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Publication numberUS2931505 A
Publication typeGrant
Publication dateApr 5, 1960
Filing dateMar 25, 1957
Priority dateMar 25, 1957
Publication numberUS 2931505 A, US 2931505A, US-A-2931505, US2931505 A, US2931505A
InventorsWinslow Fred H
Original AssigneeHammond Laundry Cleaning Machi
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Cleaning or washing apparatus
US 2931505 A
Abstract  available in
Images(6)
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Claims  available in
Description  (OCR text may contain errors)

April 5, 1960 Filed March 25, 1957 F. H. WINSLOW CLEANING OR WASHING APPARATUS 6 Sheets-Sheet 1 INVENTOR FRED H. WINSLOW ATTORNEYS April 5, 1960 F. H. wlNsLow l l 2,931,505

CLEANING OR WASHING APPARATUS Filed March 25, 1957 6 Sheets-Sheet 2 3, ssasw E l Ilulll 79 24 2,3 urulvfag! 25 i* .En -5- i UU 2 y se A l/ INVENTOR A FRED H. WINSLOW BY gne/M Y /f ATTORNEYS April 5, 1960 Filed March 25, 1957 F. H. WINSLOW CLEANING OR WASHING APPARATUS 6 Sheets-Sheet*l 5 v INVENTOR FRED H. WINSLOW BY @www wfaf /M ATTORNEYS April 5, 1960 F. H. wlNsLow CLEANING oR WASHING APPARATUS 6 Sheets-Shevet 4 Filed March 25, 1957 INVENTOR FRED H. WINSLOW ATTORNEYS April 5; 1960 Filed March 25, 1957 F. .H. WINSLOW CLEANING OR WASHING APPARATUS 6 Sheets-Sheet 5 INVENTOR FRED H. WINSLOW /QA ATTORNEYS April 5, 1960 F. H. wlNsLow 2,931,505

` CLEANING OR WASHING APPARATUS Filed March 25, 1957 6 Shee cs-Sheet 6 INVENTOR FRED H. WINSLOW 549 M f MW ATTORNEYS 2,93L5052 CLEANING on W'AsrrNG APPARATUS p Fred H. Winslow, Waco, Tex., assignmto Hammond Laundry-Cleaning Machinery and Supply Company, Inc., Waco, Tex., a corporation of Texas Application March 25, 1957, SerialNo. 648,244 7` Claims.` (ci. 4z10=-ni4y g tract the cleaning or washing liquid. When used for cleaning or washing, the inner container or cylinder which holds the clothing or other articles is rotated at` a relatively low speed, conducive to tumbling the contents, whereas when used for centrifuging or extraction, the inner container is rotated at relatively high speed. If the load'v in the cylinder is substantially unbalanced, the high speed rotation of the cylinder during the extraction cycle sets' up very appreciable unbalanced centrifugal forces, causingA excessive vibration and straining vand wearing of the parts. Many proposals' for eliminating such vibrations, or compensating for them, have been advanced heretofore, but these have left something to be desired from the standpoints of effectiveness in elimination of vibration and simplicity of construction.

An object of the present invention is to provide an improved cleaning or washing apparatus of the kind referred to characterized by increased simplicity of construction and effectiveness in minimizing vibration due to rotation of the container' or cylinderwhen the load therein is substantially unbalanced.

Another object of the invention is to provide an improved construction of the character stated' in which reduction of harmful` effects of vibration is achieved by` providing a tub and a container rotatably mounted in and carried by the tub, both b'eing of light construction and being supported for conjoint oating movement', the container being driven through an axially aligned flexible coupling only part or" the weight of which is carried by the oating' assembly.

Other objects' will become apparent from a reading of the following description, the appended claims',- and the accompanying drawings, in which:

Figure l is a front elevation of a cleaning apparatus embodying the invention, with some parts broken away and other parts shown in section;

Figure 2 is a vertical section on the line 2--2 of Figure l, with some parts shown in elevation;

Figure 3 is a rear elevation of the construction shown inrFigures' l and4 2;

Figure 4 is a fragmentary Vertical SCtiI the li l-4 of Figure 3, drawn on an enlarged scale;

Figure 5 is an enlarged scale View', partly in rear' elevation and partly in vertical section, showing a pulley and clutch assembly as viewed when looking in the direction of the arrow S inFigure 2;

Figure 6 is a vertical section on the line 6---6 of Figure 5;

Figure 7 is a. vertical section on the line- 7-7 of Figure 4, on an enlarged scale;

Patented` Arpt'. 5,L 196D Figure 8 is a-schematic view of a hydraulic-mechanism for operating a` variable ratio speed changing mechanism, some parts being shown'- in eleva-tion and others in vertical section;

Figure 9 is a fragmentary vertical section: on the line 9-9 ofv Figure 3; and

Figure 1G is a section on the line Ill-10 of Figure 2% The preferred form of cleaning apparatus embodying the invention is shown in the drawings as including a frame generally designated A including a base A1, four vertical angle member Aa, a rectangular top fabricated from angle members Ab, and a rear plate 2v suiciently strong to support driving mechanism to be described later. Ahousing, generally designated A2, carried by the frame A includes a front Wall or panel 1, and side Walls 3 and 4. The rear frame plate 2 serves also as the rear panel of the housingV A2. Mounted in the housing in a manner later to be described is an outer container or tub B adapted to contain dry cleaning or washing liquid and a rotatable container or basket C into which articles of clothing or the like may be placed for cleaning or washing. The container cylinder C is journalled on the tub B in a manner particularly to be described later so as to be rotatable about a substantially horizontal axis by power transmitted from a driving motor D through a variable ratio drive transmitting mechanism E and a flexible or universal coupling F. The tub B is provided with a front opening adapted to be closed by a door 7 hinged on the tub B as at 8. The tub B may be lled at its' top by means, not shown. For enabling removal of liquid from the tub B, a hose 9 leads from a sewer connection to the discharge spout 10 of a dump or drain valve connected by a flexible hose 11 to a fitting 12 on the bottom of the tub S. A control device 13 is connectedV to the dump or drain valve above the discharge spout 10, but does not in itself constitute the present invention and need not here be described in detail. A vent riser 14 extending rearwardly from the back wall of the tub B provides for egress of fumes and vapors from the tub. A timing control equipment box 15 is mounted on a plate 6 extending acrossl the top of the frame A at itsV front, and may be connected to suitable electrical contactors and valves for controlling the cycling of the apparatus.

In accordance with the invention, the tub and' rotati able cylinder are of quite rigid yet very light construction, and are so mounted and the cylinder is so driven as to minimize shocks and abnormal stresses resulting from rotation of the cylinder C at high speed when the load of clothing or other articles is improperly balanced. The construction is such that when the tub B is rotated at the very high speeds required for extracting washing or dry cleaning liquid centrifugally from the clothes or other aritcles, even a substantial amount of out of balance condition of the load will not materially aifect the stresses which the parts have to` endure. This desirable minimizing of stresses and vibrations and noise is achieved, in general, by constructing the ,cylinder C and tub B rigidly yet lightly, and by so mounting them. with respect to each other and to the frame and driving mechanism as to cause centrifugally unbalanced forces to be absorbed by yielding or floating movement of the lightly constructed tub and cylinder assembly. y.

n the illustrated construction, the rigid but light tub includes a dat rear end wall plate 16 joined at its periphery in any suitable manner to a frusto-conical plate structure 17, and the cylindrical Wall i8 joined to the periphery of the rear wall 16, 17. Thecylindricalwa-ll 18 is formed at its front with an inwardly turned flange 19 connected at its inner face to an annular ballast plate 20.

The tub B is supported on the frame A so as not? f acentos mally to be relatively stationary, but so as to be capable of somewhat free floating movement, mainly vertical or transverse to the horizontal axis of rotation of the cylinder C. For so mounting the tub B, four suspension springs 21 are connected at their upper ends to the frame A and are connected at their lower ends to ears or brackets 22 secured to the tub B. For damping the substantially vertical floating movement of the tub B, four dash pots 23 are interposed between the bottom of the tub and the frame side walls 3 and 4, as shown in Figure 1. Each dash pot device 23 includes a cylinder 24 pivoted at its lower outer end at 25 to the frame A, and a piston, not shown, connected by a rod 26 to a pivot 27 on the bottom of the tub B. Preferably, the dash pot devices 23 are inclined inwardly and upwardly from the frame side walls toward the tub B.

The basket or cylinder C, also of rigid but light construction, includes a rear wall comprising a circular flat plate 28 connected at its periphery to the outer edge of a frusto-conical plate 29. A cylindrical wall 30 extends forwardly from the jointure of the plates 29 and 30 and is provided at its front with an inwardly directed flange 31. The cylindrical wall 30 of the cylinder C is formed of perforated sheet material to provide for ready ingress and egress of cleaning or washing liquid and preferably is provided with a plurality of inwardly extending ridges 32 for augmenting the tumbling action imparted to the articles being washed or cleaned when the cylinder is rotated at relatively slow speed.

As previously stated, the elimination or minimizing of undesirable or abnormal. stresses which otherwise would result from high. speed rotation of the cylinder C with an unbalanced load is achieved by the cooperative or conjoint effects of the rigid yet light construction of the tub `and cylinder, and the improved mounting and cooperative arrangement of the tub and cylinder and the driving mechanism. In the preferred construction shown more clearly in Figures 2 and 4, the tub B is fitted at the center of its rear walls 16-17 with a journal box 34 equipped with anti-friction roller bearings 35 which rotatably support a stub shaft 36, the front end or left end as viewed in Figure 4, of the shaft 36 being secured to a hub 37 at the center of the basket rear walls 28, 29 by a retainer cap 38 and screw 39. A seal 40 in the front end of the bore of the journal box 34 prevents cleaning liquid from leaking from the tub into the bearing structure 34, 35.

The mounting of the tub B on the frame A for relatively free floating movement, and the mounting of the cylinder C on the tub B results in transmission of unbalanced forces from the cylinder through the shaft 36 and to the tub B, so that the tub and cylinder, both of light but rigid construction, will float vertically as is permitted by the spring suspension 21 with the floating movements being damped by the dash pots 23. Consequently, the shaft 36 and the associated bearing equipment are not subjected to harmful abnormal stresses even when the cylinder is rotated at the high speeds required for fluid extraction.

In order that the tub B and basket C may float freely to provide the operational advantages described above without its being necessary for the tub also to carry heavy driving or power equipment such as an electric motor, the power for driving the cylinder C is transmitted to the driven shaft 36 by way of the flexible or universal coupling F, which is of light weight as compared to a driving motor and only a part of the weight of which is carried by the stub shaft 36. As shown in Figure 4, a driving shaft 41 is mounted for rotation in Ia journal box 42 having a flange 42a secured to the rear housing wall 2 by bolts 42h. Bearing inserts or liners 43 in the journal box 42 mount the shaft 41 for rotation about a fixed axis substantially aligned with the axis of rotation of the stub shaft 36 when the tub B and cylinder C are in their normal or neutral positions,

that is the positions occupied when the tub and cylinder have not been deflected transversely of the shaft 36 by unbalanced load created stresses.

The flexible coupling F is so constructed as continuously to transmit drive to the stub shaft 36 and basket C although the axis of rotation of the shaft 41 remains fixed and the axis of the stub shaft 36 floats transversely Y to varying extents dependent upon the degree of out of balance of loading in the tub C. In the construction shown, the flexible coupling F includes a rigid disk member 44 having a hub 45 keyed and secured to the rear end of the stub shaft 36. A flexible disk 46, which may be of heavy duty multi-ply belting or similar flexible material, is secured to circumferentially spaced raised parts 47 on the coupling member 44 by bolts 48 and clamping plates 49. Another rigid disk 50 is secured to the flexible disk 46 at circumferentially spaced points at which it is separated from the disk 46 by spacers 51. Bolts 52 and clamping plates 53 may be provided for securing the disk 50 to the flexible disk 46. The points at which the rigid disk 50 is secured to the flexible disk 46 are circumferentially spaced or staggered with respect to the points at which the flexible disk 46 is secured to the rigid disk 44.

A plurality of torque transmitting parts, shown as tubes 54, are welded or otherwise secured to the rigid disk 50 at circumferentially spaced points and extend parallel to the axes of the shafts 36 and 41 and are secured at their rear ends at circumferentially spaced points to a rigid disk 55, as by welding. The rigid disk 55 is secured at circumferentially spaced points to a flexible disk 56 by spacers 57, clamping plates 57a and bolts 58, the connection of the disk 55 to the disk 56 thus being similar to the connection of the disk 50 to the flexible disk 46 at the front end of the coupling F. A further rigid coupling member 59 is formed to include a disk part 60 and a sleeve part 61 which is keyed to the shaft 41 by a hub part 62. Circumferentially spaced raised parts 63 on the disk part 60 of the coupling member 59 co-act with bolts 64 and clamping plates 65 for conuecting the flexible disk 56 to the coupling member 59.

In operation, rotation of the driving shaft 41 by the mechanism E to be described hereinafter transmits drive through the coupling F to the stub shaft 36 and cylinder C while permitting the shaft 36 to float from a neutral position in which it is coaxial with the shaft 41 to laterally offset positions in which the axes of the shafts 36 and 41 are offset from one another. The required relative lateral displacement of the shaft 36 relative to the shaft 41 is permitted by flexing of the coupling disks or members 46 and 56. Consequently, the floating of the tub and basket transversely, which is so effective in preventing undue stresses, can take place without interference with the driving of the cylinder.

` In accordance with the invention, the variable speed ratio drive transmitting mechanism E is constructed so as to respond automatically to a change in the driving speed. Any suitable kind of variable speed prime mover may be employed. In the form shown, the motor D is a constant speed motor and has a shaft on which is fitted the hollow inner hub 66 of a variable diameter V pulley 67, as shown in Figure 9. The pulley 67 includes axially separable and approachable pulley sections 68 and 69 mounted on the hub 66. The pulley section 68 is formed with an elongated sleeve-like hub 68B part mounted for sliding movement on the inner hub 66 but being constrained to rotate with the inner hub 66 by a driving key 70 extending from the inner hub 66 into a spline or groove, not shown, in the hub part 683. The pulley section 69 is formed with a sleeve-like hub part 69"', somewhat shorter than the hub part 68a, slidably mounted on the outside of the hub part 68a and being constrained to rotate with the latter and with the inner hub 66 by the driving key 70 which extends into a spline or groove, not shown, in the hub part 69a. Mounted on the outside of huh: part 69a l is a -capv or. coi/enh 71,., heldby a.. shouldered hollow -sterr'rl 72, having, threaded.. conneev tionat its inner end with the-end of theinner. hubti. Anspring 73 is interposed under compressionbetweenthe outer end ofthe vhub part 69a and ther outer end ofL-the cap 71. Another spring 74 isl interposedk undercompression, between the end of the inner hub aandzaaspring Seaty or retainer 75 anchored at the end of the hub part 68%by a snap ring 76. A grease gun t'ting 77 atythe end of the hollow stem 72 providesy for lubricationw of the parts through the hollow: stem and a passage 78. As is a well known characteristic of adjustablediameter, V.- pulleys of this kind,v imposing additional tension on the belt trained aroundthe pulley causes the` pulleysections 68 and 69 to move axially away from. eachother in opposite directions, as is permitted `by the springs-73; and 74, thus enabling the belt to iind contact withthe-pulley sections closer to the inner huhl 66 with consequent der creasing of the driving speed of the belt asmcornpared tothepulleyspeed. On the other hand,plesseningoflgthe b elttension enableskthe pulley sectionsfsnd 69,:to moverelatively toward each other, therebyfrnovingthe belt radially outwardly and increasing; thegspeedeofthe beltias; compared to that of the pulley, The adjustable pulley-shown and described is only representativeof one form of variable speed prime mover equipment, vsince other pulleyconstructions or change speed, gearing,or even variable speed motors, may be used.

Referring now to theconstructionof the changefspeed drive mechanism E, a V beltl 79 driven byftheyprin 1e tn over pulley 67 is, trained around a5; relati. ly large diameter pulley 80 fast witha relatiyelysrnallgdiamter Pulley 31.; both 0f the puller/$.80' and.8.1 being :rotatable on and relatively to the driving shaft 41., AsfbelhiSZ transmitsdrive from thev small diameter pulley Silto-a large diameter pulley 83 journalled; for; rotation .onia

shaft 84 supported on the frame A. AISOjournalled on the shaft 84 by anti-friction bearings 85 is; a;smal1 `...dif ameterpulley 86.

When relatively low or washing speed;drive.isrtra-ns: mittedto thek mechanism E by the primegmoverD, the pulleys83 and 86, both journalled on the shaft184, are rotatable in unison, the pulley 83 transmittingsdriveto the pulley 86. For this purpose, the pulley; 86' is;formed with a ange 87 and a drum 88 which is surroundedrby aflange 89 on the large diameter pulley 83. v Threefcentrifugal` clutch assemblies; are interposedbet-Ween the fiange189 and-the drum 88 and areso constructed'. that when-the pulley 83 is drivenat1a1relatively.lovwspeedthe clutch assemblies transmit drive from the pulley;83to the drum 88 of the pulley 86, whereas whenl the: pulley 83". is driven at relatively high speed the. clutchesare disengaged so asno longer to transmit drive from the pulley 83 to the pulley 86. Each clutch assemblyain.- cludesla shoe element 90 of generally sector shape-formed Withan outwardly opening radial bore which slidably receives a tube 91 mounted on the flange 89offthe.. pulley-83. The tube 91 houses a spring92, both the -tube 91 and spring 92 being held-in place by.a.-cap plate 93 secured to a pad 94 on the iiange 89 bymeans of screws 9S: The ysprings 92 are pre-loaded in compression so as to urge the shoes 90 normally into contactfwithl the clutch drum 88 on the pulley 86. At apredetermined relatively high rotative speed of the pulleyn83the. shoes 90 arecentrifugally thrown outwardly against the-urge ofthe springs 92 to disengage the shoes Afron-l the-drum 88, thereby rendering the pulleys 83 and-86 free t'ofrotaterelatively to each other.

. When the pulley 86 is driven throughv the intermediary o fgthe clutch shoes 90 it transmits drive through .twin V belts 96 trained around a relatively large diameterpulley 97 having a hub 98 keyed and secured directly-to the driving shaft 41, the arrangement being suchrthaLwh'en the prime mover is-operated at relatively lowl-speedgfor washing or. cleaning. dfiveis.. transmitted-.through @ebelt 96 and pulley/597m.:thezdrivihgg shaft.. 1;. which; drives theeleaningcylinder- C.

studs3102' extendingy rearwardly from the; web ofgthe pulley80, themounting of thefshoes :llli'beinggsuch asjo permitthemto moyeradiallyl outwardlyfforengagement with thefclutch drum 99 orto .be moved.radially-inwardly to disengagedposition; The cl'1 1tch; shoesgllli)v areurged inwardly -to their disengaged-positions;by two` springs 103 connected Ybetween the shoestandjpreloaded under tension'.

In operation, when` the belt V79 isdriveu at arelativel-y low-speed accordingtothe adjustment ofthe effectivev diameter of the pulley 67, the pulley 80, is-drivenat ,a reduced speed such` that the centri-fugalforce exertednby the clutch shoes 100 is insutiicient to'movethe shoes out' Wardly against the urge of the springs 103, Consequently; the pulley 80 will not be clutched to the pulleyv 97` for driving) the latter directly. Instead, thesmall `diameter pulley 81, driven at the same rotativespeed as thefpulley 80, will drive the large dameterpulleyfSl throughv the belt` 82. The rotative speed/ofthe pulley 83 willbe sui'ricientlylow to permit the ysprings 91. to: maintain the clutch sh'oes 90, carried bythe pulley 83, in .drive/transf mitting connection` withrthe drum; 8S on the Small.di'.

y ameter pulleyY 86 so thatY the;pulleys `83 andl86 will'be rof tated in unison. Reduced speed drive .will be transmitted from the. small` diameter pulley through' the twin. belts 96y tofthel-argediameter pulley 97 which is ziixedv tor'the driving `shaft 41. Thus, when theeifective driving. speed of the prime mover pulley 67 is low, there will-be three speed'reductions, respectively from the pulley 7 to the pulley 80, from the pulley 81 `to the pulley. 83, andzfrom. the-pulley 86 tothe-pulley 97. v

When it isdesired` tof-rotate the drivingV` shaft 41 atrahigher` speed, adjustment of the effective diameter of the prime.-m,over pul 1`ey67 isfmadein a-fmannerfto -.h'e-. l.e;v scribed later for.causingthefassociated;belt'"79 toengagefthepulley at a relatively-greater. radius soY that the beltwill be, driven` faster. In consequence,.the pulleyz180 willflbe driven faster than it isdriven for thelow speed setting of the pulley-67, the relatively. lhigh speedLof the pulley 86 beingsUCient tocausethe centrifugal'force eXer-tedby the,` clutch shoes 100. to move. the..shoes;out-.` wardly. against theurge of the springswli4 andinto clutchingengagement with the drum 99 on thek pulley 97, thereby effecting a direct connection between the pulleys :80 and .97.' At `this time, the: rotativev speed of Vthe pulley 83 driven from the pulley 81 throughthe belt 82 .will be suiciently high to cause thevclutch'shoes'9i to be moved outwardly by the action Ofcentrifugalforce against` the urge of the springs 92 so as tobecome. disengaged fromthe'drum 88 on the pulley 86." This perf mits the pulley 83 to be driven idl'y by the Ybelt82, andpermits the pulley 86 to be driven. idly bythetwimbeltsy 96;" The nel effect Vis that the driveis transmittedfrom the pulley 67 tothe pulley 8) andthence directly to,the,

E itself, and is responsive to decrease in the effective-f driving speed of' the prime mover 67 for decreasing the speed ratio within the mechanism E itself.

The illustrated mechanism for changing the effective driving speed of the prime mover 67 includes a platform 104 pivoted at one end at 105 on the main frame A and supporting the motor D at its opposite or free end. Depending from the free end of the platform 104 is a strut 106 pivoted at 107 to the upper end of a piston rod 108 extending downwardly into a cylinder 109. The lower end of the piston rod 108 is seated in a conical depression 111 in the top of a piston 110 reciprocably mounted in the cylinder 109. The cylinder 109 is housed in a reservoir 112 containing hydraulic liquid. The lower end of the cylinder is closed by a plug 113 formed with a passage 114 for the admission and discharge of hydraulic uid for operating the piston 110 to lift and lower the platform 104 and motor D. When the piston 110 is in its lowermost position, the platform 104 and motor D will be in such a relatively low position that the belt 79 will be pulled radially inwardly with respect to the pulley 67 to spread the pulley halves and cause the belt to engage the pulley at a relatively small radius for low speed driving. When fluid under pressure is delivered to the cylinder 109 below the piston 1.10, the piston and platform 104 and motor D are raised, thus effecting relative approaching movement of the pulley halves 69, 68 and causing the belt 79 to engage the pulley at a relatively greater radius for effecting high speed driving. Raising of the motor D is limited by engagement of the platform 104 with a stop 104n carried by the frame rear wall 2, and shown in Figure 3.

A simple and effective hydraulic circuitry is provided for effecting operation of the piston 110. As shown in Figure 8, a pump 115 mounted in the reservoir 112 at a level to be immersed in the hydraulic fluid is drivable by a motor 116 and flexible coupling 1,17. The pump 115 includes .a centrifugal impeller ll'comprising a disk having a plurality of radially extending bores communicating at their inner ends with an axial intake passage 119 which opens downwardly into the reservoir 112. Fluid discharged through the radial pu-mp bores is conducted through a discharge fitting 120 to a conduit 121 which extends to the inlet passage 114 of the cylinder 109. Broadly considered, the arrangement is such that uid delivered under pressure by the pump 115 passes through the conduit 121 to raise the fluid pressure actuatable piston element 110 when itis desired to increase the effective driving speed of the pulley 67.

As previously stated, raising of the platform 104 is limited by engagement of the platform with the limit block 104e. In order to permit stopping of the platform 104 at its -uppermost position and attendant stopping of the piston 110 without breaking or straining the parts, the pump 115 is of the centrifugal discharge type and is characterized by impositive displacement or delivery so that when the platform 104 and piston 110 have been arrested by the stop 104e, the pump may continue to run without, however, delivering further fluid through the conduit 121, nevertheless maintaining sufiicient pressure on the piston 110 to hold the latter and the platform 104 in raised positions.

Valve mechanism is provided for controlling the rate of raising of the piston 110 and platform 104 and for permitting and controlling the rate of lowering of the piston and the platform when changing the drive transmitting speed ratio. As shown in Figure 8, two branch conduits 121EL and 121b are interposed in the conduit 121 in parallel relation to each other. Connected in the branch conduit 121a are a check valve 122, which permits flow of liquid only from the pump 115 to the cylinder 109, and an adjustable restrictor valve 123. Connected in the branch conduit 121b are a check valve 124whichpermits flow of uid only from the cylinder 109 to the reservoir 112, and an adjustable restrictor valve 125.

When the pump 115 is operated to deliver fluid to the uid pressure actuatable motor 109-110, fluid will flow through the branch conduit section 121, check valve 122 and restrictor valve 123 to the cylinder 109. When the piston and motor D are to be lowered for effecting low speed operation, the pump will be stopped and the weight of the motor D, the platform 104, piston rod 108 and piston 110 will force the fluid from the bottom of the cylinder 109 through the conduit 121 and its branch conduit section 1211, the check valve 124 opening to enable the return flow to take place. The rate of raising of the piston 110 may be varied by adjusting the restrictor valve 123, and the rate of lowering of the piston may be varied by adjusting the restrictor valve 125.

The construction shown embodies the invention in a preferred form, but it is intended that the disclosure be illustrative rather than definitive, the invention being defined in the appended claims.

I claim:

l. In a cleaning apparatus, an outer container for cleaning liquid; an inner container for articles to be cleaned; means including a driven shaft connected to said inner container and bearing means on said outer container for mounting said inner container within and for rotation relative to said outer container about an axis fixed with respect to said outer container; means mounting said outer container relatively stationarily but with provision for floating movement of said outer container both radially and inclined with respect to the position of the axis of said driven shaft when said outer container is in a normal neutral position; a driving shaft; means mountingrsaid driving shaft for rotation about a substantially fixed axis with which the axis of said driven shaft is substantially aligned when said outer container is in its normal neutral position; and a flexible coupling interposed axially between and connecting said driving shaft to said driven shaft and comprising separate but operatively connected members movable relatively to each other both radially and at an inclination to the axis of said driving shaft. y

2. In a cleaning apparatus, a frame; an outer container for cleaning liquid; an inner container for articles to be cleaned; means including a driven shaft connected to said inner container and bearing means on said outer container for mounting said inner container within and for rotation relative to said outer container about an axis fixed with respect to said outer container; means mounting said outer container relatively stationarily on said frame but with provision for floating movement of said outer container both radially and inclined relative to said frame; a driving shaft; means mounting said driving shaft on said frame for rotation about a substantially fixed axis with which the axis of said driven Vshaft is substantially aligned when said outer container is in its normal neutral position; and a flexible coupling interposed axially between and connecting said driving shaft to said driven shaft and comprising two pairs of members spaced from each other axially of said driving shaft, the members included in each of said pairs of members being tiltable relatively to each other about the axis of said driving shaft and at locations spaced from each other along the axis of said driving shaft.

3. In a cleaning apparatus, an outer container for cleaning liquid; an inner container for articles to be cleaned; means including a driven shaft connected to said inner container and bearing means on said outer container for mounting said inner container within and for rotation relative to said outer container about an axis fixed with respect to said outer container; means mounting said outer container relatively stationarily but with provision for conjoint floating movement of said outer container and said inner container both radial and inclined-with respect to the position of the axis of said ldriven shaft when said outer container is in a normal neutrall position; a driving shaft; means mounting said driving shaft for rotation about a substantially xed axis with which the axis of said driven shaft is substantially aligned when said outer container is in its normal neutral position; and a flexible coupling interposed axially between and connecting said driving shaft to said driven shaft and comprising separate but operatively connected members movable relatively to each other both radially and at an inclination to the axis of said drivingshaft.

4. In a cleaning apparatus, an outer container for cleaning liquid; an inner container for articlesto be cleaned; means including a driven shaft connected to said inner container and bearing means on said outer container for mounting said inner container within and for rotation relative to said outer container about an axis fixed with respect to said outer container; means mounting said outer container relatively stationarily but with provision for floating movement of said outer container both radial and inclined with respect to the position of the axis of said driven shaft when said outer container is in a normal neutral position; a driving shaft; means mounting said driving shaft for rotationabout a substantially fixed axis with which the axis of said driven shaft is substantially aligned when said outer container is in its normal neutral position; and a flexible coupling interposed axially between and connecting said driving shaft to said driven shaft and comprising a first coupling member connected to one of said shafts, a second and flexible coupling member connected to said first coupling member, a third coupling member connected to said second and flexible coupling member, said second and flexible coupling member being between said first and third coupling members, and means universally flexibly connecting said third coupling member to the other of said shafts at a location spaced from said third coupling member axially of said other of said shafts.

5. In a cleaning apparatus, an outer container for cleaning liquid; an inner container for articles to be cleaned; means including a driven shaft connected to said inner container and bearing means on said outer container for mounting said inner container within and for rotation relative to said outer container about an axis fixed with respect to said outer container; means mounting said outer container relatively stationarily ybut with provision for floating movement of said outer container both radial and inclined with respect to the position of the axis of said driven shaft when said outer container is in a normal neutral position; a driving shaft; means mounting said driving shaft Vfor rotation about a substantially fixed axis with which the axis of said driven shaft is substantially aligned when said outer container is in its normal neutral position; and a flexible coupling interposed axially between and connecting said driving shaft to said driven shaft and comprising a first relatively rigid disk secured to one of said shafts, a flexible disk connected to said first relatively rigid disk at circumferentially spaced points, a second relatively rigid disk connected to said flexibledisk on the `side thereof opposite said first relatively rigid disk and at circumferentally spaced points staggered with respect to the points of connection of said flexible disk to said first relatively rigid disk, and means universally flexibly connecting said second relatively rigid disk to the other of said shafts at a location spaced from said second relatively rigid disk axially of said other of said shafts.

6. In a cleaning apparatus, an outer container for cleaning liquid; an inner container for articles to be cleaned; means including a driven shaft connected to said inner container and bearing means on said outer container for mounting said inner container within and for rotation relative to said outer container about an axis fixed with respect to said outer container; means mounting said outer container relatively stationarily but with provision for floating movement of said outer container both radial and inclined with respect to the position of the axis of said driven shaft when said outer container is in a normal neutral position; a driving shaft; means mounting said driving shaft for rotation about a substantially fixed axis with which the axis of said driven shaft is substantially aligned when said outer container is in its normal neutral position; and a flexible coupling interposed axially between and connecting said driving shaft to said driven shaft and comprising a first relatively rigid disk secured to one of said shafts, a first flexible disk connected to said first relatively rigid disk at circumferentially spaced points, a second relatively rigid disk connected to said first flexible disk on the side thereof opposite said first relatively rigid disk and at circumferentially spaced points staggered with respect to the points of connection of said first flexible disk to said first relatively rigid disk, a third relatively rigid disk spaced from said second relatively rigid disk axially ofsaid one of said shafts, a plurality of torque transmitting members extending parallel to and being spaced radially from the axis of said one of said shafts and being connected at their opposite ends respectively to said second and third relatively rigid disks, a second flexible disk connected to said third relatively rigid disk at circumferentially spaced points, and a fourth relatively rigid disk connected to said other of said shafts and to said second flexible disk on the side thereof opposite said third relatively rigid disk at circumferentially spaced points staggered with respect to the points of connection of said second flexible disk to said third relatively rigid disk.

7. In a cleaning apparatus, an outer container for cleaning liquid; an inner container for articles to be cleaned; means including a driven shaft connected to said inner container and bearing means on said outer container for mounting said inner container within and for rotation relative to said outer container about an axis lixed with respect to said outer container; means mounting said outer container relatively stationarily but with provision for floating movement of said outer container both radial and inclined with respect to the position of the axis of said driven shaft when said outer container is in a normal neutral position; a driving shaft; means mounting said driving shaft for rotation about a substantially fixed axis with which the axis of said driven shaft is substantially alinged when said outer container is in its normal neutral position; and flexible coupling means interposed axially between and connecting said driving shaft to said driven shaft at two locations spaced from each other axially of said shafts and enabling rela tive radial displacement of said shafts, relative angular displacement of said shafts and combined relative radial and angular displacement of said shafts.

References Cited in the le of this patent UNITED STATES PATENTS

Patent Citations
Cited PatentFiling datePublication dateApplicantTitle
US305026 *Sep 9, 1884 edward stillman
US339119 *Mar 30, 1886F ThbeeJames e
US1246445 *Feb 6, 1917Nov 13, 1917Edwin H LudemanFlexible shaft-coupling.
US1322087 *Jun 30, 1919Nov 18, 1919Edwin H LudemanFastening.
US2182711 *Sep 2, 1937Dec 5, 1939Thomas Flexible Coupling CompaFlexible coupling
US2337586 *Mar 25, 1942Dec 28, 1943Bendix Home Appliances IncBelt transmission mechanism
US2343742 *Nov 21, 1939Mar 7, 1944Westinghouse Electric & Mfg CoWashing apparatus
US2435058 *Mar 6, 1943Jan 27, 1948Thomas Bertha EFlexible coupling
US2461643 *Mar 20, 1944Feb 15, 1949Hemmeter George TDynamic balancer
US2463100 *Dec 19, 1947Mar 1, 1949Marcellus W GredellTwo-speed automatic power transmission
US2629245 *Nov 29, 1946Feb 24, 1953Avco Mfg CorpReciprocating washer and centrifugal drier provided with shock absorbing hydraulic suspension assembly
US2642996 *May 1, 1946Jun 23, 1953Avco Mfg CorpWashing machine centrifugal extractor support and damping mechanism
Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US4819459 *Aug 19, 1988Apr 11, 1989Keith John RFront loading cleaning machine
US5463883 *Nov 22, 1994Nov 7, 1995Pellerin Milnor CorporationTextile treating machine
US5548978 *Nov 29, 1994Aug 27, 1996Merloni Elettrodomestici S.P.A.Front loading washing machine
US5570597 *Nov 29, 1994Nov 5, 1996Merloni Elettrodomestici S.P.A.Simplified front loading laundry washing machine
US5927106 *Oct 29, 1997Jul 27, 1999Pellerin Milnor CorporationTextile treating machine
Classifications
U.S. Classification210/364, 68/23.1, 68/140, 464/95
International ClassificationD06F23/00, D06F37/22, D06F37/20, D06F23/02
Cooperative ClassificationD06F37/22, D06F23/02
European ClassificationD06F37/22, D06F23/02