WO2015180473A1 - 洗衣机 - Google Patents

洗衣机 Download PDF

Info

Publication number
WO2015180473A1
WO2015180473A1 PCT/CN2014/095722 CN2014095722W WO2015180473A1 WO 2015180473 A1 WO2015180473 A1 WO 2015180473A1 CN 2014095722 W CN2014095722 W CN 2014095722W WO 2015180473 A1 WO2015180473 A1 WO 2015180473A1
Authority
WO
WIPO (PCT)
Prior art keywords
displacement
tension spring
main body
vibration
spring
Prior art date
Application number
PCT/CN2014/095722
Other languages
English (en)
French (fr)
Inventor
广濑彻
中本重阳
Original Assignee
海尔亚洲国际株式会社
青岛海尔洗衣机有限公司
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
Application filed by 海尔亚洲国际株式会社, 青岛海尔洗衣机有限公司 filed Critical 海尔亚洲国际株式会社
Publication of WO2015180473A1 publication Critical patent/WO2015180473A1/zh

Links

Images

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
    • 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

Definitions

  • the present invention relates to a washing machine capable of suppressing vibration when a washing and dewatering tank is rotated.
  • a washing machine having a structure in which a cylindrical outer tank is supported inside a main body formed in a box shape and a washing and dewatering tank as an inner tank is rotatably supported inside the outer tank (for example, refer to Patent Document 1).
  • the outer groove is elastically supported on the main body at four locations via a suspension including a spring and a hanger hanging thereon, thereby suppressing vibration during operation.
  • the number of low-order natural vibrations of the vibration mode in which the outer groove vibrates around the rotation axis of the washing and dewatering tank occurs in a region lower than the rotation speed of the washing and dewatering tank.
  • a pulsator agitating blade
  • the washing and dewatering tank and the pulsator are integrally rotated at a high speed inside the outer tank at the time of dehydration.
  • the outer tub has to be miniaturized as compared with the main body, and a large dead zone is required inside the main body. Further, when the vibration countermeasure is performed by the control, the vibration detecting device and the complicated control are required, resulting in an increase in cost.
  • Patent Document 2 There is disclosed a configuration in which a ring is coaxially disposed in a state where a clearance is provided outside the outer tub of the washing machine, and a leaf spring is provided outside the ring (see paragraphs 0094 and 0095 and FIGS. 19D and 19E).
  • the leaf spring is held by the stopper in a state where the pressure is applied to the displacement in advance, and when the displacement is shifted to the above and the restriction of the stopper disappears, a large spring force including the amount of pressurization can be applied.
  • Patent Document 1 Japanese Laid-Open Patent Publication No. 2011-240041
  • Patent Document 2 Japanese Patent No. 3984630
  • the mechanism for supporting the leaf spring and the mechanism for supporting the ring are complicated to change, and the manufacturing cost is further increased.
  • the present invention has an object of solving such a problem, and an object of the present invention is to provide a washing machine which can suppress not only the vibration of the outer tub but also the gap between the outer tub and the main body, and can also be simplified.
  • the construction makes assembly easy and reduces manufacturing costs.
  • the present invention seeks the following technical solutions.
  • the present invention provides a washing machine including: a main body in which an internal space is formed, an outer tank disposed in an internal space of the main body, and an inner tank that is disposed rotatably and supported inside the outer tank, and is provided in the washing machine An electric motor for rotating the inner groove and an elastic support device for elastically supporting the outer groove with respect to the main body, wherein: a plurality of tension springs are disposed on the outer groove and the Between the bodies, by transmitting the displacement of the outer groove, a reaction force for returning the outer groove to the original position is given; The position transmitting device transmits the displacement of the outer groove to the tension spring only when the displacement of the outer groove increases to a predetermined value or more; and the pressurizing setting device sets the addition of the tension spring Pressure.
  • the present invention is characterized in that the pressurizing setting device includes a spring end restricting portion integrally provided at both ends of the tension spring, and a restricting shaft body disposed along the tension spring, in the displacement In a state where the displacement of the transmission device is not transmitted, the relative position of the spring end regulating portion is restricted by the end portion of the restriction shaft body, and the extension of the tension spring is allowed, and the pressurization is given.
  • the displacement transmission device includes an annular vibration restricting member that is disposed with a predetermined gap with respect to an outer circumference of the outer tub, and a string member for supporting the same, and the pulling member is pulled
  • the extension spring and the string member are connected in series, and the vibration restricting member is supported by the body via the tension spring and the string member.
  • the displacement transmission device is a string member provided between an outer circumference of the outer tub and the main body, and when the displacement of the outer groove is equal to or greater than a predetermined value, The string member is tensioned and a tensile force is applied to the tension spring.
  • the displacement transmission device includes a belt-shaped body that surrounds at least a part of an outer circumference of the outer tank, and is disposed at a predetermined gap with an outer circumference of the outer tank. Connected to the body, the strip body and the tension spring are connected in series.
  • the elastic body provided on the outer periphery of the outer groove is in contact with the inside of the main body.
  • the natural vibration number is changed to reduce the vibration.
  • the number of natural vibrations of the vibration mode of the outer groove vibration depends on the elastic support strength (spring constant) of the elastic support device that supports the outer groove, and since the rotation speed is close to the natural vibration number, the outer groove vibrates in a state of large vibration.
  • the displacement of the outer groove is equal to or greater than a predetermined value
  • the displacement of the outer groove is transmitted to the tension spring via the displacement transmission device, whereby the reaction force can be generated by the tension spring and given to the outer groove.
  • the tension spring is pressurized in advance, a large reaction force is generated with respect to the outer groove. Therefore, the elastic support strength of the outer groove abruptly changes, and the number of natural vibrations changes, and the vibration of the outer groove can be suppressed, and the inner groove can be further accelerated to a predetermined rotation frequency.
  • the restricting shaft body is provided along the tension spring, and the relative position of the both ends of the spring is restricted by the restricting shaft body via the spring end restricting portion, thereby not only the structure is simple And it is possible to apply pressure to the tension spring while allowing deformation of the tension spring in the elongation direction.
  • the displacement transmitting device includes the annular vibration restricting member and the string member
  • the tension spring can be pulled regardless of the direction in which the outer groove is displaced.
  • the extension force acts on the outer groove to sharply change the elastic support strength, whereby the vibration suppression can be quickly achieved without depending on the direction of the vibration.
  • the displacement transmission device is a string member provided between the outer periphery of the outer tub and the main body
  • the displacement of the outer groove is transmitted to the stretching via the string member.
  • the spring and the tensile force of the tension spring can be applied to the outer groove, which is not only simple in structure, but also can rapidly change the strength of the elastic support when the outer groove vibrates to quickly suppress the vibration.
  • the displacement transmitting device includes the belt-shaped body surrounding the outer circumference of the outer tank, and when the displacement of the outer tank is equal to or greater than a predetermined value, the outer tank is conveyed to the tension spring via the belt-shaped body disposed on the outer circumference of the outer tank.
  • the displacement and the tensile force of the tension spring can be applied to the outer groove, which is not only simple in structure, but also can rapidly change the strength of the elastic support when the outer groove vibrates to quickly suppress the vibration. Further, when the outer groove vibrates, frictional resistance is generated between the inner side and the inner side of the strip body, whereby the vibration can be attenuated, so that a larger vibration suppressing effect can be obtained.
  • Fig. 1 is a longitudinal sectional view showing a washing machine in accordance with a first embodiment of the present invention.
  • Fig. 2 is a cross-sectional view taken along line A-A of Fig. 1;
  • Fig. 3 is a plan view showing a pressurizing setting device of the washing machine.
  • Fig. 4 is an explanatory view schematically showing a force acting on an outer tub of the washing machine.
  • Fig. 5 is an explanatory diagram for explaining a relationship between a force acting on the outer groove and a displacement.
  • Fig. 6 is a longitudinal sectional view showing a washing machine in accordance with a second embodiment of the present invention.
  • Fig. 7 is a vertical cross-sectional view showing a state in which the washing and dewatering tank is displaced from the state of Fig. 6;
  • Fig. 8 is a cross-sectional view taken along line A-A of Fig. 6;
  • Fig. 9 is a longitudinal sectional view showing a washing machine in accordance with a third embodiment of the present invention.
  • Fig. 10 is a cross-sectional view taken along line A-A of Fig. 9;
  • Fig. 11 is a view showing a state in which a part of the strip body is removed from the state of Fig. 10 and simplified.
  • Fig. 12 is a view showing a state in which the washing and dewatering tank is displaced from the state of Fig. 11;
  • FIG. 1 is a longitudinal cross-sectional view showing a washing machine 1 according to a first embodiment of the present invention
  • FIG. 2(a) is a cross-sectional view taken along line A-A of FIG. 1.
  • Fig. 1 shows a cross section of the B-B position of Fig. 2(a), that is, a diagonal position.
  • FIG. 2(b) shows a state in which the outer tank 3 is displaced as will be described later.
  • the washing machine 1 described in these FIGS. 1 and 2 has a schematic configuration, and a portion that is not related to the present invention is omitted.
  • the elastic support apparatus 5 mentioned later in FIG. 1 is abbreviate
  • the washing machine 1 includes a main body 2, an outer tub 3, a washing and dewatering tank 4 as an inner tub, and elastic support devices 5 to 5.
  • the main body 2 includes an internal space 2a which is formed in a substantially rectangular parallelepiped shape in which the lower plate 22 having a substantially square shape in plan view and the side plates 21 to 21 which are formed on the four sides from the edge portion and the upper plate 23 connected to the upper portion thereof are integrally formed.
  • a substantially rectangular parallelepiped shape By forming a substantially rectangular parallelepiped shape by being surrounded by them.
  • the side plates 21 and the lower plate 22 are formed of a metal plate, and the upper plate 23 is formed of a resin.
  • the lower plate 22 has legs 22a to 22a which can provide the main body 2 on the floor surface near the four corners below.
  • a substantially circular opening 23a through which the laundry can be discharged into the washing and dewatering tank 4 is provided on the upper plate 23.
  • the upper plate 23 can be detached from the side plate 21, whereby the outer groove 3 can be easily fitted into the inner space 2a of the main body 2.
  • the upper plate 23 may be integrally formed with an operation panel for performing the operation of the washing machine 1.
  • the outer tub 3 is molded of a heat-resistant synthetic resin, and is a bottomed cylindrical member having a bottom plate 31 that is substantially circular in plan view and a side plate 32 that rises from the edge of the bottom plate 31.
  • the outer tub 3 is suspended by the elastic support device 5 in the inner space 2a of the main body 2, and the engaging portion 33 for attaching the elastic supporting device 5 is provided at four portions of the lower portion of the side plate 32.
  • the washing and dewatering tank 4 is made of metal and is a bottomed cylindrical member having a bottom plate 41 that is substantially circular in plan view and a side plate 42 that rises from the edge of the bottom plate 41.
  • the washing and dewatering tank 4 is disposed coaxially with the outer tank 3 inside the outer tank 3, and is rotatably supported by the outer tank 3.
  • a plurality of openings are provided in the side plates 42 and the bottom plate 41, and the water in the washing and dewatering tank 4 can be discharged through the openings.
  • the washing and dewatering tank 4 is rotated by the motor 34 to rotate the drive shaft 35 that extends toward the upper surface side of the bottom plate 31. Further, the motor 34 is also directed to the bottom plate provided in the washing and dewatering tank 4 via a transmission device (not shown).
  • the center pulsator (stirring blade) 43 imparts a driving force to rotate the pulsator 43. Therefore, the washing machine 1 can mainly rotate only the pulsator 43 at the time of washing, and the washing and dewatering tank 4 and the pulsator 43 can be integrally rotated at high speed during dehydration.
  • the center of the rotation of the pulsator 43 and the center of the rotation of the washing and dewatering tank 4 are set to the same rotation axis Ra arranged in the vertical direction. Further, the rotation axis Ra also passes through the center of the bottom plate 41 of the washing and dewatering tank 4 and the center of the bottom plate 31 of the outer tank 3.
  • the elastic support devices 5 to 5 suspend the outer groove 3.
  • four elastic support devices 5 to 5 are provided, and each of them is composed of a boom 51 and a suspension 52 attached to the front end thereof.
  • the suspension 52 has an outer cylinder 53 and a compression coil spring 54 disposed inside thereof.
  • the boom attachment portions 24 to 24 are respectively provided at the four corners 2a1 to 2a1 (see FIG. 2) on the upper portion of the internal space 2a, and the base end sides of the boom 51 are attached to the respective boom attachment portions 24 to 24.
  • the outer cylinder 53 of the suspension 52 is engaged with the engaging portion 33 in a state of being hooked on the engaging portion 33 of the outer tub 3.
  • the outer tub 3 is suspended in the inner space 2a by the four elastic supporting means 5 to 5.
  • each elastic supporting device 5 is compressed by the weight of the outer groove 3 to generate a reaction force, and elastically supports the outer groove 3 while absorbing the displacement. Further, the four elastic supporting devices 5 to 5 respectively suspend the outer tub 3 from the oblique direction, thereby cooperatively achieving the function of maintaining the balance of the outer tub 3 in the center direction of the main body 2.
  • the elastic supporting device 5 not only generates the elasticity of the compression coil spring 54 of the suspension 52, but also generates a restoring force for returning the center of the suspended outer groove 3 just like the vibrator by its positional relationship. Therefore, when the outer tub 3 is displaced from the center position, the restoring force corresponding to the displacement amount is obtained by the elastic supporting device 5, and is returned to the center position of the main body 2 by the restoring force.
  • the number of low-order natural vibrations corresponding to the vibration mode of the outer groove 3 about the rotation axis Ra is very low rotation of about 2 to 3 Hz.
  • the speed zone appears.
  • the most likely vibration in the washing machine 1 is that the washing and dewatering tank 4 rotates at a high speed together with the pulsator 43.
  • the washing dewatering tank 4 rotates at a predetermined operating speed that is extremely higher than the number of low-order natural vibrations, the speed is increased after starting.
  • the washing machine 1 of the present embodiment suppresses the vibration of the outer tub 3 as shown in FIG. 1 and FIG. 2(a). Further, it is provided that four tension springs 6 to 6 for imparting a reaction force for returning the outer groove 3 to the original position are provided by transmitting the displacement of the outer groove 3; only the displacement of the outer groove 3 is increased to a predetermined value or more. In this case, the displacement of the outer tank 3 is transmitted to the displacement transmission device 8 of the tension spring 6, and the pressurized pressure setting device 7 for setting the tension spring 6.
  • each of the tension springs 6 to 6 is disposed at the corner portion 2a1 of the main body 2 which is likely to be a dead zone, it is possible to have a function for suppressing vibration, and it is possible to suppress an increase in size of the entire apparatus.
  • the displacement transmission device 8 is composed of a ring-shaped vibration restricting member 81 and four string members 82 to 82 for supporting the vibration restricting member 81.
  • the vibration restricting member 81 may be formed of metal or resin.
  • the string member 82 is made of a metal wire which is difficult to expand and contract, and has flexibility to transmit force only in the stretching direction, and almost no force is transmitted in the compression direction.
  • the string members 82 to 82 have one end connected to the four portions of the vibration restricting member 81 and the other end connected to one of the tension springs 6 to 6, respectively. Further, each of the tension springs 6 to 6 is connected to the corner portions 2a1 to 2a1 of the main body 2. Therefore, the vibration restricting member 81 is supported by the four corners (corner portions 2a1 to 2a1) of the main body 2 via the tension springs 6 to 6 and the string members 82 to 82.
  • the vibration restricting member 81 is disposed coaxially with the outer tub 3 in the vicinity of the upper portion of the outer tub 3, and forms a substantially uniform gap E between the outer peripheral surface 32a of the outer tub 3 and the entire circumference.
  • FIG. 3 is a cross-sectional view showing the tension spring 6 and the pressurizing setting device 7. Specifically, FIG. 3( a ) shows a state in which the tension spring 6 is in a state of a natural length L. Moreover, FIG. 3(b) shows a state in which the pressurization Fp which is a tensile force is applied to both ends of the tension spring 6, and ⁇ L is extended and the length is maintained.
  • the tension spring 6 used in the present embodiment uses a tension coil spring composed of a metal coil, and spring end restricting portions 71 and 71 are integrally provided at both ends of the tension spring 6, and inside the tension spring 6, A restriction shaft 72 is provided along the longitudinal direction of the tension spring 6. Further, if it is a spring that generates a reaction force with respect to the tensile force, instead of the tension spring, other elastic bodies may be used as the tension spring 6.
  • Each of the spring end restricting portions 71 includes a disc portion 71a and an annular mounting portion 71b that protrudes outward from the disc portion 71a.
  • the disc portion 71a is fixed after being inserted into the inside of the spiral constituting the end portion of the tension spring 6, and can be displaced together with the end portion of the tension spring 6.
  • One of the spring end regulating portions 71 and 71 disposed at both ends of the tension spring 6 is attached to the string member 82 (see FIG. 2) by the annular mounting portion 71b, and the spring end regulating portions 71 and 71 are attached to the spring end regulating portions 71 and 71.
  • the corner portion 2a1 of the main body 2 is attached by the attachment portion 71b (see Fig. 2).
  • the vibration restricting member 81 is supported by the four corners (corner portions 2a1 to 2a1) of the main body 2 via the tension springs 6 to 6 and the string members 82 to 82.
  • the restriction shaft 72 is inserted into the inside of the tension spring 6, and the restriction shaft is utilized.
  • the body 72 limits the relative positions of the disc portions 71a, 71a of the spring end restricting portions 71, 71.
  • the tension spring 6 can be pressurized Fp via the spring end restricting portions 71, 71 and held in a state of being extended by ⁇ L from the natural length L. That is, the spring end restricting portions 71 and 71 and the regulating shaft body 72 function as the pressurizing setting device 7 for setting the pressurizing Fp to the tension spring 6.
  • the initial tension is generated in the tension coil spring which is usually densely wound, the elongation does not occur even if the force exceeding the initial tension is not applied. Therefore, when the initial tension is used as the above-described pressurization Fp, It is also possible to adopt a configuration in which the shaft body 72 is not used.
  • Fig. 3(c) shows a state in which the tension spring 6 is further extended from the state of Fig. 3(b).
  • the pressurizing setting device 7 applies a force exceeding the pressurizing Fp to both ends of the tension spring 6, the tension spring 6 can be extended.
  • the pressurizing setting device 7 restricts deformation in the direction in which the tension spring 6 is shortened in the direction in which the pressurizing Fp is set, while allowing the tension spring 6 to deform in the extending direction.
  • the vibration restricting member 81 is disposed with the gap E with respect to the outer circumference of the outer tub 3. Therefore, if the outer tub 3 is in the horizontal direction (the lower right direction in the example in the drawing), the gap E is used.
  • the outer peripheral surface 32a of the outer tub 3 abuts against the vibration restricting member 81.
  • the displacement of the outer groove 3 is transmitted to the tension spring 6 located on the opposite side (the upper left in the example of the drawing) of the outer groove 3 via the vibration restricting member 81 and the string member 82 constituting the displacement transmitting device 8. . Further, even if the string member 82 attached to the opposite side of the string member 82 is increased in slack, no force is applied to the tension spring 6 connected thereto.
  • FIG. 4(a) and 4(b) schematically show the structure of the washing machine 1 of the present embodiment.
  • the force acting on the outer tub 3 of the washing machine 1 will be described with reference to Fig. 1 using Figs. 4(a) and 4(b).
  • the outer tub 3 is suspended by the above-described four elastic supporting devices 5 to 5, and a restoring force k ⁇ e for returning the outer tub 3 to the center is generated in accordance with the displacement e from the center.
  • k is to be supported by the elastic support device 5 ⁇ 5
  • the restoring force acting in the center direction is regarded as the spring constant under the case of the elastic force (refer to Fig. 4 (a)).
  • the spring constant k can also be said to be the elastic support strength for elastically supporting the outer groove 3.
  • FIG. 5 is a graph showing the relationship between the above equation with the amplitude (displacement) e being the horizontal axis and the vibration force F including the inertial force Fi or the spring force Fk being the vertical axis.
  • the straight lines L1 to L10 shown in the drawing are inertial characteristic straight lines indicating the relationship of the formula (3), and the straight line La is a spring characteristic straight line indicating the relationship of the formula (4), and the intersection point thereof represents the amplitude (displacement) at the angular frequency ⁇ . e and vibration force F.
  • the inclination is proportional to the square of the angular frequency ⁇ , and the slice (intersection) on the horizontal axis is represented by ⁇ m ⁇ r/M.
  • the inertial characteristic lines L1 to L10 are described so that the magnitude of the angular frequency ⁇ is different, and the relationship between the amplitude e and the inertial force Fi such as L2, L3, ... L10 from the straight line L1 increases as the angular frequency ⁇ increases. A change has occurred. Therefore, the intersection of each of the inertial characteristic straight lines L1 to L10 and the spring characteristic straight line La shows the relationship between the amplitude e of each angular frequency ⁇ and the vibration force F.
  • the amplitude e and the vibration force F are changed as follows in consideration of the process of increasing the angular frequency ⁇ .
  • the amplitude e and the vibration force F corresponding to the intersection P1 of the inertia characteristic line L1 and the spring characteristic line La are generated.
  • the amplitude e and the vibration force F corresponding to the intersection point P2 of the inertia characteristic line L2 and the spring characteristic line La are generated.
  • the amplitude e and the vibration force F corresponding to the intersection P3 of the inertia characteristic line L3 and the spring characteristic line La are generated.
  • the amplitude e corresponding to the intersection with the inertia characteristic line La is extremely large.
  • the vibration restricting member 81 constituting the displacement transmission device 8 is provided between the outer tub 3 and the main body 2 via the gap E, and the vibration restricting member 81 is stretched via the string member 82 and the tension member 82.
  • the spring 6 is connected to the main body 2, and the outer groove 3 is pulled back to the center direction with a stronger force by the action of the tension spring 6.
  • the tension spring 6 is used to pressurize the Fp in advance by the pressurizing setting device 7. Therefore, when the elongation is extremely small, the restriction of the pressurizing setting device 7 is released, and the amount of the pressurized Fp is added.
  • the spring constant k is apparently increased by the particularly large spring force due to the pressure Fp.
  • the spring characteristic straight line La transitions to the spring characteristic line Lb having a larger inclination in a region where the amplitude e is equal to or larger than the gap E.
  • the amplitude e When the amplitude e is smaller than the gap E, the number of low-order natural vibrations of the outer tank 3 is again reduced. However, at this time, the angular frequency ⁇ is larger than the number of low-order natural vibrations, and resonance does not occur again, and the state in which the amplitude e is small can be maintained. That is, even if the angular frequency ⁇ increases and moves like the inertial straight lines L5 and L6, as shown by the intersections P5 and P6 of the spring characteristic straight line La, the amplitude e does not exceed the gap E and can be maintained at a small level.
  • the spring characteristic straight line Lb does not have to pass through the origin as long as the apparent spring constant k is in a sharply increasing relationship.
  • the pressurization Fp is set to be very large, the amount of elongation ⁇ L or the gap E (see FIG. 2) when the pressurization Fp is applied can be appropriately changed.
  • the vibration restricting member 81 constituting the displacement transmission device 8 is provided between the outer tub 3 and the main body 2 via the gap E, and the vibration restricting member 81 is connected to the main body 2 via the string member 82 and the tension spring 6, and therefore While the washing and dewatering tank 4 is rotated and increased to a predetermined operating speed, the angular frequency ⁇ , that is, the rotational speed is close to the number of low-order natural vibrations of the outer tank 3, and when the amplitude e is increased beyond the gap E, The outer tank 3 is in contact with the vibration restricting member 81.
  • the tension spring 6 connected to the vibration restricting member 81 via the string member 82 is restricted to the displacement in the shortened direction in a state where the pressurization Fp is given in advance, and when the elongation based on the state is generated, Add the amount of pressurized Fp and apply to both Therefore, the number of low-order natural vibrations can be greatly changed, whereby vibration can be reduced.
  • the amplitude e is smaller than the gap E, the number of low-order natural vibrations is reduced, and the rotational speed of the washing and dewatering tank 4 is increased to be separated from the number of low-order natural vibrations, thereby suppressing an increase in vibration. .
  • the washing machine 1 can be made good. Further, even if the gap between the main body 2 and the outer tub 3 is made small, it is possible to suppress the collision between the entire 2 and the outer tub 3 by the vibration, and therefore the main body 2 can be reduced with respect to the outer tub 3, and the entire washing machine 1 can be miniaturized. . Further, in the case where the size of the main body 2 is maintained and the outer tub 3 is increased, the washing capacity can be increased without changing the size of the entire washing machine 1.
  • the tension spring 6 Pressurization setting device 7 for pressurizing Fp the tension spring 6 Pressurization setting device 7 for pressurizing Fp.
  • the spring end restricting portions 71 and 71 provided at both ends of the tension spring 6 and the restricting shaft body 72 provided inside the tension spring 6 constitute a pressurizing setting device 7 by which the tension spring is managed.
  • the amount of elongation of 6 can be suitably imparted to the pressurized Fp.
  • tension spring 6 and the pressurizing setting device 7 can be handled as a unit that is integrally configured, the management and assembly of the components can be easily performed.
  • the vibration restricting member 81 and the tension spring 6 are connected by the string member 82, the tension spring 6 does not cause elongation when the pressure Fp is exceeded, and assembly can be performed more easily.
  • the vibration restricting member 81 is formed in a ring shape, even when the outer groove 3 is displaced in an arbitrary direction intersecting the rotation axis Ra, the amount of displacement in the horizontal direction exceeds the gap E, and the outer groove 3 can be vibrated.
  • the restricting member 81 is displaced in contact with each other. Therefore, by the action of one tension spring 6 or a plurality of tension springs 6 to 6 on the opposite side to the displacement direction, the elastic support strength of the support outer groove 3 can be changed, and the natural vibration number can be shifted.
  • FIG. 6 corresponds to Fig. 1 of the first embodiment described above, and is a longitudinal sectional view showing a washing machine 201 according to a second embodiment of the present invention.
  • FIG. 8(a) corresponds to FIG. 2(a) of the first embodiment described above. That is, Fig. 8(a) is a cross-sectional view taken along line A-A in Fig. 6, and Fig. 6 is a cross-sectional view taken along line B-B in Fig. 8(a).
  • the washing machine 201 shown in Fig. 6 and Fig. 8(a) is the same as the washing machine 1 shown in the first embodiment (Figs. 1 to 5) except for the configuration described later. Therefore, the same portions are denoted by the same symbols. and The description is omitted.
  • the washing machine 201 does not include a member corresponding to the vibration restricting member 81 (see FIG. 1) of the first embodiment, and the displacement transmitting device 208 is composed of four string members 282 to 282. Further, one end of each of the string members 282 to 282 is attached to the fixing members 236 to 236 which are integrally provided at the upper four portions of the outer peripheral surface 32a of the side plate 32 constituting the outer tub 3.
  • the string members 282 to 282 are made of a metal wire such as a metal that is not easily stretched, and because of the flexibility, the force is transmitted only in the stretching direction, and almost no force is transmitted in the compression direction.
  • the other ends of the string members 282 to 282 are connected to the main body 2 via a tension spring 6 to which the pressurizing setting device 7 is attached. At this time, since the length of each of the string members 282 to 282 has a margin, the tension springs 6 to 6 do not cause elongation beyond the pressurization setting.
  • the outer groove 3 vibrates largely and the displacement e becomes a predetermined value or more, the displacement is transmitted to the tension spring 6 through the string member 282 constituting the displacement transmission device 208, and the tension spring 6 can function externally.
  • the groove 3 pulls back the force in the opposite direction of the displacement. Therefore, as in the case of the first embodiment, by changing the elastic support strength of the outer tub 3 abruptly, the natural vibration number can be shifted and the vibration can be reduced.
  • the displacement transmission device 208 is constituted by the string member 282, the structure can be simplified and the manufacturing cost can be reduced as compared with the case of the first embodiment.
  • Fig. 9 is a longitudinal sectional view showing a washing machine 301 according to a third embodiment of the present invention, corresponding to Fig. 1 of the first embodiment. Furthermore, Fig. 10 corresponds to Fig. 2(a) of the first embodiment described above. That is, Fig. 10 is a cross-sectional view taken along line A-A in Fig. 9, and Fig. 9 is a cross-sectional view taken along line B-B in Fig. 10.
  • the washing machine 301 shown in FIG. 9 and FIG. 10 is the same as the washing machine 1 shown in the first embodiment (FIGS. 1 to 5) except for the configuration described below. Therefore, the same portions are denoted by the same reference numerals and the description thereof will not be repeated. In addition, a part of the displacement transmission device 308 which will be described later is omitted in FIG.
  • the washing machine 301 does not include a member corresponding to the vibration restricting member 81 (see FIG. 1) of the first embodiment, and the displacement transmitting device 308 is constituted by the strip bodies 381 to 381.
  • Four tension springs 6 to 6 are provided on the outer circumference of the outer tub 3, and pressurizing setting devices 7 to 7 that are integrally formed with the tension springs 6 to 6 to pressurize the tension springs 6.
  • a flexible strip-shaped body 381 is connected to both ends of the tension springs 6 to 6, respectively.
  • FIG. 11(a) shows only one tension spring 6 provided on the washing machine 301 of Fig. 10 and is simplified.
  • FIG. 11(b) shows an enlarged view of the periphery of the tension spring 6 in FIG. 11(a).
  • the tension spring 6 is placed on the pedestal 336 provided on the outer peripheral surface 32a of the outer tub 3, and is restrained in the vertical direction.
  • One ends of the strip bodies 381, 381 are connected to the both ends of the tension spring 6, respectively.
  • the spring end regulating portion 71 constituting the pressurizing setting device 7 is fixed to both ends of the tension spring 6, and the strip-shaped body 381 is connected to the end portion of the tension spring 6 via the spring end restricting portion 71. Further, the other ends of the strips 381 and 381 are fixed to the corner portion 2a1 of the main body 2.
  • the tension spring 6 and the strip-shaped bodies 381 and 381 connected in series have a margin, and a predetermined gap is formed between the tension spring 6 and the outer peripheral surface 32a of the outer tub 3, and covers about 2/3 of the circumference of the outer tub 3. In this state, the tension spring 6 does not generate elongation beyond the pressurization setting.
  • FIGS. 12(a) and 12(b) show a state in which the outer tub 3 is displaced from the above-described state to the direction intersecting the rotation axis Ra (the lower left direction in the drawing).
  • the displacement e in the horizontal direction of the outer tub 3 is increased to a predetermined value or more, the strip-shaped body 381 fixed to the corner portion 2a1 in the opposite direction to the displacement direction is tensioned, and the outer groove 3 is transmitted to the tension spring 6.
  • the predetermined value set as the displacement amount required to transmit the displacement of the outer tub 3 to the tension spring 6 via the tensioned strip-shaped body 381 corresponds to the gap E (see FIG. 2) of the first embodiment.
  • the displacement is transmitted to the tension spring 6 by the belt-shaped body 381 constituting the displacement transmission device 308, and the tension spring 6 can function.
  • the outer groove 3 pulls back the force of the original position in the opposite direction of the displacement.
  • Four sets of such strips 381 and tension springs 6 are provided, and the outer grooves 3 are equally centered.
  • the displacement can be transmitted to the tension spring 6 even when the outer groove 3 is displaced in an arbitrary direction. Therefore, as in the case of the first embodiment, by changing the elastic support strength of the outer tub 3 abruptly, the natural vibration number can be shifted and the vibration can be reduced.
  • the strip body 381 and the tension spring 6 are only required to be provided at the minimum, and the same effect as described above can be obtained by arranging the strip body 381 as a center.
  • the displacement of the outer groove 3 is transmitted to the tension spring 6 by the displacement transmission device 308, and the extension spring 6 is extended, and the total length of the tension spring 6 is shortened as the outer groove 3 is restored to the original position.
  • the inner side of the strip 381 slides with the outer peripheral surface 32a of the outer tub 3 to generate frictional resistance, whereby the effect as a damper can also be obtained. Therefore, according to the present embodiment, by using the strip-shaped body 381, a larger vibration suppressing effect can be obtained.
  • the spring end regulating portion 71 provided at both ends of the tension spring 6 may be integrally formed by bending a part of the elastic material constituting the tension spring 6.
  • one of the spring end regulating portions 71 and 71 and the regulating shaft body 72 may be integrally formed.
  • restriction shaft body 72 can restrain the relative displacement of both ends of the tension spring 6 by being engaged with the spring end restriction portions 71 and 71, and can be configured to cover the inside of the tension spring 6 in addition to the inside.
  • the tubular shape of the outer circumference of the tension spring 6 or the configuration of a plurality of shaft bodies extending in parallel in the longitudinal direction outside the tension spring 6 is variously changed.
  • the vibration restricting member 81 is supported from the four corners (corner portions 2a1 to 2a) of the main body 2 via the four tension springs 6 to 6, but the tension springs 6 to 6 may be at least three. By arranging around the center of the vibration restricting member 81, the vibration restricting member 81 can be stably supported. Similarly, the vibration restricting member 81 may be supported by five or more tension springs 6 to 6.
  • the elastic supporting devices 5 to 5 are disposed below the tension springs 6 to 6, but it is not necessary to set such a positional relationship. That is, as long as the outer grooves 3 can be elastically supported by the elastic supporting devices 5 to 5, and the force generated by the tension springs 6 is applied when the displacement of the outer grooves 3 is increased to a predetermined value or more, they can be viewed in a plan view. Staggered configuration.
  • the strip-shaped bodies 381 and 381 are connected in series to both ends of one tension spring 6, and the outer tank 3 is surrounded by them.
  • the plurality of tension springs 6 may be connected via the strip-shaped body. 381 structure connected in series.
  • the inner tank that supports the outer tank 3 inside is used as the washing and dewatering tank 4
  • the present invention can be suitably used in the case where the inner tank is required to rotate at a high speed, and the above configuration can be applied even if the inner tank is a simple washing tank or a dewatering tank.
  • the axial direction of the outer tub 3 is set to the vertical direction, but the present invention can be applied similarly even in the manner of being inclined upward. Further, even in the drum type washing machine in which the axial direction of the outer tub 3 is horizontal, the above-described standard effect can be obtained by the present invention.

Landscapes

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

Abstract

本发明提供一种洗衣机，不仅能够适宜地抑制外槽的振动，而且通过设为简单的构造，可以使组装容易，实现制造成本的降低。该洗衣机具备相对于主体（2）弹性支承外槽（3）的弹性支承装置（5），其中，设有配置于外槽（3）和主体（2）之间且通过传递外槽（3）的位移而赋予用于使外槽（3）返回本来位置的反作用力的多个拉伸弹簧（6～6）、仅在外槽（3）的位移增大至规定值以上的情况下将外槽（3）的位移传递给拉伸弹簧（6～6）的位移传递装置（8）、以及设定拉伸弹簧（6）的加压（Fp）的加压设定装置（7）。

Description

洗衣机 技术领域
本发明涉及可抑制洗涤脱水槽旋转时的振动的洗衣机。
背景技术
目前，通常已知有如下结构的洗衣机，即，在形成为箱状的主体的内部支承有底圆筒状的外槽，在该外槽的内侧可旋转地支承作为内槽的洗涤脱水槽(例如参照专利文献1)。
在这样的一般的洗衣机中，经由包含弹簧而构成的悬架和吊挂其的吊棒将外槽在四个部位弹性支承于主体上，由此抑制动作时的振动。
在设为这种结构的情况下，外槽绕洗涤脱水槽的旋转轴振动的振动方式的低次固有振动数在比洗涤脱水槽的旋转速度低的区域出现。具体而言，在洗涤脱水槽的底部设置波轮(搅拌翼)，在脱水时在外槽的内部使洗涤脱水槽和波轮一体地高速旋转。在开始洗涤脱水槽的旋转使其增速的过程中，如果洗涤脱水槽的旋转速度与上述低次固有振动数一致，则振动暂时增大。随着进一步提高洗涤脱水槽的旋转速度，脱离低次固有振动数，振动减小，可以在所设定的旋转速度下稳定地动作。
但是，也认为在进入洗涤脱水槽的洗涤物有偏斜，绕旋转轴的不平衡量大的情况下，外槽的振动增大，特别是在低次固有振动数下，外槽大幅振动并与主体的内部接触。而且，由于洗衣机整体产生大的噪音、振动，从而洗衣机的设置场所周围的环境恶化，并且可能损伤构成洗衣机的部件。
为抑制上述的不良，通常考虑使外槽和主体之间具有一定以上的间隙来减少外槽和主体的碰撞。另外，还考虑在检测到过大的振动时进行停止旋转、或纠正洗涤物的偏斜的控制。
但是，在使外槽和主体之间具有一定以上的间隙的情况下，与主体相比，不得不使外槽小型化，在主体内部需要大的死区。另外，在通过控制来进行振动对策的情况下，需要振动检测装置及复杂的控制，导致成本增大。
因此，为解决上述问题，考虑使用下述专利文献2记载的技术。专利文献2 中公开有如下结构，即，在使洗衣机的外槽的外侧拥有余隙的状态下同轴配置环，且在该环的外侧设置板簧(参照段落0094、0095及图19D、19E)。该板簧在预先赋予加压使其位移的状态下由止动件保持，在位移至其以上而止动件的限制消失的情况下，可以作用包含加压量的大的弹簧力。
因此，专利文献2记载的技术中，在洗涤脱水槽的旋转速度接近低次固有振动数，外槽大幅振动并与环接触时，外槽为不仅由包含于上述悬架的弹簧弹性支承，而且还由设于环上的板簧弹性支承的状态，通过低次固有振动数变化，可以降低振动。
现有技术文献
专利文献
专利文献1：日本特开2011-240041号公报
专利文献2：日本特许第3984630号公报
发明所要解决的课题
但是，在上述专利文献2中，将板簧的一端固定，在赋予加压对其压缩(位移)的状态下通过止动件卡合另一端，同时使板簧的中央部附近与环抵接。这样，对板簧的两端赋予相对位移，赋予加压并同时使中央部与环抵接极其困难，为实现该情况需要进行实物吻合的微细的位置调整，因此，制造成本增大。
另外，如上述，因为需要微细的位置调整，所以用于支承板簧的机构及用于支承环的机构变动复杂，制造成本进一步增加。
发明内容
本发明以有效解决这样的课题为目的，具体而言，其目的在于，提供一种洗衣机，不仅可以适宜抑制外槽的振动，减小外槽和主体的间隙，而且还可以通过设为简单的构造使组装容易，实现制造成本的降低。
用于解决课题的技术方案
本发明为实现这样的目的，寻求如下的技术方案。
即，本发明提供一种洗衣机，其具备：形成有内部空间的主体、配置于该主体的内部空间的外槽、配置于该外槽的内部且被旋转自如地支承的内槽、设于所述外槽且使所述内槽旋转的电机、相对于所述主体弹性支承所述外槽的弹性支承装置，其特征在于，设有：多个拉伸弹簧，配置于所述外槽和所述主体之间，通过传递所述外槽的位移，赋予用于使该外槽返回本来位置的反作用力； 位置传递装置，仅在所述外槽的位移增大至规定值以上的情况下将该外槽的位移传递给所述拉伸弹簧；加压设定装置，设定所述拉伸弹簧的加压。
另外，本发明的特征在于，所述加压设定装置具备分别一体设于所述拉伸弹簧的两端的弹簧端限制部、和沿所述拉伸弹簧配置的限制轴体，在所述位移传递装置的位移未能传递的状态下，通过利用所述限制轴体的端部限制所述弹簧端限制部的相对位置，在容许所述拉伸弹簧的伸长的同时，赋予加压。
而且，本发明的特征在于，所述位移传递装置具备相对于所述外槽的外周设定规定的间隙配置的环状的振动限制部件、和用于支承其的绳状部件，将所述拉伸弹簧和所述绳状部件串联连接，经由这些拉伸弹簧及绳状部件将所述振动限制部件支承于所述主体。
另外，本发明的特征在于，所述位移传递装置是设于所述外槽的外周和所述主体之间的绳状部件，在所述外槽的位移为规定值以上的情况下，所述绳状部件张紧，对所述拉伸弹簧作用拉伸力。
进而，本发明的特征在于，所述位移传递装置具备带状体，该带状体包围所述外槽的外周的至少一部分，并且与该外槽的外周隔着规定的间隙配置，其端部连接于所述主体，将该带状体和所述拉伸弹簧串联连接。
发明效果
根据以上说明的本发明，在通过电机使内槽旋转时，在因旋转速度接近外槽的固有振动数而外槽大幅振动时，通过设于外槽的外周的弹性体与主体内部接触，可以使固有振动数变化，降低振动。
具体而言，外槽振动的振动方式的固有振动数依赖于支承外槽的弹性支承装置的弹性支承强度(弹簧常数)，由于旋转速度接近该固有振动数，从而外槽以大幅振动的状态振动，在外槽的位移成为规定值以上的情况下，经由位移传递装置向拉伸弹簧传递外槽的位移，由此，可以通过拉伸弹簧产生反作用力，并将其赋予外槽。此时，由于预先对拉伸弹簧赋予加压，所以相对于外槽产生大的反作用力。因此，通过外槽的弹性支承强度急剧变化，使固有振动数变化，可以抑制外槽的振动，可以使内槽进一步升速至规定的旋转频率。
这样，可以在振动过大之前降低起因于外槽的固有振动数的振动，可以使内槽增速至规定的旋转速度，因此，可以防止噪音或振动，可以抑制设置场所的环境恶化。另外，作为用于使外槽的弹性支承强度变化的弹性体，使用多个拉伸弹簧，因此，可以简单地实现赋予加压的结构，并且可以使调整容易，实 现制造成本的降低。
特别是，根据具体化了加压设定装置的结构的本发明，沿拉伸弹簧设置限制轴体，利用该限制轴体经由弹簧端限制部限制弹簧两端的相对位置，由此，不仅结构简单，并且可以在容许拉伸弹簧向伸长方向的变形的同时对拉伸弹簧赋予加压。
另外，根据位移传递装置具备环状的振动限制部件和绳状部件的本发明，只要位移量为规定值以上，则无论在外槽位移至哪一方向的情况下，都能够使拉伸弹簧的拉伸力作用于外槽，使弹性支承强度急剧变化，由此，可以不取决于振动的方向而快速实现振动的抑制。
另外，根据位移传递装置为设于外槽的外周和主体之间的绳状部件的本发明，在外槽的位移为规定值以上的情况下，经由绳状部件将外槽的位移传递至拉伸弹簧，并且可以使拉伸弹簧的拉伸力作用于外槽，不仅结构简单，并且可以在外槽振动时使弹性支承强度急剧变化而快速实现振动的抑制。
而且，根据位移传递装置具备包围外槽的外周的带状体的本发明，在外槽的位移为规定值以上的情况下，经由配置于外槽的外周的带状体向拉伸弹簧传递外槽的位移，并且可以使拉伸弹簧的拉伸力作用于外槽，不仅结构简单，并且可以在外槽振动时使弹性支承强度急剧变化而快速实现振动的抑制。另外，在外槽振动时在与带状体的内侧之间产生摩擦阻力，由此也可以实现振动的衰减，因此，可以得到更大的振动抑制效果。
附图说明
图1是表示本发明第一实施方式的洗衣机的纵剖图。
图2是图1的A-A剖面向视图。
图3是表示该洗衣机的加压设定装置的俯视图。
图4是示意性表示作用于该洗衣机的外槽的力的说明图。
图5是用于说明作用于该外槽的力和位移的关系的说明图。
图6是表示本发明第二实施方式的洗衣机的纵剖图。
图7是表示洗涤脱水槽从图6的状态位移的状态的纵剖图。
图8是图6的A-A剖面向视图。
图9是表示本发明第三实施方式的洗衣机的纵剖图。
图10是图9的A-A剖面向视图。
图11是表示从图10的状态拆下带状体的一部分而简化的状态的图。
图12是表示洗涤脱水槽从图11的状态位移的状态的图。
具体实施方式
下面，参照附图说明本发明的实施方式。
<第一实施方式>
图1是表示本发明第一实施方式的洗衣机1的纵剖面图，图2(a)是图1所记载的A-A位置的剖面向视图。但是，图1表示图2(a)的B-B位置、即对角位置的剖面。另外，图2(b)如后述表示外槽3位移的状态。这些图1、2所记载的洗衣机1表示概略结构，与本发明无关的部分省略。另外，图2中，省略图1中记载的后述的弹性支承装置5。
该洗衣机1具备主体2、外槽3、作为内槽的洗涤脱水槽4、弹性支承装置5～5。
主体2具备内部空间2a，该内部空间将俯视下大致正方形状的下板22、从其缘部立起的形成四面的侧板21～21、与其上部连接的上板23一体构成为大致长方体状，通过由它们包围而形成大致长方体状。
侧板21及下板22由金属板形成，上板23由树脂形成。下板22在其下面的四角附近具有可将主体2设于地板面上的脚22a～22a。在上述上板23上设置可使洗涤物出入洗涤脱水槽4的大致圆形的开口23a。另外，上板23可从侧板21拆装，由此可以容易地将外槽3装入主体2的内部空间2a。此外，上板23也可以与用于进行洗衣机1的操作的操作面板一体构成。
外槽3由具备耐热性的合成树脂成型，为具有俯视下大致圆形的底板31和从底板31的缘部立起的侧板32的有底圆筒状的部件。外槽3通过弹性支承装置5在主体2的内部空间2a吊挂，且在侧板32的下部的四个部位具备用于安装弹性支承装置5的卡合部33。
洗涤脱水槽4由金属形成，为具有俯视下大致圆形的底板41和从底板41的缘部立起的侧板42的有底圆筒状的部件。洗涤脱水槽4在外槽3的内部与该外槽3同轴配置，并且由外槽3旋转自如地支承。在侧板42及底板41上设置未图示的多个开口，可通过该开口排出洗涤脱水槽4内的水。
洗涤脱水槽4通过电机34使朝向底板31的上面侧延伸的驱动轴35旋转而进行旋转。另外，电机34经由未图示的传递装置也向设于洗涤脱水槽4的底板 41中央的波轮(搅拌翼)43赋予驱动力，使波轮43旋转。因此，洗衣机1可以在洗涤时主要仅使波轮43旋转，在脱水时使洗涤脱水槽4和波轮43一体地高速旋转。
波轮43的旋转的中心和洗涤脱水槽4的旋转的中心设定与沿竖直方向配置的同一旋转轴Ra。此外，旋转轴Ra也通过洗涤脱水槽4的底板41的中心、及外槽3的底板31的中心。
弹性支承装置5～5悬挂外槽3。本实施方式中，弹性支承装置5～5设置四个，分别由吊棒51和安装于其前端的悬架52构成。悬架52具有外筒53和配置于其内部的压缩螺旋弹簧54。在主体2上，在其内部空间2a上部的四角2a1～2a1(参照图2)分别设置吊棒安装部24～24，且在各吊棒安装部24～24安装吊棒51的基端侧。进而，悬架52的外筒53在钩挂于上述外槽3的卡合部33的状态下与该卡合部33卡合。这样，外槽3通过四个弹性支承装置5～5在内部空间2a内吊挂。
各弹性支承装置5的压缩螺旋弹簧54通过外槽3的重量压缩，产生反作用力，并且，在吸收位移的同时，弹性支承外槽3。另外，四个弹性支承装置5～5分别从斜方向吊挂外槽3，由此协动地实现用于使外槽3位于主体2的中央方向的保持平衡的作用。
即，弹性支承装置5不仅产生悬架52的压缩螺旋弹簧54的弹性，而且还可以通过其位置关系，产生使吊挂的外槽3恰如振子那样返回中心的恢复力。因此，外槽3在从中心位置位移的情况下，由弹性支承装置5得到与其位移量相对应的恢复力，并通过该恢复力返回主体2的中心位置。
在此，如上述，通过利用弹性支承装置5弹性地支承外槽3，与外槽3绕旋转轴Ra振动的振动方式相对应的低次固有振动数在约2～3Hz程度的非常低的旋转速度区域出现。洗衣机1中最容易产生振动的是洗涤脱水槽4与波轮43一同高速旋转的情况，通常，虽然以比上述低次固有振动数非常高的规定的运转速度旋转，但在起动后到升速的过程、或从上述运转速度减速的过程中，在洗涤脱水槽4的旋转速度与低次固有振动数一致或接近的情况下，外槽3以绕旋转轴Ra振动的方式大幅振动。另外，在进入洗涤脱水槽4的内部的洗涤物有偏斜的情况下，其成为绕旋转轴Ra的不平衡，加振力增加，外槽3的振动进一步增大。
因此，本实施方式的洗衣机1为将外槽3的振动抑制地小，如图1、图2(a) 所示，还具备：通过传递外槽3的位移，赋予用于使外槽3返回本来位置的反作用力的四个拉伸弹簧6～6；仅在外槽3的位移增大至规定值以上的情况下将该外槽3的位移传递给拉伸弹簧6的位移传递装置8；设定拉伸弹簧6的加压的加压设定装置7。
各拉伸弹簧6～6由于配置在容易成为死区的主体2的角部2a1，所以可以具有用于抑制振动的功能，并且可以抑制装置整体的大型化。
位移传递装置8由形成环状的振动限制部件81和用于支承该振动限制部件81的四个绳状部件82～82构成。振动限制部件81可以由金属或树脂形成。绳状部件82利用难以伸缩的金属制的金属线构成，由于具有挠性，从而仅在拉伸方向进行力的传递，在压缩方向几乎不会产生力的传递。
绳状部件82～82，其一端连接于振动限制部件81的四个部位，另一端与上述拉伸弹簧6～6的一个分别连接。另外，各拉伸弹簧6～6连接于主体2的角部2a1～2a1。因此，振动限制部件81经由拉伸弹簧6～6及绳状部件82～82由主体2的四角(角部2a1～2a1)支承。振动限制部件81在外槽3的上部附近与外槽3同轴配置，且在与外槽3的外周面32a之间遍及全周形成大致均等的间隙E。
图3是表示拉伸弹簧6及加压设定装置7的剖面图。具体而言，图3(a)表示拉伸弹簧6处于自然长度L的状态的情况。而且，图3(b)表示对拉伸弹簧6的两端赋予成为拉伸力的加压Fp而伸长ΔL并保持其长度的状态。
本实施方式中使用的拉伸弹簧6使用由金属线圈构成的拉伸螺旋弹簧，在该拉伸弹簧6的两端分别一体地设置弹簧端限制部71、71，在拉伸弹簧6的内部，沿拉伸弹簧6的长度方向设置限制轴体72。此外，如果为相对于拉伸力产生反作用力的弹簧，则代替拉伸弹簧，也可以利用其它弹性体作为拉伸弹簧6。
弹簧端限制部71分别具备圆板部71a和从该圆板部71a朝向外方伸出的圆环状的安装部71b。上述圆板部71a在插入构成拉伸弹簧6的端部的螺旋的内部之后进行固定，可以与拉伸弹簧6的端部一同进行位移。在配置于拉伸弹簧6的两端的各弹簧端限制部71、71的一方，利用圆环状的安装部71b安装上述绳状部件82(参照图2)，在弹簧端限制部71、71的另一方，利用安装部71b安装主体2的角部2a1(参照图2)。由此，如图2所示，经由拉伸弹簧6～6及绳状部件82～82，由主体2的四角(角部2a1～2a1)支承振动限制部件81。
返回图3(b)，通过在拉伸弹簧6的内部插入限制轴体72，利用该限制轴 体72限制弹簧端限制部71、71的圆板部71a、71a彼此的相对位置。由此，可以经由弹簧端限制部71、71给予拉伸弹簧6加压Fp，并将其在比自然长度L伸长ΔL的状态保持。即，弹簧端限制部71、71及限制轴体72作为用于对拉伸弹簧6设定加压Fp的加压设定装置7起作用。此外，由于在通常密集卷绕的拉伸螺旋弹簧上产生初期张力，不赋予超过该初期张力的力就不会产生伸长，因此，在将该初期张力作为上述的加压Fp利用的情况下，也可以设为不使用限制轴体72的结构。
图3(c)表示从图3(b)的状态使拉伸弹簧6进一步伸长的状态。如该图所示，加压设定装置7在对拉伸弹簧6的两端赋予超过加压Fp的力的情况下，可以使拉伸弹簧6伸长。即，加压设定装置7在容许拉伸弹簧6向伸长方向的变形的同时，限制向以设定了加压Fp的状态为基准缩短的方向的变形。
这样，不仅利用通过加压设定装置7赋予了加压的四个拉伸弹簧6～6，而且还如图1及图2(a)所示，利用与拉伸弹簧6～6串联连接的绳状部件82～82支承振动限制部件81。此时，由于各绳状部件82～82的长度拥有极小余裕，从而即使在支承着振动限制部件81的状态下，各拉伸弹簧6～6也不会产生超过加压设定时的伸长。
使用图2(b)，如上述，振动限制部件81相对于外槽3的外周拥有间隙E而配置，因此，如果外槽3向水平方向(图中的例中为右下方向)以间隙E以上大幅位移，则外槽3的外周面32a与振动限制部件81抵接。此时，经由构成位移传递装置8的振动限制部件81及绳状部件82向位于外槽3的位移方向的相反侧(图中的例中为左上)的拉伸弹簧6传递外槽3的位移。此外，安装于该绳状部件82的相反侧的绳状部件82即使松弛增加，也不会对与其连接的拉伸弹簧6带来力。
在通过传递外槽3的位移，拉伸弹簧6上稍微产生以加压设定时为基准的伸长的情况下，通过解除加压设定装置7的限制，迄今为止加压设定装置7所负担的加压Fp量作用于拉伸弹簧6的两端，可经由振动限制部件81赋予将外槽3拉回与位移相反的本来的位置的力。
图4(a)、(b)示意性表示本实施方式的洗衣机1的构造。下面，参照图1，使用图4(a)、(b)说明作用于洗衣机1的外槽3的力。
首先，外槽3通过由上述的四个弹性支承装置5～5吊挂，根据从中心的位移e产生用于使外槽3返回中心的恢复力k·e。在此，k是将由弹性支承装置5～ 5在中心方向作用的恢复力看作是弹力的情况(参照图4(a))下的弹簧常数。弹簧常数k也可以说是用于弹性支承外槽3的弹性支持强度。
另外，在设外槽3的质量为M，外槽3绕离开重心位置Cg距离(位移)e的旋转中心Cr进行振动运动的情况下，产生朝向外径方向的惯性力(离心力)M·ω2·e。在此，ω是外槽3振动时的角频率，与洗涤脱水槽4旋转时的角频率ω相等。另外，在将洗涤脱水槽4(参照图2)那样的外槽3的内部的旋转部分的不平衡设为Δm，将距旋转中心Cr的距离设为r时，该不平衡引起的惯性力(离心力)为Δm·r·ω2。
因此，在从这些考虑到力的均衡的情况下，得到下式的关系。
M·ω2·e+Δm·r·ω2＝k·e···式(1)
将其变形后，得到下式。
e＝Δm·r·ω2/(M·ω2-k)···式(2)
根据式(2)，在成为满足M·ω2-k＝0的旋转速度的情况下，位移e极大，即成为振动增大的共振状态。
另外，如果将式(1)的左边产生的力设为惯性力Fi、将右边产生的弹簧力设为Fk，则可以如下表示。
Fi＝M·ω2·e+Δm·r·ω2···式(3)
Fk＝k·e···式(4)
图5是将振幅(位移)e设为横轴，将包含惯性力Fi或弹簧力Fk的振动力F设为纵轴来表示上式的关系的图表。图中所示的直线L1～L10是表示式(3)的关系的惯性特性直线，直线La是表示式(4)的关系的弹簧特性直线，它们的交点表示角频率ω时的振幅(位移)e和振动力F。
就惯性特性直线L1～L10而言，倾斜与角频率ω的平方成比例，与横轴的切片(交点)由Δm·r/M表示。惯性特性直线L1～L10分别以使角频率ω的大小不同的方式记载，表示的是随着角频率ω增大，从直线L1起如L2、L3、…L10那样振幅e和惯性力Fi的关系发生变化。因此，各惯性特性直线L1～L10和弹簧特性直线La的交点显示每角频率ω的振幅e和振动力F的关系。
使洗涤脱水槽4(参照图1)起动，在考虑角频率ω增大的过程的情况下，振幅e和振动力F如下变化。
首先，在成为与惯性直线L1相对应的角频率ω的情况下，产生与惯性特性直线L1和弹簧特性直线La的交点P1相对应的振幅e和振动力F。在角频率ω 增大，与惯性特性直线L2相对应的情况下，产生与惯性特性直线L2和弹簧特性直线La的交点P2相对应的振幅e和振动力F。进而，在角频率ω增大，与惯性特性直线L3相对应的情况下，产生与惯性特性直线L3和弹簧特性直线La的交点P3相对应的振幅e和振动力F。在角频率ω从该状态进一步增大并欲过渡到惯性直线L4的状态的情况下，与和惯性特性直线La的交点相对应的振幅e非常大。
但是，如上述，在本实施方式中，在外槽3和主体2之间，经由间隙E设置构成位移传递装置8的振动限制部件81，通过将该振动限制部件81经由绳状部件82及拉伸弹簧6与主体2连接，通过拉伸弹簧6的作用，将外槽3以更强的力拉回中心方向。此时，通过加压设定装置7预先给予拉伸弹簧6加压Fp，因此，在产生极小的伸长的情况下，解除加压设定装置7的限制，追加加压Fp的量作用于外槽3。即，在外槽3大幅振动并位移了间隙E以上的情况下，由于含有加压Fp，从而特别大的弹簧力作用，弹簧常数k表观上增大。即，弹簧特性直线La在振幅e为间隙E以上的区域，向倾斜更大的弹簧特性直线Lb过渡。
由此，成为与惯性直线L4和弹簧特性直线Lb的交点P4相对应的振幅e和振动力F，振幅e急剧减小。这表示的是外槽3的低次固有振动数因拉伸弹簧6的作用而发生变化，由于与角频率ω产生错位，所以振动降低。
通过使振幅e比间隙E小，外槽3的低次固有振动数再次还原，但此时，角频率ω比低次固有振动数大，不会再次产生共振，可以维持振幅e小的状态。即，即使角频率ω增大且如惯性直线L5、L6那样移动，如与弹簧特性直线La的交点P5、P6所示，振幅e也不会超过间隙E，可以维持小的水平。
此外，弹簧特性直线Lb未必要通过原点，只要表观上的弹簧常数k处于急剧增大的关系即可。即，如果将加压Fp设定地非常大，则也可以适宜变更赋予加压Fp时的伸长量ΔL或间隙E(参照图2)的大小。
如上述，在外槽3和主体2之间，经由间隙E设置构成位移传递装置8的振动限制部件81，且将该振动限制部件81经由绳状部件82及拉伸弹簧6与主体2连接，因此，在使洗涤脱水槽4旋转并增速至规定的运转速度的期间，角频率ω、即旋转速度与外槽3的低次固有振动数接近，在超过间隙E而振幅e增大的情况下，外槽3与振动限制部件81抵接。经由绳状部件82与振动限制部件81连接的拉伸弹簧6被限制在预先赋予了加压Fp的状态下向缩短的方向的位移，在产生了以该状态为基准的伸长的情况下，追加加压Fp量并作用于两 端，因此，可以使低次固有振动数大幅变化，由此可以降低振动。另外，在振幅e比间隙E小的情况下，低次固有振动数还原，洗涤脱水槽4的旋转速度增大，成为已从低次固有振动数离开的状态，由此可以抑制振动的增大。
因此，可以将振动及噪音抑制地极小，可以使洗衣机1的设置场所周边的环境良好。另外，即使减小主体2和外槽3的间隙，也能够抑制因振动而整体2和外槽3激烈地碰撞损伤，因此，可以相对于外槽3减小主体2，使洗衣机1整体小型化。另外，在保持主体2的尺寸而增大外槽3的情况下，可以不改变洗衣机1整体的尺寸而增大洗涤容量。
而且，在外槽3的位移增大的情况下，得到不仅弹性支承装置5～5，而且外槽3也返回中心方向的恢复力，因此，可以简单地构成用于通过利用拉伸弹簧6而赋予加压Fp的加压设定装置7。具体而言，由设于拉伸弹簧6的两端的弹簧端限制部71、71和设于拉伸弹簧6的内部的限制轴体72构成加压设定装置7，通过利用它们管理拉伸弹簧6的伸长量，可以适宜赋予加压Fp。而且，也可以在拉伸弹簧6的两端容许向伸长方向的相对位移，同时限制向比加压设定时更短的方向的位移。
另外，由于也可以将拉伸弹簧6和加压设定装置7作为一体构成的单元进行处理，所以也可以容易地进行零件的管理及组装。
另外，由于利用绳状部件82将振动限制部件81和拉伸弹簧6连接，所以拉伸弹簧6不会产生超过加压Fp时的伸长，可以更容易地进行组装。
而且，由于振动限制部件81构成为环状，所以即使外槽3向与旋转轴Ra交叉的任意方向位移的情况下，由于向水平方向的位移量超过间隙E，从而外槽3也可以与振动限制部件81相接触地位移。因此，通过位移方向的相反侧的一个拉伸弹簧6、或多个拉伸弹簧6～6的作用，可以变更支承外槽3的弹性支承强度，使固有振动数错开。
<第二实施方式>
图6与上述的第一实施方式的图1相对应，是表示本发明第二实施方式的洗衣机201的纵剖面图。另外，图8(a)与上述的第一实施方式的图2(a)相对应。即，图8(a)是图6中的A-A位置的剖面图，图6是图8(a)中的B-B位置的剖面图。
这些图6及图8(a)所示的洗衣机201除后述的结构之外，与第一实施方式(图1～图5)所示的洗衣机1相同，因此，对于相同的部分标注同一符号并 省略说明。
洗衣机201不具备相当于第一实施方式的振动限制部件81(参照图1)的部件，位移传递装置208由四个绳状部件282～282构成。而且，各绳状部件282～282的一端被安装在一体设于构成外槽3的侧板32的外周面32a的上部四个部位的固定部件236～236上。绳状部件282～282利用不易伸长的金属制等的金属丝构成，由于具备挠性，从而仅在拉伸方向进行力的传递，在压缩方向几乎不会产生力的传递。
进而，绳状部件282～282的另一端经由安装有加压设定装置7的拉伸弹簧6与主体2连接。此时，由于各绳状部件282～282的长度拥有余裕，从而各拉伸弹簧6～6不会产生超过加压设定时的伸长。
图7及图8(b)表示外槽3从上述的状态向与旋转轴Ra交叉的方向位移的状态。在外槽3向水平方向的位移e增大至预先决定的规定值以上的情况下，位移方向的相反侧的绳状部件282张紧，向拉伸弹簧6传递外槽3的位移。此时，安装于张紧的绳状部件282的相反侧的绳状部件282即使松弛增加，也不会对外槽3带来力。此外，作为为经由张紧的绳状部件282将外槽3的位移向拉伸弹簧6传递所需的位移量设定的上述规定值相当于第一实施方式的间隙E(参照图2)。
通过上述那样构成，在外槽3大幅振动，其位移e成为规定值以上的情况下，该位移通过构成位移传递装置208的绳状部件282传递到拉伸弹簧6，拉伸弹簧6可以作用将外槽3拉回位移的相反方向的力。因此，与第一实施方式的情况相同，通过使外槽3的弹性支承强度急剧变化，可以错开固有振动数，降低振动。
另外，由于位移传递装置208由绳状部件282构成，所以相较于第一实施方式的情况，可以将结构更加简单化，且也可以实现制造成本的降低。
<第三实施方式>
图9与上述的第一实施方式的图1相对应，是表示本发明第三实施方式的洗衣机301的纵剖面图。进而，图10与上述的第一实施方式的图2(a)相对应。即，图10是图9中的A-A位置的剖面图，图9是图10中的B-B位置的剖面图。
这些图9及图10所示的洗衣机301除后述的结构以外，与第一实施方式(图1～图5)所示的洗衣机1相同，所以对相同的部分标注相同的符号并省略说明。 此外，图9中省略记载后述的位移传递装置308的一部分。
洗衣机301不具备与第一实施方式的振动限制部件81(参照图1)相当的部件，而位移传递装置308由带状体381～381构成。在外槽3的外周设置四个拉伸弹簧6～6、和通过与该拉伸弹簧6～6一体构成而赋予拉伸弹簧6加压的加压设定装置7～7。在这些拉伸弹簧6～6的两端分别连接具有挠性的带状体381。
图11(a)仅设置一个图10的洗衣机301上设置的拉伸弹簧6并简化表示。另外，图11(b)将图11(a)中的拉伸弹簧6的周边放大表示。
如图11(a)、(b)所示，拉伸弹簧6由于被配置在设于外槽3的外周面32a的台座336上，从而在上下方向被限制位置。在拉伸弹簧6的两端分别连接带状体381、381的一端。更具体而言，在拉伸弹簧6的两端固定构成加压设定装置7的弹簧端限制部71，经由该弹簧端限制部71将带状体381与拉伸弹簧6的端部连接，进而将各带状体381、381的另一端固定于主体2的角部2a1。
拉伸弹簧6及与其串联连接的带状体381、381的长度拥有余裕，它们在与外槽3的外周面32a之间设定规定的间隙，覆盖外槽3的周围的约2/3。在该状态下，拉伸弹簧6不产生超过加压设定时的伸长。
此外，不必由拉伸弹簧6及与其串联连接的带状体381、381覆盖外槽3的2/3，而只要通过所有的拉伸弹簧6～6(参照图10)进行向与旋转轴Ra正交的全方向的限制即可。
图12(a)及图12(b)表示外槽3从上述的状态向与旋转轴Ra交叉的方向(图中的左下方向)位移的状态。在外槽3向水平方向的位移e增大至预先决定的规定值以上的情况下，固定于位移方向的相反方向的角部2a1的带状体381张紧，向拉伸弹簧6传递外槽3的位移。此外，作为为经由张紧的带状体381向拉伸弹簧6传递外槽3的位移所需的位移量设定的上述规定值与第一实施方式的间隙E(参照图2)相当。
在拉伸弹簧6以加压设定时为基准稍微伸长，两端的弹簧端限制部71、71的相对位置位移的情况下，限制轴体72和弹簧端限制部71、71进行的限制被解除，追加加压Fp的量作用于两端的带状体381、381。
通过如上述那样构成，在外槽3大幅振动，其位移量成为规定值以上的情况下，该位移通过构成位移传递装置308的带状体381向拉伸弹簧6传递，拉伸弹簧6可以作用将外槽3拉回位移的相反方向的本来位置的力。由于具备四组这样的带状体381及拉伸弹簧6(参照图10)，且以外槽3为中心均等地配 置，从而即使在外槽3向任意的方向位移的情况下，也能够将其位移传递给拉伸弹簧6。因此，与第一实施方式的情况相同，通过使外槽3的弹性支承强度急剧变化，可以错开固有振动数，降低振动。此外，带状体381及拉伸弹簧6只要最低设置两组即可，通过以旋转轴Ra为中心对置配置，可以得到与上述相同的效果。
另外，在通过位移传递装置308将外槽3的位移传递给拉伸弹簧6，拉伸弹簧6伸长的过程、进而在伴随外槽3恢复到本来的位置而拉伸弹簧6的全长缩短的过程中，带状体381的内侧与外槽3的外周面32a滑动而产生摩擦阻力，由此也可以得到作为缓冲器的效果。因此，如本实施方式，通过使用带状体381，可以得到更大的振动抑制效果。
以上，说明了本发明的实施方式，但各部分的具体的结构不仅仅限定于上述的实施方式。
例如，设于拉伸弹簧6的两端的弹簧端限制部71也可以通过将构成拉伸弹簧6的弹性材料的一部分折弯而一体构成。
另外，也可以将弹簧端限制部71、71的一方和限制轴体72构成为一体。
进而，限制轴体72只要通过与弹簧端限制部71、71卡合，可以限制拉伸弹簧6的两端的相对位移，就除设于拉伸弹簧6的内部之外，还可以以构成为覆盖拉伸弹簧6的外周的筒状、或由在拉伸弹簧6的外侧沿长度方向平行地延伸的多个轴体构成等各种方式变更。
在上述的第一实施方式中，振动限制部件81从主体2的四角(角部2a1～2a)经由四个拉伸弹簧6～6支承，但该拉伸弹簧6～6最低只要三个即可，通过绕振动限制部件81的中心配置，可以稳定地支承振动限制部件81。同样，也可以设为由五个以上的拉伸弹簧6～6支承振动限制部件81的结构。
在上述的第一实施方式及第二实施方式中，弹性支承装置5～5配置于拉伸弹簧6～6的下方，但未必要设为这样的位置关系。即，只要可以由弹性支承装置5～5弹性地支承外槽3，且在外槽3的位移增大至规定值以上的情况下作用拉伸弹簧6产生的力，就也可以将它们在俯视下相互错开配置。
上述的第三实施方式中，在一个拉伸弹簧6的两端串联地连接带状体381、381，由它们包围外槽3，但也可以设为将多个拉伸弹簧6经由带状体381串联连接的结构。
进而，在上述的实施方式中，将在内部支承外槽3的内槽作为洗涤脱水槽4 构成，但本发明在需要内槽高速旋转的情况下可以适宜利用，即使内槽是简单的洗涤槽或脱水槽，也可以应用上述结构。
而且，在上述的实施方式中，将外槽3的轴向设定为竖直方向，但即使为朝向斜上方的方式，也能够同样应用本发明。另外，即使是外槽3的轴向成为水平方向的滚筒式洗衣机，利用本发明也可以得到上述基准的效果。
附图标记说明
2...主体
2a...内部空间
2a1...角部
3...外槽
4...洗涤脱水槽(内槽)
5...弹性支承装置
6...拉伸弹簧
7...加压设定装置
8、208、308...位移传递装置
21a...(主体的)内表面
32a...(外槽的)外周面
34...电机
71...弹簧端限制部
72...限制轴体
81...振动限制部件
82...绳状部件
282...绳状部件
381...带状体
Fp...加压
Ra...旋转轴

Claims (5)

  1. 一种洗衣机，其具备：形成有内部空间的主体、配置于该主体的内部空间的外槽、配置于该外槽的内部且被旋转自如地支承的内槽、设于所述外槽且使所述内槽旋转的电机、以及相对于所述主体弹性支承所述外槽的弹性支承装置，其特征在于，
    设有：多个拉伸弹簧，配置于所述外槽和所述主体之间，通过传递所述外槽的位移，赋予用于使该外槽返回本来位置的反作用力；位置传递装置，仅在所述外槽的位移增大至规定值以上的情况下将该外槽的位移传递给所述拉伸弹簧；以及加压设定装置，设定所述拉伸弹簧的加压。
  2. 根据权利要求1所述的洗衣机，其特征在于，
    所述加压设定装置具备分别一体设于所述拉伸弹簧的两端的弹簧端限制部、和沿所述拉伸弹簧配置的限制轴体，
    在所述位移传递装置的位移未能传递的状态下，通过利用所述限制轴体的端部限制所述弹簧端限制部的相对位置，在容许所述拉伸弹簧的伸长的同时，赋予加压。
  3. 根据权利要求1或2所述的洗衣机，其特征在于，
    所述位移传递装置具备相对于所述外槽的外周设定规定的间隙配置的环状的振动限制部件、和用于支承其的绳状部件，将所述拉伸弹簧和所述绳状部件串联连接，经由这些拉伸弹簧及绳状部件将所述振动限制部件支承于所述主体。
  4. 根据权利要求1或2所述的洗衣机，其特征在于，
    所述位移传递装置是设于所述外槽的外周和所述主体之间的绳状部件，在所述外槽的位移为规定值以上的情况下，所述绳状部件张紧，对所述拉伸弹簧作用拉伸力。
  5. 根据权利要求1或2所述的洗衣机，其特征在于，
    所述位移传递装置具备带状体，该带状体包围所述外槽的外周的至少一部分，并且与该外槽的外周隔着规定的间隙配置，其端部连接于所述主体，将该带状体和所述拉伸弹簧串联连接。
PCT/CN2014/095722 2014-05-27 2014-12-30 洗衣机 WO2015180473A1 (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014109355A JP6426916B2 (ja) 2014-05-27 2014-05-27 洗濯機
JP2014-109355 2014-05-27

Publications (1)

Publication Number Publication Date
WO2015180473A1 true WO2015180473A1 (zh) 2015-12-03

Family

ID=54698032

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2014/095722 WO2015180473A1 (zh) 2014-05-27 2014-12-30 洗衣机

Country Status (2)

Country Link
JP (1) JP6426916B2 (zh)
WO (1) WO2015180473A1 (zh)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017107988A1 (zh) * 2015-12-24 2017-06-29 青岛海尔洗衣机有限公司 洗衣机
CN107663740A (zh) * 2016-07-28 2018-02-06 青岛海尔洗衣机有限公司 一种洗衣机减振组件及洗衣机
CN111684122A (zh) * 2017-12-08 2020-09-18 Lg电子株式会社 衣物处理装置
CN111684123A (zh) * 2017-12-08 2020-09-18 Lg电子株式会社 衣物处理装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101683402B1 (ko) * 2015-12-24 2016-12-06 엘지전자 주식회사 스태빌라이저 및 이를 구비한 세탁물 처리 기기

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6129392A (ja) * 1984-07-18 1986-02-10 松下電器産業株式会社 脱水洗濯機の防振装置
JPS6315998A (ja) * 1986-07-04 1988-01-23 松下電器産業株式会社 洗濯機
JPS6395094A (ja) * 1986-10-08 1988-04-26 松下電器産業株式会社 脱水洗濯機の防振装置
JPS6395086A (ja) * 1986-10-08 1988-04-26 松下電器産業株式会社 洗濯機の防振装置
JPS63212400A (ja) * 1987-02-27 1988-09-05 松下電器産業株式会社 脱水洗濯機の防振装置
JPS63229094A (ja) * 1987-03-17 1988-09-22 松下電器産業株式会社 脱水洗濯機の防振装置
CN1508330A (zh) * 2002-12-17 2004-06-30 乐金电子(天津)电器有限公司 洗衣机的振动减弱装置

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6335291A (ja) * 1986-07-31 1988-02-15 松下電器産業株式会社 洗濯機の防振装置
JPS63132687U (zh) * 1987-02-20 1988-08-30
EP1666763B1 (en) * 2003-09-10 2012-10-31 Sintokogio, Ltd. Device and method for damping vibration of rotating shaft system
KR101934735B1 (ko) * 2012-08-31 2019-01-03 엘지전자 주식회사 세탁기

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6129392A (ja) * 1984-07-18 1986-02-10 松下電器産業株式会社 脱水洗濯機の防振装置
JPS6315998A (ja) * 1986-07-04 1988-01-23 松下電器産業株式会社 洗濯機
JPS6395094A (ja) * 1986-10-08 1988-04-26 松下電器産業株式会社 脱水洗濯機の防振装置
JPS6395086A (ja) * 1986-10-08 1988-04-26 松下電器産業株式会社 洗濯機の防振装置
JPS63212400A (ja) * 1987-02-27 1988-09-05 松下電器産業株式会社 脱水洗濯機の防振装置
JPS63229094A (ja) * 1987-03-17 1988-09-22 松下電器産業株式会社 脱水洗濯機の防振装置
CN1508330A (zh) * 2002-12-17 2004-06-30 乐金电子(天津)电器有限公司 洗衣机的振动减弱装置

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017107988A1 (zh) * 2015-12-24 2017-06-29 青岛海尔洗衣机有限公司 洗衣机
CN108431323A (zh) * 2015-12-24 2018-08-21 青岛海尔洗衣机有限公司 洗衣机
CN108431323B (zh) * 2015-12-24 2020-11-06 青岛胶南海尔洗衣机有限公司 洗衣机
CN107663740A (zh) * 2016-07-28 2018-02-06 青岛海尔洗衣机有限公司 一种洗衣机减振组件及洗衣机
CN111684122A (zh) * 2017-12-08 2020-09-18 Lg电子株式会社 衣物处理装置
CN111684123A (zh) * 2017-12-08 2020-09-18 Lg电子株式会社 衣物处理装置
US11686039B2 (en) 2017-12-08 2023-06-27 Lg Electronics Inc. Clothes treatment apparatus
CN111684123B (zh) * 2017-12-08 2023-07-25 Lg电子株式会社 衣物处理装置
US11821134B2 (en) 2017-12-08 2023-11-21 Lg Electronics Inc. Clothes treatment apparatus

Also Published As

Publication number Publication date
JP6426916B2 (ja) 2018-11-21
JP2015223283A (ja) 2015-12-14

Similar Documents

Publication Publication Date Title
WO2015180473A1 (zh) 洗衣机
US20090151398A1 (en) Anti-vibration device
TW564276B (en) Drum washing machine
KR20140014331A (ko) 수직 펌프의 상승관의 진동을 제어하기 위한 장치 및 방법
CN108431323B (zh) 洗衣机
JP2007100929A (ja) 振動低減装置
CN107021406B (zh) 电梯装置
RU2533368C1 (ru) Виброизолятор с тросовым демпфером
US20190124437A1 (en) Damper and speaker apparatus
WO2015180478A1 (zh) 洗衣机
EP2504480A1 (en) Laundry treating machine provided with a vibration damper device
JP2015012804A (ja) ステータコアの支持システム
US8746016B2 (en) Suspension system for washing machines
JP2012249695A (ja) ドラム式洗濯機の防振装置
WO2014147931A1 (ja) 洗濯機
JP6233647B2 (ja) エレベータ用動吸振器
JP2002200392A (ja) 洗濯機の防振装置
JP2007320680A (ja) エレベータの防振装置
JP6646449B2 (ja) 立軸ポンプ
JP3688896B2 (ja) 洗濯機の槽体吊持装置
JPS6315998A (ja) 洗濯機
KR102098882B1 (ko) 세탁기의 진동·소음 저감 메커니즘
RU2538853C1 (ru) Виброизолятор кочетова
JP5261519B2 (ja) 洗濯機の振動吸収装置
CN109306599B (zh) 一种洗衣机防撞桶装置的设计方法

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 14892908

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 14892908

Country of ref document: EP

Kind code of ref document: A1