WO2022121292A1 - 洗衣机 - Google Patents

洗衣机 Download PDF

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Publication number
WO2022121292A1
WO2022121292A1 PCT/CN2021/103924 CN2021103924W WO2022121292A1 WO 2022121292 A1 WO2022121292 A1 WO 2022121292A1 CN 2021103924 W CN2021103924 W CN 2021103924W WO 2022121292 A1 WO2022121292 A1 WO 2022121292A1
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WIPO (PCT)
Prior art keywords
elastic body
free piston
elastic
tub
piston
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PCT/CN2021/103924
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English (en)
French (fr)
Inventor
川口智也
永井孝之
Original Assignee
青岛海尔洗衣机有限公司
Aqua株式会社
海尔智家股份有限公司
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Application filed by 青岛海尔洗衣机有限公司, Aqua株式会社, 海尔智家股份有限公司 filed Critical 青岛海尔洗衣机有限公司
Publication of WO2022121292A1 publication Critical patent/WO2022121292A1/zh

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    • D—TEXTILES; PAPER
    • D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F37/00—Details specific to washing machines covered by groups D06F21/00 - D06F25/00
    • D06F37/20—Mountings, e.g. resilient mountings, for the rotary receptacle, motor, tub or casing; Preventing or damping vibrations
    • D06F37/24—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 vertical axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means

Definitions

  • the present invention relates to washing machines.
  • a washing machine generally has a structure in which a tub unit is accommodated in a case, and the tub unit is configured by arranging an inner tub or the like as a washing and dewatering tub inside an outer tub for storing wash water.
  • Patent Document 1 proposes a structure of an anti-vibration damper provided between a case and an outer tub in a drum washing machine.
  • the anti-vibration damper proposed here includes a damping cylinder, a piston rod provided inside the damping cylinder, and a set of pistons (a first piston and a pair of second pistons) that slide inside the damping cylinder to generate a damping force ).
  • the first piston is not fixed to the piston rod and can freely move along the piston rod.
  • the pair of second pistons are provided on both sides of the first piston, and the movement of the first piston is restricted to a predetermined range by being fixed to the piston rod.
  • the first piston When the vibration amplitude of the outer tub is relatively small and the first piston vibrates within the range limited by the pair of second pistons, the first piston does not slide relative to the damping cylinder but moves integrally with the damping cylinder, so no large buffering power. In addition, in this case, since the first piston does not collide with the pair of second pistons, the vibration of the tub is not transmitted to the case via the piston rod.
  • the vibration amplitude of the outer tub is relatively large and the first piston vibrates beyond the range limited by the pair of second pistons, the first piston collides with the second piston and slides relative to the damping cylinder during the vibration. Generates greater buffering force.
  • the vibration of the tub is transmitted to the case (and thus to the floor on which the case is provided) via the piston rod.
  • the tub is supported in the case in a state of being suspended by a plurality of hangers whose one end is fixed to the case.
  • a suspension in which a coil spring is arranged in a damper cylinder is provided at the front end of each hanger rod, and the outer tub is elastically supported by the coil spring (refer to Patent Document 1).
  • the suspension functions to attenuate the vibration of the tub by transmitting and releasing the vibration of the tub so that the vibration amplitude of the tub is not excessively large.
  • the suspension it is preferable for the suspension to perform the damping function only when the necessity of damping is high, that is, when the vibration amplitude of the outer tub is large, and when the vibration amplitude of the outer tub is relatively small, the vibration of the outer tub is not transmitted. to the box.
  • the tub is directly placed on the plurality of suspensions, and its own load is given to the suspensions. Therefore, when the pistons collide with each other in the suspension, the shock is directly transmitted to the outer tub. As a result, the outer barrel will resonate due to shocks from the suspension, resulting in a rattling sound. Needless to say, the size of the rattle generated by the resonance of the outer barrel is much larger than the sound of the pistons colliding with each other.
  • Patent Document 1 Japanese Patent No. 2868688
  • Patent Document 2 Japanese Patent Laid-Open No. 2017-113310
  • the present invention has been made in view of the above circumstances, and an object of the present invention is to provide a method that does not transmit the vibration to the casing when the vibration amplitude of the outer tub is relatively small, and attenuates the vibration when the vibration amplitude of the outer tub is relatively large. And the technology that can fully suppress the abnormal sound caused by the resonance of the outer barrel.
  • the present invention adopts the following scheme.
  • the present invention is a washing machine comprising: a case; and an outer tub, which is mounted on a plurality of suspensions connected to the case via a hanger bar, and is suspended and supported in the case, characterized in that:
  • the suspension includes: a damping cylinder into which a rod connected to the hanger rod is inserted; a support elastic body disposed in the damping cylinder for elastically supporting the outer tub; and a free piston for opposing the rod
  • a pair of fixed pistons are provided with a separation distance covering the movable clearance of the free piston, and are fixedly assembled to the rod; the upper side an elastic body arranged between the free piston and the fixed piston arranged on the upper side of the free piston; and a lower elastic body arranged between the free piston and the fixed piston arranged on the lower side of the free piston
  • the elastic coefficient of the upper elastic body and the elastic coefficient of the lower elastic body are respectively limited so that the deformation threshold value is equal to or greater than an allowable deformation threshold value corresponding to a predetermined noise
  • the elastic coefficient of the upper elastic body is larger than the elastic coefficient of the lower elastic body.
  • the elastic coefficient of the upper elastic body is limited so that the deformation threshold value is 1 mm or more.
  • the elastic coefficient of the lower elastic body is limited so that the deformation threshold value is 3 mm or more.
  • the elastic coefficient of the lower elastic body is defined by a composite elastic coefficient based on the elastic coefficient of the lower elastic body and the elastic coefficient of the support elastic body.
  • the resonant rotational speed of the outer tub is higher than the resonant rotational speed of the outer tub defined based on the elastic coefficient of the support elastic body by a predetermined value or more.
  • the elastic modulus of the lower elastic body is defined by a composite elastic modulus based on the elastic modulus of the lower elastic body and the elastic modulus of the support elastic body.
  • the resonant rotational speed of the outer tub is a value lower than a predetermined value or less than the rotational speed during stable dehydration.
  • the vibration when the vibration amplitude of the tub is relatively small, the vibration can be prevented from being transmitted to the case, and when the vibration amplitude of the tub is relatively large, the vibration can be attenuated.
  • the vibration amplitude of the outer tub when the vibration amplitude of the outer tub is relatively small and the free piston vibrates along the rod so as not to contact the fixed piston, the free piston does not slide relative to the damping cylinder but vibrates integrally therewith, so the free piston does not function. attenuation force. In this case, the vibration of the tub is not transmitted to the rod (or even the case).
  • the vibration amplitude of the outer barrel is relatively large and the free piston collides with the fixed piston via the elastic body during the vibration process, since the free piston slides relative to the damping cylinder after the collision, the damping force of the free piston is exerted, and the external The vibration of the barrel is damped.
  • the shock is transmitted to the outer barrel and generates abnormal sound due to resonance
  • the magnitude of the damping force generated by the sliding of the free piston relative to the damping cylinder and the value (deformation threshold) obtained by dividing the damping force of the elastic body by the elastic coefficient of the elastic body. Tendency to decrease in size.
  • the elastic coefficient of each elastic body is limited so that the deformation threshold value is equal to or higher than the allowable deformation threshold value corresponding to the predetermined noise threshold value, the magnitude of the abnormal noise is suppressed to be equal to or less than the predetermined noise threshold value. That is, the abnormal sound generated by the resonance of the outer tub is sufficiently suppressed, and the user of the washing machine is less likely to perceive the abnormal sound as noise.
  • the elastic coefficient of the upper elastic body is set to be larger than the elastic coefficient of the lower elastic body, it is possible to sufficiently suppress the abnormal sound caused by the resonance of the outer tub while ensuring a sufficient damping force.
  • the lower elastic body functions to attenuate the impact (downward impact) caused by the collision between the free piston and the lower fixed piston via the lower elastic body
  • the upper elastic body functions to attenuate the impact caused by the free piston passing through the upper elastic body
  • the downward shock received when the outer tub is close to the suspension is compared with the upward shock received when the outer tub is far away from the suspension, the downward shock is more easily transmitted to the outer tub, and the lower elastic body acts to weaken the downward shock
  • the coefficient of elasticity of the upper side elastic body is set to be smaller than the elastic coefficient of the upper side elastic body to reduce the effect of the upward impact, and the downward impact which is relatively easily transmitted to the outer tub can be sufficiently reduced. Thereby, the abnormal sound caused by the resonance of the outer barrel can be effectively suppressed.
  • the elastic coefficient of the upper elastic body to be larger than the elastic coefficient of the lower elastic body, the timing of exerting the damping force of the free piston is not too late, and sufficient damping force is ensured.
  • the elastic coefficient of the upper elastic body is limited so that the deformation threshold of the upper elastic body is 1 mm or more, it is possible to suppress the magnitude of the abnormal sound produced by a general-purpose outer tub to a sufficiently small value.
  • the elastic coefficient of the lower elastic body is limited so that the deformation threshold of the lower elastic body is 3 mm or more, it is possible to suppress the magnitude of the abnormal sound generated by a general-purpose outer tub to a sufficiently small value.
  • the elastic coefficient of the side elastic body is defined so that the resonance rotation speed (specific resonance rotation speed) of the outer tub, which is defined based on the combined elastic coefficient of the elastic coefficient of the lower elastic body and the elastic coefficient of the support elastic body, is higher than that based on Since the resonance rotation speed (basic resonance rotation speed) of the tub, which is limited by the elastic coefficient of the elastic body, is higher than a predetermined value, the resonance state of the tub can be quickly converged.
  • the resonance rotational speed of the tub intermittently changes to the specific resonance.
  • Rotating speed when the elastic modulus of the lower elastic body is limited to a value higher than the basic resonance rotation speed by a predetermined value or more, the specific resonance rotation speed is limited to a predetermined value or more. That is, when the damping force of the free piston acts to damp the barrel in the resonant state, the resonant rotational speed of the outer barrel temporarily changes greatly by a variation width greater than or equal to a predetermined value. Thereby, the resonance state of the outer tub quickly converges.
  • the elastic coefficient of the lower elastic body is limited so that the resonance rotation speed (specific resonance rotation speed) of the outer tub, which is defined based on the combined elastic coefficient of the elastic coefficient of the lower elastic body and the elastic coefficient of the supporting elastic body, is relatively stable.
  • the rotation speed during dehydration (stable dehydration rotation speed) is lower than a predetermined value, so that the occurrence of abnormal vibration due to resonance of the tub during stable dehydration is avoided.
  • the specific resonance rotation speed becomes a value close to the stable dehydration rotation speed
  • the resonance rotation speed of the outer tub changes to the specific resonance rotation speed due to some unexpected factors during the stable dehydration, it may cause resonance and become Abnormal vibration.
  • the elastic modulus of the lower elastic body is limited to a value lower than the stable dehydration rotation speed by a predetermined value or less, even if the resonance rotation speed of the outer tub changes to the specific resonance rotation speed during stable dehydration, the specific resonance rotation speed is Since the resonance rotation speed and the stable dehydration rotation speed differ by a predetermined value or more, it is difficult to generate such abnormal vibration.
  • the elastic coefficient of the elastic body is maintained during the period from when the free piston comes into contact with the fixed piston via the elastic body until it starts to slide with respect to the damping cylinder. Since the damping force is constant, the timing at which the damping force is exerted is constant, and the damping force can be stably exerted.
  • FIG. 1 is a vertical cross-sectional view showing a schematic configuration of a washing machine 100 according to the embodiment.
  • FIG. 2 is a vertical cross-sectional view showing the structure of the suspension 32 .
  • FIG. 3 is a diagram for explaining the operation of the suspension 32 when the vibration amplitude of the tub 21 is smaller than the amplitude threshold value.
  • FIG. 4 is a diagram for explaining the operation of the suspension 32 when the vibration amplitude of the tub 21 is equal to or larger than the amplitude threshold value.
  • FIG. 5 is a diagram showing a state in which the free piston 325 collides with the lower fixed piston 323b without passing through the lower elastic body 326b in stages.
  • FIG. 6 is a diagram showing a state in which the free piston 325 collides with the upper fixed piston 323a via the upper elastic body 326a in stages.
  • FIG. 7 is a diagram showing the relationship between the deformation thresholds of the elastic bodies 326a and 326b and the magnitude of the generated abnormal sound.
  • FIG. 1 is a vertical cross-sectional view showing a schematic configuration of a washing machine 100 according to the embodiment.
  • the washing machine 100 is configured as a so-called vertical washing machine, and includes a case 1 , a washing tub unit 2 , a hanger unit 3 , and the like.
  • the box 1 is an outer casing for forming an accommodating space inside, and is composed of a substantially rectangular lower plate in plan view, four side plates forming four sides rising from the edge of the lower plate, and a lower plate connected to the upper part of the four side plates. It consists of a substantially rectangular parallelepiped box-shaped member in which the upper plate is integrally formed. Legs 11 are provided in the vicinity of the four corners on the lower surface of the lower plate.
  • an opening 12 is provided in the upper plate, and laundry and the like can be taken in and out of the washing tub unit 2 through the opening 12 .
  • the cover member 13 for opening and closing the opening 12 is provided in the upper part of the upper board.
  • the washing tub unit 2 is accommodated in the casing 1 and includes an outer tub 21 , an inner tub (washing and dewatering tub) 22 arranged in a box shape inside the outer tub 21 , a drive unit 23 provided at the bottom of the outer tub 21 , and the like.
  • the outer tub 21 is a storage tub for storing water (wash water), and is composed of a cylindrical member whose upper surface is open and whose bottom surface is closed.
  • the outer tub 21 is formed of, for example, resin (preferably a synthetic resin excellent in heat resistance).
  • the inner tub 22 is a so-called washing and dewatering tub, and is composed of a cylindrical member whose upper surface is open and whose bottom surface is closed.
  • the inner tub 22 is formed of metal, for example.
  • a pulsator (stirring blade) 221 is provided in the center of the bottom surface of the inner tub 22 .
  • the peripheral wall etc. of the inner tub 22 are perforated with many water passage holes (illustration omitted).
  • the inner tub 22 is set at a position and posture such that its central axis coincides with the central axis of the outer tub 21, and is supported rotatably around the central axis.
  • the water supply pipe is arrange
  • One end of the water supply pipe is connected to external water supply equipment and the like, and a water supply valve is provided in the middle part of the water supply pipe.
  • a drain pipe is connected to the bottom of the outer tub 21 .
  • One end of the drain pipe is connected to an external drain facility or the like, and a drain valve is provided in the middle part of the drain pipe.
  • a drain valve is provided in the middle part of the drain pipe.
  • the drive unit 23 is a mechanism for rotating the inner tub 22 and the like, and includes a motor 231 arranged below the inner tub 22 .
  • the driving force of the motor 231 is transmitted to the pulsator 221 via the first output shaft 232 , and the pulsator 221 is rotated about its central axis by the driving force from the motor 231 . Further, the driving force of the motor 231 is transmitted to the inner tub 22 via the second output shaft 233 , and the inner tub 22 is rotated about the central axis of the inner tub 22 by the driving force from the motor 231 .
  • the motor 231 is provided with a clutch mechanism (not shown), and is set to either a state in which the driving force is transmitted only to the first output shaft 232 and a state in which the driving force is transmitted to both the first output shaft 232 and the second output shaft 233 . switch between.
  • the driving force of the motor 231 is only transmitted to the first output shaft 232, and only the pulsator 221 rotates.
  • the driving force of the motor 231 is transmitted to the output shafts 232 and 233 of both sides, and the inner tub 22 and the pulsator 221 rotate integrally.
  • the hanger unit 3 is a member for supporting the tub 21 (further, the washing tub unit 2 ) by being elastically suspended inside the casing 1 , and is arranged to include four hangers 31 and one provided at the front end of each hanger 31 . Suspension 32 .
  • the hanger bar 31 is a rod-shaped member, and one end thereof is fixed to the casing 1 .
  • hook-shaped locking portions 14 are provided at the four corners in the vicinity of the upper end of the case 1 , and the proximal end side of the hanger bar 31 is attached to each locking portion 14 .
  • the locking portion 14 functions as a fulcrum for suspending the hanger bar 31 by locking the proximal end side of the hanger bar 31 .
  • four engaging portions 211 are provided at equal intervals in the circumferential direction in the vicinity of the rising portion of the outer tub 21 from the bottom surface to the side wall, and the front end side of each hanging rod 31 is inserted into the engaging portion 211 .
  • the suspension 32 provided at the front end thereof is engaged so as to be hooked on each engaging portion 211 from the lower side.
  • the tub 21 is placed on the four hangers 32 (that is, the four hangers connected to the case 1 via the hanger rods 31 ) which are arranged at equal intervals in the circumferential direction with the central axis along the vertical direction. 32) above, it is suspended and supported in the box 1.
  • the suspension 32 is configured to include a compression coil spring 324 disposed inside the damping cylinder 321 .
  • the compression coil spring 324 is a supporting elastic body for supporting the tub 21 elastically. That is, the compression coil spring 324 is compressed by the weight of the outer tub 21 to generate a reaction force, and elastically supports the outer tub 21 (and thus the washing tub unit 2 ) while absorbing displacement.
  • the suspension 32 will be described in detail later.
  • the washing machine 100 is provided with the control part which controls each part with which it is equipped.
  • the control unit is composed of, for example, a microcomputer and the like, and is configured to include a CPU as a central processing unit, a memory composed of a volatile memory device such as a RAM, and a storage unit composed of a nonvolatile memory device such as a ROM and a network interface, ie, a communication unit, for communicating with external devices via a communication network such as the Internet.
  • the storage unit stores a program for executing a series of operations in the washing machine 100, various parameters for executing the program, and the like.
  • the control unit is connected to each unit (specifically, the motor 231, the clutch mechanism, the water supply valve, the drain valve, etc.) included in the washing machine 100, and controls each unit according to a program stored in the storage unit.
  • FIG. 2 is a vertical cross-sectional view showing the structure of the suspension 32 .
  • the suspension 32 includes a damping cylinder 321, a rod 322, a pair of fixed pistons 323a, 323b, a compression coil spring 324, a free piston 325, and a pair of elastic bodies 326a, 326b.
  • the suspension 32 is arranged from one end side of a substantially cylindrical damper cylinder (outer cylinder) 321 by a rod 322 connected to the hanger bar 31 .
  • the rod 322 may be formed integrally with the hanger bar 31 . That is, the front end portion of the hanger bar 31 may constitute the rod 322 .
  • a pair of fixed pistons 323 a , 323 b are spaced apart from each other, and are fixedly fitted with respect to the rod 322 .
  • the piston arranged on the proximal end side (ie, the upper side) of the rod 322 will be referred to as the "upper side fixed piston 323a”, and will be arranged on the distal end side (ie, the lower side) of the rod 322.
  • the piston is called "lower fixed piston 323b".
  • a compression coil spring 324 which is a supporting elastic body for elastically supporting the tub 21 , is provided at a position above the upper fixed piston 323 a of the rod 322 .
  • One end (lower end) of the compression coil spring 324 is fitted on the upper surface of the upper fixed piston 323 a, and the other end (upper end) is in contact with the inner wall of the damping cylinder 321 .
  • the compression coil spring 324 is compressed by the weight of the tub 21 to generate a reaction force, and elastically supports the tub 21 while absorbing displacement.
  • a free piston 325 is arranged between the upper fixed piston 323a and the lower fixed piston 323b.
  • the free piston 325 is not fixed with respect to the rod 322 but is provided so as to be slidable with respect to the damping cylinder 321 .
  • the free piston 325 is a cylindrical member, and the rod 322 is inserted through a through passage 3251 provided at the center in the axial direction thereof.
  • the inner diameter of the through passage 3251 is set to be slightly larger than the outer diameter of the rod 322 , and the free piston 325 can freely move forward and backward with respect to the rod 322 in the axial direction.
  • a sliding contact member 3252 is provided around the free piston 325 .
  • the sliding contact member 3252 is provided in sliding contact with the inner wall of the damping cylinder 321 .
  • the free piston 325 slides (ie, frictionally slides) with respect to the damping cylinder 321 against the frictional force generated at the sliding contact member 3252 , thereby exerting a damping force.
  • a pair of elastic bodies 326a and 326b are provided on both sides of the free piston 325 .
  • Each of the elastic bodies 326a and 326b has a cylindrical shape and is formed of a low-hardness elastomer.
  • the elastic body arranged above the free piston 325 that is, between the free piston 325 and the upper fixed piston 323a
  • upper elastic body 326a the elastic body arranged above the free piston 325
  • lower elastic body 326b The elastic body on the lower side of the free piston 325 (that is, between the free piston 325 and the lower fixed piston 323b) is referred to as a "lower elastic body 326b".
  • each elastic body 326a, 326b is fixed with respect to the free piston 325. That is, the upper elastic body 326a is fixed to the upper surface of the free piston 325 (the surface facing the upper fixed piston 323a), and the lower elastic body 326b is fixed to the lower surface of the free piston 325 (the surface facing the lower fixed piston 323b) face).
  • the elastic bodies 326a and 326b do not necessarily need to be fixed to the free piston 325 originally, but may be fixed to the fixed pistons 323a and 323b, or may not be fixed to both.
  • the separation distance L1 of the pair of fixed pistons 323a and 323b is set to the length L2 of the free piston 325 and the pair of elastic bodies 326a and 326b together (dimension in the axial direction of the rod 322) by adding the clearance. Therefore, as shown in FIG. 2 , in a state in which the free piston 325 is located at the center of the pair of fixed pistons 323a and 323b (hereinafter, also referred to as a “reference state”), between the free piston 325 and each of the fixed pistons 323a and 323b is formed. There is a gap G which forms a play in which the free piston 325 can move freely.
  • the suspension 32 does not transmit the vibration of the outer tub 21 to the casing 1 when the vibration amplitude of the outer tub 21 is smaller than a predetermined amplitude threshold value, and attenuates the vibration of the outer tub 21 when the vibration amplitude of the outer tub 21 is greater than or equal to the amplitude threshold value. vibration.
  • FIG. 3 is a diagram for explaining the operation of the suspension 32 when the vibration amplitude of the tub 21 is smaller than the amplitude threshold value.
  • FIG. 4 is a diagram for explaining the operation of the suspension 32 when the vibration amplitude of the tub 21 is equal to or larger than the amplitude threshold value.
  • the tub 21 is placed on the four hangers 32 , and the outer peripheral surface of the tub 21 is in contact with the damper cylinder 321 of the hangers 32 . Therefore, when the outer tub 21 vibrates, the damping cylinder 321 vibrates accordingly.
  • the inner wall of the damping cylinder 321 is provided with a free piston 325 which is in sliding contact with the inner wall of the damping cylinder 321.
  • the damping cylinder 321 starts to vibrate with the vibration of the outer barrel 21, the free piston 325 acts between the damping cylinder 321 and the damping cylinder 321.
  • the static friction force is integrated with the damping cylinder 321 and starts to vibrate.
  • the vibration amplitude of the outer tub 21 is relatively small and the vibration amplitude of the free piston 325 is smaller than the length ⁇ L of the gap G, as shown in FIG. That is, as long as the vibration amplitude of the free piston 325 is smaller than the length ⁇ L of the gap G, the free piston 325 does not slide relative to the damping cylinder 321 , but vibrates integrally with the damping cylinder 321 . Therefore, the damping force of the free piston 325 is not exerted. In this case, the vibration of the tub 21 is not transmitted to the rod 322 (or the hanger bar 31, and thus the case 1).
  • the vibration amplitude of the outer tub 21 is relatively large and the vibration amplitude of the free piston 325 is equal to or larger than the length ⁇ L of the gap G, as shown in FIG.
  • the lower fixed piston 323b collides and then slides (frictional slide) with respect to the damping cylinder 321 .
  • the free piston 325 collides with the upper fixed piston 323 a via the upper elastic body 326 a during the vibration process, and then slides with respect to the damping cylinder 321 .
  • the free piston 325 slides with respect to the damping cylinder 321 to exert the damping force of the free piston 325 .
  • the damping force of the free piston 325 is transmitted to the tub 21 via the damping cylinder 321, whereby its vibration is damped so that the vibration amplitude of the tub 21 is not excessively large. Further, when the free piston 325 collides with the fixed pistons 323a and 323b via the elastic bodies 326a and 326b, the vibration is transmitted to the rod 322 (and thus the hanger bar 31 and thus the case 1).
  • the vibration amplitude of the free piston 325 is the length ⁇ L of the gap G
  • the vibration amplitude of the tub 21 is the “vibration threshold”
  • the vibration amplitude of the tub 21 is smaller than the vibration threshold
  • the damping of the free piston 325 is not exerted force
  • the vibration of the outer tub 21 is not transmitted to the case 1 .
  • the vibration amplitude of the tub 21 is equal to or larger than the amplitude threshold value, the damping force of the free piston 325 is exerted, and the vibration of the tub 21 is damped.
  • the value of the vibration threshold can be adjusted according to the length ⁇ L of the gap G.
  • the vibration amplitude of the outer tub 21 during such high-speed rotation is relatively small (for example, about 5 mm).
  • the vibration amplitude of the outer tub 21 is relatively large (for example, about 20 mm).
  • the length ⁇ L of the gap G is limited so that the vibration threshold value is larger than the vibration amplitude of the tub 21 during stable dehydration and smaller than the vibration amplitude of the tub 21 during resonance vibration. In this way, the vibration of the tub 21 can be prevented from being transmitted to the case 1 during stable dehydration, and the vibration of the tub 21 can be attenuated during resonant vibration at the start of dehydration so that the vibration amplitude does not become excessively large.
  • FIG. 5 is a diagram showing a state in which the free piston 325 collides with the lower fixed piston 323b via the lower elastic body 326b in stages.
  • FIG. 6 is a diagram showing a state in which the free piston 325 collides with the upper fixed piston 323a via the upper elastic body 326a in stages.
  • the free piston 325 slides relative to the damping cylinder 321 to exert a damping force, but actually, after the free piston 325 contacts the lower fixed piston 323b via the lower elastic body 326b until the free piston 325 starts to slide relative to the damping cylinder 321 period, there is a time lag.
  • the lower elastic body 326b is deformed so as to be crushed . That is, the free piston 325 moves downward integrally with the damper cylinder 321 while deforming the lower elastic body 326b. Then, when the deformation amount of the lower elastic body 326b reaches a certain value (deformation threshold value) ⁇ Db, the free piston 325 starts to slide with respect to the damper cylinder 321 ( FIG. 5( c )). That is, the damping force of the free piston 325 starts to be exerted.
  • the lower elastic body 326b is formed between the state shown in FIG. 5( b ) to the state shown in FIG. 5( c ) (that is, from the natural state in which no external force is applied, until the The axial direction is compressed and the length (dimension in the axial direction) is shortened by the deformation threshold value ⁇ Db), and the elastic coefficient kb in the axial direction is kept constant. That is, the elastic coefficient kb of the lower elastic body 326b is maintained constant during the period from when the free piston 325 comes into contact with the lower fixed piston 323b via the lower elastic body 326b until the free piston 325 starts to slide relative to the damper cylinder 321 .
  • the dimension in the radial direction and the dimension in the longitudinal direction of the lower elastic body 326b are adjusted so as not to bend during the above-mentioned period.
  • the free piston 325 slides relative to the damping cylinder 321 to exert damping force, but here, after the free piston 325 comes into contact with the upper fixed piston 323 a via the upper elastic body 326 a until the free piston 325 starts to slide relative to the damping cylinder 321 There is also a time lag during the period.
  • the upper elastic body 326a is deformed so as to be crushed . That is, the free piston 325 moves upward integrally with the damper cylinder 321 while deforming the upper elastic body 326a. Then, when the deformation amount of the upper elastic body 326a reaches a certain value (deformation threshold value) ⁇ Da, the free piston 325 starts to slide with respect to the damping cylinder 321 ( FIG. 6( c )). That is, the damping force of the free piston 325 starts to be exerted.
  • the upper elastic body 326a is formed between the state shown in FIG. 6( b ) and the state shown in FIG. 6( c ) (that is, never applied).
  • the elastic coefficient ka in the axial direction is kept constant from the natural state of the external force until the length (dimension in the axial direction) is shortened by the deformation threshold value ⁇ Da by being compressed in the axial direction. That is, the elastic coefficient ka of the upper elastic body 326a is maintained constant during the period from when the free piston 325 comes into contact with the upper fixed piston 323a via the upper elastic body 326a until the free piston 325 starts to slide with respect to the damping cylinder 321 .
  • the upper elastic body 326a is adjusted in radial dimension and longitudinal dimension so as not to bend during the above-mentioned period.
  • the free piston 325 starts to slide relative to the damping cylinder 321 with a certain time lag.
  • the time lag is the collision time between the free piston 325 and each of the fixed pistons 323a and 323b, and the longer the time lag, the weaker the impact of the collision.
  • the longer the time lag the later the timing at which the damping force of the free piston 325 is exerted.
  • the time lag is a value limited by the deformation thresholds ⁇ Da and ⁇ Db, and the larger the deformation thresholds ⁇ Da and ⁇ Db, the longer the time lag.
  • the deformation threshold ⁇ Da of the elastic bodies 326a, 326b , ⁇ Db (mm) is defined by the following (Equation 1) and (Equation 2) using the damping force F (N) of the free piston 325 and the elastic coefficients ka and kb (N/mm) of the elastic bodies 326a and 326b.
  • the impact of the collision between the pistons is directly transmitted to the tub 21 .
  • the free piston 325 collides with the upper fixed piston 323a via the upper elastic body 326a (upper impact)
  • the free piston 325 collides with the lower fixed piston 323b via the lower elastic body 326b (lower impact)
  • the outer tub 21 may resonate and generate abnormal sound.
  • the magnitude of the abnormal sound caused by the transmission of the upper impact to the outer tub 21 and the deformation threshold ⁇ Da of the upper elastic body 326a (that is, the damping force F divided by the elastic coefficient ka of the upper elastic body 326a)
  • the value obtained, the damping force F is generated by the sliding of the free piston 325 relative to the damping cylinder 321) has a correlation.
  • the magnitude of the abnormal sound caused by the transmission of the downward impact to the outer tub 21 and the deformation threshold ⁇ Db of the lower elastic body 326b that is, the damping force F is obtained by dividing the elastic coefficient kb of the lower elastic body 326b) value
  • the deformation threshold ⁇ Da of the upper elastic body 326a and the deformation threshold ⁇ Db of the lower elastic body 326b are the same, the magnitude of the abnormal sound generated by the transmission of the downward impact to the outer tub 21 can be seen It is larger than the size of the abnormal sound generated by the upper impact transmitted to the outer tub 21 . This is considered to be because the downward impact is more easily transmitted to the outer tub 21 than the upward impact as described above.
  • the elastic coefficient ka of the upper elastic body 326a is limited to a value obtained by dividing the deformation threshold ⁇ Da of the upper elastic body 326a (that is, the damping force F by the elastic coefficient ka of the upper elastic body 326a, This damping force F is generated by sliding of the free piston 325 with respect to the damping cylinder 321 ) is equal to or greater than the allowable deformation threshold value ⁇ Da(T) corresponding to the predetermined noise threshold value T.
  • the noise threshold value T an appropriate value can be adopted.
  • the elastic coefficient ka of the upper elastic body 326a is defined in this way, the magnitude of the abnormal sound caused by the resonance of the outer tub 21 due to the transmission of the upper impact to the outer tub 21 is suppressed to be equal to or less than the predetermined noise threshold value T. That is, the abnormal sound generated by the resonance of the outer tub 21 is sufficiently suppressed, and the user of the washing machine 100 is less likely to perceive the abnormal sound as noise.
  • the specific value of the allowable deformation threshold ⁇ Da(T) varies according to the size, shape, wall thickness, forming material, and the like of the outer tub 21 .
  • the allowable deformation threshold ⁇ Da(T) is about 1 mm. Therefore, it is also preferable to limit the elastic coefficient ka of the upper elastic body 326a so that the deformation threshold value ⁇ Da of the upper elastic body 326a is 1 mm or more. In this way, the magnitude of the abnormal sound generated by the general-purpose outer tub 21 can be suppressed to a sufficiently small value.
  • the elastic coefficient kb of the lower elastic body 326b is limited to a value obtained by dividing the deformation threshold ⁇ Db of the lower elastic body 326b (that is, the damping force F by the elastic coefficient kb of the lower elastic body 326b, This damping force F is generated by sliding of the free piston 325 with respect to the damping cylinder 321 ) is equal to or greater than the allowable deformation threshold ⁇ Db(T) corresponding to the predetermined noise threshold T.
  • the noise threshold value T an appropriate value can be adopted. Even if the noise threshold T is the same, the allowable deformation threshold ⁇ Db(T) of the lower elastic body 326b is larger than the allowable deformation threshold ⁇ Da(T) of the upper elastic body 326a.
  • the elastic coefficient kb of the lower elastic body 326b is limited in this way, the magnitude of the abnormal sound caused by the resonance of the outer tub 21 due to the transmission of the downward impact to the outer tub 21 is suppressed to a value equal to or less than the predetermined noise threshold value T. That is, the abnormal sound generated by the resonance of the outer tub 21 is sufficiently suppressed, and the user of the washing machine 100 is less likely to perceive the abnormal sound as noise.
  • the specific value of the allowable deformation threshold ⁇ Db(T) also varies according to the size, shape, wall thickness, forming material, and the like of the outer tub 21 .
  • the allowable deformation threshold ⁇ Db(T) is about 3 mm. Therefore, it is also preferable to limit the elastic coefficient kb of the lower elastic body 326b so that the deformation threshold value ⁇ Db of the lower elastic body 326b is 3 mm or more. In this way, the magnitude of the abnormal sound generated by the general-purpose outer tub 21 can be suppressed to a sufficiently small value.
  • the deformation thresholds ⁇ Da and Db are defined by the elastic coefficients ka and kb of the elastic bodies 326 a and 326 b and the damping force F generated by the sliding of the free piston 325 relative to the damping cylinder 321 . Therefore, in order to keep the deformation thresholds ⁇ Da and ⁇ Db within the predetermined ranges, not only the elastic coefficients ka and kb of the elastic bodies 326 a and 326 b but also the magnitude of the damping force F must be considered. In most cases, the damping force required to sufficiently damp the outer tub 21 is first calculated, and the size and material of the sliding contact member 3252 are selected to obtain the damping force.
  • the magnitude of the damping force F is determined. Therefore, based on the determined damping force F, the values of the elastic coefficients ka and kb of the elastic bodies 326a and 326b are adjusted so that the deformation thresholds ⁇ Da and ⁇ Db fall within a predetermined range.
  • the washing machine 100 of the present embodiment includes: a case 1; Further, the suspension 32 includes: a damping cylinder 321 into which a rod 322 connected to the hanger bar 31 is inserted; a supporting elastic body 324 arranged in the damping cylinder 321 for elastically supporting the outer tub 21; 322 is not fixed but is set in a freely slidable manner relative to the damping cylinder 321; a pair of fixed pistons 323a, 323b are mutually provided with a separation distance L1 covering the movable clearance of the free piston 325, and are fixedly assembled to the rod 322; The upper elastic body 326a is arranged between the free piston 325 and the fixed piston 323a arranged on the upper side of the free piston 325; Between the pistons 323b, the elastic coefficient ka of the upper elastic body 326a and the elastic coefficient kb of the lower elastic body 326b are respectively limited so that the deformation thresholds ⁇ Da and ⁇ Db are the allowable deformation thresholds ⁇ Da(
  • the deformation thresholds ⁇ Da, ⁇ Db are values obtained by dividing the damping force F generated by the sliding of the free piston 325 relative to the damping cylinder 321 by the elastic coefficients ka, kb.
  • the vibration when the vibration amplitude of the outer tub 21 is relatively small, the vibration can be prevented from being transmitted to the case 1, and when the vibration amplitude of the outer tub 21 is relatively large, the vibration can be attenuated.
  • the shock when the free piston 325 collides with the fixed pistons 323a and 323b can be reduced.
  • the elastic coefficient ka of the upper elastic body 326a and the elastic coefficient kb of the lower elastic body 326b are respectively limited so that the deformation thresholds ⁇ Da and ⁇ Db are the allowable deformation thresholds ⁇ Da (T ), ⁇ Db(T) or more, the abnormal sound caused by the resonance of the outer tub 21 can be sufficiently suppressed.
  • the elastic coefficients ka and kb of the elastic bodies 326a and 326b are limited to satisfy the condition that the deformation thresholds ⁇ Da and ⁇ Db are equal to or greater than the allowable deformation thresholds ⁇ Da(T) and ⁇ Db(T).
  • the elastic coefficients ka and kb may be limited to satisfy at least one of the following first to third additional conditions.
  • the timing at which the damping force of the free piston 325 is exerted later that is, the smaller the elastic coefficients ka and kb of the elastic bodies 326a and 326b, the more advantageous it is to reduce the impact, but the elastic coefficients ka and kb of the elastic bodies 326a and 326b are more advantageous in that the damping force by the piston 325 is exerted as soon as possible. The bigger the better.
  • the first additional condition is that the elastic coefficients ka and kb of the elastic bodies 326a and 326b are limited to satisfy the condition that the elastic coefficient ka of the upper elastic body 326a is larger than the elastic coefficient kb of the lower elastic body 326b.
  • the lower elastic body 326b functions to attenuate the impact (downward impact) caused by the collision of the free piston 325 with the lower fixed piston 323b via the lower elastic body 326b
  • the upper elastic body 326a functions to attenuate the impact caused by the free piston 325 passing through the upper fixed piston 323b.
  • the side elastic body 326a acts as a shock (upper shock) caused by the collision with the upper fixed piston 323a.
  • the elastic coefficient kb of the lower elastic body 326b is set to be smaller than the elastic coefficient ka of the upper elastic body 326a for reducing the effect of the upward impact, and the downward impact which is relatively easily transmitted to the outer tub 21 can be sufficiently reduced.
  • the impact of the collision between the pistons is directly transmitted to the outer barrel 21, so that the impacted outer barrel 21 resonates and generates abnormal sound
  • the abnormal sound generated by the resonance of the outer tub 21 can be effectively suppressed.
  • the outer tub 21 has its own resonant rotational speed. As described above, the outer tub 21 is elastically supported by the compression coil spring 324 , and the resonance rotational speed of the outer tub 21 is basically a value defined based on the elastic coefficient of the compression coil spring 324 .
  • the resonance rotational speed of the outer tub 21 defined based on the elastic coefficient of the compression coil spring 324 is referred to as "basic resonance rotational speed R1".
  • the resonance rotational speed of the tub 21 is a value defined based on the combined elastic coefficient of the elastic coefficient kb of the lower elastic body 326b and the elastic coefficient of the compression coil spring 324 .
  • the resonance rotation speed of the outer tub 21 defined based on the combined elastic coefficient of the elastic coefficient kb of the lower elastic body 326b and the elastic coefficient of the compression coil spring 324 is referred to as "specific resonance rotation speed Rt”.
  • the second additional condition is a condition in which the elastic coefficient kb of the lower elastic body 326b is limited so that the specific resonance rotational speed Rt is higher than the basic resonance rotational speed R1 by a predetermined value ⁇ R1 or more.
  • the predetermined value ⁇ R1 may be a minimum value required to make the difference between the specific resonance rotational speed Rt and the basic resonance rotational speed R1 sufficiently large, and can be set to, for example, about 300 rpm (ie, 5 Hz).
  • the elastic modulus kb of the lower elastic body 326b is limited to the specific resonance rotational speed Rt of 500 rpm or more.
  • the variation width at this time is equal to or greater than the predetermined value ⁇ R1. That is, when the damping force of the free piston 325 acts to damp the tub 21 in the resonant state, the resonant rotational speed of the tub 21 temporarily changes greatly by a change width greater than or equal to the predetermined value ⁇ R1. Thereby, the resonance state of the outer tub 21 is rapidly converged.
  • the third additional condition is that the elastic coefficient kb of the lower elastic body 326b is limited to a condition that the specific resonance rotation speed Rt is lower than the rotation speed (stable dehydration rotation speed) R2 of the inner tub 22 during stable dehydration by a predetermined value ⁇ R2 or less .
  • the predetermined value ⁇ R2 may be a minimum value necessary to make the difference between the specific resonance rotational speed Rt and the stable dehydration rotational speed R2 sufficiently large, and can be set to, for example, about 300 rpm (ie, 5 Hz).
  • the elastic modulus kb of the lower elastic body 326b is limited to a specific resonance rotation speed Rt of 500 rpm or less.
  • the vibration amplitude of the tub 21 is relatively small.
  • the length ⁇ L of the gap G is appropriately limited so that the free The piston 325 exerts no damping force. Therefore, during the period of stable dehydration, the resonance rotation speed of the tub 21 should be the basic resonance rotation speed R1.
  • the possibility that a specific state is formed at the time of stable dehydration and the resonant rotational speed of the tub 21 becomes the specific resonant rotational speed Rt is not zero. Assuming that the specific resonance rotation speed Rt is a value close to the stable dehydration rotation speed R2, if the resonance rotation speed of the outer tub 21 changes to the specific resonance rotation speed Rt during stable dehydration, resonance may be caused to cause abnormal vibration.
  • the elastic coefficient kb of the lower elastic body 326b is defined based on the third additional condition, even if the resonance rotation speed of the outer tub 21 changes to the specific resonance rotation speed Rt during stable dehydration, the specific resonance rotation speed Rt and the stable dehydration rotation speed R2 Since the difference is greater than or equal to the predetermined value ⁇ R2, it is difficult to generate such abnormal vibration. That is, it is possible to avoid the occurrence of a situation in which the tub 21 resonates and causes abnormal vibration during stable dehydration.
  • the tub 21 may be placed on the plurality of suspensions 32 in a state in which the central axis is inclined with respect to the vertical axis, and may be suspended and supported in the casing 1 .
  • the number of suspensions 32 supporting the tub 21 is not limited to four, and may be three or five or more.

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Abstract

一种洗衣机，其中，将洗衣机的外桶（21）支承于箱体（1）内的悬架(32)具备：自由活塞(325)，以相对于阻尼筒(321)滑动自如的方式设置；一对固定活塞(323a、323b)，设有涵盖自由活塞(325)可移动的游隙的分离距离(L1)，并且固定于杆(322)；以及上侧弹性体(326a)和下侧弹性体(326b)，配置于自由活塞(325)与各固定活塞(323a、323b)之间，上侧弹性体(326a)的弹性系数(ka)和下侧弹性体(326b)的弹性系数(kb)分别被限定为使变形阈值(ΔDa、ΔDb)为与规定的噪音阈值(T)对应的允许变形阈值(ΔDa(T)、ΔDb(T))以上。

Description

洗衣机 技术领域
本发明关于洗衣机。
背景技术
洗衣机一般具备在箱体内容纳有洗涤桶单元的结构，该洗涤桶单元通过在用于贮留洗涤水的外桶的内部配置作为洗涤脱水桶的内桶等而构成。
专利文献1中提出了一种在滚筒洗衣机中设于箱体与外桶之间的防振阻尼器(damper)的结构。在此提出的防振阻尼器具备：阻尼筒(cylinder)、设于该阻尼筒内部的活塞杆、在阻尼筒的内部滑动而产生缓冲力的一组活塞(第一活塞和一对第二活塞)。第一活塞不固定于活塞杆，能够沿活塞杆自由地运动。另一方面，一对第二活塞设于第一活塞的两侧，通过固定于活塞杆而将第一活塞的运动限制于规定的范围。
在外桶的振动振幅比较小而第一活塞在由一对第二活塞限制的范围内进行振动的情况下，第一活塞相对于阻尼筒不滑动而与阻尼筒一体地运动，因此不会产生大的缓冲力。此外，在该情况下，第一活塞不与一对第二活塞碰撞，因此外桶的振动不会经由活塞杆传递至箱体。
另一方面，在外桶的振动振幅比较大而第一活塞超过由一对第二活塞限制的范围进行振动的情况下，第一活塞在振动过程中与第二活塞碰撞而相对于阻尼筒滑动，产生较大的缓冲力。此外，在该情况下，第一活塞与一对第二活塞碰撞，因此外桶的振动会经由活塞杆传递至箱体(进而传递至设置该箱体的地面)。
这样，如果使用专利文献1的防振阻尼器，能在外桶的振动振幅比较小的情况下抑制外桶的振动传递至箱体乃至地面，另一方面，在外桶的振动振幅比较大的情况下，能使外桶的振动衰减。
另外，在立式洗衣机的情况下，外桶以通过一端固定于箱体的多个吊棒被悬挂的状态支承于箱体内。在各吊棒的前端设有在阻尼筒内配置有螺旋弹簧而成的悬架，外桶被该螺旋弹簧弹性地支承(参照专利文献1)。
该悬架起到通过将外桶的振动传递给箱体使其释放来使该振动衰减以使外桶的振动振幅不会过大的功能。但是，当外桶的振动被传递至箱体时，设置有洗衣机的地面会振动，恐怕会给使用者带来不快感。因而，悬架优选仅限于在衰减的必要性高的情况下即外桶的振动振幅大的情况下发挥该衰减的功能，在外桶的振动振幅比较小的情况下，不使外桶的振动传递至箱体。
因此，考虑将专利文献1中提出的滚筒洗衣机的防振阻尼器的结构应用于立式洗衣机的悬架。
在专利文献1中提出的防振阻尼器中，在外桶的振动振幅比较大而第一活塞超过由一对第二活塞限制的范围进行振动的情况下，会反复发生第一活塞与第二活塞的碰撞。由此，会不断地产生碰撞声。原本，只消除活塞彼此的碰撞声的话，如专利文献1所记载的那样在两活塞之间设置缓冲材料这样的对策就足够。然而，要将该防振阻尼器的结构应用于立式洗衣机的悬架的情况下，第一活塞与第二活塞的碰撞会引起远超碰撞声的产生的非常严重的问题。
即，在立式洗衣机中，与滚筒洗衣机不同，外桶直接载置于多个悬架之上，将自身的载荷交给悬架。因此，当在悬架中活塞彼此碰撞时，该冲击会直接传递至外桶。这样一来，外桶会因从悬架受到冲击而谐振，由此产生异音。不用说，外桶谐振而产生的异音的大小与活塞彼此的碰撞声相比大得多。
现有技术文献
专利文献
专利文献1：日本专利第2868688号公报
专利文献2：日本特开2017－113310号公报
发明内容
发明所要解决的问题
本发明是鉴于上述的情况而完成的，其目的在于提供一种在外桶的振动振幅比较小的情况下不将该振动传递给箱体并且在外桶的振动振幅比较大的情况下使该振动衰减且能充分抑制外桶谐振而产生的异音的技术。
用于解决问题的方案
本发明为了达到这样的目的，采用了如下的方案。
即，本发明是一种洗衣机，具备：箱体；以及外桶，载置于经由吊棒连结于所述箱的多个悬架之上，从而悬挂支承于所述箱体内，其特征在于，所述悬架具备：阻尼筒，供与所述吊棒相连的杆插入；支承弹性体，配置于所述阻尼筒内，用于弹性地支承所述外桶；自由活塞，以相对于所述杆不固定而相对于所述阻尼筒滑动自如的方式设置；一对固定活塞，相互之间设有涵盖所述自由活塞可移动的游隙的分离距离，并且固定地装配于所述杆；上侧弹性体，配置于所述自由活塞与配置于所述自由活塞的上侧的所述固定活塞之间；以及下侧弹性体，配置于所述自由活塞与配置于所述自由活塞的下侧的所述固定活塞之间，所述上侧弹性体的弹性系数和所述下侧弹性体的弹性系数分别被限定为使变形阈值为与规定的噪音阈值对应的允许变形阈值以上，所述变形阈值是将所述自由活塞相对于所述阻尼筒滑动而产生的衰减力除以所述弹性系数而得的值。
在本发明的洗衣机中，优选的是，所述上侧弹性体的弹性系数比所述下侧弹性体的弹性系数大。
在本发明的洗衣机中，优选的是，所述上侧弹性体的弹性系数被限定为使所述变形阈值为1mm以上。
在本发明的洗衣机中，优选的是，所述下侧弹性体的弹性系数被限定为使所述变形阈值为3mm以上。
在本发明的洗衣机中，优选的是，所述下侧弹性体的弹性系数被限定为：使基于所述下侧弹性体的弹性系数与所述支承弹性体的弹性系数的合成弹性系数来限定的所述外桶的共振转速为比基于所述支承弹性体的弹性系数来限定的所述外桶的共振转速高规定值以上的值。
在本发明的洗衣机中，优选的是，所述下侧弹性体的弹性系数被限定为： 使基于所述下侧弹性体的弹性系数与所述支承弹性体的弹性系数的合成弹性系数来限定的所述外桶的共振转速为比稳定脱水时的转数低规定值以下的值。
在本发明的洗衣机中，对于所述下侧弹性体和所述上侧弹性体各自而言，在所述自由活塞从经由该弹性体与所述固定活塞接触后到相对于所述阻尼筒开始滑动为止的期间，该弹性体的弹性系数被维持为恒定。
发明效果
根据本发明，能在外桶的振动振幅比较小的情况下使该振动不传递至箱体并且在外桶的振动振幅比较大的情况下使该振动衰减。
即，在外桶的振动振幅比较小而自由活塞以不与固定活塞接触的方式沿着杆振动的情况下，由于自由活塞相对于阻尼筒不滑动而与之成为一体地振动，因此不发挥自由活塞的衰减力。在该情况下，外桶的振动不会传递至杆(乃至箱体)。另一方面，在外桶的振动振幅比较大而自由活塞在振动过程中经由弹性体与固定活塞碰撞的情况下，由于碰撞之后自由活塞相对于阻尼筒滑动，因此发挥了自由活塞的衰减力，外桶的振动被衰减。
而且，通过将上侧弹性体的弹性系数和下侧弹性体的弹性系数分别限定为使变形阈值为与规定的噪音阈值对应的允许变形阈值以上，能充分抑制外桶谐振而产生的异音。
即，在上侧弹性体和下侧弹性体起到减弱因自由活塞经由该弹性体与固定活塞碰撞而产生的冲击的作用的情况下，该冲击传递至外桶并因谐振而产生的异音的大小与通过自由活塞相对于阻尼筒滑动而产生的衰减力除以该弹性体的弹性系数而得的值(变形阈值)具有相关关系，存在随着该变形阈值变大而产生的异音的大小变小的倾向。根据上述的结构，由于各弹性体的弹性系数被限定为使变形阈值为与规定的噪音阈值对应的允许变形阈值以上，因此该异音的大小被抑制在规定的噪音阈值以下。即，外桶谐振而产生的异音被充分抑制，洗衣机的使用者不易感觉该异音为噪音。
根据本发明，通过上侧弹性体的弹性系数被设为比下侧弹性体的弹性系数大，能够在确保发挥充分的衰减力的同时充分抑制外桶谐振而产生的异音。
即，下侧弹性体起到减弱因自由活塞经由下侧弹性体与下侧的固定活塞碰 撞而产生的冲击(下方冲击)的作用，上侧弹性体起到减弱因自由活塞经由上侧弹性体与上侧的固定活塞碰撞而产生的冲击(上方冲击)的作用。
各弹性体的弹性系数越小，减弱碰撞的冲击的作用越强，但另一方面，自由活塞的衰减力发挥的时机越晚。就是说，在减弱冲击这一点上，弹性体的弹性系数越小越有利，但在尽早发挥自由活塞的衰减力这一点上，弹性体的弹性系数越大越有利。
在此，对外桶靠近悬架时受到的下方冲击与外桶远离悬架时受到的上方冲击进行比较，下方冲击更容易传递至外桶，通过将起到减弱下方冲击的作用的下侧弹性体的弹性系数设为比起到减弱上方冲击的作用的上侧弹性体的弹性系数小，能够充分减弱比较容易传递至外桶的下方冲击。由此，能有效抑制外桶谐振而产生的异音。另一方面，通过将上侧弹性体的弹性系数设为比下侧弹性体的弹性系数大，自由活塞的衰减力发挥的时机不会过晚，确保发挥充分的衰减力。
根据本发明，由于上侧弹性体的弹性系数被限定为使上侧弹性体的变形阈值为1mm以上，因此能将通用的外桶所发出的异音的大小抑制为充分小的值。
根据本发明，由于下侧弹性体的弹性系数被限定为使下侧弹性体的变形阈值为3mm以上，因此能将通用的外桶所发出的异音的大小抑制为充分小的值。
根据本发明，侧弹性体的弹性系数被限定为：使基于下侧弹性体的弹性系数与支承弹性体的弹性系数的合成弹性系数来限定的外桶的共振转速(特定共振转速)为比基于支承弹性体的弹性系数来限定的外桶的共振转速(基本共振转速)高规定值以上的值，因此能使外桶的共振状态迅速地收敛。
即，例如，当在脱水启动等时转数达到基本共振转速而外桶中产生了共振振动的状况下，成为自由活塞的衰减力发挥的状态时，外桶的共振转速间歇地变化为特定共振转速。在下侧弹性体的弹性系数被限定为使特定共振转速为比基本共振转速高规定值以上的值的情况下，此时的变化幅度为规定值以上。即，在自由活塞的衰减力起作用以使呈共振状态的外桶衰减时，外桶的共振转速临时按照规定值以上的变化幅度大幅变化。由此，外桶的共振状态迅速地收敛。
根据本发明，将下侧弹性体的弹性系数限定为使基于下侧弹性体的弹性系 数与支承弹性体的弹性系数的合成弹性系数来限定的外桶的共振转速(特定共振转速)为比稳定脱水时的转数(稳定脱水转数)低规定值以下的值，因此避免稳定脱水时引起外桶共振而成为异常振动这样的事态的产生于未然。
即，在当特定共振转速成为接近稳定脱水转数的值时，稳定脱水时外桶的共振转速由于某些预料不到的因素等而变化为特定共振转速的情况下，恐怕会引起谐振而成为异常振动。然而，在将下侧弹性体的弹性系数限定为使特定共振转速为比稳定脱水转数低规定值以下的值的情况下，即使稳定脱水时外桶的共振转速变化为特定共振转速，由于特定共振转速与稳定脱水转数相差规定值以上，因此也难以产生这样的异常振动。
根据本发明，对于下侧弹性体和上侧弹性体各自而言，在自由活塞从经由该弹性体与固定活塞接触后到相对于阻尼筒开始滑动为止的期间，该弹性体的弹性系数被维持为恒定，因此衰减力发挥的时机恒定，能稳定地发挥衰减力。
附图说明
图1是表示实施方式的洗衣机100的概略结构的纵剖视图。
图2是表示悬架32的结构的纵剖视图。
图3是用于说明外桶21的振动振幅比振幅阈值小的情况下的悬架32的动作的图。
图4是用于说明外桶21的振动振幅为振幅阈值以上的情况下的悬架32的动作的图。
图5是分阶段地表示自由活塞325不经由下侧弹性体326b与下侧固定活塞323b碰撞时的情形的图。
图6是分阶段地表示自由活塞325经由上侧弹性体326a与上侧固定活塞323a碰撞时的情形的图。
图7是表示弹性体326a、326b的变形阈值与产生的异音的大小的关系的图。
附图标记说明
1：箱体；2：洗涤桶单元；21：外桶；22：内桶；23：驱动部；3：吊棒单 元；31：吊棒；32：悬架；321：阻尼筒；322：杆；323a：上侧固定活塞；323b：下侧固定活塞；324：支承弹性体(压缩螺旋弹簧)；325：自由活塞；326a：上侧弹性体；326b：下侧弹性体；L1：分离距离；ka：上侧弹性体的弹性系数；kb：下侧弹性体的弹性系数；ΔDa：上侧弹性体的变形阈值；ΔDb：下侧弹性体的变形阈值；100：洗衣机。
具体实施方式
以下，参照附图，并且针对本发明的实施方式进行说明。
＜1.整体结构＞
参照图1对实施方式的洗衣机的结构进行说明。图1是表示实施方式的洗衣机100的概略结构的纵剖视图。
洗衣机100配置为所谓的立式洗衣机，具备箱体1、洗涤桶单元2、吊棒单元3等。
箱体1是用于在内部形成容纳空间的外壳，由将俯视大致长方形的下板、形成从下板的缘部立起的四面的四个侧板以及与连接于四个侧板的上部的上板一体构成的大致长方体状的箱状构件构成。在下板的下表面，于四角的附近设有腿部11。此外，在上板设有开口12，能经由该开口12向洗涤桶单元2取放洗涤物等。而且，在上板的上部设有用于使开口12可开闭的盖构件13。
洗涤桶单元2容纳于箱体1内，具备：外桶21、在外桶21的内部以套匣状配置的内桶(洗涤脱水桶)22、设于外桶21的底部的驱动部23等。
外桶21为用于蓄留水(洗涤水)的贮留桶，由上表面开口且底面封闭的圆筒状的构件构成。外桶21例如由树脂(优选地耐热性优异的合成树脂)形成。
内桶22是所谓的洗涤脱水桶，由上表面开口且底面封闭的圆筒状的构件构成。内桶22例如由金属形成。在内桶22的底面的中央设有波轮(搅拌翼)221。此外，内桶22的周壁等被穿孔出许多通水孔(省略图示)。内桶22被设为其中心轴与外桶21的中心轴一致的位置和姿态，被支承为绕该中心轴旋转自如。
需要说明的是，虽然省略了图示，但在外桶21和内桶22的上方，以使供 水口面对内桶22的开口的方式配置有供水管。供水管一端与外部的供水设备等连接，并且在供水管的中途部分设有供水阀。当该供水阀被设为开状态时，从外部的供水设备等供给来的水经由供水管流入内桶22，进而经过形成于内桶22的通水孔(省略图示)流入外桶21。此外，在外桶21的底部连接有排水管。排水管一端与外部的排水设备等连接，并且在排水管的中途部分设有排水阀。当该排水阀被设为开状态时，外桶21内和内桶22内的水经由排水管被排水。
驱动部23是用于使内桶22等旋转的机构，具备配置于内桶22的下方的马达231。马达231的驱动力经由第一输出轴232被传递至波轮221，波轮221受到来自马达231的驱动力而绕其中心轴旋转。此外，马达231的驱动力经由第二输出轴233被传递至内桶22，内桶22受到来自马达231的驱动力而绕内桶22的中心轴旋转。
马达231中设有离合机构(省略图示)，被设为在仅向第一输出轴232传递驱动力的状态与向第一输出轴232和第二输出轴233的双方传递驱动力的状态之间进行切换。例如在洗涤过程中，马达231的驱动力仅传递至第一输出轴232，仅有波轮221旋转。此外，例如在脱水过程中，马达231的驱动力传递至双方的输出轴232、233，内桶22和波轮221一体地旋转。
吊棒单元3是用于在箱体1的内部弹性地悬挂来支承外桶21(进而，洗涤桶单元2)的部件，配置为包括四个吊棒31和设于各吊棒31的前端的悬架32。
吊棒31为棒状的构件，一端相对于箱体1被固定。具体而言，在箱体1的上端附近的四角设有钩状的卡定部14，在各卡定部14装配有吊棒31的基端侧。该卡定部14作为用于通过使吊棒31的基端侧卡定来悬挂吊棒31的支点发挥功能。另一方面，在外桶21的从底面连向侧壁的立起部分的附近，设有在周向上隔开相等间隔的四个卡合部211，各吊棒31的前端侧插通于该卡合部211，设于该前端的悬架32以从下侧挂在各卡合部211上的方式被卡定。
这样，外桶21处于以中心轴沿着铅垂方向的姿态载置于周向上隔开相等间隔地配置的四个悬架32(即，经由吊棒31与箱体1连结的四个悬架32)之上的状态，被悬挂支承于箱体1内。
悬架32配置为包括配置于阻尼筒321的内部的压缩螺旋弹簧324。该压缩 螺旋弹簧324为用于弹性地支承外桶21的支承弹性体。即，压缩螺旋弹簧324被外桶21的重量压缩而产生反作用力，并且在吸收位移的同时弹性地支承外桶21(进而支撑洗涤桶单元2)。针对悬架32将在后面详细叙述。
需要说明的是，虽然省略了图示，但洗衣机100具备控制其所具备的各部的控制部。控制部例如由微型计算机等构成，配置为包括：作为中央运算处理装置的CPU、由RAM等的易失性存储装置构成的内存(memory)、由ROM等非易失性存储装置构成的存储部以及用于经由因特网等的通信网络与外部设备进行通信的网络接口即通信部等。存储部中存储有用于在洗衣机100中执行一系列动作的程序、用于该程序的执行的各种参数等。控制部与洗衣机100所具备的各部(具体而言，马达231、离合机构、供水阀、排水阀等)连接，根据存储于存储部的程序来控制各部。
＜2.悬架32的结构＞
如上所述，外桶21被设为载置于四个悬架32之上的状态，由此弹性地悬挂支承于箱体1内。参照图2对该悬架32的结构进行说明。图2是表示悬架32的结构的纵剖视图。
悬架32具备：阻尼筒321、杆322、一对固定活塞323a、323b、压缩螺旋弹簧324、自由活塞325、一对弹性体326a、326b。
具体而言，悬架32配置为被与吊棒31相连的杆322从大致圆筒状的阻尼筒(外筒)321的一端侧。杆322也可以与吊棒31一体地构成。即，吊棒31的前端部分也可以构成杆322。
在杆322的前端部分，一对固定活塞323a、323b相互隔开间隔，并且相对于杆322被固定地装配。以下，将这一对固定活塞323a、323b中配置于杆322的基端侧(即上侧)的活塞称为“上侧固定活塞323a”，将配置于杆322的前端侧(即下侧)的活塞称为“下侧固定活塞323b”。
在杆322的比上侧固定活塞323a靠上侧的位置，设有用于弹性地支承外桶21的支承弹性体即压缩螺旋弹簧324。压缩螺旋弹簧324一端(下端)装配于上侧固定活塞323a的上表面，另一端(上端)与阻尼筒321的内壁抵接。如上所述，该压缩螺旋弹簧324被外桶21的重量压缩而产生反作用力，并且在吸收 位移的同时弹性地支承外桶21。
在上侧固定活塞323a与下侧固定活塞323b之间配置有自由活塞325。自由活塞325以相对于杆322不固定而相对于阻尼筒321滑动自如的方式设置。具体而言，自由活塞325是圆柱状的构件，在设于其轴向的中心的贯通路3251中插通有杆322。贯通路3251的内径被设为比杆322的外径稍大，自由活塞325能在轴向上相对于杆322自由地进退移动。此外，在自由活塞325的周围设有滑动接触构件3252。滑动接触构件3252以与阻尼筒321的内壁滑动接触的方式设置。自由活塞325对抗滑动接触构件3252处产生的摩擦力而相对于阻尼筒321进行滑动(即，摩擦滑动)，由此发挥衰减力。
在自由活塞325的两侧设有一对弹性体326a、326b。各弹性体326a、326b为圆筒形状，由低硬度高弹体(elastomer)形成。以下，将这一对弹性体326a、326b中配置于自由活塞325的上侧(即自由活塞325与上侧固定活塞323a之间)的弹性体称为“上侧弹性体326a”，将配置于自由活塞325的下侧(即自由活塞325与下侧固定活塞323b之间)的弹性体称为“下侧弹性体326b”。
在此，各弹性体326a、326b相对于自由活塞325被固定。即，上侧弹性体326a固定于自由活塞325的上表面(与上侧固定活塞323a对置的面)，下侧弹性体326b固定于自由活塞325的下表面(与下侧固定活塞323b对置的面)。各弹性体326a、326b本来未必需要固定于自由活塞325，也可以固定于固定活塞323a、323b，还可以不固定于这两方。
一对固定活塞323a、323b之间设有涵盖自由活塞325可移动的游隙的分离距离L1。即，一对固定活塞323a、323b的分离距离L1设为在将自由活塞325与一对弹性体326a、326b合在一起的长度(杆322的轴向的尺寸)L2上加上游隙的长度。因而，如图2所示，在自由活塞325位于一对固定活塞323a、323b的中央的状态下(以下也称为“基准状态”)，在自由活塞325与各固定活塞323a、323b之间形成有间隙G，该间隙G形成自由活塞325能自由移动的遊隙。
＜3.悬架32的动作＞
悬架32在外桶21的振动振幅比规定的振幅阈值小的情况下不使外桶21的振动传递至箱体1，在外桶21的振动振幅为该振幅阈值以上的情况下衰减外桶 21的振动。针对这一点，参照图1、图2再加上图3、图4进行说明。图3是用于说明外桶21的振动振幅比振幅阈值小的情况下的悬架32的动作的图。图4是用于说明外桶21的振动振幅为振幅阈值以上的情况下的悬架32的动作的图。
如上所述，外桶21被设为载置于四个悬架32之上的状态，外桶21的外周面与悬架32的阻尼筒321接触。因而，当外桶21振动时，阻尼筒321随之振动。在阻尼筒321的内壁设有与阻尼筒321的内壁滑动接触的自由活塞325，当阻尼筒321随着外桶21的振动而开始振动时，自由活塞325通过作用于其与阻尼筒321之间的静摩擦力，与阻尼筒321成为一体开始振动。
在外桶21的振动振幅比较小而自由活塞325的振动振幅小于间隙G的长度ΔL的情况下，如图3所示，自由活塞325不与固定活塞323a、323b接触，沿杆322振动。即，自由活塞325只要其振动振幅比间隙G的长度ΔL小，就不会相对于阻尼筒321滑动，而与阻尼筒321一体地振动。因而，不发挥自由活塞325的衰减力。在该情况下，外桶21的振动不会传递至杆322(乃至吊棒31，进而箱体1)。
另一方面，在外桶21的振动振幅比较大而自由活塞325的振动振幅为间隙G的长度ΔL以上的情况下，如图4所示，自由活塞325在振动过程中经由下侧弹性体326b与下侧固定活塞323b碰撞，之后，相对于阻尼筒321滑动(摩擦滑动)。此外，自由活塞325在振动过程中经由上侧弹性体326a与上侧固定活塞323a碰撞，之后，相对于阻尼筒321滑动。自由活塞325相对于阻尼筒321滑动，从而发挥自由活塞325的衰减力。自由活塞325的衰减力经由阻尼筒321传递至外桶21，由此，其振动被减弱以使外桶21的振动振幅不会过大。此外，通过自由活塞325经由弹性体326a、326b与固定活塞323a、323b碰撞，振动被传递至杆322(乃至吊棒31，进而箱体1)。
这样，自由活塞325的振动振幅为间隙G的长度ΔL时，外桶21的振动振幅为“振动阈值”，在外桶21的振动振幅比该振动阈值小的情况下，不发挥自由活塞325的衰减力，外桶21的振动不会传递至箱体1。另一方面，在外桶21的振动振幅为振幅阈值以上的情况下，发挥自由活塞325的衰减力，外桶21的振动被衰减。
振动阈值的值能够根据间隙G的长度ΔL来进行调整。例如，在稳定脱水 时的内桶22的转数(稳定脱水转数)为600rpm～800rpm左右的情况下，这样的高速旋转时的外桶21的振动振幅比较小(例如为5mm左右)。另一方面，例如在脱水启动等时，当转数达到外桶21固有的共振转速时，外桶21中产生共振振动。此时的外桶21的振动振幅比较大(例如为20mm左右)。因此，在这里，间隙G的长度ΔL被限定为使振动阈值为比稳定脱水时的外桶21的振动振幅大的值并且为比共振振动时的外桶21的振动振幅小的值。如此，能在稳定脱水时使外桶21的振动不传递至箱体1，并且在脱水启动时的共振振动中使外桶21的振动衰减从而使振动振幅不过度变大。
＜4.弹性体326a、326b的弹性系数＞
如上所述，在外桶21的振动振幅为振幅阈值以上的情况下，自由活塞325在振动过程中经由弹性体326a、326b与固定活塞323a、323b碰撞，之后，相对于阻尼筒321滑动。针对此时的举动，参照图5、图6进行更具体的说明。图5是分阶段地表示自由活塞325经由下侧弹性体326b与下侧固定活塞323b碰撞时的情形的图。图6是分阶段地表示自由活塞325经由上侧弹性体326a与上侧固定活塞323a碰撞时的情形的图。
当外桶21从基准状态(图5的(a))向下方移动时，阻尼筒321与自由活塞325成为一体向下方移动。在自由活塞325向下方移动了间隙G的长度ΔL的量时，下侧弹性体326b与下侧固定活塞323b接触(图5的(b))。即，自由活塞325经由下侧弹性体326b与下侧固定活塞323b接触。
之后，自由活塞325相对于阻尼筒321滑动而发挥衰减力，但实际上，在自由活塞325经由下侧弹性体326b与下侧固定活塞323b接触之后到自由活塞325相对于阻尼筒321开始滑动为止的期间，存在时滞。
即，当自由活塞325从自由活塞325经由下侧弹性体326b与下侧固定活塞323b接触的状态(图5的(b))进一步向下方移动时，下侧弹性体326b以压扁的方式变形。即，自由活塞325在使下侧弹性体326b变形的同时与阻尼筒321成为一体向下方移动。然后，当下侧弹性体326b的变形量达到某值(变形阈值)ΔDb时，自由活塞325开始相对于阻尼筒321滑动(图5的(c))。即，开始发挥自由活塞325的衰减力。
但是，下侧弹性体326b形成为：在从图5的(b)所示的状态到图5的(c)所示的状态之间(即，从未施加外力的自然状态起，直至通过在轴向上被压缩而长度(轴向的尺寸)缩短了变形阈值ΔDb的量的期间)，轴向的弹性系数kb被保持为恒定。即，在从自由活塞325经由下侧弹性体326b与下侧固定活塞323b接触起，直至自由活塞325相对于阻尼筒321开始滑动为止的期间，下侧弹性体326b的弹性系数kb被维持为恒定。此外，下侧弹性体326b被调整了径向的尺寸和长度方向的尺寸，使得上述期间不发生弯曲，。
一方面，当外桶21从基准状态(图6的(a))向上方移动时，阻尼筒321与自由活塞325成为一体向上方移动。在自由活塞325向上方移动了间隙G的长度ΔL的量时，上侧弹性体326a与上侧固定活塞323a接触(图6的(b))。即，自由活塞325经由上侧弹性体326a与上侧固定活塞323a接触。
之后，自由活塞325相对于阻尼筒321滑动而发挥衰减力，但在这里，在自由活塞325经由上侧弹性体326a与上侧固定活塞323a接触之后到自由活塞325相对于阻尼筒321开始滑动为止的期间，也存在时滞。
即，当自由活塞325从自由活塞325经由上侧弹性体326a与上侧固定活塞323a接触的状态(图6的(b))进一步向上方移动时，上侧弹性体326a以压扁的方式变形。即，自由活塞325在使上侧弹性体326a变形的同时与阻尼筒321成为一体向上方移动。然后，当上侧弹性体326a的变形量达到某值(变形阈值)ΔDa时，自由活塞325开始相对于阻尼筒321滑动(图6的(c))。即，开始发挥自由活塞325的衰减力。
但是，与下侧弹性体326b同样地，上侧弹性体326a形成为：在从图6的(b)所示的状态到图6的(c)所示的状态之间(即，从未施加外力的自然状态起，直至通过在轴向上被压缩而长度(轴向的尺寸)缩短了变形阈值ΔDa的量的期间)，轴向的弹性系数ka被保持为恒定。即，在从自由活塞325经由上侧弹性体326a与上侧固定活塞323a接触起，直至自由活塞325相对于阻尼筒321开始滑动为止的期间，上侧弹性体326a的弹性系数ka被维持为恒定。此外，上侧弹性体326a被调整了径向的尺寸和长度方向的尺寸，使得上述期间不发生弯曲。
这样，在自由活塞325经由各弹性体326a、326b与各固定活塞323a、323b 接触之后，间隔某个时滞，自由活塞325开始相对于阻尼筒321滑动。该时滞是自由活塞325与各固定活塞323a、323b的碰撞时间，该时滞越长则碰撞的冲击越弱。另一方面，该时滞越长则自由活塞325的衰减力发挥的时机越晚。
该时滞是根据变形阈值ΔDa、ΔDb来限定的值，变形阈值ΔDa、ΔDb越大则时滞越长。在自由活塞325相对于阻尼筒321开始滑动的时机，自由活塞325的衰减力(即，摩擦力)与从各弹性体326a、326b受到的弹力平衡时，各弹性体326a、326b的变形阈值ΔDa、ΔDb(mm)使用自由活塞325的衰减力F(N)和各弹性体326a、326b的弹性系数ka、kb(N/mm)，由以下的(式1)、(式2)限定。
ΔDa＝F/ka(式1)
ΔDb＝F/kb(式2)
另外，在如本洗衣机100那样外桶21直接载置于多个悬架32之上的结构中，活塞彼此的碰撞的冲击会直接传递至外桶21。当因自由活塞325经由上侧弹性体326a与上侧固定活塞323a碰撞而产生的冲击(上方冲击)、因自由活塞325经由下侧弹性体326b与下侧固定活塞323b碰撞而产生的冲击(下方冲击)被传递至外桶21时，外桶21恐怕会谐振而产生异音。
在此，根据实验可知，起因于上方冲击被传递至外桶21而产生的异音的大小与上侧弹性体326a的变形阈值ΔDa(即，衰减力F除以上侧弹性体326a的弹性系数ka而得的值，该衰减力F通过自由活塞325相对于阻尼筒321滑动而产生)之间具有相关关系。同样地，可知起因于下方冲击被传递至外桶21而产生的异音的大小与下侧弹性体326b的变形阈值ΔDb(即，该衰减力F除以下侧弹性体326b的弹性系数kb而得的值)之间具有相关关系。
图7中分别示出了上侧弹性体326a的变形阈值ΔDa与通过上方冲击被传递至外桶21而产生的异音的大小的关系Ra和下侧弹性体326b的变形阈值ΔDb与通过下方冲击被传递至外桶21而产生的异音的大小之间的关系Rb。这里所示的关系Ra、Rb通过实验等事先获取。
如图7中所示，可知随着各弹性体326a、326b的变形阈值ΔDa、Db变大，所产生的异音的大小有变小的倾向。这一点认为是由于如上所述发挥了变形阈 值ΔDa、Db越大则减弱因各弹性体326a、326b所引起的冲击的作用越强的效果。
此外，如图7中所示，可知在上侧弹性体326a的变形阈值ΔDa与下侧弹性体326b的变形阈值ΔDb相同的情况下，通过下方冲击传递至外桶21而产生的异音的大小比通过上方冲击传递至外桶21而产生的异音的大小大。这一点认为是由于如上所述下方冲击比上方冲击容易传递至外桶21。
因此，在本实施方式中，将上侧弹性体326a的弹性系数ka限定为使上侧弹性体326a的变形阈值ΔDa(即衰减力F除以上侧弹性体326a的弹性系数ka而得的值，该衰减力F通过自由活塞325相对于阻尼筒321滑动而产生)为与规定的噪音阈值T对应的允许变形阈值ΔDa(T)以上。作为噪音阈值T，可以采用适当的值。
如果这样规定上侧弹性体326a的弹性系数ka，则由于上方冲击传递至外桶21导致外桶21谐振而产生的异音的大小被抑制在规定的噪音阈值T以下。即，外桶21谐振而产生的异音被充分抑制，洗衣机100的使用者不易感觉该异音为噪音。
允许变形阈值ΔDa(T)的具体值根据外桶21的尺寸、形状、壁厚、形成材料等而改变。例如，设想通用的外桶，在采用一般被视为噪音的声音的大小即50dB来作为噪音阈值T的情况下，允许变形阈值ΔDa(T)为1mm左右。因而，也优选以上侧弹性体326a的变形阈值ΔDa为1mm以上的方式限定上侧弹性体326a的弹性系数ka。如此，能将通用的外桶21所发出的异音的大小抑制为充分小的值。
而且，在本实施方式中，将下侧弹性体326b的弹性系数kb限定为使下侧弹性体326b的变形阈值ΔDb(即衰减力F除以下侧弹性体326b的弹性系数kb而得的值，该衰减力F通过自由活塞325相对于阻尼筒321滑动而产生)为与规定的噪音阈值T对应的允许变形阈值ΔDb(T)以上。作为噪音阈值T，可以采用适当的值。即使噪音阈值T相同，下侧弹性体326b的允许变形阈值ΔDb(T)也是比上侧弹性体326a的允许变形阈值ΔDa(T)大的值。
如果这样限定下侧弹性体326b的弹性系数kb，则由于下方冲击传递至外桶 21导致外桶21谐振而产生的异音的大小被抑制在规定的噪音阈值T以下的值。即，外桶21谐振而产生的异音被充分抑制，洗衣机100的使用者不易感觉该异音为噪音。
允许变形阈值ΔDb(T)的具体值也根据外桶21的尺寸、形状、壁厚、形成材料等而改变。例如，设想通用的外桶，在采用一般被视为噪音的声音的大小即50dB来作为噪音阈值T的情况下，允许变形阈值ΔDb(T)为3mm左右。因而，也优选以下侧弹性体326b的变形阈值ΔDb为3mm以上的方式限定下侧弹性体326b的弹性系数kb。如此，能将通用的外桶21所发出的异音的大小抑制为充分小的值。
需要说明的是，变形阈值ΔDa、Db的值由各弹性体326a、326b的弹性系数ka、kb和通过自由活塞325相对于阻尼筒321滑动而产生的衰减力F来限定。因而，为了将变形阈值ΔDa、ΔDb收敛于规定的范围内，不仅要考虑各弹性体326a、326b的弹性系数ka、kb，还需要考虑衰减力F的大小。在多数情况下，最先计算出充分衰减外桶21所需的衰减力，并选定滑动接触构件3252的尺寸、材质以得到该衰减力。即，首先确定衰减力F的大小。因而，根据该确定出的衰减力F，调整各弹性体326a、326b的弹性系数ka、kb的值以使变形阈值ΔDa、ΔDb收敛于规定的范围内。
＜5.效果＞
本实施方式的洗衣机100具备：箱体1；以及外桶21，载置于经由吊棒31连结于箱体1的多个悬架32之上，从而悬挂支承于箱体1内。并且，悬架32具备：阻尼筒321，供与吊棒31相连的杆322插入；支承弹性体324，配置于阻尼筒321内，用于弹性地支承外桶21；自由活塞325，以相对于杆322不固定而相对于阻尼筒321滑动自如的方式设置；一对固定活塞323a、323b，相互之间设有涵盖自由活塞325可移动的游隙的分离距离L1，并且固定地装配于杆322；上侧弹性体326a，配置于自由活塞325与配置于自由活塞325的上侧的固定活塞323a之间；以及下侧弹性体326b，配置于自由活塞325与配置于自由活塞325的下侧的固定活塞323b之间，上侧弹性体326a的弹性系数ka和下侧弹性体326b的弹性系数kb分别被限定为使变形阈值ΔDa、ΔDb为与规定的噪音阈值T对应的允许变形阈值ΔDa(T)、ΔDb(T)以上，该变形阈值ΔDa、ΔDb 是将自由活塞325相对于阻尼筒321滑动而产生的衰减力F除以该弹性系数ka、kb而得的值。
根据该结构，能在外桶21的振动振幅比较小的情况下使该振动不传递至箱体1并且在外桶21的振动振幅比较大的情况下使该振动衰减。
此外，根据该结构，通过在自由活塞325与各固定活塞323a、323b之间设置上侧弹性体326a或者下侧弹性体326b，能减弱自由活塞325与各固定活塞323a、323b碰撞时的冲击。
而且，根据该结构，上侧弹性体326a的弹性系数ka和下侧弹性体326b的弹性系数kb分别被限定为使变形阈值ΔDa、ΔDb为与规定的噪音阈值T对应的允许变形阈值ΔDa(T)、ΔDb(T)以上，由此能充分抑制外桶21谐振而产生的异音。
此外，在上述的实施方式的洗衣机100中，对于下侧弹性体326b和上侧弹性体326a各自而言，在自由活塞325从经由该弹性体326a、326b与固定活塞323a、323b接触后到相对于阻尼筒321开始滑动为止的期间，该弹性体326a、326b的弹性系数ka、kb被维持为恒定。
根据该结构，衰减力发挥的时机恒定，因此能够稳定地发挥衰减力。
＜6.对各弹性系数ka、kb进行限定时的附加条件＞
在上述的实施方式中，各弹性体326a、326b的弹性系数ka、kb被限定为满足变形阈值ΔDa、ΔDb为允许变形阈值ΔDa(T)、ΔDb(T)以上这一条件，但除了这样的条件以外，还可以将各弹性系数ka、kb限定为满足以下的第一至第三附加条件中的至少一条件。
(第一附加条件)
如上所述，各弹性体326a、326b的弹性系数ka、kb越小，则变形阈值ΔDa、ΔDb越大，减弱碰撞冲击的作用越强，但另一方面，自由活塞325的衰减力发挥的时机越晚。即，在减弱冲击这一点上，弹性体326a、326b的弹性系数ka、kb越小越有利，但在尽早发挥由活塞325的衰减力这一点上，弹性体326a、326b的弹性系数ka、kb越大越有利。
第一附加条件为将各弹性体326a、326b的弹性系数ka、kb限定为满足上侧弹性体326a的弹性系数ka比下侧弹性体326b的弹性系数kb大这一条件的条件。
下侧弹性体326b起到减弱因自由活塞325经由下侧弹性体326b与下侧固定活塞323b碰撞而产生的冲击(下方冲击)的作用，上侧弹性体326a起到减弱因自由活塞325经由上侧弹性体326a与上侧固定活塞323a碰撞而产生的冲击(上方冲击)的作用。在此，对外桶21靠近悬架32时受到的下方冲击与外桶21远离悬架32时受到的上方冲击进行比较，下方冲击更容易传递至外桶21，通过将起到减弱下方冲击的作用的下侧弹性体326b的弹性系数kb设为比起到减弱上方冲击的作用的上侧弹性体326a的弹性系数ka小，能够充分减弱比较容易传递至外桶21的下方冲击。
如上所述，在外桶21直接载置于多个悬架32上的结构中，活塞彼此的碰撞的冲击会直接传递至外桶21，因此会有受到冲击的外桶21发生谐振而产生异音的隐患，通过充分减弱比较容易传递至外桶21的下方冲击，能有效地抑制外桶21谐振而产生的异音。
另一方面，通过上侧弹性体326a的弹性系数ka被设为比下侧弹性体326b的弹性系数kb大，自由活塞325的衰减力发挥的时机不会过晚，确保发挥充分的衰减力。
当像这样采用上侧弹性体326a的弹性系数ka比下侧弹性体326b的弹性系数kb大的结构时，能够在确保发挥充分的衰减力的同时充分抑制外桶21谐振而产生的异音。
(第二附加条件)
外桶21具有其固有的共振转速。如上所述，外桶21由压缩螺旋弹簧324弹性地支承，外桶21的共振转速基本上是基于该压缩螺旋弹簧324的弹性系数来限定的值。以下，将基于压缩螺旋弹簧324的弹性系数来限定的外桶21的共振转速称为“基本共振转速R1”。
另一方面，如上所述，在外桶21的振动振幅为振幅阈值以上的情况下，发挥自由活塞325的衰减力，外桶21的振动被衰减。此时，间歇地形成与自由活塞325向下方移动相应地下侧弹性体326b以压扁的方式变形的状态(图5的 (b)～图5的(c))。在该状态(以下称为“特定状态”)下，外桶21的共振转速是基于下侧弹性体326b的弹性系数kb与压缩螺旋弹簧324的弹性系数的合成弹性系数来限定的值。以下，将基于下侧弹性体326b的弹性系数kb与压缩螺旋弹簧324的弹性系数的合成弹性系数来限定的外桶21的共振转速称为“特定共振转速Rt”。
第二附加条件为将下侧弹性体326b的弹性系数kb限定为使特定共振转速Rt为比基本共振转速R1高规定值ΔR1以上的值这样的条件。作为该规定值ΔR1，采用使特定共振转速Rt与基本共振转速R1相差足够大所需的最小值即可，例如能设为300rpm(即，5Hz)左右。
在基本共振转速R1为例如200rpm的情况下，若将规定值ΔR1设为300rpm，则将下侧弹性体326b的弹性系数kb限定为使特定共振转速Rt为500rpm以上。
设想如下的状况：例如在脱水启动等时，转数达到基本共振转速R1而外桶21中产生了共振振动。在这样的状况下，当成为发挥自由活塞325的衰减力的状态时，则间歇地形成特定状态，此时，外桶21的共振转速临时变化为特定共振转速Rt。
在基于第二附加条件来限定下侧弹性体326b的弹性系数kb的情况下，此时的变化幅度为规定值ΔR1以上。即，在为了使呈共振状态的外桶21衰减而使自由活塞325的衰减力起作用时，外桶21的共振转速临时按照规定值ΔR1以上的变化幅度大幅变化。由此，外桶21的共振状态迅速地收敛。
(第三附加条件)
第三附加条件为将下侧弹性体326b的弹性系数kb限定为使特定共振转速Rt为比稳定脱水时的内桶22的转数(稳定脱水转数)R2低规定值ΔR2以下的值这样的条件。作为该规定值ΔR2，采用使特定共振转速Rt与稳定脱水转数R2相差足够大所需的最小值即可，例如能设为300rpm(即，5Hz)左右。
在稳定脱水转数R2为例如800rpm的情况下，若将规定值ΔR2设为300rpm，则将下侧弹性体326b的弹性系数kb限定为使特定共振转速Rt为500rpm以下。
在进行稳定脱水的期间(即，转数为稳定脱水转数R2的期间)，外桶21的振动振幅比较小，通常，在这样的状态下，间隙G的长度ΔL被适当地限定为 使自由活塞325不发挥衰减力。因而，在进行稳定脱水的期间，外桶21的共振转速应该为基本共振转速R1。然而，由于某些预料不到的因素，在稳定脱水时形成特定状态而外桶21的共振转速变为特定共振转速Rt的可能性不为零。假设特定共振转速Rt为接近稳定脱水转数R2的值，则在稳定脱水时外桶21的共振转速变化为特定共振转速Rt的情况下，恐怕会引起谐振而造成异常振动。
在基于第三附加条件来限定下侧弹性体326b的弹性系数kb的情况下，即使在稳定脱水时外桶21的共振转速变化为特定共振转速Rt，由于特定共振转速Rt与稳定脱水转数R2相差规定值ΔR2以上，因此也难以产生这样的异常振动。即，能避免在稳定脱水时引起外桶21谐振而导致异常振动这样的事态的发生于未然。
＜7.变形例＞
其他的结构能够在不脱离本发明的主旨的范围进行各种变形。
例如，可以以是，外桶21设为以使中心轴相对于铅直轴倾斜的姿态载置于多个悬架32之上的状态，悬挂支承于箱体1内。
此外，支承外桶21的悬架32的个数并不限于四个，也可以是三个，还可以是五个以上。

Claims (7)

  1. 一种洗衣机，具备：箱体；以及外桶，载置于经由吊棒连结于所述箱体的多个悬架之上，从而悬挂支承于所述箱体内，其特征在于，
    所述悬架具备：
    阻尼筒，供与所述吊棒相连的杆插入；
    支承弹性体，配置于所述阻尼筒内，用于弹性地支承所述外桶；
    自由活塞，以相对于所述杆不固定而相对于所述阻尼筒滑动自如的方式设置；
    一对固定活塞，相互之间设有涵盖所述自由活塞可移动的游隙的分离距离，并且固定地装配于所述杆；
    上侧弹性体，配置于所述自由活塞与配置于所述自由活塞的上侧的所述固定活塞之间；以及
    下侧弹性体，配置于所述自由活塞与配置于所述自由活塞的下侧的所述固定活塞之间，
    所述上侧弹性体的弹性系数和所述下侧弹性体的弹性系数分别被限定为使变形阈值为与规定的噪音阈值对应的允许变形阈值以上，所述变形阈值是将所述自由活塞相对于所述阻尼筒滑动而产生的衰减力除以该弹性系数而得的值。
  2. 根据权利要求1所述的洗衣机，其特征在于，
    所述上侧弹性体的弹性系数比所述下侧弹性体的弹性系数大。
  3. 根据权利要求1或2所述的洗衣机，其特征在于，
    所述上侧弹性体的弹性系数被限定为使所述变形阈值为1mm以上。
  4. 根据权利要求1至3的任一项所述的洗衣机，其特征在于，
    所述下侧弹性体的弹性系数被限定为使所述变形阈值为3mm以上。
  5. 根据权利要求1至4的任一项所述的洗衣机，其特征在于，
    所述下侧弹性体的弹性系数被限定为：使基于所述下侧弹性体的弹性系数 与所述支承弹性体的弹性系数的合成弹性系数来限定的所述外桶的共振转速为比基于所述支承弹性体的弹性系数来限定的所述外桶的共振转速高规定值以上的值。
  6. 根据权利要求1至5的任一项所述的洗衣机，其特征在于，
    所述下侧弹性体的弹性系数被限定为：使基于所述下侧弹性体的弹性系数与所述支承弹性体的弹性系数的合成弹性系数来限定的所述外桶的共振转速为比稳定脱水时的转数低规定值以下的值。
  7. 根据权利要求1至6的任一项所述的洗衣机，其特征在于，
    对于所述下侧弹性体和所述上侧弹性体各自而言，在所述自由活塞从经由该弹性体与所述固定活塞接触后到相对于所述阻尼筒开始滑动为止的期间，该弹性体的弹性系数被维持为恒定。
PCT/CN2021/103924 2020-12-09 2021-07-01 洗衣机 WO2022121292A1 (zh)

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JPH06134178A (ja) * 1992-10-27 1994-05-17 Matsushita Electric Ind Co Ltd 自動洗濯機の防振装置
JPH06327892A (ja) * 1993-05-26 1994-11-29 Matsushita Electric Ind Co Ltd ドラム式洗濯機
JPH0824474A (ja) * 1994-07-13 1996-01-30 Matsushita Electric Ind Co Ltd 全自動洗濯機
JPH0975581A (ja) * 1995-09-14 1997-03-25 Hitachi Ltd 電気洗濯機の防振装置
KR100273405B1 (ko) * 1998-03-10 2000-12-15 구자홍 세탁기의 댐퍼
KR100273397B1 (ko) * 1998-01-20 2001-01-15 구자홍 세탁기의댐퍼구조
CN1526972A (zh) * 2003-03-06 2004-09-08 Lg������ʽ���� 组合型阻尼器和具有这种阻尼器的洗衣机
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WO2011057372A1 (pt) * 2009-11-11 2011-05-19 Whirlpool S.A. Dispositivo de amortecimento para o sistema de suspensão de uma máquina lavadora de roupas
CN108930133A (zh) * 2017-05-24 2018-12-04 青岛海尔洗衣机有限公司 洗衣机用吊杆组件及波轮洗衣机

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06134178A (ja) * 1992-10-27 1994-05-17 Matsushita Electric Ind Co Ltd 自動洗濯機の防振装置
JPH06327892A (ja) * 1993-05-26 1994-11-29 Matsushita Electric Ind Co Ltd ドラム式洗濯機
JPH0824474A (ja) * 1994-07-13 1996-01-30 Matsushita Electric Ind Co Ltd 全自動洗濯機
JPH0975581A (ja) * 1995-09-14 1997-03-25 Hitachi Ltd 電気洗濯機の防振装置
KR100273397B1 (ko) * 1998-01-20 2001-01-15 구자홍 세탁기의댐퍼구조
KR100273405B1 (ko) * 1998-03-10 2000-12-15 구자홍 세탁기의 댐퍼
CN1526972A (zh) * 2003-03-06 2004-09-08 Lg������ʽ���� 组合型阻尼器和具有这种阻尼器的洗衣机
CN1730784A (zh) * 2004-08-06 2006-02-08 乐金电子(天津)电器有限公司 洗衣机的双重减震装置
WO2011057372A1 (pt) * 2009-11-11 2011-05-19 Whirlpool S.A. Dispositivo de amortecimento para o sistema de suspensão de uma máquina lavadora de roupas
CN108930133A (zh) * 2017-05-24 2018-12-04 青岛海尔洗衣机有限公司 洗衣机用吊杆组件及波轮洗衣机

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