WO2011025320A2 - Procédé de commande d'un lave-linge - Google Patents

Procédé de commande d'un lave-linge Download PDF

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Publication number
WO2011025320A2
WO2011025320A2 PCT/KR2010/005816 KR2010005816W WO2011025320A2 WO 2011025320 A2 WO2011025320 A2 WO 2011025320A2 KR 2010005816 W KR2010005816 W KR 2010005816W WO 2011025320 A2 WO2011025320 A2 WO 2011025320A2
Authority
WO
WIPO (PCT)
Prior art keywords
drum
control method
rotation speed
balls
transient region
Prior art date
Application number
PCT/KR2010/005816
Other languages
English (en)
Other versions
WO2011025320A3 (fr
Inventor
Jae Hyuk Jang
Bon Kwon Koo
Original Assignee
Lg Electronics Inc.
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from KR1020090079912A external-priority patent/KR101741549B1/ko
Priority claimed from KR1020090079923A external-priority patent/KR20110022367A/ko
Priority claimed from KR1020090079922A external-priority patent/KR101721871B1/ko
Application filed by Lg Electronics Inc. filed Critical Lg Electronics Inc.
Priority to RU2012111661/12A priority Critical patent/RU2496934C1/ru
Priority to CN201080042202.2A priority patent/CN102510915B/zh
Priority to EP10812333.2A priority patent/EP2470703B1/fr
Priority to US13/392,682 priority patent/US20120151693A1/en
Priority to AU2010287084A priority patent/AU2010287084B2/en
Publication of WO2011025320A2 publication Critical patent/WO2011025320A2/fr
Publication of WO2011025320A3 publication Critical patent/WO2011025320A3/fr

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Classifications

    • 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
    • D06F37/20—Mountings, e.g. resilient mountings, for the rotary receptacle, motor, tub or casing; Preventing or damping vibrations
    • D06F37/22—Mountings, e.g. resilient mountings, for the rotary receptacle, motor, tub or casing; Preventing or damping vibrations in machines with a receptacle rotating or oscillating about a horizontal axis
    • D06F37/225—Damping vibrations by displacing, supplying or ejecting a material, e.g. liquid, into or from counterbalancing pockets
    • 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
    • D06F33/00—Control of operations performed in washing machines or washer-dryers 
    • D06F33/30—Control of washing machines characterised by the purpose or target of the control 
    • D06F33/48—Preventing or reducing imbalance or noise
    • 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
    • D06F2103/00—Parameters monitored or detected for the control of domestic laundry washing machines, washer-dryers or laundry dryers
    • D06F2103/26—Imbalance; Noise level
    • 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
    • D06F2105/00—Systems or parameters controlled or affected by the control systems of washing machines, washer-dryers or laundry dryers
    • D06F2105/46—Drum speed; Actuation of motors, e.g. starting or interrupting
    • D06F2105/48—Drum speed

Definitions

  • the present invention relates to a control method of a laundry machine.
  • a drum laundry machine includes a drum arranged in a horizontal direction and a drum also arranged in a horizontal direction inside the tub. Laundry is located inside the drum and is washed with tumbling in accordance with rotation of the drum.
  • the tub serves to receive washing water therein, and the drum serves to carry out washing of the laundry.
  • the drum is rotatably installed inside the tub.
  • a rotational shaft is connected with a rear portion of the drum, and a rotational force is forwarded from a motor to the rotational shaft.
  • the rotational force is forwarded to the drum through the rotational shaft by rotation of the motor, whereby the drum is rotated.
  • the drum is rotated during rinsing and spinning cycles as well as a washing cycle.
  • the drum is vibrated with rotating.
  • the rotational shaft is projected outside the tub while passing through a rear wall of the tub.
  • a bearing housing may be inserted into the rear wall of the tub by insert molding.
  • the bearing housing may be fixed to the rear wall of the tub.
  • the rotational shaft is supported by the bearing housing, and vibration of the drum is forwarded to the bearing housing and the tub through the rotational shaft.
  • the tub is vibrated together with the drum.
  • a damping support member is connected with the tub.
  • vibration is forwarded to the tub, and is supported through the damping support member connected with the tub.
  • the present invention is directed to a control method of a laundry machine.
  • An object of the present invention is to provide a control method of a laundry machine which can solve the above problem.
  • an object of the present invention is to provide a method for passing through a transient region while reducing vibration of a drum when the drum is rotated at a speed more than the transient region in a laundry machine.
  • Another object of the present invention is to provide a method for controlling positions of balls of a balancer by considering characteristics of a vibration mode at a transient region.
  • vibration of the drum can be reduced effectively even in a vibration mode, i.e., a diagonal vibration mode where displacement at a front portion of the drum with respect to a rotational shaft is contrary to displacement at a rear portion of the drum.
  • a vibration mode i.e., a diagonal vibration mode where displacement at a front portion of the drum with respect to a rotational shaft is contrary to displacement at a rear portion of the drum.
  • FIG. 1 is a diagram illustrating a laundry machine according to one embodiment of the present invention
  • FIG. 2 is a partial sectional view illustrating a laundry machine of FIG. 1;
  • FIG. 3 is a sectional view illustrating a front balancer
  • FIG. 4 is a diagram illustrating the relation between mass and natural vibration
  • FIG. 5 is a diagram illustrating the position relation between balls and unbalance based on rotation of a drum
  • FIG. 6 is a diagram illustrating a spinning method according to one embodiment of the present invention.
  • Fig. 7 is a graph showing a relation of mass vs. a natural frequency. ;
  • Fig. 8 is a graph illustrating vibration characteristics of the laundry machine of FIG. 2.
  • FIG. 1 is a partial exploded perspective view illustrating a laundry machine according to one embodiment of the present invention.
  • the tub may be fixedly supported to the cabinet or it may be supplied to the cabinet by a flexible supporting structure such as a suspension unit which will be described later. Also, the supporting of the tub may be between the supporting of the suspension unit and the completely fixed supporting.
  • the tub may be flexibly supported by the suspension unit which will be described later or it may be complete-fixedly supported to be movable more rigidly.
  • the cabinet may not be provided unlike embodiments which will be described later.
  • a predetermined space in which the built-in type laundry machine will be installed may be formed by a wall structure and the like, instead of the cabinet.
  • the built-in type laundry machine may not include a cabinet configured to define an exterior appearance thereof independently.
  • the laundry machine includes a tub fixedly supported to a cabinet.
  • the tub includes a tub front 100 configured to define a front part thereof and a tub rear 120 configured to define a rear part thereof.
  • the tub front 100 and the tub rear 120 are assembled to each other by screws and a predetermined space is formed in the assembled structure to accommodate a drum.
  • the tub rear 120 may include an opening formed in a rear surface thereof and an inner circumference of the rear surface of the tub rear 120 is connected with an outer circumference of a rear gasket 250.
  • An inner circumference of the rear gasket 250 is connected with a tub back 130.
  • the tub back 130 includes a through-hole formed in a center thereof and a shaft passes the through-hole.
  • the rear gasket 250 may be made of flexible material not to transmit the vibration of the tub back 130 to the tub rear 120.
  • the tub rear 120 includes a rear surface 128.
  • the rear surface 128 of the tub rear 120, the tub back 130 and the rear gasket 250 define a rear wall of the tub.
  • the rear gasket 250 is sealingly connected with the tub back 130 and the tub rear 120 and it prevents wash water held in the tub from leaking out.
  • the tub back 130 is vibrated together with the drum during the rotation of the drum. At this time, the tub back 130 is spaced apart from the tub rear 120 at a predetermined distance enough not to interfere with the tub rear 120. Since the rear gasket 250 is made of a flexible material, it allows the tub back 130 to relative-move without interfering with the tub rear 120.
  • the rear gasket 250 may include a corrugation part 252 extendible enough to allow such a relative movement of the tub back 130.
  • a foreign-substance-preventing member 200 is connected with a front portion of the tub front 100 to prevent foreign substances from coming between the tub and the drum.
  • the foreign-substance-preventing member 200 is made of a flexible material and it is fixedly installed to the tub front 100.
  • the foreign-substance-preventing member 200 may be made of the same material as that used to make the rear gasket 250 and it will be referenced to as front gasket for convenience sake.
  • the drum includes a drum front 300, a drum center 320 and a drum back 340.
  • Balancers 310 and 330 are installed in front and rear portions of the drum, respectively.
  • the drum back 340 is connected with a spider 350, and the spider 350 is connected with a rotational shaft 351.
  • the drum 32 is rotated in the tub by the rotational force transmitted via the rotational shaft 351.
  • the rotational shaft 351 is directly connected with a motor by passing through the tub back 130. Specifically, the rotational shaft 351 is directly connected with a rotor of the motor.
  • a bearing housing 400 is coupled to a rear surface of the tub back 130. The bearing housing 400 is located between the motor and the tub back 130 to rotatably support the rotational shaft 351.
  • a stator is fixedly installed to the bearing housing 400 and the rotor is located around the stator. As mentioned above, the rotor is directly connected with the rotational shaft 351.
  • the motor is an outer rotor type motor and it is directly connected with the rotational shaft 351.
  • the bearing housing 400 is supported from a cabinet base 600 through a suspension unit.
  • the suspension unit includes three perpendicular supporting suspensions and two oblique-supporting suspensions configured to support the bearing housing obliquely in a forward and rearward direction.
  • the suspension unit may include a first cylinder spring 520, a second cylinder spring 510, a third cylinder spring 500, a first cylinder damper, and a second cylinder damper 530, wherein the first cylinder damper, although not shown, is symmetrically installed to be opposite to the second cylinder damper.
  • the first cylinder spring 520 is connected between a first suspension bracket 450 and the cabinet base 600
  • the second cylinder spring 510 is connected between a second suspension bracket 440 and the cabinet base 600.
  • the third cylinder spring 500 is directly connected between the bearing housing 400 and the cabinet base 600.
  • the first cylinder damper 540 is obliquely installed between the first suspension bracket 450 and a rear portion of the cabinet base.
  • the second cylinder damper 530 is obliquely installed between the second suspension bracket 440 and the rear portion of the cabinet base.
  • the cylinder springs 520, 510 and 500 of the suspension unit may be connected to the cabinet base 600 flexibly enough to allow the drum to move in a forward-and-rearward direction and a rightward-and-leftward direction, not completely fixed to the cabinet base 600. That is, the cylinder springs 520, 510 and 500 elastically support the drum to allow the drum to rotate vertically and horizontally with respect to the connected point with the cabinet base.
  • the perpendicular ones of the suspensions suspend the vibration of the drum elastically and the oblique ones dampen the vibration. That is, out of the vibration system that includes springs and damping means, the perpendicularly installed ones are employed as springs and the obliquely installed ones are employed as damping means.
  • the tub front and the tub rear are fixedly secured to the cabinet and the vibration of the drum is suspendingly supported by the suspension unit. Substantially, the structure of the tub and the drum may be separate. Even when the drum is vibrated, the tub may not be vibrated structurally.
  • the bearing housing and the suspension brackets are connected by first and second weights 431 and 430.
  • unbalance may be generated by the laundry. Since such unbalance may cause high vibration of the drum during a spinning cycle, it is preferably required to reduce such unbalance (UB). In particular, as the rotation speed of the drum is increased, it reaches a natural vibration region of the laundry machine. In this case, a problem may occur in that the vibration becomes great if unbalance is too great.
  • An allowable unbalance rate may be required for the laundry machine considering characteristics of the laundry machine. In this respect, it is required to sense unbalance and compare the sensed unbalance with allowable unbalance to control rotation of the drum.
  • One of the several solutions is laundry distribution or uniform laundry distribution for varying the position of the laundry inside the drum.
  • a fluid may be located in an opposite position of an unbalanced position of the laundry to compensate for unbalance of the laundry.
  • a balancer may be used.
  • a ball balancer is used as the balancer.
  • the balancer is respectively used at the front and rear portions of the drum.
  • the front balancer 310 is provided at the front portion of the drum, and the rear balancer 330 is provided at the rear portion of the drum.
  • the front balancer 310 is mounted on a front surface of the drum front 300
  • the rear balancer 330 is mounted on a rear surface of the drum back 340.
  • the drum front 300 may have a front recess recessed in a rearward direction on the front surface
  • the drum back 340 may have a rear recess recessed in a forward direction.
  • the front balancer 310 is structurally the same as the rear balancer 330.
  • FIG. 3 illustrates a sectional structure of the front balancer 310.
  • the front balancer 310 includes a race 31, a ball 32, and an oil 33.
  • the race 31 may have a ring shaped ball space portion 31a where the ball 32 can move therein.
  • the ball space portion 31a may have a square shape roughly as shown.
  • a plurality of balls 32 are received in the ball space portion 31a.
  • the number of balls received in the ball space portion 31a and a diameter of the ball are defined considering the unbalance rate, together with vibration characteristics of the laundry machine.
  • the number and diameter of balls received in the ball space portion 31a are preferably defined considering the amount and viscosity of the oil 33, which affect movement of the ball 32.
  • the amount and viscosity of the oil 33 may be determined such that the ball 32 of the balancer may have required movement. Also, the amount and viscosity of the oil 33 may be determined considering vibration characteristics of the laundry machine.
  • each of the balls has a diameter of 18.55mm to 19.55mm, preferably 19.05mm.
  • the ball space portion 31a of the race has a sectional area in the range of 410mm 2 to 413mm 2 , preferably 412mm 2 .
  • a center diameter of the sectional area of the ball space portion 31a is in the range of 500mm to 510mm, preferably 505mm.
  • Silicon based oil such as Poly Dimethylsiloxane (PDMS) is used as the oil 33.
  • the oil 33 has viscosity of 300cs at a room temperature, and has a filling level of 340cc to 360cc, preferably 350cc. It is to be understood that the present invention is not limited to the aforementioned characteristic values of the balancer.
  • a natural vibration mode occurs in the range of 200rpm to 270rpm. Such a period where the natural vibration mode occurs may be referred to as a transient region. In this transient region, a plurality of natural vibration modes may exist. If the drum should be rotated at a rotation speed more than the transient region, it is important to control the ball such that the vibration of the drum becomes low.
  • Fig. 7 illustrates a graph showing a relation of mass vs. a natural frequency. It is assumed that, in vibration systems of two laundry machines, the two laundry machines have mass of m0 and m1 respectively and maximum holding laundry amounts are ⁇ m, respectively. Then, the transition regions of the two laundry machines can be determined taking ⁇ nf0 and ⁇ nf1 into account, respectively. In this instance, amounts of water contained in the laundry will not be taken into account, for the time being.
  • the laundry machine with smaller mass m1 has a range of the transition region greater than the laundry machine with greater mass m0. That is, the range of the transition region having variation of the laundry amount taken into account becomes the greater as the mass of the vibration system becomes the smaller.
  • the related art laundry machine has a structure in which vibration is transmitted from the drum to the tub as it is, causing the tub to vibrate. Therefore, in taking the vibration of the related art laundry machine into account, the tub is indispensible.
  • the tub has, not only a weight of its own, but also substantial weights at a front, a rear or a circumferential surface thereof for balancing. Accordingly, the related art laundry machine has great mass of the vibration system.
  • the tub since the tub, not only has no weight, but also is separated from the drum in view of a supporting structure, the tub may not be put into account in consideration of the vibration of the drum. Therefore, the laundry machine of the embodiment may have relatively small mass of the vibration system.
  • the related art laundry machine has mass m0 and the laundry machine of the embodiment has mass m1, leading the laundry machine of the embodiment to have a greater transition region, at the end.
  • a start RPM of the transient region of the laundry machine according to this embodiment may be similar to a start RPM of the transient region of the conventional laundry machine.
  • An end RPM of the transient region of the laundry machine according to this embodiment may increase more than a RPM calculated by adding a value of approximately 30% of the start RPM to the start RPM.
  • the transient region finishes at an RPM calculated by adding a value of approximately 80% of the start RPM to the start RPM.
  • the transient region may include a RPM band of approximately 200 to 350 rpm.
  • a balancer In a case, a balancer is used, a method may be put into account, in which the rotation speed of the drum passes through the transition region while movable bodies provided in the balancer are positioned on an opposite side of an unbalance of the laundry. In this instance, it is preferable that the movable bodies are positioned at exact opposite of the unbalance in middle of the transition region.
  • the transient region of the laundry machine according to this embodiment is relatively wide in comparison to that of the conventional laundry machine. Because of that, even if the laundry even-spreading step or ball balancing is implemented in a RPM band lower than the transient region, the laundry might be in disorder or balancing might be failed with the drum speed passing the transient region.
  • balancing may be implemented at least one time in the laundry machine according to this embodiment before and while the drum speed passing the transient region.
  • the balancing may be defined as rotation of the drum at a constant-speed for a predetermined time period.
  • Such the balancing allows the movable body of the balancer to the opposite positions of the laundry, only to reduce the unbalance amount. By extension, the effect of the laundry even-spreading.
  • the balancing is implemented while the drum speed passing the transient region and the noise and vibration generated by the expansion of the transient region may be prevented.
  • the balancing when the balancing is implemented before the drum speed passing the transient region, the balancing may be implemented in a different RPM band from the RPM of the conventional laundry machine. For example, if the transient region starts at 200 RPM, the balancing is implemented in the RPM band lower than approximately 150 RPM. Since the conventional laundry machine has a relatively less wide transient region, it is not so difficult for the drum speed to pass the transient region even with the balancing implemented at the RPM lower than approximately 150 RPM. However, the laundry machine according to this embodiment has the relatively wide expanded transient region as described above.
  • the laundry machine may increase the balancing RPM in comparison to the conventional balancing RPM, when the balancing is implemented before the drum speed enters the transient region. That is, if the start RPM of the transient region is determined, the balancing is implemented in a RPM band higher than a RPM calculated by subtracting a value of approximately 25% of the start RPM from the start RPM. For example, the start RPM of the transient region is approximately 200 RPM, the balancing may be implemented in a RPM band higher than 150RPm lower than 200 RPM.
  • the unbalance amount may be measured during the balancing. That is, the control method may further include a step to measure the unbalance amount during the balancing and to compare the measured unbalance amount with an allowable unbalance amount allowing the acceleration of the drum speed. If the measured unbalance amount is less than the allowable unbalance amount, the drum speed is accelerated after the balancing to be out of the transient region. In contrast, if the measured unbalance amount is the allowable unbalance amount or more, the laundry even-spreading step may be re-implemented. in this case, the allowable unbalance amount may be different from an allowable unbalance amount allowing the initial accelerating.
  • the transient region may be defined as a rotation speed range of the drum.
  • the transient region may be defined as a region that includes natural vibration.
  • natural vibration is determined by mass and rigidity (for example, spring constant). Since mass may be varied depending on the amount of laundry in the laundry machine, the transient region is preferably controlled considering mass.
  • the unbalance rate may be reduced.
  • uniform laundry distribution for uniformly distributing the laundry inside the drum is carried out before the rotation speed of the drum enters the transient region.
  • the rotation speed of the drum may quickly pass through the transient region while the balls are being located at an opposite position of the unbalanced position of the laundry.
  • the balls are preferably located at the opposite position of the unbalanced position.
  • the relation between the position of the balls and the unbalanced position can be defined by an angle (hereinafter, referred to as‘nearest ball angle’) of the ball located nearest to unbalance with respect to the centrifugal force center of the unbalance.
  • FIG. 4 illustrates the position relation between unbalance (UB) and the balls.
  • the position relation between the balls and unbalance illustrate that the nearest ball angle is ⁇ 1 and a centrifugal force center angle is ⁇ 2.
  • the angle between the ball and unbalance will mean ⁇ 1 or ⁇ 2.
  • a steel ball can be used as the ball. If the sizes of the balls are uniformly provided and the balls are arranged in parallel to adjoin one another, the centrifugal force center is P1 as shown in FIG. 4.
  • the ball is rotated by a friction force generated when the drum is rotated.
  • the ball is not kept in the drum and it is rotated at a different speed from that of the drum.
  • unbalance means the laundry being in close contact with an inner wall of the drum and it can be rotated at almost the same speed as that of the drum because of an enough friction force and the lift of the inner wall.
  • the rotation speed of the unbalance is different from that of the ball. Since the balls are rotated by rotation of the drum, the rotation speed of the unbalance is faster than that of the balls. Precisely, an angular velocity of the unbalance is faster than that of the balls.
  • the balls will be in close contact with an outer circumferential surface of the ball space portion of the racer because of a centrifugal force. If the friction force between the circumferential surface and the balls is a predetermined value or more, the balls will be rotated with the same rotation speed as that of the drum. In this case, the balls are located at a predetermined position with respect to the drum in the same manner as the unbalance. In this specification, the case of the ball being rotated at the predetermined position with respect to the drum will be referenced to as‘balancing position’or‘balancing’for convenience’sake.
  • the minimum rotation speed may be varied depending on the balancer. Also, the minimum rotation speed may be varied depending on whether the balancer is installed perpendicularly or horizontally. If the balancer is installed perpendicularly, the positions of the balls being in contact with the outer circumferential surface of the ball space portion of the race may be varied by gravity. The balls maintained at constant speed rotation of the ball balanced rotation speed may be located at the opposite position of the unbalanced position. Referring to FIG. 4, the balls may be located at P2.
  • balancing may not be carried out at a rotation speed lower than the transient region due to a low centrifugal force. Accordingly, when the rotation speed of the drum passes through the transient region, instead of carrying out balancing, the position of the balls is checked while the drum is being rotated at a constant speed, whereby the balls can be located at the opposite position of the unbalanced position when the rotation speed of the drum passes through the transient region. In other words, even though balancing is not carried out, it can be controlled such that the rotation speed of the drum passes through the transient region while the balls are being located at the opposite position of the unbalanced position. For example, referring to FIG.
  • the rotation speed of the drum passes through the transient region when the angle ⁇ 1 or ⁇ 2 between the ball and unbalance is more than 90 ⁇ . At this time, in the middle of the transient region, it may be preferable that the angle is 180 ⁇ .
  • FIG. 5 is a diagram illustrating the position relation between the front balls 32f and the rear balls 32e when viewed through the drum in a forward direction.
  • a vibration mode where front displacement of the vibration of the drum is different from rear displacement thereof may occur.
  • a vibration mode where front displacement of the vibration of the drum is opposite to rear displacement thereof may occur.
  • this vibration mode will be referred to as a diagonal vibration mode.
  • the transient region of the laundry machine of this embodiment may expand compared to the conventional laundry machine. Therefore, the vibration mode of the drum may be changed due to the expanded transient region, for example, the diagonal vibration mode can be generated. In this diagonal vibration mode, if the rear balls 32f and the rear balls 32e are maintained at an angle within the range of 90 ⁇ as described above, unbalance to the diagonal vibration mode may not be compensated normally, whereby the vibration of the drum may become severe.
  • the aforementioned diagonal vibration mode may start to occur as the vibration of the drum becomes close to natural vibration of the natural vibration mode corresponding to the diagonal vibration mode.
  • the positions of the front balls 32f and the rear balls 32e should be corrected before the vibration of the drum reaches the natural vibration of the diagonal vibration mode.
  • the drum is preferably subjected to constant speed rotation for a predetermined time at a rotation speed where the diagonal vibration mode occurs, whereby the positions of the front balls 32f and the rear balls 32e are corrected to compensate for unbalance.
  • the aforementioned laundry machine of this embodiment has a different structure from that of the related art. Since the natural vibration mode corresponding to the diagonal vibration mode may occur at the transient region, it is preferably required to correct the positions of the balls as described above.
  • period ‘a’ denotes a first constant speed rotation step
  • period ‘b’ a second constant speed rotation step
  • period‘c1’ a first transient region step
  • period‘c2’ third constant speed rotation step
  • period‘c3’ a second transient region step
  • period‘d’fourth constant speed rotation step a control method for passing through the transient region to carry out a spinning cycle in the aforementioned laundry machine
  • the drum is accelerated to reach a second rotation speed and then rotated at a constant speed (period‘b’).
  • a second unbalance value is sensed and then the sensed second unbalance value is compared with a second allowable unbalance value. If the sensed second unbalance value is less than the second allowable unbalance value, the drum is subjected to warming-up for passing through the transient region period‘c’.
  • the drum is rotated at a constant speed at the period‘b’to check the position of the ball, whereby an acceleration timing t1 is determined.
  • t1 and its acceleration inclination are determined such that the angle between the unbalance and the ball is in the range of 90 ⁇ or more.
  • t1 and its acceleration inclination can be determined such that the angle between the unbalance and the ball is in the range of 180 ⁇ .
  • the centrifugal force center of the front balls 32f and the centrifugal force center of the rear balls 32e can define an angle within the range of 90 ⁇ based on the rotation center of the drum when viewed in a forward direction.
  • the front balls 32f and the rear balls 32e are located within the range of 90 ⁇ to reduce the vibration of the vibration mode where displacement at the front portion of the drum and displacement at the rear portion of the drum are equal to each other in a perpendicular direction with respect to the rotational shaft.
  • the drum is rotated at a constant speed for a predetermined time (period‘c2’).
  • the period‘c2’ may be regarded as a warming-up period for passing through the natural vibration mode corresponding to diagonal vibration that may occur at the period‘c3’.
  • the drum may be vibrated in the diagonal vibration mode as it is rotated at a rotation speed near the natural vibration of the natural vibration mode corresponding to the diagonal vibration.
  • the position of the balls of the front balancer and the rear balancer is varied depending on the corresponding vibration mode.
  • the rotation speed of the drum After passing through the period‘c2’, the rotation speed of the drum passes through the transient region at the period‘c3’in a state that the angle between the front balls 32f and the front unbalance and the angle between the rear balls 32e and the rear unbalance are 90 ⁇ or more, respectively.
  • the angle between the front balls 32f and the rear balls 32e may be 90 ⁇ or more.
  • it is preferable that the angle between the front balls 32f and the rear balls 32e is 90 ⁇ or more.
  • the third rotation speed and the predetermined time can be determined considering that the front balancer and the rear balancer are subjected to balancing.
  • the third rotation speed and the predetermined time can be determined in such a manner that the front balls 32f and the rear balls 32e are moved to a position for compensating front unbalance and a position for compensating rear unbalance, respectively, at angles of 180 ⁇ , respectively, and then are maintained at their positions, respectively.
  • the third rotation speed is preferably set in the range of 250rpm to 290rpm. If the rotation speed of the drum is too low, a vibration level of the diagonal vibration mode becomes weak, whereby the period‘c2’becomes longer or balancing may not be carried out preferably. Also, if the rotation speed of the drum is too high, severe vibration occurs and movement of the balls becomes unstable, whereby the positions of the balls may not be varied normally.
  • the third rotation speed of the drum is set in the range of 270rpm.
  • the period‘c2’ is preferably maintained for 30seconds, approximately.
  • the rotations speed of the drum strays from the transient region while it is passing through the period‘c3’where the natural vibration mode corresponding to diagonal vibration occurs. Afterwards, the rotation speed of the drum enters the period for rotating the drum at high speed to carry out the spinning cycle. At this time, it is necessary to vary the positions of the balls before the rotation speed of the drum enters the main spinning step.
  • the front balls and the rear balls are located to be suitable for compensating the unbalance to diagonal vibration, they may not be suitable for the main spinning step having a vibration mode different from the diagonal vibration mode.
  • the period‘d’for realigning the positions of the balls while the rotation speed of the drum is maintained at a constant speed rotation of a fourth rotation speed after passing through the transient region will be required.
  • balancing is preferably carried out at the period‘d’.
  • the rotation speed of the drum is preferably maintained at the fourth rotation speed suitable for the corresponding vibration mode such that the balls are located to compensate for unbalance.
  • the fourth rotation speed is preferably determined at a rotation speed that does not allow the diagonal vibration mode if possible.
  • the fourth rotation speed is preferably determined at a rotation speed different from the natural vibration of the diagonal vibration mode as much as a predetermined rate, whereby the fourth rotation speed is not affected by the diagonal vibration mode.
  • the rotation speed of the drum can maintained in the range of 370rpm to 390rpm for 50seconds to 70seconds, preferably 60seconds.
  • the acceleration inclination at the period‘c1’ is smaller than that at the period‘c3’. If the balancing is carried out at the third rotation speed, since the balls may little be moved, the rotation speed of the drum can quickly pass through the period ‘c3’. However, the balls continue to move without being balanced at the period‘c1’and considering such a movement of the balls, the rotation speed for passing through the period‘c1’is determined.
  • the main spinning step is carried out at 1000rpm or more to spin the laundry.
  • this embodiment may be applied to any other case where the drum is rotated at a speed more than the transient region.
  • transient vibration region a region where irregular transient vibration with high amplitude occurs.
  • the transient vibration region irregularly occurs with high amplitude before vibration is transited to a steady-state vibration region (hereinafter, referred to as“steady-state region”), and has vibration characteristics determined if a vibration system (laundry machine) is designed.
  • the transient vibration region is different according to the type of the laundry machine, transient vibration occurs approximately in the range of 200rpm to 270rpm. It is regarded that transient vibration is caused by resonance. Accordingly, it is necessary to design the balancer by considering effective balancing at the transient vibration region.
  • the vibration source i.e., the motor and the drum connected with the motor are connected with the tub 12 through the rear gasket 250. Accordingly, vibration occurring in the drum is little forwarded to the tub, and the drum is supported by a damping means and the suspension unit 180 via a bearing housing 400. As a result, the tub 12 can directly be fixed to a cabinet 110 without any damping means.
  • vibration As a result of studies of the inventor of the present invention, vibration characteristics not observed generally have been found in the laundry machine according to the present invention.
  • vibration dislacement
  • a region hereinafter, referred to as“irregular vibration”
  • irregular vibration is generated.
  • an average drum displacement in the transient region +20% to -20% of the average drum displacement in the transient region or 1/3 or more of the maximum drum displacement in the natural frequency of the transient region are generated, it may be determined that the irregular vibration is generated.
  • irregular vibration has occurred in a RPM band higher than the transient region, for example has occurred at a region (hereinafter, referred to as“irregular vibration region”) in the range of 350 rpm to 1000rpm, approximately. Irregular vibration may be generated due to use of the balancer, the damping system, and the rear gasket. Accordingly, in this laundry machine, it is necessary to design the balancer by considering the irregular vibration region as well as the transient vibration region.
  • the balancer is provide with a ball balancer
  • the structure of the balancer i.e., the size of the ball, the number of balls, a shape of the race, viscosity of oil, and a filling level of oil are selected by considering the irregular vibration region as well as the transient vibration region.
  • the ball balancer has a greater diameter of 255.8mm and a smaller diameter of 249.2.
  • a space of the race, in which the ball is contained, has a sectional area of 411.93mm 2 .
  • the number of balls is 14 at the front and the rear, respectively, and the ball has a size of 19.05mm.
  • Silicon based oil such as Poly Dimethylsiloxane (PDMS) is used as the oil.
  • PDMS Poly Dimethylsiloxane
  • oil has viscosity of 300CS at a room temperature, and has a filling level of 350cc.
  • the irregular vibration region as well as the transient vibration region is considered.
  • the balancing may be implemented at least one time before, while and after the drum speed passes the irregular vibration region.
  • the rotation speed of the drum is relatively high, the balancing of the balancer may not be implemented properly and the balancing may be implemented with decreasing the rotation speed of the drum.
  • the rotation speed of the drum is decreased to be lower than the transient region to implement the balancing, it has to pass the transient region again. In decreasing the rotation speed of the drum to implement the balancing, the decreased rotation speed may be higher than the transient region.

Landscapes

  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Main Body Construction Of Washing Machines And Laundry Dryers (AREA)
  • Control Of Washing Machine And Dryer (AREA)

Abstract

L'invention concerne un procédé de commande d'un lave-linge équipé d'un tambour, d'un dispositif d'équilibrage avant associé à une partie avant du tambour, et d'un dispositif d'équilibrage arrière associé à une partie arrière du tambour. Le procédé consiste à accélérer le tambour et le faire tourner à une vitesse de rotation constante prédéterminée pendant une période prédéterminée, la vitesse de rotation prédéterminée assurant, au niveau de la partie avant du tambour, un déplacement perpendiculaire différent de celui accompli au niveau de la partie arrière du tambour.
PCT/KR2010/005816 2009-08-27 2010-08-27 Procédé de commande d'un lave-linge WO2011025320A2 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
RU2012111661/12A RU2496934C1 (ru) 2009-08-27 2010-08-27 Способ управления машиной для обработки белья
CN201080042202.2A CN102510915B (zh) 2009-08-27 2010-08-27 洗衣机的控制方法
EP10812333.2A EP2470703B1 (fr) 2009-08-27 2010-08-27 Procédé de commande d'un lave-linge
US13/392,682 US20120151693A1 (en) 2009-08-27 2010-08-27 Control method of laundry machine
AU2010287084A AU2010287084B2 (en) 2009-08-27 2010-08-27 Control method of laundry machine

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
KR1020090079912A KR101741549B1 (ko) 2009-08-27 2009-08-27 세탁장치 및 그 제어방법
KR10-2009-0079912 2009-08-27
KR10-2009-0079922 2009-08-27
KR10-2009-0079923 2009-08-27
KR1020090079923A KR20110022367A (ko) 2009-08-27 2009-08-27 세탁장치
KR1020090079922A KR101721871B1 (ko) 2009-08-27 2009-08-27 세탁장치

Publications (2)

Publication Number Publication Date
WO2011025320A2 true WO2011025320A2 (fr) 2011-03-03
WO2011025320A3 WO2011025320A3 (fr) 2011-04-21

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PCT/KR2010/005816 WO2011025320A2 (fr) 2009-08-27 2010-08-27 Procédé de commande d'un lave-linge

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US (1) US20120151693A1 (fr)
EP (1) EP2470703B1 (fr)
CN (1) CN102510915B (fr)
AU (1) AU2010287084B2 (fr)
RU (1) RU2496934C1 (fr)
WO (1) WO2011025320A2 (fr)

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Also Published As

Publication number Publication date
EP2470703A2 (fr) 2012-07-04
WO2011025320A3 (fr) 2011-04-21
EP2470703A4 (fr) 2015-02-18
US20120151693A1 (en) 2012-06-21
CN102510915A (zh) 2012-06-20
RU2496934C1 (ru) 2013-10-27
EP2470703B1 (fr) 2017-07-05
AU2010287084B2 (en) 2013-08-22
AU2010287084A1 (en) 2012-03-22
CN102510915B (zh) 2014-12-17

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