US3402819A - Safety control mechanism - Google Patents

Description

P 24, 1963 J. c. MELLlNER 3,402,819

SAFETY CQNTROL MECHANISM I Filed June 22, 1964 3 Shets-Sheet 1 INVENTOR.

Jokzz C Ned/r561 ,aw/ aidw AGENT Sept. 24, 1968 J. c. MELLINGER SAFETY CONTROL MECHANISM 5 Sheets-Sheet 2 Filed June 22, 1964 h. u 1 1 I A I) INVENTOR. B {0/212 LT/Vdl AGENT Sept. 24, 1968 J. c. MELLINGER SAFETY CONTROL MECHANI SM 5 Sheets-Sheet Filed June 22, 1964 AGENT United States Patent 3,402,819 SAFETY CONTROL MECHANISM John C. Mellinger, Newton, Iowa, assignor to The May- 'tag Company, Newton, Iowa, a corporation of Delaware Continuatiomin-part of application Ser. No. 686,450, Sept. 26, 1957. This application June 22, 1964, Ser.

No. 377,000 The portion of the term of the patent subsequent to Apr. 9, 1980, has been disclaimed 5 Claims. (Cl. 210144) This application is a continuation-in-part of application Ser. No. 686,450, filed Sept. 26, 1957, and now abandoned.

This invention relates to a control for preventing a horizontal axis combination washer-drier, washing machine or fluid extractor from sliding on, lifting from or moving relative to its supporting floor surface in response to centrifugal forces developed by high speed rotation of acentric or unbalanced clothes loads within this type machine.

This invention relates specifically to a combination washer-drier unit capable of sensing a predetermined maximum unbalanced centrifugal force generated by the rotation of an unbalanced clothes load within this combination unit during its fluid extraction operations. The mechanism sensing this predetermined force controls a safety switch which in turn controls a transmission regulating the rotational speed of a revoluable clothes receptacle capable of retaining such unbalanced clothes loads so that upon the generation of such a predetermined centrifugal force, the drive to the clothes receptacle is automatically interrupted and the receptacles rotational speed substantially lowered to effect a redistribution or rearrangement of the clothes load within the receptacle in an effort to eliminate the unbalance before automatically shifting the transmission back into a higher range of speeds for further centrifuging. The actuation of this safety switch prevents movement of the entire combination unit relative to its supporting floor surface by preventing the generation of even greater disturbing forces which would be created by a continued acceleration of such unbalanced clothes loads.

This sensing mechanism is used in conjunction with a force isolating system which partially isolates from the units such unbalanced clothes loads. This sensing mechanism is not, however, affected by the resonant characteristics of this force isolation system. Therefore, unlike the operation of previously disclosed safety mechanisms, the clothes receptacle within this combination washer-drier may be rotated at speeds below, equal to or above the force isolation systems resonant frequency without triggering its safety switch as a result of any effects of the resonant characteristics of that force isolation system on the vibratory movements of the receptacle. This is due to the fact that the unique receptacle mounting system disclosed hereinafter is capable of not only isolating in one mode of vibration those vibrations created by the rotation of acentric loads but is also capable of sensing in a second mode of vibration the centrifugal forces which create those vibrations. The force isolating system is thereby made independent of the sensing system for controlling the centrifugal forces.

Safety controls responsive to the disturbing centrifugal forces generated in horizontal axis washing machines have previously been devised. However, to my knowledge these machines have either utilized no force isolating systems thus limiting their top spin speeds or have utilized effective force isolating systems whose resonant characteristics have adversely influenced the most eflicient operation of the safety control devices used in conjunction with this latter type machine.

It will, therefore, be appreciated that the relatively low 3,402,819 Patented Sept. 24, 1968 speed triggering of the high speed tumbler drive by means of an amplitude type sensing control may tend to prevent unbalanced clothes loads from being sufficiently accelerated to high enough speeds to effect substantial moisture extraction prior to tripping of the sensing mecha nism. Coupled with this tendency is the possibility that as a result of the failure to materially reduce the moisture content of the clothes load during the first extraction attempt, the saturated fabrics may continue to present an unbalanced load condition capable of triggering the sensing mechanism of successive attempts at tumbler accelerations with the possible end result being the failure to eliminate a substantial perventage of the retained fluids by the end of the extraction period even though the unbalanced centrifugal forces generated during these tumbler accelerations may not have even approached the magnitude necessary to produce walking, shifting or sliding of the machine on its supporting floor surface.

It is, therefore, the primary objects of this invention to provide a sensing mechanism for a horizontal or generally horizontal axis centrifugal extractor, washing machine or combination washer-drier which is responsive to a predetermined magnitude of centrifugal force generated by the rotation of an unbalanced clothes load within this particular type of machine in order to limit and prevent the development of even greater disturbing forces which would be capable of moving such a machine relative to its supporting floor surface.

Another object of this invention is to provide a sensing mechanism capable of accomplishing this primary function independently of any effects of the force isolation system used in isolating unbalanced centrifugal forces from the base frame of this type machine.

Another object is to provide such a sensing mechanism capable of accomplishing this primary function at centrifuging speeds which are less than, equal to or even greater than the resonant frequency of the force isolation sus pension system chosen without causing the safety switch sensing an unbalanced centrifugal force of predetermined magnitude to be prematurely actuated merely as a result of the receptacles passing through its critical speed.

Another object of this invention is to provide a clothes receptacle mounting system for a laundry centrifuge so that the vibrations produced by the rotation of unbalanced loads in the receptacle can be isolated from its supporting frame in one mode of vibration while the unbalanced centrifugal forces produced by the rotation of such unbalanced loads can be sensed in a second mode of vibration and controlled independently of the force isolating system used to isolate the clothes receptacle in the first mode of vibration.

These and other objects, features, capabilities and advantages are effected by the instant invention as will later appear from an inspection of the following description and claims taken in accordance with the accompanying drawings in which:

FIGURE 1 is a front elevation of a combination washer-drier, partially broken away, showing the safety control system forming the subject matter of this invention;

FIGURE 2 is a longitudinal sectional view of the machine shown in FIGURE 1, the lower half in a vertical plane and the upper half deviating therefrom to pass through the heater housing;

FIGURE 3 is a free body diagram showing the relative direction of the forces acting on the tub assembly of the illustrative combination washer-drier;

FIGURE 4 is an enlarged fragmentary view of the lower front portion of the combination washer-drier unit shown in FIGURE 1;

' FIGURE 5 is a fragmentary plan view of the front support shown in FIGURE 4;

FIGURE 6 is a cross sectional view taken through line 66 of FIGURE 4;

FIGURE 7 is a cross sectional view taken on line 7-7 of FIGURE 4;

FIGURE 8 is an enlarged diagrammatic representation of the safety switch incorporated in the illustrated washerdrier; and, 1

FIGURE 9 is an enlarged fragmentary view showing the actuation of the safety switch by the amplitude sensin device also incorporated in this washer-drier unit.

Referring now-t the accompanying drawings in detail, it will be seen that the combination washer-drier unit shown in these drawings includes a substantially flat surfaced base frame 10 mounted on legs 11. Mounted upon base frame 10 are the channel members 13 and 14 which are welded or securely aflixed in some suitable manner to base frame 10 to form the two major supports for the washer-drier unit illustrated in the accompanying figures.

Referring to FIGURE 2, the rear channel member 13 is generally triangular in elevational configuration and receives a single pivot pin 16 about which the rear portion of the machine is free to pivot in an arcuate movement. Similarly, FIGURES l and 4 show the front channel support 14 as being of identical configuration to rear channel member 13 and receiving a similar pivot pin 17 for supporting the front portion of the combination washer-drier unit for an identical rocking movement.

It will be seen that these pivot pins 16 and 17 are journa'lled in flanged bearing sleeves 18 and 19, respectively, which form a two point support for tub brackets 21 and 22, respectively. This allows the tub or casing which is generally indicated by the arrow 24, and which is fastened to brackets 21 and 22 to oscillate back and forth on pins 16 and 17 in an arcuate movement in response to various forces generated within that tub.

Tub 24 is maintained in an upright position on pins 16 and 17 by two centering springs 25 connected between tub 24 and base 10- through the spring anchor brackets 26 fastened to the latter member. FIGURE 1 shows the tub 24 as being provided with a tab damper bracket 28 which forms a support for the damper leaf spring 29 carrying the damper pad 31 in a ball and socket joint at the end of damper spring 29. Base frame 10 is provided with an upstanding damper plate 32 which is engaged by damper pad 31 to absorb and dissipate the energy imparted to the tub 24 causing it to oscillate on the supporting pivot pins 16 and 17.

While the rear channel member 13 actually receives and supports directly the rear pivot pin 16, an inspection of FIGURE 6 will indicate that the same is not true as to the connection between front channel 14 and front pivot pin 17. That cross sectional view indicates that front pivot pin 17 is actually suspended in a floating pivot in front channel member 14 and, in practice, has a clearance of approximately one-sixteenth of an inch from the closest point of channel 14. While the front end of tub 24 is supported on the front tub bracket 22, on the front hearing sleeve 19 and on the front 'pivot pin 17, the latter pin is in turn supported by a lever arm 34 nested within front channel 14 and supported on the pivot pin 35 penetrating channel member 14 as clearly shown in FIGURES 4, and 7. Movement of the long lever arm 34 about pin 35 determines whether or not the front pivot pin 17 moves relative to the front channel member 14. It will be noted that, in any event, front pivot pin 17 may move only a short distance, in the case of this illustrated embodiment approximately one-sixteenth of an inch, before the head of pivot pin 17 will contact channel member 14 and limit further movement of that pin, and consequently, tub 24, in a vertical plane. While this limit stop for pin 17 prevents tub 24 from separating from channel 14 when the entire machine is tipped over or upended, it is not necessary in the basic operation of the control device forming the basis for the instant invention due to degree of control maintained by this safety mechanism.

Three forces acting on lever arm 34 establish a condition of equilibrium about pin 35 in order to produce the described floating pivot about front pivot pin 17. The first of these three forces. is applied upwardly through the supporting foot 37, preferably formed ofrubber or some other cushioning material, located at the end o f arm ,4'. The weight of tub 24 andthe partssupported bythat casing provide the second force which is applied'directly to lever arm 34 through pin 17. The third forceiacting on member 34 is exerted? downwardly'o'n the -en'd-of the leaf spring 38 which is inserted into'opening 39 of lever arm 34 so as to form an extension'of the latter member. The adjustable machine screw 41 which passes through the base of channel 14.and' base frame 10, as well as the end of leaf spring extension 38, provides the means of varying the force exerted downwardly on leaf spring extension 38. In other words, as the end of leaf spring 38 is moved closer toward base frame 10 by tightening the adjustable screw 41, the lever arm 34 will have a greater tendency to move in a clockwise direction as viewed in FIGURE 4. It should, therefore, be apparent that the weight of tub 24 and all parts supported by it tends to move lever arm 34 in a counterclockwise direction about pin 35 whereas the flexed leaf spring extension 38 tends to move it in a clockwise direction thereby 'producing'fa floating pivot action for front pivot pin 17 relative to the front channel member 14. i

Now, with reference to the safety switch mechanism actuated by the movement of lever arm 34, it will be seen that front channel member 14 is provided with a bracket member 43 which pivotally mounts on its upper end a small lever member 44. Lever 44 is rigidly connected to the safety switch mechanism, generally iridi-v cated by the arrow 46, which with its actuating plunger 47, is movable toward and away from the longer end of lever 34 by tightening or loosening the adjustable machine screw 48 penetrating the left end of lever 44 (FIGURES 4 and 5) and threaded into a lower extension of bracket 43. For example, tightening the adjustable screw 48 to compress the spring 49 moves the safety switch mechanism 46 in a counterclockwise direction so as to move plunger 47 away from the left end of member 34 whereas loosening of the adjustable screw 48 will allow the compression spring 49 to move plunger 47 closer to lever arm 34.

While the precise details of switch 46 are notshown, the diagrammatic sketch illustrated in FIGURE 8 is capable of indicating the function performed by that particular switch assembly. FIGURE 8 shows the switch mechanism 46 as including a resilient diaphragm 51 mounted across its housing so that it tends to maintain the horizontal position shown in FIGURE 8. In addition to plunger 47, switch mechanism 46 is provided with an internal plunger 52 which is fastened to diaphragm 51 like plunger 47 and is capable of moving upwardly to separate the insulated resilient arms of switch 54 positioned within the switch assembly housing. This housing is provided with an air escape port 55 which allows movement of air into and out of that portion of the housing above diaphragm 51.

From this it will be seen that when plunger 47 is moved upwardly against diaphragm 51, the contacts of switch 54 will be separated by plunger 52 and air compressed on the upper side of diaphragm 51 thereby forcing air out through the air port 55. When the force is removed from plunger 47, diaphragm 51 will tend to return to its normal position thus allowing switch 54 to close and also allowing air to come back into the switch housing through port 55. Since diaphragm 51 will not return to its normal position until a sufficient amount of air has returned through port 55 to equalize the pressure on opposite sides of that diaphragm, a variable time delay can be built into this switch mechanism byproviding a prescttable r. valve for port 55. In practice, this valve is diagrammatically shown in FIGURES 4, 5 and 8 as being provided with a needle valve 58 and vent hole 59. A snap action switch may be substituted for switch 54 to prevent minor vibrations magnified through lever arm 34 from causing that switch to make and break in a hunting action.

It will also be noticed that lever arm 34 provides a support for the pivoted lever member 61 which includes a flat extension 62 abutting the extreme left end of lever arm 34. Since there is normally a slight clearance between plunger 47 and extension 62, the latter extension serves merely as a force transmitting member when lever 34 is moved toward plunger 47 by vertical movements of tub 24. Tub 24 is provided with a supporting bracket 64 from which depends a cushioned plunger member 65 capable of being adjusted toward and away from lever 61. From FIGURE 4 it will be apparent that arcuate movement of tub 24 about it supporting pivot pins 16 and 17 toward switch 46 will cause plunger 65 to engage lever 61 and move it into the position shown in FIGURE 9 causing extension 62 to engage switch plunger 47 and open switch 54 independently of any movement of member 34. A small coil spring 66 wound around the pivot pin 67 of lever 61 returns lever 61 to the position of FIGURE 4 after plunger 65 rocks away from its engagement with a force transmitting member during this latter movement.

In other words, switch 54 may be opened either by a large arcuate movement of tub 24 or by an upward movement of that tub member. It is emphasized at this point that while each tub movement may open switch 54, the controls sensing these two movements perform separate functions since an arcuate movement of tub 24 opens switch 54 to prevent contact between tub 24 and its cabinet 119 while vertical movement of tub 24 opens switch 54 to prevent movement of the entire machine relative to its supporting floor surface.

As indicated in other portions of this specification, switch 54 may be opened by either a large arcuate movement of casing 24 about its supporting pivot pins 16 and 17 independently of any vertical movement of tub 24 or it may be opened by a vertical movement of casing 24 independently of any rocking motion of that casing on pins 16 and 17.

The arcuate movement of tub 24 is controlled in this illustrative machine to prevent contact between tub 24 and the sides of cabinet 119. The tub carried plunger 65 and the amplitude sensing lever 61 could, therefore, be eliminated if this type control were not desired.

If this amplitude control were correlated to sense those centrifugal forces produced by high speed rotation of tumbler 95 with unbalanced loads in order to prevent movement of the machine relative to its supporting floor surface at its top spin speeds as has previously been done by others in this art, the amplitude sensing mechanism in this illustrative washer-drier would have to be set to sense a six pound unbalance as it passed through its critical speed which is approximately 65 revolutions per minute.

However, since the amplitude sensing mechanism incorporating elements 61 and 65 merely prevents contact between casing 24 and cabinet 119 and has nothing to do with the prevention of the entire machine walking, sliding or lifting on its supporting fioor surface, the setting for the control, which is adjusted by adjusting the length of plunger 65, is limited only by the cabinet dimensions so that this control actually is set to a value equivalent to a clothes load unbalance of between ten to eighteen pounds. The presence of such a large unbalance within receptacle 95 would, therefore, produce movement of the illustrative machine on its floor surface during the fluid extraction operations were it not for the centrifugal force sensing mechanism used in conjunction with this amplitude control device.

For an understanding of the mechanism preventing movement of the entire machine relative to its supporting floor surface, reference is made particularly to FIGS. 1, 2, 3 and 4. FIGS. 1 and 2 indicate that the weight of the tub or casing 24 and all elements journalled in or supported thereon is carried by pins 16 and 17 which represent the upwardly directed forces F and F respectively, in FIG. 3. The weight of tub 24 and the mass supported by that container is shown as the force W, which is directed downwardly in FIG. 3 in which the rectangle represents tub 24. Since the centering springs 25 include a downward component due to their angular positioning relative to base frame 10, this downward component is represented in FIG. 3 by means for the symbol S It is emphasized here that this downward component of these centering springs is not necessary for the operation of this centrifugal force sensing mechanism and that horizontally positioned springs capable of maintaining tub 24 in an upright position and having no vertical component at all can be considered to be their equivalent for this purpose.

Although the biasing of leaf spring 38 is in a downward direction on the right side of the pivot pin 35 as viewed in FIGS. 1 and 4, it tends to lift tub 24 on the opposite side of pin 35 so that its equivalent biasing force S is directed upwardly as it is shown in FIG. 3. The symbol F represents the centrifugal force or disturbing force tending to lift the entire machine from its floor surface at the instant when an unbalanced clothes load is carried to the top of receptacle during the rotation of that latter member.

From this it can be seen that a given centrifugal force, F will be represented by the sum of W and S less the sum of the forces F F and S By increasing the bias force S exerted by the leaf spring 38, the disturbing force which can be tolerated without triggering the safety switch 54 by the slight vertical movement of tu-b 24 becomes smaller. This means that with an increase in this biasing force S a smaller unbalanced load within receptacle 95 will be capable of causing the front end of tub 24 together with its pivot pin 17 and the bearing sleeve 19 to move upwardly within the slightly enlarged hole in front channel 14 receiving member 19 so as to lift the left end of arm 34 and open switch 54.

It should, therefore, be apparent that this control may be preset to carry a predetermined maximum load unbalance within receptacle 95 by rotating that receptacle at its top spin speed and then adjusting screw 41 until the machine does not move relative to its supporting floor surface when a test weight slightly less than the predetermined maximum unbalance is rotated within receptacle 95, but will move on that surface when a test weight slightly exceeding the predetermined maximum is carried within that receptacle.

In this embodiment of my invention, the upward movement of tub 24 in response to this predetermined maximum centrifugal force is reflected in a slight pivotal movement between the flanged bearing sleeve 18 and the rear channel member 13. While it is more economical to use a single switch 54 actuated by the upward movement of one end of tube 24, it should be apparent that a similar control may be applied to both major supports of this illustrative machine or to various support of other machines utilizing even a different type of tub support and still conform to the principles presented with reference to FIGURE 3.

As previously stated, the force S produced by the vertical component of centering springs 25 is not essential to the operation of this invention even though it must be considered whenever such diagonally positioned centering springs are used. Likewise, it is possible to provide a safety control mechanism without the refinement provided by 7 spring biasing force S as produced by leaf spring 38. Such a biasing force could be reduced to zero or a simple two point support eliminating lever arm 34 could be provided without any spring biasing mechanism without departing from the basic theory of operation of my invention.

It will be seen from an inspection of FIGURE 3 that by reducing the forces S and S to zero and by controlling the magnitudes and application points of these various forces, the reactionary force at one end of the machine, F for example, can be reduced to zero causing the one end of the machine to lift and thereby actuate a switch whenever a predetermined disturbing force, F is reached so as to produce a slight lifting movement of tub 24 about pin 16 in response to the resultant movement produced by forces W, R, and F acting through their respective lever arms. It will also be seen that if forces W and F were permitted to act midway between pins 16 and 17, the resultant tendency for tub 24 to move upwardly rather than pivotally about the rear pivot pin 16 could also be utilized to control one or more solenoid shifter switches or some similar control.

It will be noted that tube 24 has for all practical purposes, only one degree of freedom, i.e., an arcuate movement back and forth around pins 16 and 17 and that the slight, restricted upward movement of the tub 24 takes place in the same vertical plane, but in another mode of vibration so that the centrifugal force sensing device is entirely independent of the force isolation system used to isolate the disturbing forces generated within tub 24 from base frame 10.

For example, the illustrative unit has a tumble speed of approximately 50 revolutions per minute, a partially damped isolation system provided by springs 25 with a resonant frequency of approximately 65 cycles per minute, and a spin speed of approximately 300 revolutions per minute. Without the force isolation system, it would be impossible to carry the prescribed unbalanced loads up to that top spin speed and yet the resonant point of this isolation system, which is far below the top spin speed, has no detrimental effect on the centrifugal force sensing mechanism interrupting the power to the drum 95 in case of an excessive unbalance within that latter receptacle.

With respect to the operation of the control mechanism, it should be apparent that tub assembly 24 may be filled to the desired fluid level for the washing operations by regulating the solenoid valve (not shown) controlling the fluid flow to the tub assembly. Following the conventional washing operations during which time drum 95 is rotated at a tumbling speed of approximately 50 revolutions per minute, tub 24 is drained preparatory to the subsequent centrifuging operations.

At the beginning of the centrifuging operations, the

' tumbler speed is shifted from 50 revolutions per minute to approximately 300 revolutions per minute to centrifugal separate most of the residual fluids from the fabrics carried within drum 95. Should an excessively unbalanced load such as a fourteen pound unbalance or the torque reaction to this speed change cause a wide arcuate movement of the tub assembly 24 relative to the base frameat speeds in the region of resonance, plunger 65 will rock lever 61 into the position of FIGURE 9 thereby opening switch 54 for a period dependent upon the setting of needle valve 58. This amplitude type control will therefore reduce the rotational speed of drum 95 to its tumbling speed in order to prevent contact between tub assembly 24 and its enclosing cabinet 119 at rotational speeds just above the tumble speed. It will also permit a redistribution of the fabrics within drum 95 prior to subsequent tumbler accelerations.

As drum 95 is accelerated toward its top spin speed, any existing acentric loads within tumbler 95, which are always present in some degree in all clothes loads, will generate a progressively increasing unbalanced centrifugal force, illustrated in FIGURE 3 as F which may be of sufiicient magnitude to warrant operation of switch 54 by lever 34 to prevent the entire machine from lifting or moving relative to its supporting floor surface.'If the centrifugal force generated by the rotation of these acentric clothes loads is of such a value as to cause the front end of tub 24 to lift thereby causing lever 34 to also lift and open switch 54, the rotational speed of tumbler will be reduced to its tumbling speed forthe period determined by the setting of needle valve 58 thereby allow; ing a redistribution of fabric to occur prior to the next tumbler acceleration. It will be'noted that the chances for subsequent triggering of switch 54 by lever; 34 is substantially lessened each time not only' by the rearrangement of clothes loads withinturribler 95, but also by the progressively decreasing Weight of the fabrics themselves due to the partial moisture extraction achieved during each tumbler acceleration prior to the triggering of switch 54. v

The triggering of switch 54 by either lever 61. orlevefr 34 may normally occur several times'in each centrifuging operation depending upon whether or not it is caused by a torque reaction or an acentric load rotated at high speed within tumbler 95. If desired, the centrifuging operation may be interspersed with tumbler operations controlled by a timer to positively assure a number of redistribution steps in each such centrifuging operation. By the use of these controls, the fabrics will be efiicicntly centrifuged prior to the start of the drying operations.

In the drawings and specification there has been set forth a preferred embodiment of the invention, and although specific terms are employed, these are used in a generic and descriptive sense only, and not for purposes of limitation. Changes in form and the proportion of parts, as well asthe substitution of equivalents are contemplated, as circumstances may suggest or render expedient, without departing from the spirit or scope of this invention as further defined in the following claims.

I claim:

1. Laundry apparatus for centrifuging fluid from fabrics comprising, a support, a casing, a clothes receptacle revolubly mounted within said casing on a nonvertical axis and adapted to receive said fabrics, drive means for rotating said receptacle, means mounting said casing on said support in one primary degree of freedom about a non-vertical primary axis for attainment of a force isolation system having a resonant frequency during the rotation of said receptacle, and means sensitive to a predetermined amount of centrifugal force measured by movement of said casing in a secondary degree of freedom relative to said support for decreasing the power supplied by said drive means to said receptacle.

2. Laundry apparatus for centrifuging fluid from fabrics comprising, a support, a casing, a clothes receptacle revolubly mounted within said casing on a nonvertical axis and adapted to receive said fabrics, drive means for rotating said receptacle, means pivotally mounting said casing on said support for arcuate movement about a pivotal axis positioned parallel to the axis of rotation of said receptacle for attainment of a force isolation system having a resonant frequency during the rotation of said receptacle, and means sensitive to a predetermined amount of centrifugal force measured by movement of said casing relative to said support and transverse to said pivotal axis for decreasing the power supplied by said drive means to said receptacle.

3. Laundry apparatus for centrifuging fluid from fabrics comprising, a support, a lever pivoted on said support, a casing pivoted on said lever, a receptacle revolubly mounted on a non-vertical axis within said casing and adapted to receive fabrics to be centrifuged, the weight of said casing and said receptacle urging said lever in a first direction, drive means'for rotating said receptacle at a tumbling speed and at higher extraction speeds, and control means responsive to movement of said lever in a second direction for reducing the rotational speed of said receptacle from said extraction speeds to said tumbling speed to effect a redistribution of said fabrics within said receptacle when centrifugal forces generated by rotation of unbalanced loads within said receptacle move said lever in said second direction.

4. Laundry apparatus for centrifuging fluid from fabrics comprising, a support, a lever pivoted on said support, a casing pivoted on said lever, a receptacle revolubly mounted on a non-vertical axis within said casing and adapted to receive fabrics to be centrifuged, the weight of said casing and said receptacle urging said lever in a first direction, drive means for rotating said receptacle at a tumbling speed and at higher extraction speeds, bias means urging said lever in a second direction, and control means responsive to movement of said lever in said second direction for reducing the rotational speed of said receptacle from said extraction speeds to said tumbling speed to effect a redistribution of said fabrics within said receptacle when the combined torque produced by said bias means and by centrifugal forces generated by the rotation of unbalanced loads Within said receptacle moves said lever in said second direction.

5. Laundry apparatus for centrifuging fluid from fabrics comprising, a support, a first lever pivoted on said support for movement in first and second directions, a casing pivoted on said first lever, a receptacle revolubly mounted on a non-vertical axis within said casing and adapted to receive fabrics to be centrifuged, the weight of said casing and said receptacle urging said first lever in a first direction, bias means urging said first lever in said second direction, drive means for rotating said receptacle at a tumbling speed and at a higher extraction speed, a second lever pivoted on said first lever, a plunger member connected to said casing and engageable with said second lever during arcuate movements of said casing on said first lever, and common control means including a time delay shifter mechanism for temporarily reducing the rotation speed of said receptacle from said extraction speeds to said tumbling speed upon either movement of said second lever by said plunger during arcuate movement of said casing or upon movement of said first lever in said second direction by the combined torque produced by said bias means and centrifugal forces generated by the rotation of unbalanced loads Within said receptacle.

References Cited UNITED STATES PATENTS SAMIH N. ZAHARNA, Primary Examiner.

Claims (1)

1. LAUNDRY APPARATUS FOR CENTRIFURING FLUID FROM FABRICS COMPRISING, A SUPPORT, A CASING, A CLOTHES RECEPTACLE REVOLUBLY MOUNTED WITHIN SAID CASING ON A NONVERTICAL AXIS AND ADAPTED TO RECEIVE SAID FABRICS, DRIVE MEANS FOR ROTATING SAID RECEPTACLE, MEANS MOUNTING SAID CASING ON SAID SUPPORT IN ONE PRIMARY DEGREE OF FREEDOM ABOUT A NON-VERTICAL PRIMARY AXIS FOR ATTAINMENT OF A FORCE ISOLATION SYSTEM HAVING A RESONANT FREQUENCY DURING THE ROTATION OF SAID RECEPTACLE, AND MEANS SENSITIVE TO A PREDETERMINED AMOUNT OF CENTRIFUGAL FORCE MEASURED BY MOVEMENT OF SAID CASING IN A SECONDARY DEGREE OF FREEDOM RELATIVE TO SAID SUPPORT FOR DECREASING THE POWER SUPPLIED BY SAID DRIVE MEANS TO SAID RECEPTACLE.

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