US20070050921A1 - Appliance having a driving mechanism - Google Patents
Appliance having a driving mechanism Download PDFInfo
- Publication number
- US20070050921A1 US20070050921A1 US11/594,731 US59473106A US2007050921A1 US 20070050921 A1 US20070050921 A1 US 20070050921A1 US 59473106 A US59473106 A US 59473106A US 2007050921 A1 US2007050921 A1 US 2007050921A1
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- US
- United States
- Prior art keywords
- appliance
- locking mechanism
- input gear
- output gears
- gearbox
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
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Classifications
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- D—TEXTILES; PAPER
- D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
- D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
- D06F37/00—Details specific to washing machines covered by groups D06F21/00 - D06F25/00
- D06F37/30—Driving arrangements
- D06F37/304—Arrangements or adaptations of electric motors
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- D—TEXTILES; PAPER
- D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
- D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
- D06F37/00—Details specific to washing machines covered by groups D06F21/00 - D06F25/00
- D06F37/30—Driving arrangements
- D06F37/32—Driving arrangements for rotating the receptacle at one speed only
- D06F37/34—Driving arrangements for rotating the receptacle at one speed only in opposite directions, e.g. oscillating
Definitions
- the invention relates to an appliance having a driving mechanism.
- the invention relates particularly, but not exclusively, to a domestic appliance, for example a washing machine, having a driving mechanism.
- the invention also relates to a method of operating such an appliance.
- Driving mechanisms for use in appliances in general are well known. Furthermore, such driving mechanisms in the form of planetary or epicyclic gears are well known and are commonly used to drive rotating bodies when it is desired periodically to reverse the direction of the output rotation. Under such circumstances, the configuration of the epicyclic gear is altered so that, for a given direction of input rotation, the direction of the output rotation can be selected.
- a domestic appliance in the form of a washing machine which incorporates a drum having two rotatable portions and drive means for rotating the rotatable portions so that relative rotation between the rotatable portions can be achieved.
- the two rotatable portions of the drum are rotatable at substantially the same speed in opposite directions for at least part of the period of operation of the washing machine. This arrangement causes increased agitation to the articles contained within the washing machine during the washing portion of the operating cycle.
- the rotatable portions of the drum are then also required to rotate at the same speed and in the same direction in order adequately to spin rinse water out of the articles during the spinning portion of the operating cycle.
- each drum has been provided with a separate drive mechanism so that each drum can be rotated at the required speed and in the required direction at the appropriate time in the operating cycle.
- Control means are then required to ensure that each drive mechanism operates correctly during each part of the operating cycle.
- two separate motors are required which adds to the cost of the appliance and also to the volume of components which need to be housed within a fixed space.
- U.S. Pat. No. 4,910,979 and U.S. Pat. No. 5,000,016 each disclose a vertical-axis washing machine having a tub, a basket in which articles to be washed are received, and a central agitator located inside the basket.
- the basket and the agitator are each freely rotatable, in an oscillating manner, with respect to the tub.
- the driving mechanism which causes the basket and agitator to oscillate is an epicyclic arrangement by means of which, when the agitator is driven through a given angle in a first direction about the vertical axis, the basket rotates, albeit through a smaller angle of rotation, in the opposite direction.
- the angle of rotation of the basket is dependent upon many factors, including the system inertia, the angle of the agitator stroke and the size of the load in the washing machine. Such an arrangement is not suitable for use in horizontal-axis washing machines primarily because the washing action in a horizontal-axis machine is very different from that in a vertical-axis machine.
- An object of the invention is to provide an appliance having a driving mechanism which is suitable for use in a horizontal axis washing machine.
- a further object of the invention is to provide an appliance having a driving mechanism which can be used to drive two rotatable portions of the drum of a horizontal-axis washing machine.
- Another object of the invention is to provide a horizontal-axis washing machine in which the number of drive motors required to be used is reduced.
- a still further object of the present invention is to provide an appliance of the type described above in which the cost of manufacture is reduced and/or in which the number of drive motors required is reduced.
- the invention provides an appliance comprising two rotatable portions and a driving mechanism for rotating the rotatable portions about an axis, the driving mechanism comprising a gearbox having an input gear, two output gears connected to the rotatable portions and a locking mechanism movable between a first position and a second position, the arrangement being such that, when the locking mechanism is in the first position and the input gear is driven, both output gears rotate in the same direction and, when the locking mechanism is in the second position and the input gear is driven, the output gears rotate in opposite directions, characterized in that the axis is arranged horizontally or substantially horizontally.
- the arrangement according to the invention allows an appliance having two portions rotatable about a horizontal axis to be provided with a single drive mechanism having a single input gear but having two output gears.
- the output gears can be selected to rotate either in the same direction when they are required to do so (e.g., during delicate washing portions and spinning portions of an operating cycle in a washing machine) or in opposite directions when they are required to do so (e.g., during normal or “heavy soil” washing portions of an operating cycle in a washing machine).
- Only a single drive motor is then required to be connected to the input gear, with no additional drive motors being required to achieve either synchronized rotation or counter rotation during the relevant portions of the operating cycle.
- each output gear is arranged coaxially and that the input gear is coaxial with the output gears.
- each output gear is connected to a shaft and the shafts are arranged coaxially, one inside the other.
- the arrangement is such that, when the locking mechanism is in the first position and the input gear is driven, both output gears rotate in the same direction and at the same speed. More preferably, when the locking mechanism is in the second position and the input gear is driven, the output gears rotate in opposite directions at substantially the same speed.
- This arrangement is particularly suitable for use in a washing machine of the type described in WO 99/58753, because the operating cycle of the washing machine requires the drum portions to rotate in the same direction and at the same speed for some of the time and in opposite directions at substantially the same speed for some of the time.
- the gearbox comprises a gear with a planetary arrangement and having an annulus, a plurality of planet wheels carried on a planet carrier, and two sun wheels. It is preferred that, when the locking mechanism is in the first position, the locking mechanism engages both the planet carrier and the annulus so as to prevent relative rotation therebetween. More preferably, the locking mechanism and the annulus each carry a plurality of projections, the projections carried by the locking mechanism interengaging with the projections carried by the annulus when the locking mechanism is in the first position. Even more preferably, the locking mechanism is mounted on the planet carrier.
- the arrangement thus provided is compact and relatively easy to incorporate into an appliance of the type described in WO 99/58753.
- the operation of the locking mechanism is also reliable and not greatly prone to failure, as is required in the envisaged application of a washing machine.
- the driving mechanism preferably incorporates an actuator for moving a locking plate of the locking mechanism from a first position to a second position.
- the actuator preferably comprises a first actuator ring and a second actuator ring, the first actuator ring being attached to a fixed portion of the appliance in a manner which allows rotation thereof about an axis of the gearbox and having inclined surfaces facing the second actuator ring, the second actuator ring being engaged with the fixed portion of the appliance in a manner which allows movement thereof parallel to the axis of the gearbox and having inclined surfaces facing the first actuator ring and complimentary to the inclined surfaces of the first actuator ring, such that rotational movement of the first actuator ring causes movement of the second actuator ring parallel to the axis of the gearbox as a result of the movement of the inclined surfaces across one another.
- This arrangement allows the driving mechanism to be converted between synchronized rotation and counter rotation simply by rotation of the first actuator ring about an axis of the gearbox.
- the rotation of the first actuator ring can be achieved simply and effectively using known techniques.
- the invention further provides a method of operating an appliance of the type described above, the method comprising the steps of:
- step (c) the output gears rotate in opposite directions at substantially the same rotational speed.
- Such a method is highly suitable for operating a washing machine of the type described in WO 99/58753.
- FIG. 1 is a schematic side view of an appliance, being a washing machine, having a driving mechanism and according to the invention
- FIG. 3 a is a perspective view of a first group of the components shown in FIG. 2 in an assembled form
- FIG. 4 is a sectional view through a second group of the components shown in FIG. 2 in an assembled form
- FIG. 5 is a perspective view of a third group of the components shown in FIG. 2 in an assembled form
- FIG. 6 a is an exploded view of several of the components shown in FIG. 2 and forming the working parts of the gearbox;
- FIG. 6 b is a first perspective view of the components of FIG. 6 a in assembled form and illustrating the action of the gearbox;
- FIG. 7 is an exploded view of an actuator forming part of the driving mechanism incorporated into the washing machine shown in FIG. 1 ;
- FIG. 9 a is a schematic plan view of the rear of the tub and part of the actuator showing the position thereof when synchronized rotation of the drum portions is required;
- FIG. 9 b is a schematic plan view of the rear of the tub and part of the actuator showing the position thereof when counter rotation of the drum portions is required;
- FIG. 10 a is a cross-section through the gearbox and actuator during synchronized rotation of the drum portions
- FIG. 10 b is a cross-section through the gearbox and actuator during counter rotation of the drum portions.
- the invention is embodied in a domestic washing machine having a driving mechanism.
- a washing machine is illustrated, schematically, in side view in FIG. 1 .
- the washing machine 10 has an outer casing 12 having a front panel 14 in which is located a door 16 .
- a water-tight tub 18 is mounted inside the casing 12 in a known manner by a spring damper mechanism 20 .
- a water inlet conduit 22 communicates with an upper portion of the tub 18 via a soap tray 24 .
- a water drainage conduit 26 communicates with a lower portion of the tub 18 and also with a drainage outlet 28 .
- Appropriate pumps and valves (not shown) are provided for controlling the inlet and drainage of water to and from the tub 18 .
- the components described thus far are all well known in the art and form no part of the present invention.
- a drum 30 consisting of a first rotatable portion 32 and a second rotatable portion 34 .
- the first rotatable portion 32 is mounted in cantilever fashion on a first shaft 36 and the second rotatable portion 34 is mounted coaxially with the first rotatable portion on a second shaft 38 .
- the second shaft 38 is rotatably mounted within the first shaft 36 , which is hollow.
- the first and second shafts 36 , 38 are rotatable about an axis 40 of the drum 30 .
- the driving mechanism 50 comprises a gearbox 60 and an actuator 70 .
- the components of the gearbox 60 are shown in exploded form in FIG. 2 .
- the components of the gearbox will be grouped into three groups of components; a first group of components 100 , a second group of components 200 and a third group of components 300 . Each group of components will now be described in detail.
- the first group of components 100 includes a drive wheel 102 which is generally dish shaped.
- the drive wheel 102 has a generally circular cover plate 104 which has a central aperture 106 .
- Extending axially from the periphery of the cover plate 104 is a cylindrical surface 108 .
- a flange 110 extends radially outwardly from the cylindrical surface 108 on the side thereof remote from the cover plate 104 .
- the cover plate 104 has three radially extending ribs 112 which are formed integrally therewith.
- the ribs 112 are equispaced about the central aperture 106 .
- a plurality of holes 114 are equispaced about the central aperture 106 in the vicinity thereof.
- the first group of components 100 also incorporates an input gear 116 comprising a set of teeth 118 and a support collar 120 .
- the set of teeth 118 and the support collar 120 are rigidly connected to one another.
- a bore 122 extends through the input gear 116 .
- Formed in the face of the support collar 120 facing the cover plate 104 are three equiangularly spaced recesses 124 which co-operate with the ribs 112 formed in the cover plate 104 .
- bores 126 extend through the support collar 120 so as to be aligned with the holes 114 formed in the cover plate 104 .
- the bore 122 formed in the input gear 116 is sufficiently large to receive a sleeve 128 and two axially spaced bearings 130 therein without play.
- a lip 122 a extends radially inwardly at the end of the bore 122 remote from the support collar 120 .
- Each of the bearings 130 and the sleeve 128 has an inner bore which is dimensioned so as to receive a distal end of the second shaft 38 , also without play.
- a screw-threaded bolt 132 is provided to co-operate with a screw-threaded bore located in the distal end of the second shaft 38 .
- a washer 134 is provided between the head of the bolt 132 and the side of the bearing 130 closest thereto.
- the first group of components 100 is shown in assembled form in FIGS. 3 a and 3 b .
- the input gear 116 is held securely against the cover plate 104 by means of rivets 138 passing through the holes 114 of the cover plate 104 and into the bores 126 of the support collar 120 .
- the ribs 112 and the recesses 124 co-operate so as to ensure that the input gear 116 is correctly aligned about the axis 40 with respect to the cover plate 104 .
- the distal end of the shaft 38 is thus retained within the bore 122 by means of the bolt 132 .
- the bearings 130 allow the drive wheel 102 , together with the input gear 116 , to rotate freely about the distal end of the shaft 38 .
- the cylindrical surface 108 of the drive wheel 102 receives the drive belt 46 .
- the flange 110 assists in retaining the drive belt 46 in position on the cylindrical surface 108 .
- the cylindrical surface 108 can have an anti-slip coating or texturing applied thereto in order to reduce the risk of slippage between the drive belt 46 and the drive wheel 102 .
- the second group of components 200 includes a first planet carrier plate 202 , a second planet carrier plate 204 and a plurality of spacers 206 .
- the spacers 206 are equispaced about the axis of the gearbox 60 and are rigidly connected to each of the first and second planet carrier plates 202 , 204 so as to maintain the first and second planet carrier plates 202 , 204 spaced apart in the axial direction.
- the spacers 206 are tubular.
- the first planet carrier plate 204 faces the input gear 116 . It is generally circular in shape and has a central aperture 208 .
- the central aperture 208 is sufficiently large to allow the set of teeth 118 of the input gear 116 to pass therethrough.
- a planar portion 210 surrounding the central aperture 208 is radially bounded by a ridge 212 whose inner diameter is slightly larger than the outer diameter of the support collar 120 of the input gear 116 .
- the ring-shaped bearing washer 136 of the first group of components 100 is thus locatable adjacent the planar portion 210 .
- the ridge 212 maintains the ring-shaped washer 136 concentric with the rest of the gearbox 60 .
- Equispaced about the central aperture 218 are six apertures 214 .
- One end of one of the spacers 206 is cold formed or otherwise rigidly connected to the first planet carrier plate 202 about each of the apertures 214 .
- An inwardly extending lip 216 is formed about each of the apertures 214 so that the diameter of each aperture 214 is slightly less than the diameter of the hollow portion of the respective spacer 206 .
- the first planet carrier plate 202 is pressed from a suitable metal, e.g. steel.
- Arcuate shapings 218 are formed therein during manufacture. The purpose of the arcuate shapings 218 will be described below.
- the fact that the spacers 206 are hollow and located about the apertures 214 , 224 means that a plurality of passages are provided through the planet carrier assembly consisting of the first planet carrier plate 202 , the spacers 206 and the second planet carrier plate 204 .
- the second planet carrier plate 204 has a flange 226 arranged around the periphery of the central aperture 222 and extending axially towards the first planet carrier plate 202 .
- the second planet carrier plate 204 also has a flange 228 located around the periphery of the planar portion 220 , again extending towards the first planet carrier plate 202 .
- each planet wheel 230 is freely rotatable about the respective spacer 206 on which it is mounted. To achieve this, each planet wheel 230 is mounted on the respective spacer 206 by way of a bearing 232 .
- Each planet wheel 230 carries a first set of teeth 234 and a second set of teeth 236 (see FIG. 4 ).
- the first set of teeth 234 has a pitch circle which is greater than that of the second set of teeth 236 .
- the first set of teeth 234 is located adjacent the first planet carrier plate 202 and the second set of teeth 236 is located adjacent the second planet carrier plate 204 .
- Each planet wheel 230 is preferably machined as a single part or, if the first and second sets of teeth 234 , 236 are manufactured separately, they are rigidly connected together during manufacture.
- a plurality of holes 238 is also preferably machined into each planet wheel 230 in order to reduce the weight thereof.
- the positioning of the spacers 206 on which the planet wheels 230 are mounted and the pitch circle of the first set of teeth 234 are chosen so that, when the input gear 116 is introduced through the central aperture 208 of the first planet carrier plate 202 , the first set of teeth 118 of the input gear meshes with the first set of teeth 234 of each of the planet wheels 230 .
- the sun wheel 240 carries a set of teeth 246 whose pitch circle diameter is chosen such that the set of teeth 246 meshes with the second set of teeth 236 of the planet wheels 230 .
- a spacer washer 248 is positioned adjacent the sun wheel 242 and on the second shaft 38 on the side of the sun wheel 242 facing the first group of components 100 . The spacer washer 248 maintains the sun wheel and the input gear 116 at a fixed distance from one another when the gearbox 60 is assembled.
- first and second planet carrier plates 202 , 204 , the spacers 206 , the planet wheels 230 and the sun wheel 240 together form an assembly within which the planet wheels 230 are rotatable about their respective spacers 206 .
- the arcuate shapings 218 formed in the first planet carrier plate 202 are provided so as to allow the planet wheels 230 to rotate whilst keeping the spacers 206 as short as possible.
- the locking plate 250 is also included in the second group of components 200 .
- the locking plate 250 is generally planar and is formed from sheet steel.
- the locking plate 250 is generally circular and has a plurality of equispaced locking fingers 252 extending radially outwardly therefrom. Each locking finger 252 is generally trapezoidal in shape with the longest side radially outermost.
- Mounted on the locking plate 250 and radially inwardly of the locking fingers 252 are a plurality of tubular legs 254 .
- the number of tubular legs 254 provided on the locking plate 250 corresponds to the number of spacers 206 .
- the tubular legs 254 are positioned on the locking plate 250 so that the tubular legs 254 are aligned with and can pass into the passageways formed by the spacers 206 .
- the tubular legs 254 are punched into or otherwise rigidly fixed to the locking plate 250 .
- Each tubular leg 254 is hollow and has a screw-threaded portion on the internal surface thereof adjacent the locking plate 250 .
- the outer diameter of each tubular leg 254 is sufficiently small to pass through the aperture defined by the lip 216 formed in the first planet carrier plate 202 .
- a compression spring 256 is located around each tubular leg 254 .
- the diameter of each compression spring 256 is larger than the aperture formed by the respective lip 216 .
- the end of each compression spring 256 facing the first planet carrier plate 202 therefore abuts against the respective lip 216 .
- Bolts 258 having enlarged heads and screw-threaded distal ends are located inside the tubular legs 254 and held in position by means of the screw-threaded portions.
- Each bolt 258 has an enlarged head which is dimensioned so as to pass freely along the passageway formed within the spacer 206 but against which the end of the compression spring 256 closest to the second planet carrier plate 204 abuts.
- the compression spring 256 therefore abuts against the lip 216 at one end and against the head of the bolt 258 at the other end.
- the tubular legs 254 are thus slidably mounted within the spacers 206 so that the locking plate 250 can be displaced with respect to the first and second planet carrier plates 202 , 204 against the action of the compression springs 256 .
- FIG. 4 A cross section through the second group of components 200 in assembled form is shown in FIG. 4 .
- the locking plate 250 can be displaced in the direction of the arrow 260 against the biasing action of the compression springs 256 .
- the means by which the locking plate 250 can be so displaced will be described below. However, in the absence of any displacing force causing the locking plate 250 to move in the direction of the arrow 260 , the locking plate 250 will be biased into the position shown.
- the shape of the central aperture 262 of the locking plate 250 corresponds to the form of the arcuate shapings 218 formed in the first planet carrier plate 202 .
- the inwardly extending portions 264 of the central aperture 262 lie between the raised portions 218 a of the arcuate shapings 218 of the first planet carrier plate 202 . This arrangement helps to minimise the axial depth of the gearbox 60 as a whole.
- the third group of components 300 simply comprises an annulus 302 and a housing 304 .
- the annulus 302 includes a set of teeth 306 whose pitch circle diameter is chosen so that the first sets of teeth 234 of the planet wheels 230 forming part of the second group of components 200 mesh therewith.
- the annulus 302 is moulded from a hard engineering thermoplastics material, such as an acetal.
- An inwardly extending flange 308 is integrally formed with the set of teeth 306 on the side thereof closest to the housing 304 .
- Also integrally formed with the set of teeth 306 and the flange 308 are a plurality of radially outwardly extending projections 310 which are equispaced about the outer surface of the annulus 302 . In the embodiment shown, twelve outwardly extending projections 310 are provided.
- the housing 304 is generally dish-shaped and has a support plate 312 having a central aperture 314 located therein.
- the central aperture 314 is sufficiently large to allow the second shaft 38 to pass therethrough.
- the central aperture 314 has a periphery which includes projecting lugs 316 which assist in the rigid attachment of the first shaft 36 to the support plate 312 .
- a plurality of locating fingers 318 extend axially from the periphery of the support plate 312 .
- the number of locating fingers 318 corresponds to the number of locking fingers 252 of the locking plate 250 . In the embodiment shown, twelve locating fingers are provided.
- the locating fingers 318 are equispaced about the central aperture 314 .
- the locating fingers 318 are separated by recesses 320 which receive the projections 310 of the annulus 302 . When the annulus 302 is seated within the housing 304 , the inter-engagement of the projections 310 and the recesses 320 prevent any relative rotation of the annulus 302 with respect to the housing 304 .
- the locking plate 250 has two operative positions; a first position in which the only force applied thereto is the biasing force of the compression springs 256 so that the locking plate is pressed towards the housing 304 and the annulus 302 , and a second position in which a displacing force is applied to the locking plate 250 to move it away from the housing 304 and the annulus 302 .
- the locking fingers 252 interleave with the locating fingers 318 so as to prevent any relative rotation between the second group of components 200 and the third group of components 300 . Any rotation of any one of the second group of components 200 will cause the whole assembly of the first and second groups of components 200 , 300 to rotate as well.
- the whole of the gearbox 60 will be rotated in the same direction and at the same speed.
- the locking plate 250 is displaced away from the housing 304 and the annulus 302 (in the direction of the arrow 260 shown in FIG.
- FIGS. 6 b and 6 c are perspective views of the same working components 302 , 230 , 116 , 240 shown in assembled form and from two different angles. In both cases, all other components have been omitted for clarity.
- the input gear 116 is rigidly connected to the drive wheel 102 which is driven by the drive belt 46 .
- the sun wheel 240 is rigidly connected to the second shaft 38 , which carries the second rotatable portion 34 of the drum 30
- the annulus 302 is rigidly connected (via the housing 304 ) to the first shaft 36 , which carries the first rotatable portion 32 of the drum 30 .
- the input gear 116 is turned as a result of the drive belt 46 causing rotation of the drive wheel 102 .
- the intermeshing of the set of teeth 118 of the input gear with the first sets of teeth 234 of the planet wheels 230 causes the planet wheels 230 to rotate about their respective spacers 206 .
- the first sets of teeth 234 also mesh with the set of teeth 306 of the annulus 302 causing rotation thereof.
- the planet carrier plates 202 , 204 are prevented from rotating about the axis 40 .
- the rotation of the planet wheels 230 about their respective spacers 206 inevitably causes rotation of the second sets of teeth 236 of the planet wheels 230 and the intermeshing of these second sets of teeth 236 with the sun wheel 240 causes the sun wheel 240 to rotate.
- the arrangement ensures that the direction of rotation of the annulus 302 is opposite to that of the sun wheel 240 .
- the direction of rotation of the input gear 116 is as indicated by the arrow 62
- the direction of rotation of the annulus 302 is as indicated by the arrow 64
- the direction of rotation of the sun wheel 240 is as indicated by the arrow 66 .
- An actuator 70 is provided which is capable of moving the locking plate 252 towards and away from the housing 304 .
- the actuator 70 is shown in exploded form in FIG. 7 . It comprises a first actuator ring 72 and a second actuator ring 74 .
- the first actuator ring 72 has a generally ring-shaped body 76 having a flange 78 extending radially outwardly therefrom on a side remote from the second actuator ring 74 .
- the ring-shaped body 76 is planar on the side remote from the second actuator ring 74 but has a plurality of raised portions 80 arranged in the side thereof facing the second actuator ring 74 .
- Each raised portion 80 has an inclined surface 80 a arranged on either side thereof as shown in FIG. 7 .
- Two raised portions 80 are provided in the embodiment shown.
- the raised portions 80 are arranged symmetrically about the ring-shaped body 76 . It will be appreciated that more than two raised portions 80 can be provided if desired.
- On one side of the first actuator ring 72 is a radially-projecting lug 82 which carries an arcuate rack of teeth 84 whose purpose will be explained below.
- a track 81 is provided on the ring-shaped body 76 between the raised portions 80 and the flange 78 .
- a plurality of slots 83 are formed in the ring-shaped body 76 in the radially innermost surface thereof.
- the second actuator ring 74 is also generally ring-shaped.
- the diameter of the second actuator ring corresponds to the diameter of the ring-shaped body 76 of the first actuator ring 72 .
- a plurality of raised portions 86 are arranged about the outer periphery of the second actuator ring 74 and facing the first actuator ring 72 .
- Each of the raised portions 86 has an inclined surface 86 a arranged on either side thereof in the same manner as that of the raised portions 80 .
- the raised portions 86 are also symmetrically arranged about the second actuator ring 74 and the number of raised portions 86 corresponds to the number of raised portions 80 .
- the inclination of the inclined surfaces 86 a is the same as that of the inclined surfaces 80 a so that the inclined surfaces 80 a , 86 a are able to cooperate with one another to cause the axial spacing of the first and second actuator rings 72 , 74 to be varied when the first and second actuator rings 72 , 74 are rotated with respect to one another.
- a plurality of outwardly extending projections 87 are provided on the second actuator ring 74 .
- the projections 87 are dimensioned and located so that, in a specific rotational orientation of the second actuator ring 74 with respect to the first actuator ring 72 , the projections 87 can pass along the slots 83 to a position in which the projections 87 are located beneath the track 81 .
- a plurality of locating legs 88 are provided on the second actuating ring 74 .
- the locating legs 88 are arranged radially inwardly of the raised portions 86 and extend in an axial direction away from the gearbox 60 .
- the locating legs 88 can pass through the centre of the first actuator ring 72 and beyond the flange 78 .
- Each locating leg 88 has an axially extending slot 90 therein which is open at the distal end thereof. The purpose of these components will be described and explained below.
- the side of the second actuator ring 74 remote from the first actuator ring 72 is shaped so as to included a plurality of shallow depressions 92 symmetrically arranged around the periphery thereof.
- the number and size of the depressions 92 are selected so that the locking fingers 252 of the locking plate 250 can be received therein.
- the actuator 70 also includes a plurality of connectors 94 by means of which the first actuator ring 72 can be attached to the tub 18 of the washing machine 10 .
- Each connector 94 comprises a support portion 94 a having an aperture extending therethrough and an enlarged head 94 b located at the end of the support portion 94 a remote from the tub 18 .
- the head 94 b is enlarged on one side thereof so that, when the connector is fixedly attached to the tub 18 by means of a self-tapping screw being passed through the aperture and into a bore formed in the tub 18 , the enlarged head 94 b overhangs the flange 78 of the first actuator ring 72 .
- the support portion 94 a of the connector maintains the head 94 b at a fixed distance from the tub 18 , the distance being slightly more than the thickness of the flange 78 , so that the flange 78 is not pressed against the surface of the tub 18 , but can slide between the head 94 b and the surface of the tub 18 .
- a plurality of connectors 94 are provided, the connectors 94 being spaced about the periphery of the first actuator ring 72 .
- the connectors are located about the axis 40 .
- the first actuator ring 72 is held captive in a fixed position with respect to the tub 18 whilst being capable of rotational movement about the axis 40 .
- the second actuator ring 74 is then located adjacent the first actuator ring 72 with the locating legs 88 passing through the centre of the first actuator ring 72 and with the raised portions 80 , 86 of each actuator ring 72 , 74 located adjacent one another.
- the tub 18 is manufactured with a plurality of ribs 18 a extending radially outwardly from the centre thereof and these ribs 18 a are received in the slots 90 in the locating legs 88 .
- This arrangement prevents any rotation of the second actuator ring 74 with respect to the tub 18 whilst allowing the second actuator ring 74 to move axially with respect to the tub 18 , at least within certain limits. Within those limits, the ribs 18 a remain within the slots 90 to prevent rotational movement of the second actuator ring 74 with respect to the tub 18 .
- FIG. 8 shows the tub 18 with the second actuator ring 74 in place, the first actuator ring 72 having been omitted for clarity. It will be appreciated that, even if the second actuator ring 74 is displaced in the direction of the arrow 70 a , rotational movement of the second actuator ring 74 with respect to the tub 18 is prevented.
- a motor 96 carrying a pinion 96 a is provided.
- the motor 96 is mounted on a support plate 98 which is fixedly connected to the tub 18 .
- Two switches 98 a , 98 b are also mounted on the support plate 98 , the switches 98 a , 98 b being spaced from one another along an arcuate path and equidistant from the axis 40 .
- the pinion 96 a cooperates with the arcuate rack of teeth 84 carried on the lug 82 forming part of the first actuator ring 72 .
- Operation of the motor 96 causes the pinion 96 a to rotate which, in turn, causes the lug 82 to be moved with respect to the tub 18 .
- the provision and arrangement of the connectors 94 means that this movement of the lug 82 can only result in a rotation of the whole of the first actuator ring 72 about the axis 40 .
- the rotation of the first actuator ring 72 causes the raised portions 80 , 86 to cooperate so as to move the second actuator ring 74 away from the first actuator ring 72 .
- the lug 82 comes into contact with one or other of the switches 98 a , 98 b .
- the switches 98 a , 98 b are connected to circuitry (not shown) which informs the control processor of the washing machine 10 as to whether or not the gearbox 60 is operating in the manner described above to allow the first and second rotatable portions of the drum to rotate in opposite directions.
- FIG. 9 a is a plan view of the driving mechanism 50 when the first and second actuator rings 72 , 74 are positioned so that the raised portions 80 are circumferentially spaced from the raised portions 86 .
- the locking plate 250 is biased into the first position in which the locking fingers 252 of the locking plate 250 are interengaged with the locating fingers 318 .
- both the first and second rotatable portions 32 , 34 of the drum 30 are rotated at the same speed and in the same direction.
- the lug 82 is in contact with the switch 98 a , which tells the controlling circuitry that the driving mechanism 50 is operating in a manner in which rotation of the input gear 116 results in rotation of both of the first and second rotatable portions 32 , 34 of the drum 30 at the same speed and in the same direction.
- the motor 96 When it is desired to change the mode of operation of the driving mechanism 50 , the motor 96 is operated so as to rotate the pinion 96 a .
- the first actuator ring 72 is thus rotated about the axis 40 and the second actuator ring 74 then moves axially away from the tub 18 .
- the second actuator ring 74 abuts against the locking plate 250 and the locking fingers 252 of the locking plate 250 become seated in the depressions of the second actuator ring 74 . Further movement of the second actuator ring 74 causes the locking fingers 252 to become disengaged from the locating fingers 318 of the housing 304 .
- Rotation of the locking plate 250 about the axis 40 is prevented: hence, rotation of the first and second planet carrier plates 202 , 204 is also prevented.
- the lug 82 contacts the switch 98 b which 20 informs the controlling circuitry that the driving mechanism 50 is operating in a manner in which rotation of the input gear 116 will result in rotation of the first and second rotatable portions 32 , 34 of the drum 30 at the same speed but in opposite directions.
- FIG. 10 a is a cross-section through the driving mechanism 50 in the position shown in FIG. 9 a .
- the lower half of FIG. 10 a is taken along the line A-A of FIG. 9 a and the upper half is taken along the line B-B of FIG. 9 a .
- the locking plate 250 is pressed to the left under the action of the compression springs 256 so that the locking fingers 252 are interengaged with the locating fingers 318 of the housing 304 .
- the second actuator ring 74 is spaced axially from the locking plate 250 so as to maintain the locking effect between the second and third groups of components 200 , 300 .
- FIG. 10 b is a cross-section through the driving mechanism 50 in the position shown in FIG. 9 b .
- the lower half of FIG. 10 b is taken along the line A-A of FIG. 9 b and the upper half is taken along the line B-B of FIG. 9 b .
- the second actuator ring 74 maintains the locking plate 250 out of contact with the locating fingers 318 against the action of the compression springs 256 and prevents rotation thereof about the axis 40 .
- the working components 116 , 230 , 240 , 302 are thus able to operate in the manner described above in relation to FIGS. 6 b and 6 c.
- the washing machine described above can be used in the following manner. Once the articles to be washed have been placed in the interior of the drum 30 via the door 16 , the program to be used has been selected and the detergent has been placed in the soap tray 24 (not necessarily in that order), the machine 10 begins to operate a wash/spin cycle. Water is introduced to the tub 18 via the water inlet conduit 22 and the soap tray 24 so as to introduce water and detergent to the interior of the drum and thus wet the articles. It will be appreciated that the detergent can be introduced to the interior of the drum by other means such as, for example, by placing liquid detergent in a ball inside the drum 30 or by using detergent tablets. Fabric softener can also be used.
- the actuator 70 is positioned so that the first actuator ring 72 is in the position shown in FIG. 9 a .
- the locking plate 250 is biased into the first position in which the locking fingers 252 are interengaged with the locating fingers 318 of the housing 304 .
- the lug 82 is in contact with the switch 98 b which communicates to the controlling circuitry that the locking plate 250 is in the first position.
- the motor 42 is then driven so that the drive belt 46 causes rotation of the drive wheel 102 .
- This in turn causes the first and second rotatable portions 32 , 34 of the drum 30 to rotate in the same direction and at the same speed. This synchronized rotation is continued for a short period of time so as to ensure that all of the articles are thoroughly wetted by the water and to commence the washing process.
- Consecutive periods can involve rotating the first and second rotatable portions 32 , 34 in different directions if desired. To achieve this, the direction of rotation of the motor 42 is reversed after each period has been completed.
- the motor 42 is first stopped.
- the drum 30 thus stops rotating.
- the motor 96 is operated so as to turn the pinion 96 a which, in turn, causes the first actuator ring 72 to rotate about the axis 40 of the washing machine 10 .
- the second actuator ring 74 is therefore moved away from the first actuator ring 72 so that the locking plate 250 is displaced in the direction of the arrow 260 in FIG. 4 into the second position.
- the lug 82 also contacts the switch 98 a so as to communicate to the controlling circuitry that counter rotation will commence if the motor is operated.
- the motor 42 is then operated again so that the first and second rotatable portions 32 , 34 of the drum 30 rotate in opposite directions and at substantially the same speed. This allows a high rate of agitation to be applied to the articles.
- the speed of rotation of each rotatable portion 32 , 34 in this mode is less than 100 rpm, commonly around 50 rpm, but will not normally be higher than 200 rpm.
- the motor 42 When sufficient agitation has been applied to the articles to achieve the standard of cleaning required by the selected program, the motor 42 is stopped.
- the motor 96 is operated again so as to return the first actuator ring 72 to the position shown in FIG. 9 a which, in turn, causes the locking plate 250 to return to the first position. Subsequent operation of the motor 42 thus causes synchronized rotation of the first and second rotatable portions 32 , 34 as has already been described. In this mode, the washing water and detergent can be drained out of the tub 18 through the drainage outlet 28 via the water drainage conduit 26 .
- Rinse water is then introduced to the tub 18 in a known manner and the speed of rotation of the drum 30 is then increased to a spin speed (commonly 800-1500 rpm) in order to spin the rinse water out of the articles.
- the rinse and spin steps are repeated 3 or 4 times. Spin cycles of this type are well known and need not be described any further here.
- the second planet carrier could carry retractable locking pins which could be extended to lock the second planet carrier plate to the housing and retracted to allow relative rotation therebetween.
- the locking plate could carry movable pins which could be moved into the weight-reducing holes formed in the planet wheels.
- Other methods and mechanisms for achieving a similar locking effect will be apparent to a skilled reader.
- the axis 40 of the washing machine 10 about which the rotatable portions 32 , 34 of the drum 30 rotate is arranged so as to be inclined slightly to the horizontal, rather than precisely horizontal. The angle of inclination to the horizontal is unlikely to be greater than 15° because an angle much greater than this may affect the wash action achievable by the wash action described above. Nevertheless, the term “substantially horizontal” as used in the claims appended hereto is intended to include axes inclined at an angle of up to 15° to the horizontal.
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Abstract
An appliance having a driving mechanism is provided including two rotatable portions which are rotatable by the driving mechanism about an axis. The driving mechanism includes a gearbox having an input gear, two output gears and a locking mechanism movable between a first position and a second position. The arrangement is such that, when the locking mechanism is in the first position and the input gear is driven, both output gears rotate in the same direction and, when the locking mechanism is in the second position and the input gear is driven, the output gears rotate in opposite directions. The arrangement of the axis is horizontal or substantially horizontal. The invention is particularly suitable for use in a front-loading washing machine having a drum including two rotatable portions. The driving mechanism can be used to selectively cause rotation of the rotatable portions either in the same direction or in opposite directions.
Description
- This application is a continuation of Ser. No. 10/276,800, filed Nov. 19, 2002, now U.S. Pat. No. ______, which was a national stage application under 35 USC 371 of International Application No. PCT/GB 01/01999, filed May 9, 2001, the disclosures of which are incorporated herein by reference.
- The invention relates to an appliance having a driving mechanism. The invention relates particularly, but not exclusively, to a domestic appliance, for example a washing machine, having a driving mechanism. The invention also relates to a method of operating such an appliance.
- Driving mechanisms for use in appliances in general are well known. Furthermore, such driving mechanisms in the form of planetary or epicyclic gears are well known and are commonly used to drive rotating bodies when it is desired periodically to reverse the direction of the output rotation. Under such circumstances, the configuration of the epicyclic gear is altered so that, for a given direction of input rotation, the direction of the output rotation can be selected.
- It has been proposed in WO 99/58753 to provide a domestic appliance in the form of a washing machine which incorporates a drum having two rotatable portions and drive means for rotating the rotatable portions so that relative rotation between the rotatable portions can be achieved. In one embodiment, the two rotatable portions of the drum are rotatable at substantially the same speed in opposite directions for at least part of the period of operation of the washing machine. This arrangement causes increased agitation to the articles contained within the washing machine during the washing portion of the operating cycle. However, the rotatable portions of the drum are then also required to rotate at the same speed and in the same direction in order adequately to spin rinse water out of the articles during the spinning portion of the operating cycle. In order to achieve this, each drum has been provided with a separate drive mechanism so that each drum can be rotated at the required speed and in the required direction at the appropriate time in the operating cycle. Control means are then required to ensure that each drive mechanism operates correctly during each part of the operating cycle. Also, two separate motors are required which adds to the cost of the appliance and also to the volume of components which need to be housed within a fixed space.
- U.S. Pat. No. 4,910,979 and U.S. Pat. No. 5,000,016 each disclose a vertical-axis washing machine having a tub, a basket in which articles to be washed are received, and a central agitator located inside the basket. The basket and the agitator are each freely rotatable, in an oscillating manner, with respect to the tub. The driving mechanism which causes the basket and agitator to oscillate is an epicyclic arrangement by means of which, when the agitator is driven through a given angle in a first direction about the vertical axis, the basket rotates, albeit through a smaller angle of rotation, in the opposite direction. The angle of rotation of the basket is dependent upon many factors, including the system inertia, the angle of the agitator stroke and the size of the load in the washing machine. Such an arrangement is not suitable for use in horizontal-axis washing machines primarily because the washing action in a horizontal-axis machine is very different from that in a vertical-axis machine.
- An object of the invention is to provide an appliance having a driving mechanism which is suitable for use in a horizontal axis washing machine. A further object of the invention is to provide an appliance having a driving mechanism which can be used to drive two rotatable portions of the drum of a horizontal-axis washing machine. Another object of the invention is to provide a horizontal-axis washing machine in which the number of drive motors required to be used is reduced. A still further object of the present invention is to provide an appliance of the type described above in which the cost of manufacture is reduced and/or in which the number of drive motors required is reduced.
- The invention provides an appliance comprising two rotatable portions and a driving mechanism for rotating the rotatable portions about an axis, the driving mechanism comprising a gearbox having an input gear, two output gears connected to the rotatable portions and a locking mechanism movable between a first position and a second position, the arrangement being such that, when the locking mechanism is in the first position and the input gear is driven, both output gears rotate in the same direction and, when the locking mechanism is in the second position and the input gear is driven, the output gears rotate in opposite directions, characterized in that the axis is arranged horizontally or substantially horizontally.
- The arrangement according to the invention allows an appliance having two portions rotatable about a horizontal axis to be provided with a single drive mechanism having a single input gear but having two output gears. By means of the locking mechanism, the output gears can be selected to rotate either in the same direction when they are required to do so (e.g., during delicate washing portions and spinning portions of an operating cycle in a washing machine) or in opposite directions when they are required to do so (e.g., during normal or “heavy soil” washing portions of an operating cycle in a washing machine). Only a single drive motor is then required to be connected to the input gear, with no additional drive motors being required to achieve either synchronized rotation or counter rotation during the relevant portions of the operating cycle. (It will be understood that an arrangement of more than one drive motor operating in series can be provided to drive the input gear without departing from the scope of the present invention.) This means that the number of motors required to achieve the required manner of operation is reduced which, in turn, leads to a reduction in the number of bulky components requiring to be housed within the casing of the appliance and a reduction in the cost of the appliance.
- It is preferred that the output gears are arranged coaxially and that the input gear is coaxial with the output gears. In a preferred embodiment, each output gear is connected to a shaft and the shafts are arranged coaxially, one inside the other. These features provide a compact and efficient arrangement which is suitable for use in a horizontal-axis washing machine in which the drum portions are supported in a cantilever fashion to allow the provision of a front-opening door.
- Preferably, the arrangement is such that, when the locking mechanism is in the first position and the input gear is driven, both output gears rotate in the same direction and at the same speed. More preferably, when the locking mechanism is in the second position and the input gear is driven, the output gears rotate in opposite directions at substantially the same speed. This arrangement is particularly suitable for use in a washing machine of the type described in WO 99/58753, because the operating cycle of the washing machine requires the drum portions to rotate in the same direction and at the same speed for some of the time and in opposite directions at substantially the same speed for some of the time.
- In a preferred embodiment, the gearbox comprises a gear with a planetary arrangement and having an annulus, a plurality of planet wheels carried on a planet carrier, and two sun wheels. It is preferred that, when the locking mechanism is in the first position, the locking mechanism engages both the planet carrier and the annulus so as to prevent relative rotation therebetween. More preferably, the locking mechanism and the annulus each carry a plurality of projections, the projections carried by the locking mechanism interengaging with the projections carried by the annulus when the locking mechanism is in the first position. Even more preferably, the locking mechanism is mounted on the planet carrier.
- The arrangement thus provided is compact and relatively easy to incorporate into an appliance of the type described in WO 99/58753. The operation of the locking mechanism is also reliable and not greatly prone to failure, as is required in the envisaged application of a washing machine.
- The driving mechanism preferably incorporates an actuator for moving a locking plate of the locking mechanism from a first position to a second position. The actuator preferably comprises a first actuator ring and a second actuator ring, the first actuator ring being attached to a fixed portion of the appliance in a manner which allows rotation thereof about an axis of the gearbox and having inclined surfaces facing the second actuator ring, the second actuator ring being engaged with the fixed portion of the appliance in a manner which allows movement thereof parallel to the axis of the gearbox and having inclined surfaces facing the first actuator ring and complimentary to the inclined surfaces of the first actuator ring, such that rotational movement of the first actuator ring causes movement of the second actuator ring parallel to the axis of the gearbox as a result of the movement of the inclined surfaces across one another.
- This arrangement allows the driving mechanism to be converted between synchronized rotation and counter rotation simply by rotation of the first actuator ring about an axis of the gearbox. The rotation of the first actuator ring can be achieved simply and effectively using known techniques.
- The invention further provides a method of operating an appliance of the type described above, the method comprising the steps of:
- (a) driving the input gear with the locking mechanism in the first position so as to cause the output gears to rotate in the same direction;
- (b) causing the locking mechanism to move from the first position to the second position; and
- (c) driving the input gear with the locking mechanism in the second position so as to cause the output gears to rotate in opposite directions.
- Preferably, during step (c), the output gears rotate in opposite directions at substantially the same rotational speed. Such a method is highly suitable for operating a washing machine of the type described in WO 99/58753.
- An embodiment of the invention will now be described, by way of example only, with reference to the accompanying drawings, in which:
-
FIG. 1 is a schematic side view of an appliance, being a washing machine, having a driving mechanism and according to the invention; -
FIG. 2 is an exploded view of a gearbox forming part of the driving mechanism incorporated into the washing machine shown inFIG. 1 ; -
FIG. 3 a is a perspective view of a first group of the components shown inFIG. 2 in an assembled form; -
FIG. 3 b is a sectional view through the first group of components ofFIG. 3 a; -
FIG. 4 is a sectional view through a second group of the components shown inFIG. 2 in an assembled form; -
FIG. 5 is a perspective view of a third group of the components shown inFIG. 2 in an assembled form; -
FIG. 6 a is an exploded view of several of the components shown inFIG. 2 and forming the working parts of the gearbox; -
FIG. 6 b is a first perspective view of the components ofFIG. 6 a in assembled form and illustrating the action of the gearbox; -
FIG. 6 c is a second perspective view of the components ofFIG. 6 b; -
FIG. 7 is an exploded view of an actuator forming part of the driving mechanism incorporated into the washing machine shown inFIG. 1 ; -
FIG. 8 is a perspective view of the rear of a tub forming part of the washing machine ofFIG. 1 with part of the actuator ofFIG. 7 attached thereto; -
FIG. 9 a is a schematic plan view of the rear of the tub and part of the actuator showing the position thereof when synchronized rotation of the drum portions is required; -
FIG. 9 b is a schematic plan view of the rear of the tub and part of the actuator showing the position thereof when counter rotation of the drum portions is required; -
FIG. 10 a is a cross-section through the gearbox and actuator during synchronized rotation of the drum portions; and -
FIG. 10 b is a cross-section through the gearbox and actuator during counter rotation of the drum portions. - In the embodiment illustrated in the drawings, the invention is embodied in a domestic washing machine having a driving mechanism. Such a washing machine is illustrated, schematically, in side view in
FIG. 1 . Thewashing machine 10 has anouter casing 12 having afront panel 14 in which is located adoor 16. A water-tight tub 18 is mounted inside thecasing 12 in a known manner by aspring damper mechanism 20. Awater inlet conduit 22 communicates with an upper portion of thetub 18 via asoap tray 24. Awater drainage conduit 26 communicates with a lower portion of thetub 18 and also with adrainage outlet 28. Appropriate pumps and valves (not shown) are provided for controlling the inlet and drainage of water to and from thetub 18. The components described thus far are all well known in the art and form no part of the present invention. - Mounted inside the
tub 18 is adrum 30 consisting of a firstrotatable portion 32 and a secondrotatable portion 34. The firstrotatable portion 32 is mounted in cantilever fashion on afirst shaft 36 and the secondrotatable portion 34 is mounted coaxially with the first rotatable portion on asecond shaft 38. As shown inFIG. 1 , thesecond shaft 38 is rotatably mounted within thefirst shaft 36, which is hollow. The first andsecond shafts axis 40 of thedrum 30. - The features thus far described are disclosed and described in further detail in WO 99/58753. However, in the published document, the means by which the first and second
rotatable portions drum 30 comprise separately driven motors. In the embodiment according to the present invention, the first and secondrotatable portions 32 are driven by asingle motor 42. This is achieved according to the invention by providing adriving mechanism 50 located on the side of thetub 18 remote from thedoor 16. Thedriving mechanism 50 is driven by adrive belt 46 located on a shaft 48 of themotor 42. Thedriving mechanism 50 consists of agearbox 60 and anactuator 70. Theactuator 70 is mounted on thetub 18 in a manner which will be described below. Thegearbox 60 is mounted on the first andsecond shafts driving mechanism 50 allows thesingle motor 42 to drive the first and secondrotatable portions - The
driving mechanism 50 comprises agearbox 60 and anactuator 70. The components of thegearbox 60 are shown in exploded form inFIG. 2 . For the sake of clarity, the components of the gearbox will be grouped into three groups of components; a first group ofcomponents 100, a second group ofcomponents 200 and a third group ofcomponents 300. Each group of components will now be described in detail. - The first group of
components 100 includes adrive wheel 102 which is generally dish shaped. Thedrive wheel 102 has a generallycircular cover plate 104 which has acentral aperture 106. Extending axially from the periphery of thecover plate 104 is acylindrical surface 108. Aflange 110 extends radially outwardly from thecylindrical surface 108 on the side thereof remote from thecover plate 104. - The
cover plate 104 has three radially extendingribs 112 which are formed integrally therewith. Theribs 112 are equispaced about thecentral aperture 106. Also, a plurality ofholes 114 are equispaced about thecentral aperture 106 in the vicinity thereof. - The first group of
components 100 also incorporates aninput gear 116 comprising a set ofteeth 118 and asupport collar 120. The set ofteeth 118 and thesupport collar 120 are rigidly connected to one another. Abore 122 extends through theinput gear 116. Formed in the face of thesupport collar 120 facing thecover plate 104 are three equiangularly spacedrecesses 124 which co-operate with theribs 112 formed in thecover plate 104. Also, bores 126 extend through thesupport collar 120 so as to be aligned with theholes 114 formed in thecover plate 104. - The
bore 122 formed in theinput gear 116 is sufficiently large to receive asleeve 128 and two axially spacedbearings 130 therein without play. Alip 122 a extends radially inwardly at the end of thebore 122 remote from thesupport collar 120. Each of thebearings 130 and thesleeve 128 has an inner bore which is dimensioned so as to receive a distal end of thesecond shaft 38, also without play. A screw-threadedbolt 132 is provided to co-operate with a screw-threaded bore located in the distal end of thesecond shaft 38. Awasher 134 is provided between the head of thebolt 132 and the side of the bearing 130 closest thereto. The outer diameter of thewasher 134 is larger than the inner diameter of thebearing 130 so that, when theinput gear 116 is rigidly connected to thedrive wheel 102, thesleeve 128 andbearings 130 are held captive in thebore 122 between thelip 122 a and thewasher 134. Thecentral aperture 106 in thecover plate 104 is sufficiently large to allow the head of thebolt 132 and thewasher 134 to pass therethrough. A ring-shapedbearing washer 136 is provided on theinput gear 116. The ring-shapedbearing washer 136 is dimensioned so that it will fit loosely over the set ofteeth 118 but will not project radially beyond thesupport collar 120. - The first group of
components 100 is shown in assembled form inFIGS. 3 a and 3 b. As can be seen, theinput gear 116 is held securely against thecover plate 104 by means ofrivets 138 passing through theholes 114 of thecover plate 104 and into thebores 126 of thesupport collar 120. Theribs 112 and therecesses 124 co-operate so as to ensure that theinput gear 116 is correctly aligned about theaxis 40 with respect to thecover plate 104. The distal end of theshaft 38 is thus retained within thebore 122 by means of thebolt 132. However, thebearings 130 allow thedrive wheel 102, together with theinput gear 116, to rotate freely about the distal end of theshaft 38. - The
cylindrical surface 108 of thedrive wheel 102 receives thedrive belt 46. Theflange 110 assists in retaining thedrive belt 46 in position on thecylindrical surface 108. Thecylindrical surface 108 can have an anti-slip coating or texturing applied thereto in order to reduce the risk of slippage between thedrive belt 46 and thedrive wheel 102. - The second group of
components 200 will now be described. The second group ofcomponents 200 includes a firstplanet carrier plate 202, a secondplanet carrier plate 204 and a plurality ofspacers 206. In the embodiment shown, sixspacers 206 are provided. Thespacers 206 are equispaced about the axis of thegearbox 60 and are rigidly connected to each of the first and secondplanet carrier plates planet carrier plates spacers 206 are tubular. - The first
planet carrier plate 204 faces theinput gear 116. It is generally circular in shape and has acentral aperture 208. Thecentral aperture 208 is sufficiently large to allow the set ofteeth 118 of theinput gear 116 to pass therethrough. Aplanar portion 210 surrounding thecentral aperture 208 is radially bounded by aridge 212 whose inner diameter is slightly larger than the outer diameter of thesupport collar 120 of theinput gear 116. The ring-shapedbearing washer 136 of the first group ofcomponents 100 is thus locatable adjacent theplanar portion 210. Theridge 212 maintains the ring-shapedwasher 136 concentric with the rest of thegearbox 60. - Equispaced about the
central aperture 218 are sixapertures 214. One end of one of thespacers 206 is cold formed or otherwise rigidly connected to the firstplanet carrier plate 202 about each of theapertures 214. An inwardly extendinglip 216 is formed about each of theapertures 214 so that the diameter of eachaperture 214 is slightly less than the diameter of the hollow portion of therespective spacer 206. - The first
planet carrier plate 202 is pressed from a suitable metal, e.g. steel.Arcuate shapings 218 are formed therein during manufacture. The purpose of thearcuate shapings 218 will be described below. - The second
planet carrier plate 204 is also formed from a suitable metal, e.g. steel. The secondplanet carrier plate 204 has an annularplanar portion 220 having acentral aperture 222.Apertures 224 are formed in theplanar portion 220 and are equispaced about thecentral aperture 222. Theapertures 224 are axially aligned with theapertures 214 formed in the firstplanet carrier plate 202. The ends of thespacers 206 remote from the firstplanet carrier plate 202 are cold formed or otherwise rigidly fixed to the secondplanet carrier plate 204 about theapertures 224. Thus it can be seen that thespacers 206 act so as to maintain the first and secondplanet carrier plates spacers 206 are hollow and located about theapertures planet carrier plate 202, thespacers 206 and the secondplanet carrier plate 204. - The second
planet carrier plate 204 has aflange 226 arranged around the periphery of thecentral aperture 222 and extending axially towards the firstplanet carrier plate 202. The secondplanet carrier plate 204 also has aflange 228 located around the periphery of theplanar portion 220, again extending towards the firstplanet carrier plate 202. - Mounted on
alternate spacers 206 and located between the first and secondplanet carrier plates planet wheels 230. Eachplanet wheel 230 is freely rotatable about therespective spacer 206 on which it is mounted. To achieve this, eachplanet wheel 230 is mounted on therespective spacer 206 by way of abearing 232. - Each
planet wheel 230 carries a first set ofteeth 234 and a second set of teeth 236 (seeFIG. 4 ). The first set ofteeth 234 has a pitch circle which is greater than that of the second set ofteeth 236. The first set ofteeth 234 is located adjacent the firstplanet carrier plate 202 and the second set ofteeth 236 is located adjacent the secondplanet carrier plate 204. Eachplanet wheel 230 is preferably machined as a single part or, if the first and second sets ofteeth holes 238 is also preferably machined into eachplanet wheel 230 in order to reduce the weight thereof. - The positioning of the
spacers 206 on which theplanet wheels 230 are mounted and the pitch circle of the first set ofteeth 234 are chosen so that, when theinput gear 116 is introduced through thecentral aperture 208 of the firstplanet carrier plate 202, the first set ofteeth 118 of the input gear meshes with the first set ofteeth 234 of each of theplanet wheels 230. - A
sun wheel 240 is positioned between the secondplanet carrier plate 204 and the first sets ofteeth 234 of theplanet wheels 230. Thesun wheel 240 is supported on thesecond shaft 38 and rotatable therewith. This is achieved by the provision ofsplines 242 provided in a central aperture in thesun wheel 242 and on the outer surface of thesecond shaft 38. By positioning of thesun wheel 242 on thesecond shaft 38 at the point at which the splines are provided, thesun wheel 240 is made rotatable therewith. Again, holes 244 are provided in thesun wheel 240 in order to reduce the weight thereof. Thesun wheel 240 carries a set ofteeth 246 whose pitch circle diameter is chosen such that the set ofteeth 246 meshes with the second set ofteeth 236 of theplanet wheels 230. Aspacer washer 248 is positioned adjacent thesun wheel 242 and on thesecond shaft 38 on the side of thesun wheel 242 facing the first group ofcomponents 100. Thespacer washer 248 maintains the sun wheel and theinput gear 116 at a fixed distance from one another when thegearbox 60 is assembled. - It will be appreciated that the first and second
planet carrier plates spacers 206, theplanet wheels 230 and thesun wheel 240 together form an assembly within which theplanet wheels 230 are rotatable about theirrespective spacers 206. Thearcuate shapings 218 formed in the firstplanet carrier plate 202 are provided so as to allow theplanet wheels 230 to rotate whilst keeping thespacers 206 as short as possible. - Also included in the second group of
components 200 is alocking plate 250. The lockingplate 250 is generally planar and is formed from sheet steel. The lockingplate 250 is generally circular and has a plurality ofequispaced locking fingers 252 extending radially outwardly therefrom. Each lockingfinger 252 is generally trapezoidal in shape with the longest side radially outermost. Mounted on thelocking plate 250 and radially inwardly of the lockingfingers 252 are a plurality oftubular legs 254. The number oftubular legs 254 provided on thelocking plate 250 corresponds to the number ofspacers 206. Thetubular legs 254 are positioned on thelocking plate 250 so that thetubular legs 254 are aligned with and can pass into the passageways formed by thespacers 206. Thetubular legs 254 are punched into or otherwise rigidly fixed to thelocking plate 250. Eachtubular leg 254 is hollow and has a screw-threaded portion on the internal surface thereof adjacent thelocking plate 250. The outer diameter of eachtubular leg 254 is sufficiently small to pass through the aperture defined by thelip 216 formed in the firstplanet carrier plate 202. - A
compression spring 256 is located around eachtubular leg 254. The diameter of eachcompression spring 256 is larger than the aperture formed by therespective lip 216. The end of eachcompression spring 256 facing the firstplanet carrier plate 202 therefore abuts against therespective lip 216.Bolts 258 having enlarged heads and screw-threaded distal ends are located inside thetubular legs 254 and held in position by means of the screw-threaded portions. Eachbolt 258 has an enlarged head which is dimensioned so as to pass freely along the passageway formed within thespacer 206 but against which the end of thecompression spring 256 closest to the secondplanet carrier plate 204 abuts. Thecompression spring 256 therefore abuts against thelip 216 at one end and against the head of thebolt 258 at the other end. Thetubular legs 254 are thus slidably mounted within thespacers 206 so that the lockingplate 250 can be displaced with respect to the first and secondplanet carrier plates - A cross section through the second group of
components 200 in assembled form is shown inFIG. 4 . As can be seen, the lockingplate 250 can be displaced in the direction of thearrow 260 against the biasing action of the compression springs 256. The means by which thelocking plate 250 can be so displaced will be described below. However, in the absence of any displacing force causing thelocking plate 250 to move in the direction of thearrow 260, the lockingplate 250 will be biased into the position shown. - The shape of the
central aperture 262 of thelocking plate 250 corresponds to the form of thearcuate shapings 218 formed in the firstplanet carrier plate 202. When thelocking plate 250 is in the position shown inFIG. 4 , i.e. when no displacing force in the direction ofarrow 260 is applied, the inwardly extending portions 264 of thecentral aperture 262 lie between the raisedportions 218 a of thearcuate shapings 218 of the firstplanet carrier plate 202. This arrangement helps to minimise the axial depth of thegearbox 60 as a whole. - The third group of
components 300 simply comprises anannulus 302 and ahousing 304. Theannulus 302 includes a set ofteeth 306 whose pitch circle diameter is chosen so that the first sets ofteeth 234 of theplanet wheels 230 forming part of the second group ofcomponents 200 mesh therewith. Theannulus 302 is moulded from a hard engineering thermoplastics material, such as an acetal. An inwardly extendingflange 308 is integrally formed with the set ofteeth 306 on the side thereof closest to thehousing 304. Also integrally formed with the set ofteeth 306 and theflange 308 are a plurality of radially outwardly extendingprojections 310 which are equispaced about the outer surface of theannulus 302. In the embodiment shown, twelve outwardly extendingprojections 310 are provided. - The
housing 304 is generally dish-shaped and has asupport plate 312 having acentral aperture 314 located therein. Thecentral aperture 314 is sufficiently large to allow thesecond shaft 38 to pass therethrough. Thecentral aperture 314 has a periphery which includes projectinglugs 316 which assist in the rigid attachment of thefirst shaft 36 to thesupport plate 312. - A plurality of locating
fingers 318 extend axially from the periphery of thesupport plate 312. The number of locatingfingers 318 corresponds to the number of lockingfingers 252 of thelocking plate 250. In the embodiment shown, twelve locating fingers are provided. The locatingfingers 318 are equispaced about thecentral aperture 314. The locatingfingers 318 are separated byrecesses 320 which receive theprojections 310 of theannulus 302. When theannulus 302 is seated within thehousing 304, the inter-engagement of theprojections 310 and therecesses 320 prevent any relative rotation of theannulus 302 with respect to thehousing 304. -
FIG. 5 shows thehousing 304 with theannulus 302 seated therein. As can be seen, the locatingfingers 318 project beyond theannulus 302 in the axial direction. Thus, the edge of the assembled third group ofcomponents 300 facing the lockingplate 250 has a castellated appearance. The locatingfingers 318 are dimensioned so that, when the lockingplate 250 is pressed towards the firstplanet carrier plate 202 under the action of the compression springs 256, the lockingfingers 252 of thelocking plate 250 interleave with the locatingfingers 318. - The locking
plate 250 has two operative positions; a first position in which the only force applied thereto is the biasing force of the compression springs 256 so that the locking plate is pressed towards thehousing 304 and theannulus 302, and a second position in which a displacing force is applied to thelocking plate 250 to move it away from thehousing 304 and theannulus 302. In the first position, the lockingfingers 252 interleave with the locatingfingers 318 so as to prevent any relative rotation between the second group ofcomponents 200 and the third group ofcomponents 300. Any rotation of any one of the second group ofcomponents 200 will cause the whole assembly of the first and second groups ofcomponents motor 42 drives thedrive belt 46 causing theinput gear 116 to be rotated, the whole of thegearbox 60 will be rotated in the same direction and at the same speed. The fact that thefirst shaft 36 is rigidly fixed to thehousing 304 and thesecond shaft 38 is rigidly fixed to thesun wheel 240, means that the first andsecond shafts rotatable portions drum 30 will rotate at the same speed and in the same direction. In the second operative position, the lockingplate 250 is displaced away from thehousing 304 and the annulus 302 (in the direction of thearrow 260 shown inFIG. 4 ) and the lockingfingers 252 become disengaged from the locating fingers 31. At the same time, the lockingplate 250 is prevented from rotating with respect to a fixed portion of the washing machine 10 (the tub 18) as will be described below. The working components of thegearbox 60 then operate as follows. - It will be understood from the foregoing description that the working components of the
gearbox 60 include anannulus 302, threeplanet wheels 230 and two sun wheels (input gear 116 and sun wheel 240). An exploded view of these components is given inFIG. 6 a.FIGS. 6 b and 6 c are perspective views of the same workingcomponents - It will be recalled from the foregoing description that the
input gear 116 is rigidly connected to thedrive wheel 102 which is driven by thedrive belt 46. It will also be recalled that thesun wheel 240 is rigidly connected to thesecond shaft 38, which carries the secondrotatable portion 34 of thedrum 30, and that theannulus 302 is rigidly connected (via the housing 304) to thefirst shaft 36, which carries the firstrotatable portion 32 of thedrum 30. - When the working
components FIGS. 6 b and 6 c with the locking plate in the second position described above, theinput gear 116 is turned as a result of thedrive belt 46 causing rotation of thedrive wheel 102. The intermeshing of the set ofteeth 118 of the input gear with the first sets ofteeth 234 of theplanet wheels 230 causes theplanet wheels 230 to rotate about theirrespective spacers 206. The first sets ofteeth 234 also mesh with the set ofteeth 306 of theannulus 302 causing rotation thereof. Theplanet carrier plates axis 40. The rotation of theplanet wheels 230 about theirrespective spacers 206 inevitably causes rotation of the second sets ofteeth 236 of theplanet wheels 230 and the intermeshing of these second sets ofteeth 236 with thesun wheel 240 causes thesun wheel 240 to rotate. The arrangement ensures that the direction of rotation of theannulus 302 is opposite to that of thesun wheel 240. Thus, if the direction of rotation of theinput gear 116 is as indicated by thearrow 62, then the direction of rotation of theannulus 302 is as indicated by thearrow 64 and the direction of rotation of thesun wheel 240 is as indicated by thearrow 66. Hence, when thedrive belt 46 is driven by themotor 42, thefirst shaft 36 and the firstrotatable portion 32 are driven in one direction and thesecond shaft 38 and the secondrotatable portion 34 are driven in the opposite direction. - An
actuator 70 is provided which is capable of moving thelocking plate 252 towards and away from thehousing 304. Theactuator 70 is shown in exploded form inFIG. 7 . It comprises afirst actuator ring 72 and asecond actuator ring 74. Thefirst actuator ring 72 has a generally ring-shapedbody 76 having aflange 78 extending radially outwardly therefrom on a side remote from thesecond actuator ring 74. The ring-shapedbody 76 is planar on the side remote from thesecond actuator ring 74 but has a plurality of raisedportions 80 arranged in the side thereof facing thesecond actuator ring 74. Each raisedportion 80 has aninclined surface 80a arranged on either side thereof as shown inFIG. 7 . Two raisedportions 80 are provided in the embodiment shown. The raisedportions 80 are arranged symmetrically about the ring-shapedbody 76. It will be appreciated that more than two raisedportions 80 can be provided if desired. On one side of thefirst actuator ring 72 is a radially-projectinglug 82 which carries an arcuate rack ofteeth 84 whose purpose will be explained below. Atrack 81 is provided on the ring-shapedbody 76 between the raisedportions 80 and theflange 78. A plurality ofslots 83 are formed in the ring-shapedbody 76 in the radially innermost surface thereof. - The
second actuator ring 74 is also generally ring-shaped. The diameter of the second actuator ring corresponds to the diameter of the ring-shapedbody 76 of thefirst actuator ring 72. A plurality of raisedportions 86 are arranged about the outer periphery of thesecond actuator ring 74 and facing thefirst actuator ring 72. Each of the raisedportions 86 has an inclined surface 86 a arranged on either side thereof in the same manner as that of the raisedportions 80. The raisedportions 86 are also symmetrically arranged about thesecond actuator ring 74 and the number of raisedportions 86 corresponds to the number of raisedportions 80. The inclination of the inclined surfaces 86 a is the same as that of theinclined surfaces 80 a so that theinclined surfaces 80 a, 86 a are able to cooperate with one another to cause the axial spacing of the first and second actuator rings 72,74 to be varied when the first and second actuator rings 72,74 are rotated with respect to one another. A plurality of outwardly extendingprojections 87 are provided on thesecond actuator ring 74. Theprojections 87 are dimensioned and located so that, in a specific rotational orientation of thesecond actuator ring 74 with respect to thefirst actuator ring 72, theprojections 87 can pass along theslots 83 to a position in which theprojections 87 are located beneath thetrack 81. As soon as thefirst actuator ring 72 is rotated with respect to thesecond actuator ring 74, the actuator rings 72,74 are held axially with respect to one another by virtue of the fact that theprojections 87 are retained beneath thetrack 81. - A plurality of locating
legs 88 are provided on thesecond actuating ring 74. The locatinglegs 88 are arranged radially inwardly of the raisedportions 86 and extend in an axial direction away from thegearbox 60. The locatinglegs 88 can pass through the centre of thefirst actuator ring 72 and beyond theflange 78. Each locatingleg 88 has an axially extendingslot 90 therein which is open at the distal end thereof. The purpose of these components will be described and explained below. - The side of the
second actuator ring 74 remote from thefirst actuator ring 72 is shaped so as to included a plurality ofshallow depressions 92 symmetrically arranged around the periphery thereof. The number and size of thedepressions 92 are selected so that the lockingfingers 252 of thelocking plate 250 can be received therein. - The
actuator 70 also includes a plurality ofconnectors 94 by means of which thefirst actuator ring 72 can be attached to thetub 18 of thewashing machine 10. Eachconnector 94 comprises a support portion 94 a having an aperture extending therethrough and an enlarged head 94 b located at the end of the support portion 94 a remote from thetub 18. The head 94 b is enlarged on one side thereof so that, when the connector is fixedly attached to thetub 18 by means of a self-tapping screw being passed through the aperture and into a bore formed in thetub 18, the enlarged head 94 b overhangs theflange 78 of thefirst actuator ring 72. The support portion 94 a of the connector maintains the head 94 b at a fixed distance from thetub 18, the distance being slightly more than the thickness of theflange 78, so that theflange 78 is not pressed against the surface of thetub 18, but can slide between the head 94 b and the surface of thetub 18. - A plurality of
connectors 94 are provided, theconnectors 94 being spaced about the periphery of thefirst actuator ring 72. The connectors are located about theaxis 40. In this way, thefirst actuator ring 72 is held captive in a fixed position with respect to thetub 18 whilst being capable of rotational movement about theaxis 40. Thesecond actuator ring 74 is then located adjacent thefirst actuator ring 72 with the locatinglegs 88 passing through the centre of thefirst actuator ring 72 and with the raisedportions actuator ring tub 18 is manufactured with a plurality ofribs 18 a extending radially outwardly from the centre thereof and theseribs 18 a are received in theslots 90 in the locatinglegs 88. This arrangement prevents any rotation of thesecond actuator ring 74 with respect to thetub 18 whilst allowing thesecond actuator ring 74 to move axially with respect to thetub 18, at least within certain limits. Within those limits, theribs 18 a remain within theslots 90 to prevent rotational movement of thesecond actuator ring 74 with respect to thetub 18.FIG. 8 shows thetub 18 with thesecond actuator ring 74 in place, thefirst actuator ring 72 having been omitted for clarity. It will be appreciated that, even if thesecond actuator ring 74 is displaced in the direction of thearrow 70 a, rotational movement of thesecond actuator ring 74 with respect to thetub 18 is prevented. - In order to bring about rotational movement of the
first actuator ring 72, amotor 96 carrying apinion 96 a is provided. Themotor 96 is mounted on asupport plate 98 which is fixedly connected to thetub 18. Two switches 98 a, 98 b are also mounted on thesupport plate 98, theswitches axis 40. Thepinion 96 a cooperates with the arcuate rack ofteeth 84 carried on thelug 82 forming part of thefirst actuator ring 72. Operation of themotor 96 causes thepinion 96 a to rotate which, in turn, causes thelug 82 to be moved with respect to thetub 18. The provision and arrangement of theconnectors 94 means that this movement of thelug 82 can only result in a rotation of the whole of thefirst actuator ring 72 about theaxis 40. The rotation of thefirst actuator ring 72 causes the raisedportions second actuator ring 74 away from thefirst actuator ring 72. Also, as thefirst actuator ring 72 rotates, thelug 82 comes into contact with one or other of theswitches switches washing machine 10 as to whether or not thegearbox 60 is operating in the manner described above to allow the first and second rotatable portions of the drum to rotate in opposite directions. -
FIG. 9 a is a plan view of thedriving mechanism 50 when the first and second actuator rings 72,74 are positioned so that the raisedportions 80 are circumferentially spaced from the raisedportions 86. Thus the lockingplate 250 is biased into the first position in which the lockingfingers 252 of thelocking plate 250 are interengaged with the locatingfingers 318. When themotor 42 is operated, both the first and secondrotatable portions drum 30 are rotated at the same speed and in the same direction. Thelug 82 is in contact with theswitch 98 a, which tells the controlling circuitry that thedriving mechanism 50 is operating in a manner in which rotation of theinput gear 116 results in rotation of both of the first and secondrotatable portions drum 30 at the same speed and in the same direction. - When it is desired to change the mode of operation of the
driving mechanism 50, themotor 96 is operated so as to rotate thepinion 96 a. Thefirst actuator ring 72 is thus rotated about theaxis 40 and thesecond actuator ring 74 then moves axially away from thetub 18. Thesecond actuator ring 74 abuts against the lockingplate 250 and the lockingfingers 252 of thelocking plate 250 become seated in the depressions of thesecond actuator ring 74. Further movement of thesecond actuator ring 74 causes the lockingfingers 252 to become disengaged from the locatingfingers 318 of thehousing 304. Rotation of thelocking plate 250 about theaxis 40 is prevented: hence, rotation of the first and secondplanet carrier plates fingers 252 of thelocking plate 250 are not initially aligned with thedepressions 92, thesecond actuator ring 74 will still be moved away in the manner described. The lockingfingers 252 will become seated in thedepressions 92 as soon as rotation of thelocking plate 250 is commenced.) Theribs 18 a of thetub 18 remain located within theslots 90 of the locating legs of thesecond actuator ring 74 during the whole of this axial movement. When the movement is complete, thelug 82 contacts theswitch 98 b which 20 informs the controlling circuitry that thedriving mechanism 50 is operating in a manner in which rotation of theinput gear 116 will result in rotation of the first and secondrotatable portions drum 30 at the same speed but in opposite directions. -
FIG. 10 a is a cross-section through thedriving mechanism 50 in the position shown inFIG. 9 a. The lower half ofFIG. 10 a is taken along the line A-A ofFIG. 9 a and the upper half is taken along the line B-B ofFIG. 9 a. As can be seen, the lockingplate 250 is pressed to the left under the action of the compression springs 256 so that the lockingfingers 252 are interengaged with the locatingfingers 318 of thehousing 304. Thesecond actuator ring 74 is spaced axially from the lockingplate 250 so as to maintain the locking effect between the second and third groups ofcomponents - Similarly,
FIG. 10 b is a cross-section through thedriving mechanism 50 in the position shown inFIG. 9 b. The lower half ofFIG. 10 b is taken along the line A-A ofFIG. 9 b and the upper half is taken along the line B-B ofFIG. 9 b. In this position, thesecond actuator ring 74 maintains the lockingplate 250 out of contact with the locatingfingers 318 against the action of the compression springs 256 and prevents rotation thereof about theaxis 40. The workingcomponents FIGS. 6 b and 6 c. - The washing machine described above can be used in the following manner. Once the articles to be washed have been placed in the interior of the
drum 30 via thedoor 16, the program to be used has been selected and the detergent has been placed in the soap tray 24 (not necessarily in that order), themachine 10 begins to operate a wash/spin cycle. Water is introduced to thetub 18 via thewater inlet conduit 22 and thesoap tray 24 so as to introduce water and detergent to the interior of the drum and thus wet the articles. It will be appreciated that the detergent can be introduced to the interior of the drum by other means such as, for example, by placing liquid detergent in a ball inside thedrum 30 or by using detergent tablets. Fabric softener can also be used. The details of how the water, detergent and fabric softener are introduced to the interior of the drum are immaterial to the present invention, as are the means of ensuring that the correct amount of water is provided and the manner of increasing the temperature of the water to that required for the wash/spin cycle selected. Such details are well known in the art and will not be described any further here. - Initially, the
actuator 70 is positioned so that thefirst actuator ring 72 is in the position shown inFIG. 9 a. The lockingplate 250 is biased into the first position in which the lockingfingers 252 are interengaged with the locatingfingers 318 of thehousing 304. Thelug 82 is in contact with theswitch 98 b which communicates to the controlling circuitry that the lockingplate 250 is in the first position. Themotor 42 is then driven so that thedrive belt 46 causes rotation of thedrive wheel 102. This in turn causes the first and secondrotatable portions drum 30 to rotate in the same direction and at the same speed. This synchronized rotation is continued for a short period of time so as to ensure that all of the articles are thoroughly wetted by the water and to commence the washing process. Subsequent periods of synchronized rotation can be carried out if required. Consecutive periods can involve rotating the first and secondrotatable portions motor 42 is reversed after each period has been completed. - When it is required to increase the amount of agitation applied to the articles, the
motor 42 is first stopped. Thedrum 30 thus stops rotating. Next, themotor 96 is operated so as to turn thepinion 96 a which, in turn, causes thefirst actuator ring 72 to rotate about theaxis 40 of thewashing machine 10. Thesecond actuator ring 74 is therefore moved away from thefirst actuator ring 72 so that the lockingplate 250 is displaced in the direction of thearrow 260 inFIG. 4 into the second position. Thelug 82 also contacts theswitch 98 a so as to communicate to the controlling circuitry that counter rotation will commence if the motor is operated. Themotor 42 is then operated again so that the first and secondrotatable portions drum 30 rotate in opposite directions and at substantially the same speed. This allows a high rate of agitation to be applied to the articles. The speed of rotation of eachrotatable portion - When sufficient agitation has been applied to the articles to achieve the standard of cleaning required by the selected program, the
motor 42 is stopped. Themotor 96 is operated again so as to return thefirst actuator ring 72 to the position shown inFIG. 9 a which, in turn, causes thelocking plate 250 to return to the first position. Subsequent operation of themotor 42 thus causes synchronized rotation of the first and secondrotatable portions tub 18 through thedrainage outlet 28 via thewater drainage conduit 26. Rinse water is then introduced to thetub 18 in a known manner and the speed of rotation of thedrum 30 is then increased to a spin speed (commonly 800-1500 rpm) in order to spin the rinse water out of the articles. The rinse and spin steps are repeated 3 or 4 times. Spin cycles of this type are well known and need not be described any further here. - The foregoing description relates to only one embodiment of the invention. It will be understood that variations to the described embodiment can be made without departing from the scope of the invention. For example, other types of gearwheel can be used in place of the ones illustrated in the drawings. Also, any form of locking mechanism can be employed as long as the effect is that, in one position, rotation of the input gear causes both of the output gears to rotate in the same direction, and, in another position, rotation of the input gear causes the output gears to rotate in opposite directions. The interengagement or interleaving of a set of locking fingers with a set of locating fingers is not the only way of achieving this and other methods could be used. For example, the second planet carrier could carry retractable locking pins which could be extended to lock the second planet carrier plate to the housing and retracted to allow relative rotation therebetween. In another alternative arrangement, the locking plate could carry movable pins which could be moved into the weight-reducing holes formed in the planet wheels. Other methods and mechanisms for achieving a similar locking effect will be apparent to a skilled reader. In a further variation to the embodiment described above, the
axis 40 of thewashing machine 10 about which therotatable portions drum 30 rotate is arranged so as to be inclined slightly to the horizontal, rather than precisely horizontal. The angle of inclination to the horizontal is unlikely to be greater than 15° because an angle much greater than this may affect the wash action achievable by the wash action described above. Nevertheless, the term “substantially horizontal” as used in the claims appended hereto is intended to include axes inclined at an angle of up to 15° to the horizontal.
Claims (30)
1. An appliance comprising two rotatable portions and a driving mechanism for rotating the rotatable portions about a horizontal or substantially horizontal axis of rotation, the driving mechanism comprising a gearbox having an input gear, two output gears separate from the input gear each connected to respective rotatable portions and a locking mechanism movable between a first position and a second position, the arrangement of the input gear, the output gears and the locking mechanism being such that, when the locking mechanism is in the first position and the input gear is driven, the output gears each drive their respective rotatable portions to rotate in the same direction and, when the locking mechanism is in the second position and the input gear is driven, the output gears each drive their respective rotatable portions to rotate in opposite directions.
2. The appliance of claim 1 , wherein the output gears are coaxial.
3. The appliance of claim 2 , wherein the input gear is coaxial with the output gears.
4. The appliance of claim 2 , wherein each output gear is rigidly connected to a shaft, one of the said shafts being rotatably arranged inside the other of the said shafts.
5. The appliance of claim 1 , wherein, when the locking mechanism is in the first position and the input gear is driven, the driving mechanism is configured so that both output gears rotate in the same direction and at the same speed.
6. The appliance of claim 1 , wherein, when the locking mechanism is in the second position and the input gear is driven, the output gears rotate in opposite directions at substantially the same speed.
7. The appliance of claim 1 , wherein the gearbox comprises a gear arrangement having an annulus, a plurality of planet wheels carried on a planet carrier, and two sun wheels.
8. The appliance of claim 7 , wherein a first of the sun wheels comprises the input gear and a second of the sun wheels and the annulus comprise the output gears.
9. The appliance of claim 7 , wherein, when the locking mechanism is in the first position, the locking mechanism engages both the planet carrier and the annulus so as to prevent relative rotation therebetween.
10. The appliance of claim 9 , wherein the locking mechanism and the annulus each carry a plurality of projections, the projections carried by the locking mechanism interengaging with the projections carried by the annulus when the locking mechanism is in the first position.
11. The appliance of claim 10 , wherein the number of projections carried by the annulus is the same as the number of projections carried by the locking mechanism.
12. The appliance of claim 10 , wherein the projections carried by the locking mechanism extend in a radial direction away from the axis of the gearbox.
13. The appliance of claim 10 , wherein the projections carried by the annulus extend in an axial direction parallel to the axis of the gearbox.
14. The appliance of claim 7 , wherein the locking mechanism is mounted on the planet carrier.
15. The appliance of claim 14 , wherein the locking mechanism comprises a locking plate which is mounted so as to be slidably movable, with respect to the planet carrier, in the direction of the axis of the gearbox between the first position and the second position.
16. The appliance of claim 15 , wherein the locking plate is biased into the first position by a biasing device.
17. The appliance of claim 16 , wherein the biasing device comprises compression springs.
18. The appliance of claim 16 , further comprising an actuator provided to move the locking plate from the first position to the second position against the action of the biasing device.
19. The appliance of claim 18 , wherein actuation of the actuator causes movement of the locking plate in a direction parallel to the axis of the gearbox.
20. The appliance of claim 18 , wherein the actuator is attached to a fixed portion of the appliance.
21. The appliance of claim 20 , wherein the actuator comprises a first actuator ring and a second actuator ring, the first actuator ring being attached to the fixed portion of the appliance in a manner which allows rotation thereof about the axis of the gearbox and having inclined surfaces facing the second actuator ring, the second actuator ring being engaged with the fixed portion of the appliance in a manner which allows movement thereof parallel to the axis of the gearbox and having inclined surfaces facing the first actuator ring and complementary to the inclined surfaces of the first actuator ring, such that rotational movement of the first actuator ring causes movement of the second actuator ring parallel to the axis of the gearbox as a result of the movement of the inclined surfaces across one another.
22. The appliance of claim 21 , further comprising a device for rotating the first actuator ring about the axis of the gearbox.
23. The appliance of claim 22 , wherein the device for rotating the first actuator ring about the axis of the gearbox comprises a motor carrying a pinion and a rack attached to the first actuator ring, the motor being mounted on the fixed portion of the appliance.
24. The appliance of claim 20 , wherein, when the locking mechanism is in the second position, the locking plate is rotationally fixed with respect to the fixed portion of the appliance.
25. The appliance of claim 1 , wherein the appliance is a washing machine.
26. A method of operating an appliance comprising two rotatable portions and a driving mechanism for rotating the rotatable portions about a horizontal or substantially horizontal axis of rotation, the driving mechanism comprising a gearbox having an input gear, two output gears separate from the input gear each connected to respective rotatable portions and a locking mechanism movable between a first position and a second position, the arrangement of the input gear, the output gears and the locking mechanism being such that, when the locking mechanism is in the first position and the input gear is driven, the output gears each drive their respective rotatable portions to rotate in the same direction and, when the locking mechanism is in the second position and the input gear is driven, the output gears each drive their respective rotatable portions to rotate in opposite directions, the method comprising:
(a) driving the input gear with the locking mechanism in the first position so as to drive the output gears, and thus the respective rotatable portions, to rotate in the same direction;
(b) causing the locking mechanism to move from the first position to the second position; and
(c) driving the input gear with the locking mechanism in the second position so as to drive the output gears, and thus the respective rotatable portions, to rotate in opposite directions.
27. The method of claim 26 , wherein, after step (c), the locking mechanism is moved from the second position to the first position and step (a) is repeated.
28. The method of claim 26 , wherein, during step (a), the drive to the input gear is applied consecutively in opposite directions.
29. The method of claim 26 , wherein, during step (c), the output gears rotate in opposite directions at substantially the same rotational speed.
30. The method of claim 26 , wherein during step (c) neither of the output gears rotates at rotational speed of more than 200 rpm.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US11/594,731 US20070050921A1 (en) | 2000-05-19 | 2006-11-09 | Appliance having a driving mechanism |
Applications Claiming Priority (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB0011992A GB2362690A (en) | 2000-05-19 | 2000-05-19 | Counter rotating washing machine drive |
GB0011992-5 | 2000-05-19 | ||
US10/276,800 US7197783B2 (en) | 2000-05-19 | 2001-05-09 | Appliance having a driving mechanism |
PCT/GB2001/001999 WO2001088256A1 (en) | 2000-05-19 | 2001-05-09 | An appliance having a driving mechanism |
US11/594,731 US20070050921A1 (en) | 2000-05-19 | 2006-11-09 | Appliance having a driving mechanism |
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US10/276,800 Continuation US7197783B2 (en) | 2000-05-19 | 2001-05-09 | Appliance having a driving mechanism |
PCT/GB2001/001999 Continuation WO2001088256A1 (en) | 2000-05-19 | 2001-05-09 | An appliance having a driving mechanism |
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US20070050921A1 true US20070050921A1 (en) | 2007-03-08 |
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US10/276,800 Expired - Fee Related US7197783B2 (en) | 2000-05-19 | 2001-05-09 | Appliance having a driving mechanism |
US11/594,731 Abandoned US20070050921A1 (en) | 2000-05-19 | 2006-11-09 | Appliance having a driving mechanism |
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US10/276,800 Expired - Fee Related US7197783B2 (en) | 2000-05-19 | 2001-05-09 | Appliance having a driving mechanism |
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Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11560663B2 (en) * | 2018-02-07 | 2023-01-24 | Wuxi Little Swan Electric Co., Ltd. | Planetary gear assembly for drum washing machine and drum washing machine |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100763367B1 (en) * | 2000-11-15 | 2007-10-04 | 엘지전자 주식회사 | drum type washing machine |
US7475445B2 (en) * | 2001-10-18 | 2009-01-13 | Haier Group Corporation | Counter-rotation wash method and transmission machine |
KR101257702B1 (en) * | 2005-10-06 | 2013-04-24 | 삼성전자주식회사 | Washing machine and control method thereof |
BRPI0905067A2 (en) * | 2009-08-14 | 2011-04-19 | Monteiro De Lima Alan Miranda | reversibly optimized continuous automatic transmission |
US8419588B2 (en) * | 2010-11-19 | 2013-04-16 | Remy Technologies, L.L.C. | Locking ring for a planetary gear set incorporated into a transmission member |
US9121127B2 (en) | 2011-06-03 | 2015-09-01 | General Electric Company | Apparatus and system for rotating elements in an appliance |
JP6444622B2 (en) * | 2014-06-12 | 2018-12-26 | アクア株式会社 | Drum washing machine |
US10968558B2 (en) | 2018-02-14 | 2021-04-06 | Fisher & Paykel Appliances Limited | Integrated motor and gearbox drive system for a washing machine |
CN113281207B (en) * | 2021-05-12 | 2022-12-13 | 温州大学 | Test device capable of realizing friction and wear behavior research under multiple working conditions |
Citations (44)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1403235A (en) * | 1920-02-14 | 1922-01-10 | Dawson John James | Apparatus for producing copper |
US2103259A (en) * | 1936-01-15 | 1937-12-28 | Henry C Hitt | Epicyclic gear train |
US2209980A (en) * | 1938-02-16 | 1940-08-06 | Weskenson Corp | Reversing mechanism |
US2343742A (en) * | 1939-11-21 | 1944-03-07 | Westinghouse Electric & Mfg Co | Washing apparatus |
US2390240A (en) * | 1943-08-21 | 1945-12-04 | Gilbert & Barker Mfg Co | Power transmitting mechanism |
US2396749A (en) * | 1944-08-07 | 1946-03-19 | Poff Cecil | Fan |
US2399319A (en) * | 1944-05-11 | 1946-04-30 | Bendix Home Appliances Inc | Washing machine transmission and support |
US2484921A (en) * | 1947-09-06 | 1949-10-18 | Jr Christian B Wolff | Differential leverage brake transmission |
US2561090A (en) * | 1942-11-18 | 1951-07-17 | Vickers Electrical Co Ltd | Power plant, including normally contrarotating turbine elements for driving a load shaft and means for rotating said elements in the same direction when the turbine is idling |
US2637186A (en) * | 1947-09-20 | 1953-05-05 | Easy Washing Machine Corp | Laundry machine |
US2668459A (en) * | 1949-11-29 | 1954-02-09 | Berklege Emil | Power load equalizer |
US2682789A (en) * | 1949-08-23 | 1954-07-06 | Bendix Aviat Corp | Reversing drive |
US2771794A (en) * | 1952-11-20 | 1956-11-27 | American Flexible Coupling Com | Reversible reduction transmission |
US2807447A (en) * | 1954-11-09 | 1957-09-24 | Dormeyer Corp | Food mixer |
US2836046A (en) * | 1952-05-08 | 1958-05-27 | Maytag Co | Tumbler type washing machines |
US2839952A (en) * | 1954-12-20 | 1958-06-24 | Supreme Products Corp | Reversible power tool drive attachment |
US2895320A (en) * | 1955-06-15 | 1959-07-21 | Gen Motors Corp | Washer |
US2958239A (en) * | 1957-03-04 | 1960-11-01 | Chalonnaises Const Mec Met | Variable-speed epicyclic gear train transmission-device |
US2968174A (en) * | 1956-11-06 | 1961-01-17 | Hoover Co | Washing machines |
US2995023A (en) * | 1959-04-10 | 1961-08-08 | Blackstone Corp | Pulsator mechanism for washing machines |
US3182529A (en) * | 1962-05-25 | 1965-05-11 | Fichtel & Sachs Ag | Dual-speed hub |
US3203275A (en) * | 1962-11-26 | 1965-08-31 | Vaino A Hoover | Mechanical actuator |
US3306133A (en) * | 1963-07-19 | 1967-02-28 | Fichtel & Sachs Ag | Drive unit for an automatic washing machine |
US3339530A (en) * | 1965-04-29 | 1967-09-05 | Starline | Animal feeding system with reversing auger |
US3342085A (en) * | 1965-04-30 | 1967-09-19 | Emerson Electric Co | Laundry equipment power package |
US3478622A (en) * | 1967-08-30 | 1969-11-18 | Larry R Reid | Marine transmission |
US4020659A (en) * | 1974-07-04 | 1977-05-03 | Bhavsar G M | Tunnel-type commercial-duty washing machine |
US4192409A (en) * | 1976-04-30 | 1980-03-11 | Kabushiki Kaisha Komatsu Seisakusho | Clutch mechanism for winch |
US4428680A (en) * | 1981-01-30 | 1984-01-31 | Goran Persson Maskin Ab | Method and apparatus for mixing liquid and paste-like substances |
US4509390A (en) * | 1982-12-30 | 1985-04-09 | Petroleum Meter & Pump Co., Inc. | Differential summing mechanism |
US4514164A (en) * | 1983-03-02 | 1985-04-30 | Societe Dite: Usines Beyer Freres | Reduction gear system for twin screw extruding system |
US4584732A (en) * | 1984-01-30 | 1986-04-29 | Kabushiki Kaisha Toshiba | Washer/dehydrater |
US4910979A (en) * | 1989-01-03 | 1990-03-27 | Whirlpool Corporation | Counter-rotation wash system |
US4964315A (en) * | 1984-10-03 | 1990-10-23 | General Electric Company | Transmission having dual counterrotating output shafts |
US5000016A (en) * | 1989-01-03 | 1991-03-19 | Whirlpool Corporation | Counter-rotation wash system |
US5211039A (en) * | 1991-03-12 | 1993-05-18 | Pellerin Milnor Corporation | Continuous batch type washing machine |
US5322488A (en) * | 1991-07-29 | 1994-06-21 | Jong O. Ra | Continuously geared automatic transmission with controlling brakes |
US5326334A (en) * | 1991-06-26 | 1994-07-05 | Ra Jong O | Continuously engaged geared automatic transmission with controlling brakes |
US5330395A (en) * | 1991-07-29 | 1994-07-19 | Jong Oh Ra | Continuously-geared automatic transmission with controlling brakes |
US5364320A (en) * | 1993-03-10 | 1994-11-15 | Jong Oh Ra | Continuously-geared automatic transmission with controlling brakes |
US5394764A (en) * | 1993-08-18 | 1995-03-07 | Fini, Jr.; Anthony W. | Bevel gear forward/reverse |
US5950459A (en) * | 1996-10-31 | 1999-09-14 | Sharp Kabushiki Kaisha | Electric washing machine including washing tank and agitator which rotate in opposite directions |
US6112863A (en) * | 1998-12-18 | 2000-09-05 | Colletti; Gregory J. | Band brake with evenly distributed braking force application |
US6513737B2 (en) * | 2001-03-09 | 2003-02-04 | Illinois Institute Of Technology | Apparatus and process for pulverization of a polymeric material |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB538594A (en) | 1939-12-05 | 1941-08-11 | Bonham Mfg Company | Improvements in tractors |
GB678186A (en) | 1949-05-28 | 1952-08-27 | Mecanique Navale Gendron | Improvements in control devices for change-speed and/or reversing mechanism |
FR1448804A (en) | 1965-04-07 | 1966-08-12 | Speed variator for washing machine | |
US3394609A (en) * | 1966-06-15 | 1968-07-30 | Ibm | Coaxial gearing arrangement |
DE3708976A1 (en) | 1987-03-19 | 1988-10-06 | Faini Spa | BULL-EYE WASHING MACHINE |
JPS6449599U (en) * | 1987-09-21 | 1989-03-28 | ||
KR100215032B1 (en) | 1996-04-23 | 1999-08-16 | 윤종용 | A washing machine |
GB2337274B (en) | 1998-05-12 | 2001-10-17 | Notetry Ltd | Method and apparatus for agitating the contents of a container |
-
2001
- 2001-05-09 US US10/276,800 patent/US7197783B2/en not_active Expired - Fee Related
-
2006
- 2006-11-09 US US11/594,731 patent/US20070050921A1/en not_active Abandoned
Patent Citations (44)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1403235A (en) * | 1920-02-14 | 1922-01-10 | Dawson John James | Apparatus for producing copper |
US2103259A (en) * | 1936-01-15 | 1937-12-28 | Henry C Hitt | Epicyclic gear train |
US2209980A (en) * | 1938-02-16 | 1940-08-06 | Weskenson Corp | Reversing mechanism |
US2343742A (en) * | 1939-11-21 | 1944-03-07 | Westinghouse Electric & Mfg Co | Washing apparatus |
US2561090A (en) * | 1942-11-18 | 1951-07-17 | Vickers Electrical Co Ltd | Power plant, including normally contrarotating turbine elements for driving a load shaft and means for rotating said elements in the same direction when the turbine is idling |
US2390240A (en) * | 1943-08-21 | 1945-12-04 | Gilbert & Barker Mfg Co | Power transmitting mechanism |
US2399319A (en) * | 1944-05-11 | 1946-04-30 | Bendix Home Appliances Inc | Washing machine transmission and support |
US2396749A (en) * | 1944-08-07 | 1946-03-19 | Poff Cecil | Fan |
US2484921A (en) * | 1947-09-06 | 1949-10-18 | Jr Christian B Wolff | Differential leverage brake transmission |
US2637186A (en) * | 1947-09-20 | 1953-05-05 | Easy Washing Machine Corp | Laundry machine |
US2682789A (en) * | 1949-08-23 | 1954-07-06 | Bendix Aviat Corp | Reversing drive |
US2668459A (en) * | 1949-11-29 | 1954-02-09 | Berklege Emil | Power load equalizer |
US2836046A (en) * | 1952-05-08 | 1958-05-27 | Maytag Co | Tumbler type washing machines |
US2771794A (en) * | 1952-11-20 | 1956-11-27 | American Flexible Coupling Com | Reversible reduction transmission |
US2807447A (en) * | 1954-11-09 | 1957-09-24 | Dormeyer Corp | Food mixer |
US2839952A (en) * | 1954-12-20 | 1958-06-24 | Supreme Products Corp | Reversible power tool drive attachment |
US2895320A (en) * | 1955-06-15 | 1959-07-21 | Gen Motors Corp | Washer |
US2968174A (en) * | 1956-11-06 | 1961-01-17 | Hoover Co | Washing machines |
US2958239A (en) * | 1957-03-04 | 1960-11-01 | Chalonnaises Const Mec Met | Variable-speed epicyclic gear train transmission-device |
US2995023A (en) * | 1959-04-10 | 1961-08-08 | Blackstone Corp | Pulsator mechanism for washing machines |
US3182529A (en) * | 1962-05-25 | 1965-05-11 | Fichtel & Sachs Ag | Dual-speed hub |
US3203275A (en) * | 1962-11-26 | 1965-08-31 | Vaino A Hoover | Mechanical actuator |
US3306133A (en) * | 1963-07-19 | 1967-02-28 | Fichtel & Sachs Ag | Drive unit for an automatic washing machine |
US3339530A (en) * | 1965-04-29 | 1967-09-05 | Starline | Animal feeding system with reversing auger |
US3342085A (en) * | 1965-04-30 | 1967-09-19 | Emerson Electric Co | Laundry equipment power package |
US3478622A (en) * | 1967-08-30 | 1969-11-18 | Larry R Reid | Marine transmission |
US4020659A (en) * | 1974-07-04 | 1977-05-03 | Bhavsar G M | Tunnel-type commercial-duty washing machine |
US4192409A (en) * | 1976-04-30 | 1980-03-11 | Kabushiki Kaisha Komatsu Seisakusho | Clutch mechanism for winch |
US4428680A (en) * | 1981-01-30 | 1984-01-31 | Goran Persson Maskin Ab | Method and apparatus for mixing liquid and paste-like substances |
US4509390A (en) * | 1982-12-30 | 1985-04-09 | Petroleum Meter & Pump Co., Inc. | Differential summing mechanism |
US4514164A (en) * | 1983-03-02 | 1985-04-30 | Societe Dite: Usines Beyer Freres | Reduction gear system for twin screw extruding system |
US4584732A (en) * | 1984-01-30 | 1986-04-29 | Kabushiki Kaisha Toshiba | Washer/dehydrater |
US4964315A (en) * | 1984-10-03 | 1990-10-23 | General Electric Company | Transmission having dual counterrotating output shafts |
US4910979A (en) * | 1989-01-03 | 1990-03-27 | Whirlpool Corporation | Counter-rotation wash system |
US5000016A (en) * | 1989-01-03 | 1991-03-19 | Whirlpool Corporation | Counter-rotation wash system |
US5211039A (en) * | 1991-03-12 | 1993-05-18 | Pellerin Milnor Corporation | Continuous batch type washing machine |
US5326334A (en) * | 1991-06-26 | 1994-07-05 | Ra Jong O | Continuously engaged geared automatic transmission with controlling brakes |
US5322488A (en) * | 1991-07-29 | 1994-06-21 | Jong O. Ra | Continuously geared automatic transmission with controlling brakes |
US5330395A (en) * | 1991-07-29 | 1994-07-19 | Jong Oh Ra | Continuously-geared automatic transmission with controlling brakes |
US5364320A (en) * | 1993-03-10 | 1994-11-15 | Jong Oh Ra | Continuously-geared automatic transmission with controlling brakes |
US5394764A (en) * | 1993-08-18 | 1995-03-07 | Fini, Jr.; Anthony W. | Bevel gear forward/reverse |
US5950459A (en) * | 1996-10-31 | 1999-09-14 | Sharp Kabushiki Kaisha | Electric washing machine including washing tank and agitator which rotate in opposite directions |
US6112863A (en) * | 1998-12-18 | 2000-09-05 | Colletti; Gregory J. | Band brake with evenly distributed braking force application |
US6513737B2 (en) * | 2001-03-09 | 2003-02-04 | Illinois Institute Of Technology | Apparatus and process for pulverization of a polymeric material |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11560663B2 (en) * | 2018-02-07 | 2023-01-24 | Wuxi Little Swan Electric Co., Ltd. | Planetary gear assembly for drum washing machine and drum washing machine |
Also Published As
Publication number | Publication date |
---|---|
US7197783B2 (en) | 2007-04-03 |
US20030167803A1 (en) | 2003-09-11 |
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