Patent Description:
A laundry machine is an apparatus used to wash and/or dry a user's laundry (e.g., clothes, bedding, etc.). Generally, laundry machines having functionality to wash the user's laundry include a tub that receives and contains washing fluids (e.g., water, detergent, etc.), a drum rotatably installed in the tub, and a motor to rotate the drum. Through rotation of the drum, a series of washing stages including washing, rinsing, and spin cycle may be performed to substantially remove washing fluids from the laundry.

During the spin cycle, the drum typically spins laundry positioned therein at a rotational velocity sufficient for the centripetal acceleration to exceed gravitational acceleration causing the wet laundry to be pinned against the inside surface of the drum. Often the mass of the wet laundry is not uniformly distributed around the inside periphery of the drum and the composite center of mass of the rotating laundry is offset from the drum's axis of rotation. The offset of the center of mass of the rotating laundry from the primary rotation axis of the drum can generate strong vibrations, which can generate unwanted noise and/or damage components of the washing machine, such as the displaceable suspension, drum, drum bearings, tub, exterior housing, etc. Additionally, these vibrations may cause the entire laundry machine to vibrate which may be transmitted to the surrounding building in which the laundry machine is operated and/or cause the laundry machine to translate across the floor.

For this reason, laundry machines may include a balancing assembly to reduce vibration and stabilize the laundry machine by counteracting the load imbalance within the rotating drum. However, conventional balancing assemblies tend to be mounted to the drum in such a way that reduces capacity of the drum and therefore the reduces the amount of laundry the laundry machine is able to accommodate. Additionally, making a laundry machine larger to allow for greater load capacity may prevent use in smaller homes and/or apartments which may lack the appropriate space for larger laundry machines Document <CIT>discloses a washing machine comprising drum controlled balancers moving inside an orbital chamber and having brushes contacting electrodes inside the orbital chamber.

Accordingly, a need exists for laundry apparatuses that include dynamic load balancing assemblies while maximizing load capacity.

In an embodiment, a dynamic balancing assembly for a laundry apparatus includes a control unit, one or more counterweight devices, and one or more clocksprings. The one or more counterweight devices are configured to be orbited about a primary rotation axis of the laundry apparatus to counteract a load imbalance in a drum of the laundry apparatus. The one or more clocksprings communicatively couple each of the one or more counterweight devices to the control unit.

In another embodiment, a laundry apparatus includes a tub, a drum, a control unit, a motor, and a dynamic balancing assembly. The tub defines a fluid containment envelope. The drum is positioned within the fluid containment envelope of the tub and rotatable relative to the tub about a primary rotation axis. The drum includes a laundry-receiving portion for receiving one or more articles of laundry. The motor is coupled to the tub, wherein the motor is communicatively coupled to the control unit and operatively coupled to the drum to cause rotation of the drum. The motor is isolated from fluid within the fluid containment envelope. The dynamic balancing assembly is communicatively coupled to the control unit, and includes one or more counterweight devices configured to be orbited about the primary rotation axis to counteract a load imbalance in the drum, and one or more clocksprings communicatively coupling each of the one or more counterweight devices to the control unit.

In another embodiment, a laundry apparatus includes a tub, a drum, a control unit, a motor, one or more load imbalance sensors, and a dynamic balancing assembly. The tub includes a fluid containment envelope and a motor receiving envelope that extends into a volume of the fluid containment envelope and is isolated from fluid received in the fluid containment envelope. The drum is positioned within the fluid containment envelope of the tub and rotatable relative to the tub about a primary rotation axis centrally positioned in the tub. The drum includes a laundry-receiving portion for receiving one or more articles of laundry. The motor is positioned within the motor receiving envelope such that the motor is positioned within the volume of the fluid containment envelope and isolated from the fluid received in the fluid containment envelope. The motor is communicatively coupled to the control unit and operatively coupled to the drum to cause rotation of the drum. The one or more load imbalance sensors are communicatively coupled to the control unit and configured to output a load imbalance signal to the control unit, the load imbalance signal being indicative of a load imbalance within the drum. The dynamic balancing assembly is communicatively coupled to the control unit and attached to the drum within the fluid containment envelope. The dynamic balancing assembly includes an orbital balancing passage arranged concentrically around the motor, a first counterweight device positioned within the orbital balancing passage and responsive to the control unit, a second counterweight device positioned within the orbital balancing passage and responsive to the control unit, a first clockspring communicatively coupling the first counterweight device to the control unit, and a second clockspring communicatively coupling the second counterweight device to the control unit. The control unit controllably moves the first counterweight device along the orbital balancing passage to adjust an angular position of the first counterweight device around the primary rotation axis to counteract a detected load imbalance in the drum. The control unit controllably moves the second counterweight device along the orbital balancing passage to adjust an angular position of the second counterweight device around the primary rotation axis to counteract the detected load imbalance in the drum.

While the specification concludes with claims particularly pointing out and distinctly claiming the present invention, it is believed the same will be better understood from the following description taken in conjunction with the accompanying drawing in which:.

Embodiments described herein may be understood more readily by reference to the following detailed description. It is to be understood that the scope of the claims is not limited to the specific compositions, methods, conditions, devices, or parameters described herein, and that the terminology used herein is not intended to be limiting. In addition, as used in the specification, including the appended claims, the singular forms "a," "an," and "the" include the plural, and reference to a particular numerical value includes at least that particular value, unless the context clearly dictates otherwise. When a range of values is expressed, another embodiment includes from the one particular value and/or to the other particular value. Similarly, when values are expressed as approximations, by use of the antecedent basis "about," it will be understood that the particular values form another embodiment. All ranges are inclusive and combinable.

Embodiments described herein are generally directed to a laundry apparatuses that include dynamic balancing assemblies while maximizing volumetric space for receiving laundry. For example, and as illustrated in the figures, a laundry apparatus according to the present disclosure generally includes a tub, a drum, and a dynamic balancing assembly. The drum is positioned within a fluid containment envelope of the tub and is rotatable relative to the tub about a primary rotation axis, the drum defines a laundry-receiving portion for receiving one or more articles of laundry. The dynamic balancing assembly includes an orbital balancing passage, arranged concentrically around a motor of the laundry apparatus, and first and second counterweight devices are positioned within the orbital balancing passage. The dynamic balancing assembly is positioned relative to the tub and/or drum so that a common cross-sectional plane passes through the dynamic balancing assembly, the motor, and the fluid containment envelope of the tub. As shown in the illustrated embodiments, such configuration allows for maximization of volume within the tub while still providing desired load balancing. These and additional features will be discussed in greater detail below.

As used herein, the term laundry apparatus may include a washing machine or combination washer/dryer machine. For example, the term laundry apparatus can describe any machine that relies on the centripetal acceleration from spinning to extract fluid from a wetted textile material including a dry cleaning machine, a washing machine, a washing machine employing working fluid other than water, centrifugal spinner, laundry dryer, etc. Additionally, laundry apparatuses may include any sized laundry apparatus including, but not limited to, industrial or residential sized units (including miniaturized and/or apartment units).

Referring to <FIG>, a laundry apparatus <NUM> is generally depicted. The laundry apparatus <NUM> may include an enclosed exterior housing <NUM>. Positioned within and supported by the exterior housing <NUM> is a tub and drum assembly <NUM>. The tub and drum assembly <NUM> may be accessible through an exterior housing port <NUM> formed within the exterior housing <NUM> that is selectively accessible by opening/closing of a hinged door <NUM>, for example. The laundry apparatus <NUM> may be a front-load laundry apparatus (e.g., a front-load washing machine) or, in other embodiments, may be a top load laundry apparatus (e.g., a top-load washing machine). In other embodiments the exterior housing port <NUM> might be positioned anywhere around the exterior housing <NUM> such as the side, back, bottom, or at some oblique angle.

Still referring to <FIG>, the laundry apparatus <NUM> may further include a control unit <NUM>. The control unit <NUM> may include processing circuitry and a non-transitory memory that includes logic in the form of machine-readable instructions that is used to control one or more operations of the laundry apparatus <NUM> as will be described in greater detail herein. For example, the control unit <NUM> may execute logic to operate valves and pumps during the washing and/or drying cycles, thereby controlling the various washing, rinsing, and spin cycles. The control unit <NUM> may further control a balancing operation by a dynamic balancing assembly <NUM>, which will be described in greater detail below.

Referring now to <FIG> the laundry apparatus <NUM> is depicted more schematically to further illustrate the tub and drum assembly <NUM> within the exterior housing <NUM>, the tub and drum assembly <NUM> includes a tub <NUM> and a drum <NUM>. The drum <NUM> is configured to rotate about a primary rotation axis <NUM> within the tub <NUM>. The primary rotation axis <NUM> can be horizontal (e.g., parallel to the X/Y plane of the depicted coordinate axes), vertical (e.g., parallel to Z axis of the depicted coordinate axes), or at any angle, relative to the depicted coordinate axes.

Laundry <NUM> may be placed inside the drum <NUM> for laundering purposes. Laundry <NUM> may include, for example, soiled clothing, linens, and other fabric or textile articles. The laundry <NUM> may be washed and rinsed inside the drum <NUM>. During washing and rinsing with water, the laundry <NUM> may absorb water increasing the weight of the laundry <NUM>. The mass of water absorbed may be, for example, about <NUM>% to about <NUM>% the dry weight of the laundry <NUM>. Much of the absorbed water can be extracted mechanically by applying sustained high centripetal acceleration to the laundry <NUM> by spinning of the drum <NUM>. Spinning speeds may be about <NUM> rpm to about <NUM> rpm. Centrifugal water extraction is commonly referred to as the spin cycle and depending on spin speed and geometry can generate centripetal acceleration of about <NUM> to about <NUM> times the acceleration of gravity. During the spin cycle, the drum <NUM> spins the laundry <NUM> at a rotational velocity sufficient for the centripetal acceleration to exceed gravitational acceleration such that the wet laundry <NUM> is pinned against the inside surface of the drum <NUM>. The rotational velocity sufficient for the centripetal acceleration to exceed gravitation acceleration is known as the satellite speed.

As noted above, during the spin cycle, the mass of the wet laundry <NUM> may not be uniformly distributed around the inside periphery of the drum <NUM>. Referring now to <FIG>, a schematic cross-sectional view of the tub and drum assembly <NUM> is depicted. As illustrated, the center of mass <NUM> of the rotating laundry <NUM> may be offset from the primary rotation axis <NUM> of the drum <NUM>, resulting in an imbalanced load within the drum <NUM>. This imbalanced load can generate vibrations within the laundry apparatus <NUM>. Such vibrations can generate unwanted noise, cause damage to the laundry apparatus <NUM>, cause the laundry apparatus <NUM> to travel across the floor, and or transmit vibrations to the surrounding building in which the laundry apparatus <NUM> is used, and/or cause unwanted vibration of the entire laundry apparatus <NUM> which can, as noted above, transmit into surrounding structure and shake the building in which the laundry apparatus <NUM> is used. As will be described in greater detail herein, load imbalance sensors <NUM> may be provided to detect the magnitude and rotational position of the imbalance and a dynamic balancing assembly <NUM> responsive to the detected load imbalance may be actuated to balance the laundry <NUM> within the drum <NUM>.

For example, and as will be described in greater detail herein, the dynamic balancing assembly <NUM> can be employed to reduce or eliminate the vibration caused by imbalanced laundry <NUM>. The dynamic balancing assembly <NUM> may include one or more counterweight devices and can include in some embodiments, at least two counterweight devices. For example, the dynamic balancing assembly may include a first counterweight device 170a and a second counterweight device 170b that are restrained to the rotating drum <NUM>. In the illustrated embodiments, the counterweight devices 170a, 170b follow an orbital path at a fixed radius from the primary rotation axis <NUM>. The relative angular position 53a, 53b for each counterweight device 170a, 170b can be adjusted relative to the reference angular position <NUM> on drum <NUM>. As an example load balancing operation, before the spin cycle, the angular positions 53a and 53b may be adjusted such that counterweight devices 170a and 170b are across from each other to provide balance between the first counterweight device 170a and the second counterweight device 170b. The center of mass 55a for first counterweight device 170a and center of mass 55b for second counterweight device 170b have a combined center of mass at the primary rotation axis <NUM>. At speeds of about <NUM> rpm to about <NUM> rpm, the laundry <NUM> may be pinned by centripetal acceleration against the inside surface of rotating drum <NUM>. While pinned to the surface of the rotating drum, the center of mass <NUM> of the laundry <NUM> may be fixed at an angular position <NUM> from the reference angular position <NUM>. As illustrated, without balancing, the combined center of mass <NUM> (e.g., of the laundry <NUM>, the first counterweight device 170a, and the second counterweight device 170b) is offset from the primary rotation axis <NUM> and will generate an imbalance and create vibration. As will be described in greater detail herein, load imbalance sensors <NUM> can detect the magnitude and rotational position of the combined center of mass <NUM>. Based on the detected magnitude and angular position <NUM> of the combined center of mass <NUM>, the angular positions 53a and 53b of the counterweight devices 170a, 170b can be adjusted (e.g., in a direction 57a, 57b of orbital travel) to shift the combined center of mass <NUM> closer to the primary rotation axis <NUM>, as illustrated in <FIG>. When balanced, the combined center of mass <NUM> may be coincident to the primary rotation axis <NUM>. A balanced laundry apparatus <NUM> will run smoothly without substantial vibration.

<FIG> and <FIG> illustrate the tub and drum assembly <NUM> in isolation from the exterior housing <NUM> of the laundry apparatus <NUM>. <FIG> illustrates a cross-sectional view of the tub and drum assembly <NUM> of <FIG> and <FIG>. Referring collectively to <FIG>, the tub and drum assembly <NUM> generally include a tub <NUM>, a drum <NUM>, a motor <NUM>, one or more load balance sensors <NUM>, and the dynamic balancing assembly <NUM>,.

The tub <NUM> is configured to support rotation of various components of the laundry apparatus <NUM> mounted thereto, while also containing washing fluids (e.g., water, detergent, bleach, softener, etc.) therein. A cross-section of the tub <NUM> in isolation from the tub and drum assembly <NUM> is illustrated in <FIG>. The tub <NUM> comprises a tub body <NUM> that is shaped to provide a fluid containment envelope <NUM>. The tub body <NUM> may also be shaped to provide a motor receiving envelope <NUM> that extends into a volume of the fluid containment envelope <NUM>.

The tub body <NUM> may include a front wall <NUM> that is sized and shaped to surround exterior housing port <NUM> (illustrated in <FIG>) and defines a tub laundry port <NUM>. A sidewall <NUM> of the tub body <NUM> may extend from the front wall <NUM> to a rear wall <NUM>, which defines a maximum depth of the tub <NUM>, to provide the fluid containment envelope <NUM>. Ports, not shown, for the ingress and egress of fluid into the fluid containment envelope <NUM> may be provided within the tub body <NUM>.

Formed within the rear wall <NUM> of the tub body <NUM> is the motor receiving envelope <NUM> sized and shaped to receive and support the motor <NUM> therein. For example, the rear wall <NUM> may define a rear-facing surface <NUM>. The motor receiving envelope <NUM> may extend from the rear-facing surface <NUM> into a volume of the fluid containment envelope <NUM>. In particular, a depth of the motor receiving envelope <NUM> may correspond to an axial depth of the motor <NUM> such that the motor <NUM> is substantially flush with or inset from with a rear-facing surface <NUM> of the rear wall <NUM>. The tub body <NUM> may further define a drive shaft opening <NUM> to support a drive shaft <NUM> extending from the motor <NUM> to be coupled to the drum <NUM>. The drive shaft <NUM> may be supported by a main bearing assembly <NUM> that is fixedly attached to the tub <NUM> (e.g., to a surface of the drive shaft opening <NUM>) and operatively connected to the drum <NUM> thereby providing radial and axial support to the drum <NUM>.

In some embodiments, the main bearing assembly <NUM> includes a pair of rolling bearings such as deep groove ball bearings, angular contact bearings, cylindrical roller bearings, tapered roller bearings, spherical roller bearings, etc. The main roller bearing assembly may also include polymer or metallic bushings, air bearings, or magnetic bearings. The main bearing assembly <NUM> is configured to provide radial and axial support for the drum <NUM> as well as transmit any moments generated by imbalances in the drum <NUM> to the tub <NUM>.

Referring to <FIG>, the drum <NUM> is illustrated in a cantilevered configuration where the drum is supported from the rear by the main baring assembly <NUM> which is opposite of the drum opening <NUM> on the front side of the drum <NUM>. To better support moments from the drum <NUM>, it may be beneficial to maximize axial separation between bearing elements in the main bearing assembly <NUM>. As illustrated in <FIG>, the main bearing assembly <NUM> and drive shaft opening <NUM> can be axially extended back to fit inside the motor <NUM> and forward inside the protruding portion <NUM> of the drum body <NUM>. However, in other embodiments the drum <NUM> may be supported by a bearing assembly <NUM> on each end of the drum <NUM>. In such embodiment, the drum opening <NUM> might be on the front end of the drum <NUM> or might be on the side of the drum <NUM>.

As noted above, the motor <NUM> may be operatively coupled to the drum <NUM> for rotating the drum <NUM> within the fluid containment envelope <NUM> of the tub <NUM>. For example, the motor <NUM> may be rotatively coupled to the drum <NUM> via the drive shaft <NUM> that extends through the drive shaft opening <NUM>. In some embodiments, the drive shaft <NUM> might be directly attached to the drum <NUM>. In other embodiments, the drive shaft <NUM> might be attached to a support plate <NUM> and support plate <NUM> attached to the drum <NUM>. In other embodiments, the drive shaft <NUM> may be integrally formed with the drum <NUM>. In some embodiments, the drum <NUM> may be magnetically driven, such that no drive shaft <NUM> is needed. In some embodiments, the motor rotor <NUM> may be directly attached to the drum <NUM> and, such that no drive shaft <NUM> is needed.

The motor receiving envelope <NUM> of the tub <NUM> substantially isolates the motor <NUM> from washing fluid within the tub <NUM> and drum <NUM>. For example, the motor receiving envelope <NUM> may have a first inset wall <NUM> that extends into the volume of the fluid containment envelope <NUM> between the motor <NUM> and the orbital balancing passage <NUM>, as will be described in greater detail below. In some embodiments, the motor <NUM> may include a motor rotor <NUM> and a motor stator <NUM>. In the illustrated embodiment, at least a surface of the tub <NUM> and a surface of the motor <NUM> are substantially flush with one another. For example, and as illustrated an outer surface <NUM> of the motor rotor <NUM> is substantially flush with the rear-facing surface <NUM> of the tub <NUM>. Such may allow the tub <NUM> in close proximity with a back wall of the exterior housing <NUM> of the laundry apparatus <NUM>, thus maximizing the volume within the exterior housing <NUM> which may be used for laundry washing and/or drying purposes. In some embodiments, the surface of the tub <NUM> and the surface of the motor <NUM> may be offset from one another.

Referring again to <FIG>, the drum <NUM> is positioned within the fluid containment envelope <NUM> of the tub <NUM> and is rotatable relative to the tub <NUM> about a primary rotation axis <NUM> (illustrated in <FIG>). The drum <NUM> includes a drum body <NUM> that is shaped to provide a laundry-receiving portion <NUM> for receiving one or more articles of laundry therein. For example, the laundry-receiving portion <NUM> may include a drum opening <NUM> for receiving/removal of laundry into the drum body <NUM>. The drum opening <NUM> may be arranged within the fluid containment envelope <NUM> of the tub <NUM> so as to be aligned with the tub laundry port <NUM> for access into the drum body <NUM>. The drum body <NUM> may include a plurality of apertures (not shown) to allow fluid to flow into and out of the drum body <NUM>.

The drum body <NUM> may extend from the drum opening <NUM> to a base wall section <NUM>. The base wall section <NUM> may define a recessed portion <NUM> and a protruding portion <NUM>. The protruding portion <NUM> may be centrally arranged on the primary rotation axis of the drum <NUM>. The recessed portion <NUM> may be concentrically arranged around the protruding portion <NUM> with a sloping wall <NUM> joining the recessed portion <NUM> and the protruding portion <NUM>. Stated another way, a depth of the laundry-receiving portion <NUM> of the drum <NUM> may be greatest when measured at the recessed portion <NUM>, and shortest when measured at the protruding portion <NUM>. The protruding portion <NUM> may be coupled to a drive shaft <NUM> of the tub and drum assembly <NUM>.

The drum <NUM> may further include one or more agitators <NUM> coupled to or integral with the drum body <NUM>. The one or more agitators <NUM> may be arranged to provide agitation to washing fluids and laundry within the laundry-receiving portion <NUM> of the drum <NUM>. The one or more agitators <NUM> may aid in removing debris from laundry through contact of the laundry with the one or more agitators <NUM>. The one or more agitators <NUM> may extend along a sidewall section <NUM> of the drum <NUM> and along the base wall section <NUM> to the protruding portion <NUM>. The one or more agitators <NUM> may be evenly spaced around the circumference of the drum <NUM>.

Coupled to the base wall section <NUM> may be the dynamic balancing assembly <NUM>. The dynamic balancing is configured to counter imbalances within the drum and tub assembly <NUM> created by spinning laundry, which may result in a smooth operation of the laundry apparatus <NUM> and eliminate a need to suspend the tub <NUM> from the exterior housing <NUM> by a traditional displaceable suspension system (e.g., springs, dampers, masses, etc.).

The dynamic balancing assembly <NUM> is adjustably arranged by the control unit <NUM> to balance a load imbalance within the tub and drum assembly <NUM>. The load imbalance can be detected by the control unit <NUM> based on an output of one or more load imbalance sensors <NUM>. However, it is contemplated that, in some embodiments, the dynamic balancing assembly <NUM> can be passive in operation with no automatic adjustment by the control unit <NUM>. Some examples of passive dynamic balancing assembly may include rings filled with fluids or weighted balls.

Still referring to <FIG>, in order to facilitate dynamic balancing, the dynamic balancing assembly <NUM> may include an orbital balancing passage <NUM>, a first counterweight device 170a, and a second counterweight device 170b positioned within the orbital balancing passage <NUM>. As noted above with reference to <FIG> and <FIG>, the angular position for the first and second counterweight device 170a, 170b are adjustable relative to the reference angular position <NUM> of the drum to move the combined center of mass <NUM> of the laundry <NUM> and the first counterweight device 170a, and the second counterweight device 170b. The angular position 53a of the first counterweight device 170a and the angular position 53b of the second counterweight device 170b may be adjusted by any amount to move the combined center of mass <NUM> to be substantially coincident with the primary rotation axis <NUM>. During some balancing operations, the first and second counterweight devices 170a, 170b may be adjusted by a total angular displacement of <NUM> degrees or more during the spin cycle.

The orbital balancing passage <NUM> may provide a passage through which the first and second counterweight devices 170a, 170b may travel to balance a load imbalance within the tub and drum assembly <NUM>. For example, the orbital balancing passage <NUM> may be arranged concentrically around and provide an arcuate passage around the motor <NUM> and the primary rotation axis <NUM>. The orbital balancing passage <NUM> may be the coupled to the base wall section <NUM> of the drum <NUM>. In some embodiments, and as depicted, the orbital balancing passage <NUM> may be coupled to the base wall section <NUM> by a support plate <NUM>. The orbital balancing passage <NUM> may be coupled to the support plate <NUM> through any coupling techniques (e.g., welding, brazing, fastening, etc.) or may be integrally formed therewith. In some embodiments, the orbital balancing passage <NUM> may instead be directly coupled or integrally formed with the base wall section <NUM> of the drum <NUM>.

The orbital balancing passage <NUM> may include a passage body <NUM>, which constrains motion of the first and second counterweigh devices 170a, 170b to an orbiting motion about the primary rotation axis <NUM>. For example, the orbital balancing passage <NUM> may define a first orbital chamber <NUM> in which at least one of the first and second counterweight devices 170a, 170b sit. It is noted that while the first and second counterweight devices 170a, 170b are illustrated as being positioned within the same orbital chamber. In some embodiments, the first and second counterweight devices 170a, 170b may sit in parallel but separate orbital chambers. Such parallel orbital loads chambers may allow for concentration of the center of masses 55a, 55b of the first and second counterweight device 170a, 170b at the same angular position to provide greater load balance capabilities. In alternative embodiments the orbital balancing passage <NUM> does not include a passage body <NUM> that constrains radial motion of the first and second counterweight devices. Instead, the orbital chamber <NUM> may include a ring-shaped region of volume around the motor <NUM> and tub first inset wall <NUM>. For example, the first and second counterweight devices 170a, 170b can be rigidly coupled to disks coupled to a rotational shaft rotating around primary rotation axis <NUM>.

In embodiments, to maintain the first and second counterweight devices 170a, 170b within the first orbital chamber <NUM>, the dynamic balancing assembly <NUM> may include an orbital positioning device <NUM> arranged to enclose the first and second counterweight devices 170a, 170b within the orbital balancing passage <NUM>. The orbital positioning device <NUM> may further be arranged to restrain a first angular position of the first counterweight device 170a and a second angular position of the second counterweight device 170b within the orbital balancing passage <NUM>. For example, the orbital positioning device <NUM> may be a restraining wall <NUM>, which constrains the first and second counterweight devices 170a, 170b into contact with the orbital balancing passage <NUM>, such that the first and second counterweight devices 170a, 170b are only able to move in an arcuate path at a constant radius around the primary rotation axis <NUM> of the tub and drum assembly <NUM>.

In some embodiments, the orbital positioning device <NUM> may include a ring gear <NUM> that interacts with the first and second counterweight devices 170a, 170b to allow the first and second counterweight devices 170a, 170b to engage and traverse the ring gear <NUM> to move in an arcuate path about the primary rotation axis <NUM> of the tub and drum assembly <NUM> while remaining positioned within the first orbital chamber <NUM>.

In some embodiments, the orbital positioning device <NUM> may include both a ring gear <NUM> and a restraining wall <NUM>, which are positioned directly parallel to one another and are separated from one another by a gap <NUM>. As will be explained in greater detail herein, the gap <NUM> may allow for passage of one or more wires for communicatively coupling the first and second counterweigh devices 170a, 170b with the control unit <NUM>.

As noted above, motion of the first and second counterweight devices 170a, 170b may be responsive to communications from the control unit <NUM>. The control unit <NUM> may communicate with the first and second counterweight devices 170a, 170b through wireless or wired communications. Orbital movement of the first and second counterweight devices 170a, 170b may make maintaining wired communication difficult due to twisting and tangling of the wires. An alternative approach is brushed commutation with slip rings or brushes and commutators. Brushed approaches face challenges with corrosion and wear especially in a wet environment. Wired connections can be made fully hermetic and impervious to moisture if the cable management challenges can be overcome. One approach may be to use one or more clock springs. For example, the one or more clocksprings may include first and second clocksprings 180a, 180b that communicatively couple the first and second counterweight devices 170a, 170b to the control unit <NUM> (illustrated in <FIG>). The first and second clocksprings 180a, 180b may be positioned concentrically with the orbital balancing passage <NUM>. <FIG> illustrates the first and second clocksprings 180a, 180b, the first and second counterweight devices 170a, 170b, and the ring gear <NUM> in isolation from the rest of the dynamic balancing assembly <NUM>. The first and second clocksprings 180a, 180b may be axially displaced along the primary axis <NUM> to allow independent orbital motion of the first and second clocksprings 180a, 180b.

In the illustrated embodiment, the first clockspring 180a is coupled to the first counterweight device 170a and the second clockspring 180b is coupled to the second counterweight device 170b. Clocksprings may be characterized in that they generally include a flat cable wound in a coiled (spiral) shape. Each of the first and second clocksprings 180a, 180b may include, for example, an electrical cable with one more electrical conductors to communicate electrical signals and voltage. For example, a ribbon cable may be suitable for clockspring construction. Each clockspring 180a, 180b may communicate power and motor signals to driving motors 174a, 174b to move the first and/or second counterweight devices 170a, 170b along the orbital balancing passage <NUM> to adjust an angular position of the first and/or second counterweight devices 170a, 170b around the primary rotation axis <NUM>. In embodiments, the clocksprings 180a, 180b may also communicate position feedback and/or other sensor signals from the orbiting counterweight devices 170a, 170b back to the control unit <NUM>. Sensors included in or on the orbiting counterweights devices 170a, 170b may include, but are not limited to, force sensors, vibration sensors, temperature sensors, position feedback sensors, accelerometer sensors, etc..

As the first and second counterweight devices 170a, 170b orbit about the ring gear <NUM>, the coil winds tighter or loosens depending on the direction of travel while maintaining the electrical connection. A clockspring has limited range of angular travel. At the end of travel the coil cannot accommodate additional relative angular motion between the inside and outside of the coil. Clocksprings according to the present disclosure may accommodate one or more revolutions of angular travel (e.g., two or more revolution, <NUM> or more revolutions, four or more revolutions, four of fewer revolutions, etc.). The control unit <NUM> may execute logic to ensure that the first and second counterweight devices 170a, 170b are only able to make a certain number of revolutions or move a certain degree around the orbital balancing passage <NUM> to not exceed the angular travel possible for the clocksprings 180a, 180b. This may avoid stretching or damaging the cable and maintains electrical connection between the counterweight devices 170a, 170b and control unit <NUM>. After the spin cycle and balancing is complete, the position of both first and second counterweight devices 170a and 170b can be returned to a home position that is, for example, in the middle of angular travel range for the first and second clocksprings 180a and 180b.

Referring again to <FIG>, the orbital balancing passage <NUM> may further define a clockspring chamber <NUM> positioned radially inward from the first orbital chamber <NUM>. Each of the first and second clocksprings 180a, 180b may be positioned within the clockspring chamber <NUM>. To connect to the first and second counterweight devices 170a, 170b, lead wires from the first and second clocksprings 180a, 180b may extend through the gap <NUM> to be coupled to the respective first and second counterweight devices 170a, 170b.

As noted above, the orbital balancing passage <NUM> (including the first orbital chamber <NUM> and the clockspring chamber <NUM>) may be directly coupled to the base wall section <NUM> or may be coupled to the base wall section <NUM> by support plate <NUM>. The support plate <NUM> may extend along the base wall section <NUM> and be shaped to conform to a shape of the protruding portion <NUM> and the recessed portion <NUM>. That is, the support plate <NUM> may be coextensive along the at least a portion of the base wall section <NUM>. The support plate <NUM> may be coupled to the base wall section <NUM> through any coupling techniques (e.g., welding, brazing, fastening, etc.) or may be integrally formed therewith.

An extending portion <NUM> of the support plate <NUM> may separate from the base wall section <NUM> at a transition point <NUM> where the base wall section <NUM> transitions to a sidewall section <NUM> via a curved wall section <NUM>. The extending portion <NUM> may be perpendicular to the sidewall section <NUM> of the drum <NUM>. The extending portion <NUM> may extend to a diameter that is larger than a maximum diameter of the sidewall section <NUM> of the drum <NUM>. However, in some embodiments, the extending portion <NUM> may be equal to or less than a maximum diameter of the sidewall section <NUM> of the drum <NUM>. In the illustrated embodiment, the orbital balancing passage <NUM> may be arranged at the distal end of the extending portion <NUM> to maximize the applied moment provided by the first and second counterweight devices 170a, 170b. The orbital balancing passage <NUM> may enclose both the first and second counterweight devices 170a, 170b, and the first and second clocksprings 180a, 180b between the orbital balancing passage <NUM> and the support plate <NUM>.

As noted above, the drum <NUM> may be operatively coupled to the motor <NUM> via a drive shaft <NUM> defining the primary rotation axis <NUM>. In embodiments, the drive shaft <NUM> may be integrally formed within the support plate <NUM> of the drum <NUM>. In other embodiments, the drive shaft <NUM> may be fixedly coupled to the support plate <NUM> or directly fixedly coupled to the drum body <NUM> via any coupling technique (e.g., welding, brazing, fastening, etc.). It is noted that lead wires from the first and second clocksprings 180a, 180b may be routed through openings in the support plate <NUM> and through a center opening <NUM> of the drive shaft <NUM> with communication to the control unit <NUM> (illustrated in <FIG> and <FIG>). The lead wires 181a, 181b from an inner coil of the first and second clocksprings 180a, 180b may be connected to a rotational commutation device <NUM>. One side or the rotating end <NUM> of the rotational commutation device <NUM> may rotate with the drum <NUM> and may be installed at a back end of the drive shaft <NUM>. The other side or the non-rotating end <NUM> of the rotational commutation device <NUM> does not rotate with the drum <NUM> and may be connected to the tub <NUM> or exterior housing <NUM>. The rotational commutation device <NUM> communicates multiple paths of electrical current from multiple conductors of lead wires to communicate power and sensor signals between the rotating and non-rotating components of the laundry apparatus <NUM>. The rotational commutation device <NUM> may be a slip ring, brushed commutator, inductive commutator, etc. Lead wires <NUM> from the non-rotating end of the rotational commutation device <NUM> can connect to the control unit <NUM>. The control unit <NUM> may include a drive amplifier (not shown) or other electronic circuits to provide power to the driving motors 174a, 174b through the first and second clocksprings 180a, 180b to adjust angular position of the first and second counterweight devices 170a, 170b. The rotational commutation device <NUM> can also communicate sensor signals from devices in the rotating drum <NUM> such as counterweight device position sensors, homing sensors, temperature sensors, force sensors, vibration sensors, load imbalance sensors <NUM>, and accelerometers to the control unit <NUM> for processing. The rotational commutation device <NUM> can alternatively communicate power and control signals to an intermediate drive amplifier that may rotate with the drum <NUM> and is connected to the first and second counterweight devices 170a, 170b by the first and second clocksprings 180a, 180b.

Referring now to the first and second counterweight devices 170a, 170b, the first and second counterweight devices 170a, 170b are configured to be controllably moved about the orbital balancing passage <NUM> to balance an imbalanced laundry load within the laundry apparatus <NUM>. For example, the first and second counterweight devices 170a, 170b may have a combined mass that is sufficiently large to balance a moment of a combined full design capacity laundry load saturated with a washing fluid. The first and second counterweight devices 170a, 170b can be constructed of a high density material such as steel, cast iron, tungsten, bronze, brass, lead, nickel, copper, aluminum, concrete, ceramic, glass, etc to minimize the volume occupied by the first and second counterweight devices 170a, 170b and the orbital balancing passage <NUM>. As will be described in greater detail below, the first counterweight device 170a and the second counterweight device 170b may be cooperatively controlled by the control unit <NUM> in response to detecting the load imbalance in the drum <NUM> based on the load imbalance signal output by the one or more load imbalance sensors <NUM>.

<FIG> and <FIG> illustrates a counterweight device <NUM> in isolation from the tub and drum assembly <NUM>. Each of the first and second counterweight devices 170a, 170b may be substantially identical to the counterweight device <NUM> illustrated in <FIG> and <FIG>. Referring particularly to <FIG>, the counterweight device <NUM> may include a curved body <NUM> shaped to travel through the orbital balancing passage <NUM>. The curved body <NUM> may house one or more weights (not shown). Coupled to the curved body <NUM> may be a driving motor <NUM>, which is communicatively coupled to the control unit <NUM> (shown in <FIG> and <FIG>) through the clock spring <NUM>.

Referring to <FIG> which illustrates a driving assembly <NUM> of the counterweight device <NUM>, the driving motor <NUM> may drive a worm gear <NUM>. The driving motor <NUM> more be a reversible motor so as to be able to drive the counterweight device <NUM> in both a clockwise direction and a counterclockwise direction about the orbital balancing passage <NUM>. The worm gear <NUM> may be meshed with a worm wheel <NUM> that is mounted to a rotational axis <NUM>. Also mounted to the rotational axis <NUM> is a pinion gear <NUM>. That is, the pinion gear <NUM> may share a common rotational axis <NUM> with the worm wheel <NUM> such that rotation of the worm wheel <NUM> rotates the pinion gear <NUM>. Referring again to <FIG>, the pinion gear <NUM> is positioned at an edge <NUM> of the curved body <NUM> so as to be able to mesh with the ring gear <NUM> (illustrated in <FIG>). Accordingly, rotation of the worm gear <NUM> by the driving motor <NUM> causes the pinion gear <NUM> to rotate, which causes the counterweight device <NUM> to traverse the ring gear <NUM> and the orbital balancing passage <NUM>.

The counterweight device <NUM> may further include one or more wheels <NUM> positioned along the counterweight body the counterweight wheel may be arranged to contact the orbital balancing passage <NUM> and/or the retention device when positioned within the orbital balancing passage <NUM>. The one or more wheels <NUM> may be freely rotatably. In other embodiments, the one or more wheels <NUM> may be driven wheels (e.g., via a driving motor <NUM>). Alternatively the wheels <NUM> can be replaced with bushings or bearings that allow relative motion at reduced friction between the counterweight device <NUM> and the orbital balancing passage <NUM>.

Referring again to <FIG>, when assembled, a cross-sectional plane <NUM>, passing through the laundry apparatus <NUM> at a position orthogonal to the primary rotation axis <NUM>, passes through dynamic balancing assembly <NUM> (e.g., the first counterweight device 170a, the second counterweight device 170b, or a combination thereof), the motor <NUM>, the fluid containment envelope <NUM>, and the first inset wall <NUM> of tub <NUM>. Note that while the cross-sectional plane <NUM> can pass through both the motor <NUM> and dynamic balancing assembly <NUM>, the motor is isolated from washing fluid by the first inset wall <NUM> of tub <NUM>. The dynamic balancing assembly <NUM> is directly connected to the drum <NUM> which allows effective counterbalancing to an imbalance caused by the center of mass <NUM> of laundry <NUM> and the first and second counterweight devices 170a, 170b. Because of the inset wall <NUM> of tub <NUM>, the back of the motor <NUM> may, in some embodiments, be substantially flush with or closely proximate to a plane defined by a rear surface of the dynamic balancing assembly <NUM> instead of the back of the motor <NUM> being substantially offset from the back of the dynamic balancing assembly <NUM> which may cause the rear wall of the exterior housing <NUM> to increase in depth or to reduce the depth of the drum <NUM> and reduce the volume of the laundry receiving portion <NUM>. In embodiments wherein the first and second counterweight devices 170a, 170b are positioned in parallel but separate planes, the cross-sectional plate may only pass through one of the first counterweight device 170a or the second counterweight device 170b. The cross-sectional plane <NUM> may additionally pass through at least one or the first clockspring 180a and the second clock spring 180b. Accordingly, the present design provides for a more efficient use of space within the tub <NUM> and the laundry apparatus <NUM> by aligning various components along a common plane <NUM>. Such alignment allows for a greater amount of space to be reserved for the laundry-receiving portion <NUM> of the drum <NUM>.

Referring again to <FIG> and <FIG>, to provide for dynamic balancing of the laundry apparatus <NUM>, the laundry apparatus <NUM> may further include one or more load imbalance sensors <NUM> communicatively coupled to the control unit <NUM> and configured to output a load imbalance signal to the control unit <NUM>. The load imbalance signal may be indicative of a load imbalance within the drum <NUM>. For example, the load imbalance signal may be indicative of an angular position and a magnitude of the load imbalance within the drum <NUM>. The one or more load imbalance sensors <NUM> may be mounted anywhere in the laundry apparatus <NUM> and attuned to detect balance conditions within the drum <NUM>. For example, the one or more dynamic balancing sensors may include accelerometers and/or motor rotational position sensors to determine a center of mass within the load of laundry to determine if a load imbalance is present. Another embodiment may use motor torque sensors and motor rotational position sensors to determine a center of mass within the load of laundry to determine if a load imbalance is present. In yet further embodiments, force sensors may be used along with motor rotation position sensors to determine a center of mass within the load of laundry to determine if a load imbalance is present. Other sensors may include vibrational sensors or the like to determine the presence of a load imbalance. The load imbalance sensors <NUM> can detect relative and/or absolute variations in displacement, velocity, and/or acceleration of components of the laundry appliance <NUM>. For instance, a displacement-based load imbalance sensor <NUM> can measure small changes of displacement between the tub <NUM> and exterior housing <NUM> caused by an imbalanced load. In another example, an acceleration-based load imbalance sensor may measure fluctuations of acceleration of an accelerometer mounted to the tub <NUM>. In some embodiments, load imbalance may also be sensed by measuring change in force, torque, or strain between components of the laundry appliance <NUM>. In further embodiments, load imbalance may also be measured by monitoring the current to motor <NUM>. In yet further embodiments, load imbalance can also be determined based on acoustic analysis of noise during operation.

The angular position of the combined center of mass <NUM> relative to the primary rotation axis <NUM>, as illustrated in <FIG> and <FIG>, can be determined by measuring the angular position of the center of mass <NUM> of the laundry <NUM>. This is measured relative to a reference angular position <NUM> of the drum <NUM>. The reference angular position <NUM> of the drum <NUM> may be measured by a drum rotation sensor such as a magnetic or optical proximity sensor, a hall effect sensor, an encoder, resolver, etc. The reference angular position <NUM> of the drum <NUM> may, in some embodiments, be measured by motor position sensors. The angular position for center of mass <NUM> of the laundry <NUM> may be measured by the load imbalance sensor <NUM> relative to the reference angular position <NUM> of the drum <NUM>. Signals from the load imbalance sensor <NUM> can be analyzed in the time domain or alternatively in the frequency domain. Additionally, a magnitude of the imbalance signal from the load imbalance sensor <NUM> may be used to estimate the equivalent lumped mass at the center of mass <NUM> for laundry <NUM>. For example, the total mass of laundry <NUM> may be measured directly by load cells or strain gauge sensors. In some embodiments, the total mass of the laundry <NUM> may be calculated based on inertia of the laundry measured by accelerating or decelerating the spinning of the drum <NUM>. Control unit <NUM> may periodically or continuously calculate an estimate for magnitude and angle of imbalance to be countered by adjusting angular positions of the first and second counterweight devices 170a, 170b. The amount of adjustment of the first and second counterweight devices 170a, 170b may be calculated by the control unit <NUM> so as to move the combined center of mass <NUM> of the laundry <NUM>, the first counterweight device 170a, and the second counterweight device 170b, to cause the combined center of mass <NUM> to be substantially coincident with the primary rotation axis <NUM> and eliminate or substantially reduce the vibrations that would result from a load imbalance. In embodiments, the control unit may not calculate an amount of adjustment for the first and second counterweight devices 170a, 170b. Instead, the control unit may adjust the first and second counterweight devices 170a, 170b using a differential "trial and error" solution where angular positions 53a, 53b are adjusted until imbalance is reduced and eliminated. Another control strategy can employ a combination of a mathematical control scheme with fine tuning adjustments to further reduce imbalance signal.

<FIG> illustrates a flowchart depicting a method <NUM> for balancing the laundry apparatus <NUM> as described herein. The method <NUM> may start at step <NUM> and may include loading laundry within the laundry apparatus <NUM> and starting the laundry apparatus <NUM>. At step <NUM>, the method <NUM> includes rotating the drum <NUM>. At step <NUM>, the method <NUM> may further include receiving with the control unit <NUM>, a load imbalance signal output by the one or more load imbalance sensors <NUM>. At step <NUM>, the method <NUM> includes detecting, with the control unit <NUM>, a load imbalance signal output by the one or more load imbalance sensors <NUM> and determining whether a load imbalance is present within the drum <NUM> based on the load imbalance signal. Where a load imbalance is not detected, the method <NUM> may include monitoring the load for the load imbalance signal. Where a load imbalance is detected, the method <NUM> further includes, at step <NUM>, controlling the dynamic balancing assembly <NUM> to controllably move the first counterweight device 170a positioned within the orbital balancing passage <NUM> to adjust an angular position of the first counterweight device 170a around the primary rotation axis to counteract a detected load imbalance in the drum <NUM> and controllably move the second counterweight device 170b positioned within the orbital balancing passage <NUM> with the control unit <NUM> to adjust an angular position of the second counterweight device 170b around the primary rotation axis to counteract the detected load imbalance in the drum <NUM>. The control unit <NUM> may continue to monitor the laundry apparatus <NUM> for further load imbalances. In embodiments, the control unit <NUM> may only detect load imbalances and initiate movement of the first and second counterweight devices 170a, 170b during certain laundry cycles (e.g., the spin cycle). For example, the method may include monitoring the drum <NUM> with the one or more load imbalance sensors <NUM> continuously during acceleration from a satellite speed (e.g., a base operating speed sufficient for the centripetal acceleration to exceed gravitation acceleration) to a maximum water extraction speed (e.g., <NUM> RPM or greater, <NUM>,<NUM> RPM or greater, etc.).

The dynamic balancing assembly <NUM> illustrated in <FIG>, is illustrative of a single plane balancer where in the counterweight devices 170a, 170b are located on a single plane (i.e., within the same plane) perpendicular to the primary rotation axis <NUM>. Single plane balancing may be effective in many instances. In particular, single plane balancing is effective when the depth of the drum <NUM> is relatively shallow such that the center of mass <NUM> for laundry <NUM> is in proximity with the plane of the counterweight devices 170a, 170b. Single plane balancing may also be particularly effective when the geometry of the drum <NUM> causes the center of mass <NUM> for laundry <NUM> to remain in proximity with a plane in which the counterweight devices 170a, 170b are supported. Tilting the primary rotation axis <NUM> so that the back of the drum <NUM> with the dynamic balancing assembly <NUM> is lower than the front of the drum <NUM> could cause the laundry <NUM> to slide toward the back of the drum due to gravitational acceleration so as to be closely positioned to the dynamic balancing assembly <NUM>.

However, in other embodiments, counterweight devices can be located within two or more planes perpendicular to the primary rotation axis <NUM>. Two plane dynamic balance may be accomplished by configuring the tub and drum assembly <NUM> to include two or more dynamic balancing assemblies <NUM>. The two or more dynamic balancing assemblies <NUM> may be provided with some axial separation along the primary rotation axis <NUM>. Each of the two or more dynamic balancing assemblies <NUM> will be coincident with a plane oriented perpendicular to the primary rotation axis <NUM>. Two plane balancing may be additionally effective at eliminating imbalances created when the center of mass <NUM> of the laundry <NUM> is not in proximity with a single plane supporting the counterweight devices <NUM>. Two plane balancing can be useful when the depth of the drum <NUM> is deep (e.g., depth of the drum to diameter ratio is greater than <NUM>) and the center of mass <NUM> of the laundry cannot be moved proximate to a single plane supporting the counterweight devices during operation.

<FIG> show some schematic illustrative embodiments of tub and drum assemblies <NUM> with various configurations including two or more dynamic balancing assemblies <NUM>. <FIG> illustrates a tub and drum assembly <NUM> with a cantilevered drum <NUM> configured for single plane balancing with a single dynamic balancing assembly <NUM> mounted to the rear of the drum <NUM>, such as discussed in greater detail above. The cantilevered drum <NUM> employs a main bearing assembly <NUM>, such as illustrated in <FIG> at the rear of the drum. A motor <NUM> is coupled to the rear of the drum and mounted concentrically inset relative to the dynamic balancing assembly <NUM>.

<FIG> illustrates a tub and drum assembly <NUM> with a cantilevered drum <NUM> configured for two plane balancing with a first dynamic balancing assembly 150a mounted to the rear of the drum <NUM> and a second dynamic balancing assembly 150b mounted to the front of the drum <NUM>. A Motor <NUM> is coupled to the rear of the drum <NUM> and mounted concentrically inset relative to the first dynamic balancing assembly 150a.

<FIG> illustrates a tub and drum assembly <NUM> with a cantilevered drum <NUM> configured for two plane balancing with a first dynamic balancing assembly 150a mounted to the rear of the drum <NUM> and a second dynamic balancing assembly 150b mounted to the inside rear of the drum <NUM>. A Motor <NUM> is coupled to the rear of the drum <NUM> and mounted concentrically inset relative to the first dynamic balancing assembly 150a.

<FIG> illustrates a tub and drum assembly <NUM> with a cantilevered drum <NUM> configured for two plane balancing with a first dynamic balancing assembly 150a mounted to the rear of the drum <NUM> and a second dynamic balancing assembly 150b mounted behind the first dynamic balancing assembly 150a. A motor <NUM> is coupled to the rear of the drum <NUM> and mounted concentrically inset relative to the first and second dynamic balancing assemblies 150a, 150b.

<FIG> illustrates a tub and drum assembly <NUM> with a simply supported drum <NUM> (e.g., supported at both the front end and the rear end of the drum) configured for single plane balancing with a single dynamic balancing assembly <NUM> mounted to the rear of the drum <NUM>. The simply supported drum <NUM> may employ main bearing assemblies (not shown) at the rear and front of the drum <NUM>. A motor <NUM> is coupled to the rear of the drum <NUM> and mounted concentrically inset relative to the dynamic balancing assembly <NUM>.

<FIG> illustrates a tub and drum assembly <NUM> with a simply supported drum <NUM> configured for two plane balancing with a first dynamic balancing assembly 150a mounted to the rear of the drum <NUM> and a second dynamic balancing assembly 150b mounted to the front of the drum <NUM>. Motors 140a, 140b are coupled to the rear and front of the drum <NUM> and mounted concentrically inset relative to respective the first and second dynamic balancing assemblies 150a, 150b.

<FIG> illustrates a tub and drum assembly <NUM> with a simply supported drum <NUM> configured for two plane balancing with a first dynamic balancing assembly 150a mounted to the rear of the drum <NUM> and a second dynamic balancing assembly 150b mounted to the front of the drum <NUM>. A Motor <NUM> is coupled to the rear of the drum and mounted concentrically inset relative to the first dynamic balancing assembly 150a.

<FIG> illustrates a tub and drum assembly <NUM> with a simply supported drum <NUM> configured for two plane balancing with a first dynamic balancing assembly 150a mounted to the rear of the drum <NUM> and a second dynamic balancing assembly 150b mounted behind the first dynamic balancing assembly 150a. A Motor <NUM> is coupled to the rear of the drum and mounted concentrically inset relative to the first and second dynamic balancing assemblies 150a, 150b.

Alternatively for the embodiments illustrated in <FIG>, a passive dynamic balancing assembly such as a simple fluid and weighted ball filled balancing ring could be used in place of an active dynamic balancing assembly controlled by a control unit. Alternatively for the embodiments illustrated in <FIG>, the dynamic balancing assembly <NUM> could use means for dynamically balancing other than adjusting angular position of counterweight devices <NUM>. Some alternative embodiments may include counterweights having an adjustable radial position from primary rotation axis <NUM>, variable mass bodies such as fluid or powder filled bladders or cylinders, orbital masses that can shift off-center from primary rotation axis <NUM>, rings filled with weighted balls with adjustable orbital position by magnetic attraction, etc..

Referring now to <FIG>, the tub and drum assembly <NUM> is located inside of the exterior housing <NUM> of a laundry apparatus <NUM>. The tub <NUM> may be attached to the exterior housing <NUM> via a displaceable suspension <NUM>. The displaceable suspension <NUM> may include any tuned passive elements used to reduce vibrations or the effects thereof, including, but not limited to, springs <NUM>, additional suspension mass(es) <NUM> attached to the tub, and dampers <NUM> designed to reduce transmittance of vibrations and absorb energy from spinning imbalanced laundry to the exterior housing <NUM>, or the like. The displaceable suspension <NUM> allows the tub <NUM> to displace relative to the exterior housing <NUM>. The displacement of the tub <NUM> may cause travel in any direction. For example the direction of travel can be in the radial direction or axial direction relative to the primary rotation axis <NUM>. Significant displacement of the tub may absorb vibrations and dampen the motion of a vibrating tub and drum assembly <NUM>. In some embodiments, the displaceable suspension <NUM> may include active members such as linear motors, torsional motors, dampers with magnetorheological fluid, voice coil actuators, pneumatic actuators, magnetic actuators, etc. to dampen vibrations. Passive and active suspension members may rely on relative motion between the tub and drum assembly <NUM> and the exterior housing <NUM> to absorb vibrations transmitted to exterior housing <NUM>.

A travel volume <NUM> surrounding the tub <NUM> may be delineated by a swept volume of the tub and drum assembly <NUM> following the maximum possible travel distance <NUM> in all directions. That is, the travel volume <NUM> may be space within the exterior housing left empty or free from obstructions between the tub <NUM> and exterior housing <NUM> to accommodate movement of the tub and drum assembly <NUM>. The provide enough space for the travel volume <NUM>, the interior of the exterior housing <NUM> may be significantly larger than the exterior dimensions of the tub <NUM>. This may create a practical limitation to the size of the tub and drum assembly <NUM> and internal laundry capacity for a given exterior housing size. If the diameter of the tub and drum assembly <NUM> approaches the inside width or height of the exterior housing <NUM>, the displaceable suspension <NUM> would have limited travel space available and would be unable to isolate vibration from the tub and drum assembly <NUM> to the exterior housing <NUM>. Likewise, if the axial depth of the tub and drum assembly <NUM> approaches the inside depth of the exterior housing <NUM>, the displaceable suspension <NUM> would have limited travel space available and would be unable to isolate vibration due to load imbalance from transmitting to the exterior housing <NUM>.

The addition of a dynamic balancing assembly <NUM> described above to a laundry apparatus <NUM> using a displaceable suspension <NUM> can greatly reduce or eliminate the vibrations generated by the laundry imbalance. If the masses of the first and second counterweight devices 170a, 170b are not sized to balance the potential imbalance of the largest possible laundry load, then some imbalance can still be generated even with the dynamic balancing assembly <NUM> and the displaceable suspension <NUM> may dampen the remaining vibration through displacement of the displaceable suspension. The addition of the dynamic balancing assembly <NUM> may reduce the maximum travel distance <NUM> and can reduce the travel volume <NUM> needed to allow for the maximum travel. For example, the maximum travel distance for the tub and drum assembly <NUM> may be less than about <NUM>. In such embodiments, the dimensions of the tub and drum assembly <NUM> may be enlarged such that the travel volume <NUM> extends to an interior surface of the exterior housing <NUM>. Stated another way, the tub and drum assembly <NUM> may be in much closer proximity to the exterior housing <NUM>, so as to fill up more of the space within the exterior housing <NUM>.

A dynamic balancing assembly <NUM> can greatly reduce or eliminate vibration transmitted to the laundry apparatus <NUM> from laundry imbalance. Elimination of imbalance and vibration can allow construction of a laundry apparatus <NUM> without a displaceable suspension <NUM>. Referring to <FIG>, the tub and drum assembly <NUM> may be located inside of the exterior housing <NUM> of a laundry apparatus <NUM> by attaching the tub <NUM> to the exterior housing <NUM> with one or more tub mounts <NUM> or a plurality of tub mounts. The tub mounts <NUM> include of a plurality of various mounting interfaces to attach the tub <NUM> to the exterior housing <NUM>. The tub mounts <NUM> may be components separate from the tub <NUM> and exterior housing <NUM> or may be integral to the tub <NUM> and/or the exterior housing <NUM>. The tub mounts <NUM> can include any rigid or stiff material that has minimal displacement during loading of laundry <NUM> into drum <NUM>. The tub mounts <NUM> may alternatively provide some compliance and may allow minimal displacement (e.g., for example a maximum displacement of <NUM> or less with <NUM> lb force applied). Compliant tub mounts <NUM> may be constructed using vibration isolators, elastomeric motor mounts, stiff springs (e.g., a spring having a maximum extension/contraction of <NUM> or less), fluid filled motor mounts, etc. The tub mounts <NUM> may be produced from any material including, but not limited to a polymer, elastomeric, metallic components, or any combination thereof. The tub mounts <NUM> can be attached by bolts, screws, rivets, adhesive, welding, etc..

A dynamically balanced tub and drum assembly <NUM> with dynamic balancing assembly <NUM> supported by tub mounts <NUM> may be substantially free from vibration during operation such that the tub <NUM> will not substantially move relative to the exterior housing <NUM>. A balanced tub and drum assembly <NUM> without a displaceable suspension <NUM> may not require any of the travel volume <NUM> or a greatly reduced travel volume and will allow the tub and drum assembly <NUM> to fully occupy the interior volume of the exterior housing <NUM>. Given the same dimensions of exterior housing <NUM>, the tub and drum assembly <NUM> without a displaceable suspension <NUM> may be significantly larger than the tub and drum assembly <NUM> with a displaceable suspension <NUM>. The larger tub and drum assembly may have more interior volume in the laundry receiving portion <NUM> and may accommodate more laundry <NUM>. Similarly, given the same dimensions for the tub and drum assembly <NUM> and the same laundry <NUM> capacity, the exterior housing <NUM> without a displaceable suspension <NUM> can be significantly smaller than the exterior housing <NUM> with a displaceable suspension <NUM>. Eliminating the displaceable suspension <NUM> by applying a dynamic balancing assembly <NUM> may allow for construction of a compact laundry apparatus with useful volume of laundry receiving portion <NUM> and laundry <NUM> capacity. Eliminating the displaceable suspension <NUM> by applying a dynamic balancing assembly <NUM> may also allow for construction of a standard size laundry apparatus with superior volume of laundry receiving portion <NUM> and laundry <NUM> capacity.

It may be impractical to construct a compact laundry apparatus with very small external housing dimensions if the tub and drum assembly <NUM> are supported by a displaceable suspension <NUM> that accommodates a maximum travel of <NUM>, as the resulting laundry capacity may be very small. It is especially impractical to construct a compact laundry apparatus with an external housing <NUM> of a very small depth (e.g., <NUM> or less) if the tub and drum assembly <NUM> are supported by a displaceable suspension <NUM> with a maximum travel of <NUM> as the resulting laundry capacity would still be very small. TABLE <NUM> compares drum internal volume and drum dimensions for four different laundry apparatus configurations having varying exterior housing dimensions compared with and without a displaceable suspension. The radial and axial travel for the examples are is about <NUM>. The laundry apparatus configurations with the dynamic balancing assembly <NUM> and no suspension has larger drum <NUM> volume by <NUM>% - <NUM>%.

In some embodiments, instead of maximizing drum volume, the additional space provided by eliminating the displaceable suspension and/or the travel volume may be used for packing various internal laundry apparatus components <NUM> inside the volume of a laundry apparatus <NUM>. Traditionally, packaging internal laundry apparatus components has been challenging especially when the exterior housing <NUM> has compact dimensions or if the laundry apparatus is a combination washer / dryer. Referring to <FIG>, the tub and drum assembly <NUM> is located inside of the exterior housing <NUM> of a laundry apparatus <NUM> by attaching the tub <NUM> to the exterior housing <NUM> with a tub mounts <NUM>, as described above. As noted above, the tub and drum assembly <NUM> with dynamic balancing assembly <NUM> may be constructed without a displaceable suspension and will not require any travel volume or only a small travel volume (e.g., <NUM> or less radially in any direction and <NUM> axially). If the exterior dimensions of the tub and drum assembly <NUM> are smaller than the internal dimensions inside the exterior housing <NUM>, the volume between the tub and drum assembly <NUM> and the exterior housing <NUM> may be used for placement of laundry apparatus components <NUM>. Laundry apparatus components <NUM> can include, but are not limited to, pumps, water hoses, air ducts, water storage sumps, power supplies, control units, electronic circuitry, sensors, air heaters, water heaters, drying components, condensation equipment, refrigeration components, moisture storage components, vessels for storage of water. Storage of detergent and chemicals, detergent and chemical dispensers, fans, storage of hoses, hose reels, casters, etc. Substantial elimination of the travel volume <NUM> of the tub <NUM> allows design of a laundry apparatus <NUM> with a high volume capacity for the laundry-receiving portion <NUM> and volume to install internal laundry apparatus components <NUM>. For example, positions in which the tub and drum assembly <NUM> is closest to the various surfaces (e.g., front, back, top, bottom, or sidewall), may define pinch points PP. Without using the active balancing assembly <NUM>, a displaceable suspension as illustrated in <FIG> may be necessary for damping vibrations. Accordingly, the travel volume <NUM> necessary to allow for movement of the displaceable suspension likely provides too little space for storage of laundry apparatus components <NUM> within the pinch points PP, whereas, and as illustrated in <FIG>, laundry apparatus components may be positioned in the pinch points PP, without encroaching on the space needed for the travel volume <NUM>.

Embodiments can be described with reference to the following numbered clauses, with preferred features laid out in the dependent clauses.

It should now be understood that embodiments described herein are generally directed to a laundry apparatuses that include dynamic balancing assemblies that maximize volumetric space for receiving laundry. For example, and as illustrated in the figures, a laundry apparatus according to the present disclosure generally includes a tub, a drum, and a dynamic balancing assembly. The drum is positioned within a fluid containment envelope of the tub and is rotatable relative to the tub about a primary rotation axis <NUM><NUM>, the drum defines a laundry-receiving portion for receiving one or more articles of laundry. The dynamic balancing assembly includes an orbital balancing passage, arranged concentrically around a motor of the laundry apparatus, and first and second counterweight devices are positioned within the orbital balancing passage. The dynamic balancing assembly is positioned relative to the tub and/or drum so that a common cross-sectional plane passes through the dynamic balancing assembly, the motor, and the fluid containment envelope of the tub.

Claim 1:
A laundry apparatus (<NUM>) comprising:
a tub (<NUM>) defining a fluid containment envelope (<NUM>);
a drum (<NUM>) positioned within the fluid containment envelope of the tub and rotatable relative to the tub about a primary rotation axis (<NUM>), the drum comprising a laundry-receiving portion (<NUM>) for receiving one or more articles of laundry (<NUM>);
a control unit (<NUM>);
a motor (<NUM>) coupled to the tub, wherein the motor is communicatively coupled to the control unit and operatively coupled to the drum to cause rotation of the drum, wherein the motor is isolated from fluid within the fluid containment envelope;
a dynamic balancing assembly (<NUM>) communicatively coupled to the control unit, the dynamic balancing assembly comprising one or more counterweight devices (170a, 170b) configured to be orbited about the primary rotation axis to counteract a load imbalance in the drum; and
one or more clocksprings (180a, 180b) communicatively coupling each of the one or more counterweight devices to the control unit,
wherein the dynamic balancing assembly further comprises an orbital balancing passage (<NUM>) arranged concentrically around the motor, characterized by the orbital balancing passage comprising:
a first orbital chamber (<NUM>) defining a passage within which the one or more counterweight devices are moveably positioned; and
a clockspring chamber (<NUM>) open to the first orbital chamber and housing the one or more clocksprings.