverses the action described, and the cam surface 86a on the hinge means 86 forces the cam follower lever member 86 to rotate a short distance counterclockwise, exerting a force on the cable 75 to pivot the lever arm 68 to again engage the brake members 67a and 67h against the body portion 63C of the lever arm 63.

The spring means 66 (FIGURE 3) maintains the lever member flange portion 63a against the end portion 60d of the stop means 60, however, the stop member 60 and connecting control member 46 are free to pivot during performance of the counterbalancing function.

The reason for the necessity of a self compensating indexing or zero locking system can best be understood by making reference to the operation of the balance system and the relative movements between the stationary and moving parts during the balance operation. This will be explained in conjunction with the first embodiment incorporating the pivoting deflector balance system as shown in FIGURES 1 and 2, but it should be understood that the operation is generally the same for the second embodiment incorporating the pivoting nozzle balance system of FIGURE 8. In the explanation the assumption will be made that there is a negligible difference in the phase anglevbetween the unbalanced portion of the load and the de'ection it produces or stated in another way, as the unbalanced load passes the horizontal centerline through the drum shaft the deection of the pylon cross member 21 will be at a maximum distance from the vertical centerline of the machine on the same side of the vertical centerline as the unbalanced load.

Referring to FIGURE 2, it can be seen that as the unbalanced load M in the drum 17 is spun at a high extraction speed there will be a deflection of the drum 17 and pylon cross member 2l. When rotating in the direction indicated (clockwise in the rear elevation of FIGURE 2), the unbalanced load M will cause the pylon cross member 21 to begin to deilect to the left of the machine vertical centerline at the instant it crosses the vertical centerline beneath the horizontal centerline. After a predetermined amplitude of vibration or deflection of the pylon cross member 21 to the left, it is desirable to have injection of the balancing tluid into the inlet segments begin. With the proper aforementioned adjustment of the control member 46 with respect to the inner diameter 32d of the collector segments, the injection will begin at this time. Injection occurs at this time since the movement of the pylon cross member 21 causes the wall portion 54C of the plate member to drive the stop member 69, because of the resistance imparted by the stationary tab 63a, counterclockwise about the pivot 57 to the point where the end portion 46a rises enough to allow the balancing fluid emanating from the nozzle outlet 45a to enter the proper collector segment or segments from Where it enters the proper balance pocket or pockets to eticiently counterbalance the unbalanced load M.

As the unbalanced load M continues upward toward the horizontal centerline, deilection of the pylon cross member 21 to the left increases and injection continues. At the instant the unbalanced load M crosses the horizontal centerline in an upward direction, the deection of the pylon cross member 21 to the left is at a maximum. As the unbalanced load continues upward toward the upper portion of the vertical centerline, the pylon cross member deflection will be to the right toward the neutral position and at some predetermined angle of the unbalanced load before it reaches the vertical centerline the end portion 46a of the control member 46 in its downward motion will again interrupt the ow from the nozzle outlet 45a and deect it back into the sump 16a to thus end injection.

As the unbalanced load M crosses the vertical centerline as shown in FIGURE 2, the pylon cross member 21 will be in its neutral position and the control member 46 will be in its zero or adjusted position. During the next 90 of rotation of the unbalanced load the deflection of the pylon cross member continues to the right, but there will be no injection. Injection is precluded since when the pylon cross member 21 deflects to the right of the vertical centerline, the stop member 60 breaks contact with the stationary drive tab 63a of the lever member 63 and thus the control member 46 remains in its neutral position whenever the pylon cross member deects -to the right of the vertical centerline.

When the unbalanced load M passes the horizontal centerline in its downward movement, the deection of the pylon cross member 21 to the right will be at a maximum and the deection will again start to the left. At the point when the unbalanced load M again crosses the lower portion of the vertical centerline, the stop member 66 will again con-tact the tab portion 63a of the lever member to allow the control member 46 to be pivo-ted as dellection of the pylon member to the left continues.

IGURE 2 shows that since the end portion 46a of the .Control member 46 is much further from the pivot point 57 than the point on the stop member 60 that is contacted by the wall portion 54C, there will be an amplification at the end portion 46a of the pylon cross member deflections. For this illustrative structure the amplification is approximately 16 to l. Thus if the pylon cross member 21 had a maximum deection of .050 of an inch to the left of the vertical centerline, the end portion 46a of the control member 46 would rise .800 of an inch.

If an automatic indexing or zero locking system were not provided to maintain a constant immovable relationship between the tab portion 63a of the lever member 63 and the stop member 60 and the machine were bodily moved, the critical adjustment of the control member 46 would be impaired. This happens because in the bodily shifting or movement of the machine the base plate or support structure 11 may assume a somewhat different l@ angle in its new position and produce a change in angular relationship between base plate 11 and pylon structure 15. In such a case while casing 16 will keep its same angular position with respect to the support structure 11, the drum 17 and pylon cross member 21 being supported semi-rigidly from the

pylon legs

15a and 15b^may shift with respect to the casing 16 and base plate 11. This small lateral shift of the pylon cross member 21 will be amplified at the end portion 46a of the control member 46 by a factor of 16 in the illustrative machine. The end portion 46a in its new neutral position will be out of precise adjustment with respect to the inner diameter 32d of the collector segments 32a-c. This will impair or destroy the proper coordination between the deflection of lthe pylon cross member and fluid injection thereby making the balance system much less efficient or even inoperative.

The zero locking system eliminates this serious misadjustment possibility. With this system, the machine can be bodily moved from position to position with no concern for the original critical balancing adjustment since the zero locking system of this invention will always assure the original precise adjustment. This is true since whenever the machine is to be used in its new position, it will be necessary to open the door and place a clothes load in the drum 17. As explained earlier, the opening of the door 12 will release the brake or friction detent means 67 and allow the lever member 63 and the control member 46 to be pivoted by action of the spring 62 until the stop member 60 again contacts the wall portion 54e` and lost motion is eliminated between

members

60 and 63 thereby assuring the proper adjustment. It should be pointed out that when the machine is moved and even with the zero locking system there will be a very minute dimensional change in the Vertical relationship between the end portion 46a and the inner diameter 32d of the collector segments. This slight change will be the actual movement that takes place between the pylon and the casing and will not be amplified 16 times as previously explained. This slight change will not effect the balancing operation.

Although the zero locking system as explained is operated by the access door 12, it would also be possible to have the cable 75 operated by an electric or air solenoid forming a part of a manual or automatic control. It would only be necessary at sometime in the machine cycle prior to the extraction or high speed portion to energize the electric or air solenoid to release the brake 67 and allow the lever member 63 and control member 46 to be returned by the spring 62 to their zero position and then subsequently to deenergize the electric or air solenoid to relock the brake means.

The embodiments of the invention in which an exclusive property or privilege is claimed are defined as follows:

1. Counterbalancing apparatus, comprising a rotatable receptacle,

stationary support means,

a cabinet enclosing said stationary supporting means and said receptacle,

mounting means mounting said receptacle on said stationary supporting means for rotative and vibratory movements relative thereto,

a door in said cabinet controlling access to said receptacle,

a plurality of fluid-receiving pockets mounted on said receptacle for receiving counterbalancing fluid in response to vibratory movements of said receptacle,

means including control means for adding uid to said pockets to eiect the counterbalancing of said receptacle during rotation of unbalanced loads within said receptacle,

indexing means interconnected between said mounting means and said control means for automatically indexing said control means with respect to said pockets to assure addition of said counterbalancing fluid to the proper pockets during the counterbalancing of said receptacle, and

connecting means between said door and said indexing means to preindex the control means Whenever the door is actuated.

2. Counterbalancing apparatus, comprising a rotatable receptacle,

stationary supporting means,

a cabinet enclosing said stationary supporting means and said receptacle,

a door in said cabinet controlling access to said receptacle,

a plurality of fluid-receiving pockets mounted on said receptacle for receiving counterbalancing fluid,

control means including a nozzle member and a detlector member movable relative to said nozzle member controlling the addition of fluid to said pockets to effect the counterbalancing of said receptacle during rotation of unbalanced loads within said receptacle,

and indexing means interconnected between said mounting means and said dellector member for automatically indexing said deliector member With respect to said pockets to assure addition of said counterbalancing iluid to the proper pockets during the counterbalancing of said receptacle,

connecting means connected to said indexing means and having an operative connection with said door to preindex the control means Whenever the door is actuated.

3. Counterbalancing apparatus, comprising a rotatable receptacle,

stationary supporting means,

a casing,

mounting means mounting said receptacle on said supporting means for rotation Within said casing and vibratory movements relative to said supporting means,

a door supported by said casing controlling access to said receptacle,

a plurality of Huid-receiving pockets mounted on said receptacle for receiving counterbalancing fluid in response to vibratory movements ot said receptacle,

means for directing fluid into said pockets to effect a counterbalancing of unbalanced loads in said receptacle,

detlector means pivotally supported by said mounting means and movable With respect to said directing means to control the addition of fluid to said pockets,

means limiting the movement of said deflector means to position said dellector means in duid-blocking relation to said directing means when the amplitudes of the vibrations do not exceed a predetermined level,

lever means pivotally mounted by said casing and engageable with said limiting means,

locking means connected to said lever means, and means connecting said door and` said locking means to maintain said lever means in a stationary position relative to said casing when said door is closed and releasing said lever means when said door is open to return said deilector means to blocking relation relative to said directing means and indexed with respect to said pockets to assure addition of said counterbalancing uid to the proper pockets during the counterbalancing of said receptacle.

4. Counterbalancing apparatus of the character delined in claim 3 in which t2 t t resilient means connects to said limiting means to return said deflector means to an indexed position, and in which resilient means urges said lever means against said limiting means. 5. Counterbalancing means of the character deined in claim 3, in which receptacle,

stationary supporting means,

a casing,

mounting means mounting said receptacle for rotation within said casing and vibratory movements relative to said supporting means,

a door supported by said casing controlling access to said receptacle,

a plurality of fluid-receiving pockets mounted on said receptacle for receiving counterbalancing duid in response to vibratory movements of said receptacle,

control means pivotally supported by said mounting means to control the addition of tluid to said pockets,

means limiting the movement of said control means to block uid llow to said pockets when the amplitudes ofthe vibrations do not exceed a predetermined level,

locking means connected to said lever means, and means connecting said door and said locking means to maintain said lever means in a stationary position relative to said casing when said door is closed and releasing said lever means when said door is open to return said control means to said blocking position and indexed with respect to said pockets to assure addition of said counterbalancing duid to the proper pockets during tlie counterbalancing of said receptacle.

7. Counterbalancing apparatus comprising a rotatable receptacle,

stationary supporting means,

a casing,

a door supported by said casing controlling access to said receptacle,

control means pivotally supported by said mounting means,

said directing means mounted on said control means and movable with said control means to control the addition of uid to said pockets,

means limiting the movement of said control means to block duid ow from said directing means to said pockets when the amplitudes of the vibrations do not exceed a predetermined level,

lever means pivotally mounted by said casing and er1- gageable with said limiting means,

locking means connected to said lever means, and

eans connecting said door and said locking means to maintain said lever means in a stationary position relative to said casing when said door is closed and releasing said lever means when said door is open to return said control means to said blocking position and indexed with respect to said pockets to assure addition of said counterbalancing fluid to the proper pockets during the counterbalancing of said receptacle.

References Cited in the le of this patent UNITED STATES PATENTS Armstrong Sept. 13, 1955 De Moss Aug. 28, 1956 Burkall Oct. 30, 1962 Scott et al. Mar. 5, 1963

Claims

1. COUNTERBALANCING APPARATUS COMPRISING A ROTATABLE RECEPTACLE, STATIONARY SUPPORT MEANS, A CABINET ENCLOSING SAID STATIONARY SUPPORTING MEANS AND SAID RECEPTABLE, MOUNTING MEANS MOUNTING SAID RECEPTACLE ON SAID STATIONARY SUPPORTING MEANS FOR ROTATIVE AND VIBRATORY MOVEMENTS RELATIVE THERETO, A DOOR IN SAID CABINET CONTROLLING ACCESS TO SAID RECEPTACLE, A PLURALITY OF FLUID-RECEIVING POCKETS MOUNTED ON SAID RECEPTACLE FOR RECEIVING COUNTERBALANCING FLUID IN RESPONSE TO VIBRATORY MOVEMENTS OF SAID RECEPTACLE, MEANS INCLUDING CONTROL MEANS FOR ADDING FLUID TO SAID POCKETS TO EFFECT THE COUNTERBALANCING OF SAID RECEPTACLE DURING ROTATION OF UNBALANCED LOADS WITHIN SAID RECEPTACLE, INDEXING MEANS INTERCONNECTED BETWEEN SAID MOUNTING MEANS AND SAID CONTROL MEANS WITH RESPECT TO SAID POCKETS TO ASSURE ADDITION OF SAID COUNTERBALANCING FLUID TO THE PROPER POCKETS DURING THE COUNTERBALANCING OF SAID RECEPTACLE, AND CONNECTING MEANS BETWEEN SAID DOOR AND SAID INDEXING MEANS TO PREINDEX THE CONTROL MEANS WHENEVER THE DOOR IS ACTUATED.