JP2000107488A - Device for isolating vibration of washing machine - Google Patents
Device for isolating vibration of washing machineInfo
- Publication number
- JP2000107488A JP2000107488A JP10286744A JP28674498A JP2000107488A JP 2000107488 A JP2000107488 A JP 2000107488A JP 10286744 A JP10286744 A JP 10286744A JP 28674498 A JP28674498 A JP 28674498A JP 2000107488 A JP2000107488 A JP 2000107488A
- Authority
- JP
- Japan
- Prior art keywords
- vibration
- coil spring
- compression coil
- washing machine
- elastic pipe
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Landscapes
- Main Body Construction Of Washing Machines And Laundry Dryers (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、洗濯機の外箱内に
槽体を弾性的に吊持する洗濯機の防振装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibration damping device for a washing machine in which a tub is elastically suspended in an outer box of the washing machine.
【０００２】[0002]
【従来の技術】従来、一般に全自動洗濯機の防振装置と
しては、外箱上部の四隅部から揺動自在な吊り棒を垂下
し、この吊り棒の下端部に装着した圧縮コイルばねを介
して、槽体を弾性支持する構成としている。2. Description of the Related Art Conventionally, as a vibration isolator of a fully automatic washing machine, a swingable hanging rod is hung from four corners of an upper part of an outer box, and a compression coil spring attached to a lower end of the hanging rod is used. Thus, the tank body is elastically supported.
【０００３】図１１及び図１２に、この種防振装置の一
実施例を示す。外箱１上部の四隅部（一箇所のみ図示説
明）には凹状の球面部２ａを有する補強板２を夫々設け
ていて、上端部に緩衝体３及び上部受け部材４を取着し
た吊り棒５を、上記補強板２の球面部２ａに上部受け部
材４を滑動可能に嵌合保持させることにより上端部を抜
け止め状態に挿着し、揺動可能に垂下している。この吊
り棒５は、途中槽体としての外槽６から水平方向に突設
された支持片部７を挿通し、その支持片部７の下面と吊
り棒５の下端部との間には、下端部に取着したワッシャ
８により抜け止め状態に装着さればね台座としても機能
する円盤状のダンパ部材９、その上方に圧縮コイルばね
１０及び筒状ダンパケース１１を一体に有する下部受け
部材１２を順に介して装着され、以って外槽６はその支
持片部７を介して吊り棒５にて揺動可能に吊持され、且
つ圧縮コイルばね１０にて弾性的に防振支持された構成
をなしている。FIGS. 11 and 12 show an embodiment of this type of vibration isolator. A reinforcing plate 2 having a concave spherical portion 2a is provided at each of the four corners (only one is shown and described) of the upper part of the outer box 1, and a suspension rod 5 having a buffer 3 and an upper receiving member 4 attached to an upper end thereof. The upper receiving member 4 is slidably fitted and held on the spherical surface portion 2a of the reinforcing plate 2 so that the upper end portion is inserted in a state where the upper receiving member 4 is not slipped off, and swings down. The suspension bar 5 is inserted through a support piece 7 projecting in a horizontal direction from an outer tank 6 as a middle tank body, and between the lower surface of the support piece 7 and the lower end of the suspension rod 5, A disk-shaped damper member 9 which is attached to a lower end portion by a washer 8 in a retaining state and also functions as a spring pedestal, and a lower receiving member 12 integrally including a compression coil spring 10 and a cylindrical damper case 11 above the disk-shaped damper member 9. The outer tub 6 is swingably hung by the hanging bar 5 via the support piece 7 and is elastically supported by the compression coil spring 10 for vibration isolation. Has made.
【０００４】さらにこの一例では、上記ダンパ部材９と
ダンパケース１１とは脱水運転中において略気密状態に
嵌合されて、所謂エアダンパ効果を発揮する構成とな
し、以って防振装置１３を構成している。すなわちダン
パ部材９は、図１２に拡大して示すように弾性部材製の
ダンパ基体１４，インサートされた補強体１５，ダンパ
基体１４に弾発力を付与するばね体１５及びダンパ基体
１４の外周側に加熱接着されたフッ素樹脂製の環状シー
ル体１７を具備してなり、以ってこのダンパ部材９を囲
繞しそのシール体１７と摩擦摺接する前記ダンパケース
１１とにより内部空間は略気密状態に封鎖される。た
だ、ダンパ部材９の中心部位には、吊り棒５が挿通する
周縁部において内外部を僅かに連通せしめる溝状の複数
個の空気抜き孔１８を形成している。Further, in this example, the damper member 9 and the damper case 11 are fitted in a substantially airtight state during the dewatering operation, so as to exhibit a so-called air damper effect. are doing. That is, as shown in an enlarged manner in FIG. 12, the damper member 9 includes a damper base 14 made of an elastic member, an inserted reinforcing member 15, a spring body 15 for applying elastic force to the damper base 14, and an outer peripheral side of the damper base 14. The inner space is made substantially airtight by the damper case 11 which surrounds the damper member 9 and is in frictional sliding contact with the seal body 17. Blocked. However, a plurality of groove-shaped air vent holes 18 are formed in the central portion of the damper member 9 at the peripheral edge portion where the hanging rod 5 is inserted to slightly communicate the inside and the outside.
【０００５】しかして上記防振装置１３を備えたもので
は、脱水運転時において高速回転する図示しない内槽の
内部に収容された被洗濯物のアンバランス配置に伴い振
動が発生し、吊り棒５に吊持された外槽６が振動する
が、この場合、脱水運転起動時には未だ多量の水分を含
んだ被洗濯物の重量的負荷が大きいため、大きな振動が
発生する。しかしながらこの振動は、外槽６を弾性支持
する圧縮コイルばね１０による振動吸収効果、及びダン
パ部材９のシール体１７とダンパケース１１との摺接す
る際の摩擦抵抗並びに特に圧縮コイルばね１０が圧縮さ
れダンパケース１１内の空気が圧縮されてダンパ部材９
の空気抜き孔１８から抜ける際の粘性抵抗による減衰
力、すなわちエアダンパ効果により振動を減衰し、外箱
１への振動伝達を抑制すると共に脱水運転に支障を来す
異常振動の発生を防いでいる。[0005] In the apparatus provided with the vibration isolator 13, vibration occurs due to the unbalanced arrangement of the laundry contained in the inner tub (not shown) which rotates at a high speed during the spin-drying operation. The outer tub 6 suspended in the washing machine vibrates. In this case, when the spin-drying operation is started, the laundry to be washed still contains a large amount of water, and the heavy load causes a large vibration. However, this vibration is caused by the vibration absorbing effect of the compression coil spring 10 elastically supporting the outer tub 6, the frictional resistance when the seal body 17 of the damper member 9 is in sliding contact with the damper case 11, and especially the compression coil spring 10 is compressed. The air in the damper case 11 is compressed and the damper member 9 is compressed.
Vibration is attenuated by viscous resistance at the time of exiting from the air vent hole 18, that is, the vibration is attenuated by the air damper effect, thereby suppressing the transmission of vibration to the outer case 1 and preventing the occurrence of abnormal vibration that hinders the dewatering operation.
【０００６】[0006]
【発明が解決しようとする課題】上記構成のエアダンパ
方式の防振装置１３によれば、脱水運転起動時の大きな
振動に対して効果的な振動減衰作用を発揮する。ところ
が、急激に圧縮された空気が空気抜き孔１８から抜ける
際に、その空気抜き音が騒音として発生し、且つ脱水運
転が起動時の不安定領域を乗り越え安定した脱水回転に
よる運転状態に至った、すなわち定常状態に至るとダン
パ部材９とダンパケース１１内の空気はピッチの速い小
刻みな振動に追従しきれず所謂空気ばねの働きをして、
床面への振動伝達力を大きくしてしまい、結果として騒
音への悪影響を及ぼすことになった。その対策として空
気抜き孔１８を大きくすれば上記騒音の問題は回避可能
であるが、これでは本来のエアダンパ効果が減少し、特
に脱水運転起動時の大きな振動に対処するに十分な減衰
力が得られない。According to the vibration damping device 13 of the air damper type having the above-described structure, an effective vibration damping effect is exerted against a large vibration at the start of the spin-drying operation. However, when the rapidly compressed air escapes from the air vent hole 18, the air bleeding noise is generated as noise, and the dehydration operation crosses over the unstable region at the time of startup and reaches an operation state by stable dehydration rotation, that is, When the steady state is reached, the air in the damper member 9 and the damper case 11 cannot fully follow the wiggle vibration at a high pitch and acts as a so-called air spring.
The vibration transmission force to the floor surface was increased, resulting in adverse effects on noise. The noise problem can be avoided by increasing the size of the air vent hole 18 as a countermeasure. However, this reduces the original air damper effect, and provides a sufficient damping force to cope with a large vibration particularly at the start of the dehydration operation. Absent.
【０００７】本発明は上述の事情に鑑みてなされたもの
であり、従ってその目的は、脱水運転の起動時及び定常
状態のいずれにあっても良好な防振機能を発揮し、振動
伝達や騒音に悪影響を及ぼすことのない洗濯機の防振装
置を提供するにある。SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and its object is to provide a good vibration damping function at both the start-up and the steady state of the dehydrating operation, and to transmit vibration and noise. An object of the present invention is to provide an anti-vibration device for a washing machine which does not adversely affect the washing machine.
【０００８】[0008]
【課題を解決するための手段】上記目的を達成するため
に本発明の洗濯機の防振装置は、第１に、洗濯機の外箱
内に吊り棒及び圧縮コイルばねを介して槽体を弾性的に
吊持する防振装置において、前記吊り棒に挿通せられ該
吊り棒と摺動摩擦接触するダンパ体を設け、このダンパ
体と前記圧縮コイルばねとで前記槽体を防振支持すると
共に、吊り棒にはダンパ体が摺動する範囲内にあって下
方が径大となるテーパ部を形成したことを特徴とする
（請求項１の発明）。SUMMARY OF THE INVENTION In order to achieve the above object, a vibration isolator of a washing machine according to the present invention comprises: first, a tub body is inserted into a casing of a washing machine via a hanging rod and a compression coil spring; In a vibration isolator that is elastically suspended, a damper body is provided that is inserted through the suspension rod and comes into sliding friction contact with the suspension rod, and the damper body and the compression coil spring support the tank body with vibration isolation. The suspension rod is formed with a tapered portion within a range in which the damper body slides and having a larger diameter at the lower portion (the invention of claim 1).
【０００９】斯かる構成によれば、被洗濯物のアンバラ
ンス配置に起因して槽体が大きく振動すると、吊り棒に
対しダンパ体が上下方向に摺動することによって、吊り
棒とダンパ体との摩擦抵抗、及びこの吊り棒とダンパ体
との摺接部分に塗布されたグリスの粘性抵抗などによる
減衰力が発生する。そして特に脱水運転起動時には、槽
体は脱水前の重量的負荷が大きいため圧縮コイルばねを
圧縮して降下した位置にあり、この状態での起動となる
からダンパ体が吊り棒と摺動する位置は、吊り棒の下方
部に設けたテーパ部領域と摺接することとなり、よって
起動時の大きな振動の動きに対応してその摩擦力による
減衰力もて大きく作用する。According to such a configuration, when the tub body vibrates largely due to the unbalanced arrangement of the laundry, the damper body slides vertically with respect to the hanging bar, so that the hanging bar and the damper body are connected to each other. And damping force due to the viscous resistance of grease applied to the sliding contact portion between the suspension rod and the damper body. In particular, when the dewatering operation is started, the tank body is in a position where it is compressed and lowered by compressing the compression coil spring because of a heavy weight load before dewatering, and the damper body is slid with the hanging rod because it is started in this state. Comes into sliding contact with the tapered region provided below the suspension rod, and accordingly, the damping force due to the frictional force acts greatly in response to a large vibration movement at the time of starting.
【００１０】従って、脱水起動時にはダンパ体は吊り棒
下方部の径大となるテーパ部との摺動により接触圧が増
すため、より大きな減衰力を発生して振動を抑制する。
一方、脱水運転の定常時における振幅の小さいピッチの
速い振動に対しては、ダンパ体は吊り棒の細い直線部分
との摺動となるため通常の摩擦力にて減衰力は低減し、
且つ主に圧縮コイルばねにより振動が吸収され、以って
振動伝達や騒音の発生を効果的に抑制できる。Therefore, at the start of dehydration, the contact pressure of the damper body is increased by sliding with the tapered portion having a large diameter at the lower part of the suspension rod, so that a larger damping force is generated to suppress vibration.
On the other hand, for steady vibration of the dehydration operation during fast vibration with a small amplitude, the damping body slides with the thin linear portion of the suspension rod, so the damping force is reduced by normal frictional force,
In addition, the vibration is mainly absorbed by the compression coil spring, so that the transmission of vibration and the generation of noise can be effectively suppressed.
【００１１】また、上記目的を達成するために本発明の
洗濯機の防振装置は、第２に、洗濯機の外箱内に吊り棒
及び圧縮コイルばねを介して槽体を弾性的に吊持する防
振装置において、前記吊り棒に挿通せられ該吊り棒と摺
動摩擦接触するダンパ体を設け、このダンパ体と前記圧
縮コイルばねとで前記槽体を防振支持すると共に、吊り
棒にはダンパ体が摺動する範囲のうちの下方部位の表面
粗さを摩擦係数が大となるように加工処理したことを特
徴とする（請求項２の発明）。In order to achieve the above object, the vibration isolator of the washing machine according to the present invention secondly elastically suspends the tub body through a suspension rod and a compression coil spring in an outer box of the washing machine. In the vibration isolator to be carried, a damper body is provided which is inserted through the hanging bar and comes into sliding friction contact with the hanging bar, and the tank body is vibration-isolated supported by the damper body and the compression coil spring. Is characterized in that the surface roughness of the lower part of the range in which the damper body slides is processed so as to increase the friction coefficient (the invention of claim 2).
【００１２】斯かる構成によれば、脱水起動時には槽体
は重量的負荷大のため降下した位置にあるため、起動時
の大きな振動に対しては吊り棒下方の摩擦係数大の部位
にてダンパ体と摺動し、大きな摩擦力を得て大きな減衰
力を発生し、振動を効果的に抑制する。そして定常時に
あっては通常のダンパ体と吊り棒の直線状部分での摩擦
となるため減衰力は低減し、且つ主に圧縮コイルばねに
よる振動吸収作用における防振作用によって振動伝達や
騒音発生を抑えることができる。[0012] According to such a configuration, since the tank body is in a lowered position due to a large weight load at the start of dehydration, the damper is provided at a portion having a large friction coefficient below the suspension rod against a large vibration at the start. Sliding with the body, generating a large frictional force and generating a large damping force, effectively suppressing vibration. During normal operation, the damping force is reduced due to friction between the normal damper body and the linear portion of the suspension rod, and the damping force is reduced. Can be suppressed.
【００１３】さらに、上記目的を達成するために本発明
の洗濯機の防振装置は、第３に、洗濯機の外箱内に吊り
棒及び圧縮コイルばねを介して槽体を弾性的に吊持する
防振装置において、前記吊り棒に挿通せられ該吊り棒と
摺動摩擦接触するダンパ体を設け、このダンパ体と前記
圧縮コイルばねとで前記槽体を防振支持すると共に、圧
縮コイルばねを粗巻部分と蜜巻部分とから構成し、この
粗巻部分にその外周面と摺動摩擦接触し且つ粗巻部分相
当長の筒状弾性パイプを被嵌したことを特徴とする（請
求項３の発明）。Further, in order to achieve the above object, the vibration isolator of the washing machine according to the present invention, thirdly, elastically suspends the tub body through a hanging rod and a compression coil spring in an outer box of the washing machine. A damper body which is inserted through the hanging bar and comes into sliding frictional contact with the hanging bar. The damper body and the compression coil spring support the tank body with vibration isolation, and the compression coil spring Is composed of a rough-wound portion and a honey-wound portion, and a cylindrical elastic pipe which is in sliding frictional contact with the outer peripheral surface of the rough-wound portion and has a length equivalent to the rough-wound portion is fitted. Invention).
【００１４】斯かる構成によれば、圧縮コイルばねは、
その粗巻部分で見かけ上のばね定数を大きくし、蜜巻部
分では小さくしてなり、従って脱水起動時の大きな振動
に対しては粗巻部分を含む圧縮コイルばね全体が密着す
るほどに伸縮し、且つばね定数が大きい粗巻部分に被嵌
された弾性パイプは該粗巻部分のみならず圧縮コイルば
ねの略全体に亘り相対的に摩擦接触することとなり、以
って大きな減衰力を発生する。一方、定常時の小さな振
動に対しては圧縮コイルばねの見かけ上のばね定数が小
さい蜜巻部分が伸縮して振動吸収作用するも、ばね定数
が大きい粗巻部分は殆ど伸縮動作しないためこれに被嵌
された弾性パイプとの相対的な摩擦接触も殆ど生じな
い。According to such a configuration, the compression coil spring is
The apparent spring constant is increased in the coarsely wound portion, and reduced in the honey wound portion. Therefore, for large vibrations at the start of dehydration, the compression coil spring, including the coarsely wound portion, expands and contracts so that it comes into close contact. In addition, the elastic pipe fitted to the coarsely wound portion having a large spring constant makes relatively frictional contact not only with the roughly wound portion but also substantially over the entire compression coil spring, thereby generating a large damping force. . On the other hand, for a small vibration in a steady state, the honey-winding portion having a small apparent spring constant of the compression coil spring expands and contracts to absorb the vibration, but the coarse winding portion having a large spring constant hardly expands and contracts. There is also little relative frictional contact with the fitted elastic pipe.
【００１５】従って、脱水起動時には圧縮コイルばねの
略全体に亘って弾性パイプとの摩擦接触による大きな減
衰力が発生して振動を効果的に抑える一方、定常時には
弾性パイプとの摩擦力を実質的に無効化して、ばね定数
が小さい蜜巻部分による振動吸収作用によって防振効果
を発揮し、以って振動伝達や騒音発生を抑えることがで
きる。Therefore, when dehydration is started, a large damping force is generated by frictional contact with the elastic pipe over substantially the entire compression coil spring, and vibration is effectively suppressed. On the other hand, when steady, the frictional force with the elastic pipe is substantially reduced. And the vibration absorbing effect of the honey winding portion having a small spring constant exerts a vibration damping effect, thereby suppressing vibration transmission and noise generation.
【００１６】そして請求項３記載のものにおいて、圧縮
コイルばねの下方部位を粗巻部分とし、この粗巻部分に
有底円筒状に形成した弾性パイプを下方から被嵌して、
該弾性パイプの内底部を圧縮コイルばねの粗巻側端部の
ばね台座としたことを特徴とする（請求項４の発明）。According to the third aspect of the present invention, the lower portion of the compression coil spring is a coarsely wound portion, and an elastic pipe formed in a cylindrical shape with a bottom is fitted over the coarsely wound portion from below.
The inner bottom portion of the elastic pipe is a spring pedestal at the end of the compression coil spring on the rough winding side (the invention of claim 4).
【００１７】斯かる構成によれば、圧縮コイルばねの下
端部を受け支持するばね台座を、弾性パイプと一体化し
たことにより、部品構成の簡素化が図れることはもとよ
り、粗巻部分に対峙して被嵌される弾性パイプの位置決
め及びその位置を常時維持できて防振性能の安定化を図
り得、しかも圧縮コイルばねを緩衝的に支持し得て騒音
の発生を抑えることができる点でも有利である。According to such a configuration, the spring pedestal for receiving and supporting the lower end of the compression coil spring is integrated with the elastic pipe, so that not only the structure of the parts can be simplified, but also it is opposed to the coarsely wound portion. It is also advantageous in that the positioning of the elastic pipe to be fitted and its position can be maintained at all times to stabilize the vibration isolation performance, and that the compression coil spring can be supported in a buffered manner to suppress noise generation. It is.
【００１８】さらに請求項３記載のものにおいて、圧縮
コイルばねの上方部位を粗巻部分とし、この粗巻部分に
ダンパー体から筒状に一体に延設してなる弾性パイプを
上方から被嵌したことを特徴とする（請求項５の発
明）。Further, the upper portion of the compression coil spring is a coarsely wound portion, and an elastic pipe integrally and cylindrically extended from a damper body to the coarsely wound portion is fitted from above. (The invention of claim 5).
【００１９】斯かる構成によれば、ダンパ体と弾性パイ
プとが一体化されたことにより、圧縮コイルばね上方部
位の粗巻部分に対峙して被嵌される弾性パイプとの位置
決め及びその位置を常時維持できて防振性能の安定化を
図り得、勿論、部品構成の簡素化に伴い組立製造性の向
上も期待できる。According to such a structure, the damper body and the elastic pipe are integrated, so that the positioning of the elastic pipe fitted to face the coarsely wound portion above the compression coil spring and its position can be adjusted. It can be maintained at all times and can stabilize the anti-vibration performance. Of course, improvement of assembly manufacturability can be expected with simplification of the component configuration.
【００２０】さらにまた、上記目的を達成するために本
発明の洗濯機の防振装置は、第４に、洗濯機の外箱内に
吊り棒及び圧縮コイルばねを介して槽体を弾性的に吊持
する防振装置において、前記吊り棒に挿通せられ該吊り
棒と摺動摩擦接触するダンパ体を設け、このダンパ体と
前記圧縮コイルばねとで前記槽体を防振支持すると共
に、圧縮コイルばねの外径を径大及び径小部分とから構
成し、この径小部分にその外周面と摺動摩擦接触する筒
状弾性パイプを被嵌したことを特徴とする（請求項６の
発明）。Further, in order to achieve the above object, the vibration damping device for a washing machine of the present invention has a fourth feature that the tub body is elastically provided in the outer case of the washing machine via a hanging rod and a compression coil spring. In the vibration damping device to be suspended, a damper body is provided which is inserted through the hanging rod and comes into sliding friction contact with the hanging rod, and the damper body and the compression coil spring support the tank body in a vibration isolating manner, and a compression coil is provided. The outer diameter of the spring is composed of a large-diameter part and a small-diameter part, and a cylindrical elastic pipe that is in sliding frictional contact with the outer peripheral surface is fitted on the small-diameter part (the invention of claim 6).
【００２１】斯かる構成によれば、脱水起動時の大きな
振動に対しては圧縮コイルばね全体が密着するほどに伸
縮することに伴い、その径小部分に被嵌された弾性パイ
プは径大部分とも摩擦接触することとなり、以って接触
面積が増大し大きな減衰力を発生する。一方、定常時の
小さな振動に対しては弾性パイプが圧縮コイルばねの径
小部分にのみ対峙する位置にあるため、接触面積が小さ
く接触圧は大幅に低減することで、小さな振動は実質的
に圧縮コイルばねにて振動吸収され、振動伝達や騒音発
生を抑えることができる。この場合、径小部分における
弾性パイプの接触圧はでき得る限り小さくすることが望
ましい。According to such a configuration, with respect to a large vibration at the start of dehydration, the compression coil spring expands and contracts so as to be in close contact with the compression coil spring. Are brought into frictional contact with each other, thereby increasing the contact area and generating a large damping force. On the other hand, for small vibrations in the steady state, the elastic pipe is located at a position facing only the small diameter portion of the compression coil spring, so the contact area is small and the contact pressure is greatly reduced, so that the small vibrations are substantially reduced. Vibration is absorbed by the compression coil spring, and vibration transmission and noise generation can be suppressed. In this case, it is desirable to make the contact pressure of the elastic pipe in the small diameter portion as small as possible.
【００２２】そして請求項６記載のものにおいて、弾性
パイプの圧縮コイルばねの径大側内端部を末広がりのテ
ーパ状に形成したことを特徴とする（請求項７の発
明）。According to a sixth aspect of the present invention, the large-diameter inner end of the compression coil spring of the elastic pipe is formed in a divergent taper shape (the seventh aspect of the invention).
【００２３】斯かる構成によれば、脱水起動時のように
大きく振動し圧縮コイルばねが大きき伸縮する場合に、
その径大部分が弾性パイプ内に出没し易く円滑な摩擦摺
接ができ、該パイプ端部での不要な抵抗とか衝突を避け
ることができる点で有利である。According to such a configuration, when the compression coil spring expands and contracts greatly due to large vibration such as at the start of dehydration,
This is advantageous in that a large part of the diameter easily comes into and out of the elastic pipe so that smooth frictional sliding contact can be made and unnecessary resistance or collision at the end of the pipe can be avoided.
【００２４】[0024]
【発明の実施の形態】（第１の実施の形態）以下、本発
明を全自動洗濯機に適用した第１実施例を示す図１及び
図２を参照して説明する。まず図２は、全自動洗濯機２
１の概略構成を示す縦断側面図で、２２は矩形箱状に形
成された外箱で、この外箱２２内に槽体としての外槽２
３が、外箱２２上部から揺動可能に垂下された吊り棒２
４により吊持されて後述する防振装置２５を介して弾性
的に防振支持されている。そしてこの外槽２３内には洗
濯槽と脱水槽を兼ねた回転可能な内槽２６が設けられ、
この内槽２６の内底部には被洗濯物を洗うための攪拌体
２７を具備している。DESCRIPTION OF THE PREFERRED EMBODIMENTS (First Embodiment) Hereinafter, a first embodiment in which the present invention is applied to a fully automatic washing machine will be described with reference to FIGS. 1 and 2. FIG. First of all, FIG.
1 is a longitudinal sectional side view showing a schematic configuration of an outer box 22 formed in a rectangular box shape.
3 is a hanging rod 2 suspended from the upper part of the outer box 22 so as to be swingable.
4 and is elastically supported by a vibration isolator 25 to be described later. In the outer tub 23, a rotatable inner tub 26 serving as a washing tub and a dehydration tub is provided.
The inner bottom of the inner tub 26 is provided with a stirrer 27 for washing the laundry.
【００２５】しかして前記吊り棒２４は、その上端部に
挿着された球面状の上部受け部材２８を介して外箱２２
の四隅部（一箇所のみ図示）に固着された補強板２９上
に揺動可能に支承垂下されていて、この吊り棒２４の垂
下端部は、途中に外槽２３に突設された支持片部３０を
挿通し、それ以降の下端部に亘って防振装置２５を装備
している。従って、外槽２３等の重量負荷は支持片部３
０を介して防振装置２５により弾性支持され、そして吊
り棒２４にて外箱２２内に吊持される。The hanging rod 24 is thus connected to the outer box 22 via a spherical upper receiving member 28 inserted at the upper end thereof.
Are suspended on a reinforcing plate 29 fixed to the four corners (only one is shown) of the suspension rod 24. The lower end of the hanging rod 24 is supported by a support piece protruding from the outer tank 23 in the middle. The anti-vibration device 25 is provided through the lower portion 30 after the portion 30 is inserted. Therefore, the weight load of the outer tank 23 and the like is
0, is elastically supported by a vibration isolator 25, and is suspended in an outer box 22 by a suspension rod 24.
【００２６】そしてこの防振装置２５について特に本実
施例が特徴とする吊り棒２４の下方部位との関連構成を
併せて、図１に示す要部の断面図を参照して述べる。ま
ず吊り棒２４の下端部にはワッシャ３１を介して金属製
のばね台座３２が抜け止め状態に挿着され、このばね台
座３２の上面に形成された環状受け部３３に圧縮コイル
ばね３４下端の内径部分を嵌めるようにして装着され
る。この圧縮コイルばね３４の上端部にあっては、外槽
２３から突設された支持片部３０の球面状下面部に滑動
可能に宛がわれた下部支持部材３５と、これに連接して
ゴム製のダンパ体３６が吊り棒２４と摺動可能に摩擦接
触する状態で設けられ、このダンパ体３６の上面中央部
位にはグリス溜め部３７を形成している。そしてこのダ
ンパ体３６を下方部から囲繞するように筒状のダンパケ
ース３８が設けられていて、これの環状鍔部３９は圧縮
コイルばね３４上端部のばね受け部を兼ねている。従っ
て、内槽２６及び外槽２３等の重量負荷は、防振装置２
５を構成する主に圧縮コイルばね３４による弾発力とダ
ンパ体３６の吊り棒２４との摩擦力等により弾性的に防
振支持された構成をなす。また、本実施例ではさらに圧
縮コイルばね３４の下部外周面と摩擦接触するように筒
状の弾性パイプ４０が被嵌されていて防振装置２５の一
部を構成している。The anti-vibration device 25 will be described with reference to a cross-sectional view of a main part shown in FIG. First, a metal spring pedestal 32 is inserted into the lower end of the suspension rod 24 via a washer 31 so as not to come off. A lower end of the compression coil spring 34 is attached to an annular receiving portion 33 formed on the upper surface of the spring pedestal 32. It is mounted so that the inside diameter part is fitted. At the upper end of the compression coil spring 34, a lower support member 35 slidably addressed to the spherical lower surface of the support piece 30 protruding from the outer tub 23 and a rubber A damper body 36 is provided in a state of slidably and frictionally contacting with the hanging rod 24, and a grease reservoir 37 is formed at a central portion of the upper surface of the damper body 36. A cylindrical damper case 38 is provided so as to surround the damper body 36 from below, and the annular flange 39 also serves as a spring receiving portion at the upper end of the compression coil spring 34. Therefore, the weight load of the inner tank 26, the outer tank 23, etc.
5 is elastically damped and supported mainly by the elastic force of the compression coil spring 34 and the frictional force between the suspension rod 24 of the damper body 36 and the like. Further, in this embodiment, a cylindrical elastic pipe 40 is further fitted so as to make frictional contact with the lower outer peripheral surface of the compression coil spring 34, thereby constituting a part of the vibration isolator 25.
【００２７】しかるに上記防振装置２５を装備した吊り
棒２４の下方部位は、下方ほど径大となるテーパ部２４
ａを形成している。このテーパ部２４ａの設定範囲は、
図１（ａ）に示す脱水起動時における大きく振幅運動す
るダンパ体３６と摺動接触し、同図（ｂ）に示す定常時
における小さな振幅運動する場合のダンパ体３６には接
触しない位置Ａから下端部に亘り形成してある。従っ
て、脱水起動時においてはダンパ体３６と吊り棒２４ａ
との接触圧は大きくなり、より大きな減衰力が付与され
る。However, the lower part of the suspension rod 24 equipped with the vibration isolator 25 has a tapered portion 24 whose diameter becomes larger as it goes downward.
a. The setting range of the tapered portion 24a is:
From the position A which is in sliding contact with the damper body 36 which makes a large amplitude movement at the time of dehydration start shown in FIG. 1A and does not contact the damper body 36 when making a small amplitude movement at the steady state shown in FIG. It is formed over the lower end. Therefore, at the time of starting dehydration, the damper body 36 and the hanging rod 24a
And the contact pressure increases, and a greater damping force is applied.
【００２８】尚、図２中に示す４１は外槽２３下面に設
けられたモータで、その回転力はベルト伝達機構４２及
びクラッチ等を含む駆動機構部４３を経て攪拌体２７、
或いは内槽２６に伝達され、これらを高速回転させる。
また、内槽２６上端部にはバランスリング４４が装着さ
れ、且つこのバランスリング４４との間に脱水用の透孔
４５を複数個形成している。In FIG. 2, reference numeral 41 denotes a motor provided on the lower surface of the outer tub 23, the rotational force of which is passed through a belt transmitting mechanism 42 and a driving mechanism 43 including a clutch and the like.
Alternatively, they are transmitted to the inner tank 26 and are rotated at high speed.
A balance ring 44 is attached to the upper end of the inner tub 26, and a plurality of through holes 45 for dehydration are formed between the balance ring 44 and the balance ring 44.
【００２９】このように構成された本実施例の洗濯機２
１において、モータ４１が通電駆動されると攪拌体２７
が正逆回転して洗い及びすすぎの各行程が行われ、次い
で内槽２６が高速回転する脱水行程に移行する。この脱
水運転が開始される際、内槽２６内の図示しない被洗濯
物が偏った収容状態、すなわちアンバランスな状態にあ
ると、特に起動時においては内槽２６従って外槽２３が
大きく振動し、これが外箱２２に伝達されて洗濯機２１
全体に振動を与え、さらに過大になると内槽２６の揺れ
が大きくなり、所定の回転数まで達せず円滑な脱水運転
ができないおそれが生ずる。The washing machine 2 according to the present embodiment thus configured
In 1, when the motor 41 is energized and driven, the stirring body 27
Are rotated forward and backward to perform washing and rinsing steps, and then the process shifts to a dehydration step in which the inner tub 26 rotates at a high speed. When this dehydration operation is started, if the laundry (not shown) in the inner tub 26 is in an unevenly accommodated state, that is, in an unbalanced state, the inner tub 26 and therefore the outer tub 23 vibrate greatly, especially at startup. This is transmitted to the outer box 22 and the washing machine 21
Vibration is applied to the whole, and if the vibration becomes excessive, the swing of the inner tub 26 becomes large, and the rotation speed does not reach the predetermined number of revolutions, so that there is a possibility that a smooth dewatering operation cannot be performed.
【００３０】しかるに本実施例における防振装置２５に
よれば、圧縮コイルばね３４の伸縮作用にて主として振
動吸収する一方、この圧縮コイルばね３４の外周面にて
摩擦接触する弾性パイプ４０との摩擦力及び主としてダ
ンパ体３６と吊り棒２４との摩擦力と、さらにはグリス
溜め部３７を経てこの部位に塗布された図示しないグリ
スの粘性抵抗により発生する減衰力によって振動は減衰
される。However, according to the vibration isolator 25 of the present embodiment, the vibration is mainly absorbed by the expansion and contraction of the compression coil spring 34, while the friction between the elastic pipe 40 and the outer peripheral surface of the compression coil spring 34 makes frictional contact. The vibration is attenuated by the force and the frictional force mainly between the damper body 36 and the suspension rod 24 and the damping force generated by the viscous resistance of the grease (not shown) applied to this portion via the grease reservoir 37.
【００３１】ところが上記のように振動吸収作用及び摩
擦力，抵抗力等の振動減衰作用を幾つかを採り入れて効
果的な防振性能は得ているものの、それでも実用運転に
おいてその防振性能を超える過大な振動が発生すること
がある。その対策として減衰作用を強化すべく、圧縮コ
イルばね３４と弾性パイプ４０及びダンパ体３６と吊り
棒２４との摩擦力を大きくし、且つ圧縮コイルばね３４
自体のばね定数を大きくすることが考えられるが、この
場合、防振装置２５の剛性が高められて起動時の大きな
振動に対しては減衰性能の向上が図れるものの、定常時
の小さな振動に対しては振動吸収が不十分となり振動伝
達や騒音への悪影響が生じ、結果防振性能としては満足
できない。However, as described above, although some vibration absorbing functions and vibration damping functions such as frictional force and resistance force are adopted, effective vibration damping performance is obtained, but still exceeds the vibration damping performance in practical operation. Excessive vibration may occur. As a countermeasure, the frictional force between the compression coil spring 34 and the elastic pipe 40 and between the damper body 36 and the suspension rod 24 is increased in order to strengthen the damping action.
Although it is conceivable to increase the spring constant of itself, in this case, the rigidity of the vibration isolator 25 is increased and the damping performance can be improved with respect to large vibration at the time of startup, but with respect to small vibration at steady state. As a result, the vibration absorption becomes insufficient and adverse effects on vibration transmission and noise occur, and as a result, the vibration isolation performance is not satisfactory.
【００３２】しかるに、本発明は起動時の大きな振動発
生時にのみ大きな減衰作用を得るべく、本実施例ではダ
ンパ体３６と摺動する範囲内における吊り棒２４の下方
部位にテーパ部２４ａを形成したので、外槽２３が大き
く振動し圧縮コイルばね３４が密着するほど伸縮し、ダ
ンパ体３６が吊り棒２４の下方部まで摺動すると、ダン
パ体３６は吊り棒２４のテーパ部２４ａと下方に行くほ
ど強く接触し大きな摩擦力を得ることとなり、大きな減
衰作用を発揮する。このように脱水起動時などのように
振動が大きくなるにつれて減衰作用も大きく応動し、過
大な振動に対処できる許容範囲を大きくしている。In the present embodiment, however, a tapered portion 24a is formed in the lower portion of the suspension rod 24 within a range in which it slides with the damper body 36 in order to obtain a large damping action only when a large vibration occurs at the time of startup. Therefore, the outer tub 23 vibrates greatly and the compression coil spring 34 expands and contracts as closely as possible, and when the damper body 36 slides to the lower part of the suspension rod 24, the damper body 36 goes downward with the tapered portion 24 a of the suspension rod 24. The stronger the contact, the greater the frictional force and the greater the damping effect. As described above, as the vibration increases, such as at the time of starting dehydration, the damping action also responds to increase the allowable range in which excessive vibration can be dealt with.
【００３３】一方、脱水運転が進み所定の高速回転に至
ると、すなわち定常運転領域ではピッチの速い小刻みな
振動が続くが、この場合、吊り棒２４のテーパ部２４ａ
は図１（ｂ）に示すように摩擦力を生じない位置にあっ
て、ダンパ体３６は吊り棒２４の直線状部分との所謂通
常の摩擦接触となって減衰作用は低減し、且つ主に圧縮
コイルばね３４の伸縮作用による振動吸収作用に基づく
防振効果にて振動伝達や騒音発生を抑制できる。On the other hand, when the dehydration operation proceeds and reaches a predetermined high-speed rotation, that is, in the steady operation region, small vibrations with a high pitch continue, but in this case, the tapered portion 24a of the suspension rod 24
1B is in a position where no frictional force is generated as shown in FIG. 1B, and the damper body 36 is in a so-called normal frictional contact with the linear portion of the suspension rod 24, so that the damping action is reduced. Vibration transmission and noise generation can be suppressed by an anti-vibration effect based on a vibration absorbing action by the expansion and contraction action of the compression coil spring 34.
【００３４】従って、本実施例の防振装置２５によれ
ば、脱水起動時から定常時に至り振動状態に応じた防振
性能が得られ、終始円滑な脱水運転が実行できる。尚、
本実施例では、テーパ部２４ａは吊り棒２４と一体に形
成したが、これは別体に設けても良く、例えばテーパ状
の中空円筒体を別体に設けてこれを吊り棒の下方部位に
挿着する構成としても、上記構成と同様の作用効果を奏
する。Therefore, according to the anti-vibration device 25 of this embodiment, the anti-vibration performance according to the vibration state is obtained from the start of dehydration to the steady state, and a smooth dehydration operation can be performed throughout. still,
In this embodiment, the tapered portion 24a is formed integrally with the hanging rod 24. However, this may be provided separately. For example, a tapered hollow cylindrical body is provided separately, and this is provided below the hanging rod. The same function and effect as the above-described configuration can be obtained even when the configuration is inserted.
【００３５】上記の構成に対し、図３ないし図１０は本
発明の第２ないし第８実施例を示すもので、夫々第１実
施例と同一の部分には同一の符号を付して説明を省略
し、異なる部分についてのみ述べる。3 to 10 show the second to eighth embodiments of the present invention. The same parts as those in the first embodiment are denoted by the same reference numerals, and description thereof will be made. Omitted, and only different parts will be described.
【００３６】（第２の実施の形態）図３に示す第２実施
例における防振装置６３は、上記第１実施例における吊
り棒２４のテーパ部２４ａに代わって、吊り棒４６の下
方部位にその表面粗さを摩擦係数が大となるよう窒化処
理，メッキ処理などの表面加工処理を施したもので、こ
の加工処理部４６ａをダンパ体３６と摺動する範囲のう
ちの下方部位に形成してある。(Second Embodiment) A vibration isolator 63 according to a second embodiment shown in FIG. 3 is provided at a position below the suspension rod 46 instead of the tapered portion 24a of the suspension rod 24 in the first embodiment. The surface roughness is subjected to surface processing such as nitriding and plating so as to increase the coefficient of friction. This processed portion 46a is formed in a lower portion of the range in which it slides with the damper body 36. It is.
【００３７】斯かる構成によれば、起動時などの大きな
振動発生時においてダンパ体３６は吊り棒４６との通常
の摩擦領域から摩擦係数が大なる加工処理部４６ａと摩
擦摺接することとなり、より摩擦力が高まり大きな減衰
力を発生して効果的に振動を抑制する。そして定常時に
おいては、この加工処理部４６ａは何らの摩擦作用に関
与せず、従って小刻みな振動に対しては上記実施例と同
様に通常の防振作用により振動伝達や騒音の発生に悪影
響を与えることはない。According to such a configuration, when a large vibration is generated at the time of starting or the like, the damper body 36 comes into frictional sliding contact with the processing portion 46a having a large friction coefficient from the normal friction region with the suspension rod 46. The frictional force is increased and a large damping force is generated to effectively suppress vibration. In a steady state, the processing section 46a does not participate in any frictional action, and therefore has a bad influence on vibration transmission and noise generation due to ordinary vibration damping action for small vibrations as in the above-described embodiment. I will not give.
【００３８】（第３の実施の形態）次いで図４に示す第
３実施例における防振装置６４は、単に直線状をなす従
来と同様の吊り棒４７の垂下端部に挿着した圧縮コイル
ばね４８は、その略中央部分を粗巻部分４８ａとし、両
端側を蜜巻部分４８ｂとし、その粗巻部分４８ａに対峙
して位置ずれ防止用の例えば棒状突部４９ａを内面に有
する弾性パイプ４９を被嵌したもので、その余の構成は
上記第１実施例と共通である。(Third Embodiment) Next, a vibration isolator 64 according to a third embodiment shown in FIG. 4 is a compression coil spring which is simply inserted into the hanging lower end of a hanging bar 47 similar to the conventional one. The elastic pipe 48 has a roughly wound portion 48a at a substantially central portion thereof, a honey wound portion 48b at both ends thereof, and an elastic pipe 49 having, for example, a bar-shaped projection 49a on its inner surface facing the rough wound portion 48a to prevent displacement. The remaining configuration is the same as that of the first embodiment.
【００３９】すなわち、圧縮コイルばね４８の中央部分
は粗巻部分４８ａとしたので見かけ上のばね定数を大き
くしており、且つ同図（ｂ）に示すように通常はこの粗
巻部分４８ａの外周面に摩擦接触するように該粗巻部分
４８ａ相当長の弾性パイプ４９が被嵌されている。そし
て、前記棒状突部４９ａは１個または複数個でも良く、
本実施例では中間位置の同等高さ位置に二箇所形成して
おり、これは圧縮コイルばね４８に対して弾性パイプ４
９を圧挿して弾性的に係合させるか、若しくは回動しつ
つ挿入することで容易に所定位置に被嵌することができ
る。That is, since the center portion of the compression coil spring 48 is formed as a coarsely wound portion 48a, the apparent spring constant is increased, and as shown in FIG. An elastic pipe 49 having a length equivalent to the coarsely wound portion 48a is fitted so as to make frictional contact with the surface. And one or a plurality of the rod-shaped protrusions 49a may be provided,
In the present embodiment, two portions are formed at the same height position in the middle position.
9 can be easily fitted at a predetermined position by press-fitting and elastically engaging, or by inserting while rotating.
【００４０】斯かる構成によれば、脱水起動時の大きな
振動に対しては、ダンパ体３６と吊り棒４７との通常の
摩擦力及びグリスの粘性力とによる減衰力に加えて、圧
縮コイルばね４８のばね定数を大きくしたこと、及び圧
縮コイルばね４８が図４（ａ）に示すように密着するほ
どの圧縮に伴いその全体に亘って弾性パイプ４９と摩擦
接触することとなる相乗効果により、より一層大きい減
衰力が発生する。この場合、圧縮コイルばね４８は大き
く伸縮するが、中間位置にある棒状突部４９ａは該圧縮
コイルばね４８と相対的にずれることはなく全体の動き
に追従して所定の位置に保持され、従って安定した防振
性能が得られる。According to such a structure, in addition to the normal frictional force between the damper body 36 and the suspension rod 47 and the damping force due to the viscous force of the grease, the compression coil spring against the large vibration at the time of starting dehydration. 4A, and the synergistic effect that the compression coil spring 48 comes into frictional contact with the elastic pipe 49 over its entirety as the compression coil spring 48 is compressed to the extent that it comes into close contact as shown in FIG. An even greater damping force is generated. In this case, the compression coil spring 48 expands and contracts greatly, but the rod-shaped projection 49a at the intermediate position does not relatively shift from the compression coil spring 48 and is kept at a predetermined position following the entire movement. Stable vibration isolation performance is obtained.
【００４１】しかるに、定常時における小刻みな振動に
対しては、ばね定数の大きい粗巻部分４８ａは殆ど振動
せず、従って弾性パイプ４９との間の摩擦力も殆ど発生
しないのでこの間での不要な減衰力による振動伝達や騒
音の発生要因はなく、この両端側の蜜巻部分４８ｂの伸
縮作用により有効に振動吸収が行われる。従って、本実
施例においても起動時などの大きな振動に対しては、よ
り大きな減衰力を発揮できる一方、定常時にはこの大き
な減衰力を実質的に無効化して振動伝達の要因となるこ
とを防ぎ、脱水行程を終始効果的な防振性能のもとに実
行できる。However, the sparsely wound portion 48a having a large spring constant hardly vibrates with respect to a small vibration in a steady state, and therefore little frictional force is generated between the coarsely wound portion 48a and the elastic pipe 49. There is no vibration transmission or noise due to the force, and the vibration is effectively absorbed by the expansion and contraction of the honey winding portions 48b at both ends. Therefore, even in the present embodiment, a large damping force can be exerted against a large vibration at the time of starting or the like, while at the time of a steady state, the large damping force is substantially invalidated to prevent a factor of the vibration transmission, The dehydration process can be performed with effective vibration isolation performance from beginning to end.
【００４２】尚、弾性パイプ４９の所定位置を保持すべ
く設けた棒状突部４９ａは、これに代えて圧縮コイルば
ね４８の螺旋形状に沿って延びる一本の環状突部の構成
としても良いし、また、弾性パイプ４９の寸法長はその
粗巻部分４８ａを主体に被嵌できれば若干の長短の寸法
にあっても、上記実施例と略同等の作用効果が得られる
など、種々変形して実施できるものである。The rod-like projection 49a provided to hold the elastic pipe 49 at a predetermined position may be replaced by a single annular projection extending along the spiral shape of the compression coil spring 48. Also, the elastic pipe 49 may be variously modified so as to obtain substantially the same operational effects as those of the above-described embodiment even if the elastic pipe 49 has a slightly longer or shorter dimension as long as the elastic pipe 49 can be fitted mainly. You can do it.
【００４３】（第４の実施の形態）上記第３実施例に対
し、図５に示す第４実施例における防振装置６５は、圧
縮コイルばね５０の上半部を蜜巻部分５０ｂに、下半部
を粗巻部分５０ａに構成すると共に、その粗巻部分５０
ａに対峙して摩擦摺接可能に有底円筒状の弾性パイプ５
１を被嵌したもので、この弾性パイプ５１の底部たる下
端部には内方に延びるフランジ部５２を形成して圧縮コ
イルばね５０の粗巻側下端部を受け、このフランジ部５
２の下面に補強用に宛がわれ吊り棒４７に挿着した受け
部材５３とで所謂ばね台座としての構成をなしている。(Fourth Embodiment) In contrast to the third embodiment described above, the vibration isolator 65 of the fourth embodiment shown in FIG. A half portion is constituted by the coarsely wound portion 50a, and the coarsely wound portion 50a is formed.
cylindrical elastic pipe 5 with a bottom so that it can be frictionally slid in contact with a.
The elastic pipe 51 is formed with a flange 52 at the lower end serving as the bottom to receive the lower end of the compression coil spring 50 on the coarse winding side.
The receiving member 53, which is addressed for reinforcement on the lower surface of the second member 2 and is inserted into the hanging bar 47, forms a so-called spring pedestal.
【００４４】斯かる構成によれば、脱水起動時の大きな
振動発生時には粗巻部分５０ａ及び蜜巻部分５０ｂ共密
着するほどに圧縮され、従って圧縮コイルばね５０全体
が弾性パイプ５１内面と摩擦摺接することとなり、大き
な減衰力を得ることができると共に、粗巻部分５０ａを
設けて見かけ上のばね定数を大きくしているので、減衰
力を大きくするのに有効である。一方、定常時において
は、圧縮コイルばね５０の粗巻部分５０ａはばね定数が
大きいため小刻みな振動には殆ど応動せず、従って弾性
パイプ５１との摩擦摺接も実質的にないため不要な減衰
力が振動伝達源となったり騒音が発生することを抑える
ことができると共に、この小刻みな振動に対しては蜜巻
部分５０ｂが有効に作用して振動吸収し、総じて起動時
及び定常時共に夫々に最適な防振性能が得られる。According to such a configuration, when a large vibration is generated at the start of dehydration, the coarsely wound portion 50a and the finely wound portion 50b are compressed so as to be in close contact with each other. In other words, a large damping force can be obtained, and since the apparent spring constant is increased by providing the rough winding portion 50a, it is effective to increase the damping force. On the other hand, in the steady state, the coarsely wound portion 50a of the compression coil spring 50 hardly responds to small vibrations due to a large spring constant, and therefore has substantially no frictional sliding contact with the elastic pipe 51. In addition to suppressing the transmission of the force and the generation of noise, the honey winding portion 50b effectively acts to absorb the small vibration and absorbs the vibration. Optimum anti-vibration performance is obtained.
【００４５】そして特に本実施例では、弾性パイプ５１
の底部にフランジ部５２を設け、圧縮コイルばね５０の
下端部を受けているので、粗巻部分５０ａに対峙する弾
性パイプ５１の位置決めとその位置での保持が確実にで
き、防振性能の安定化が図れる。また、フランジ部５２
が受け部材５３とでばね台座として機能し、且つ圧縮コ
イルばね５０はフランジ部５２で緩衝的に支持されるの
でこの部分での騒音発生も生じない。In particular, in this embodiment, the elastic pipe 51
Since the flange 52 is provided at the bottom of the elastic pipe 51 and receives the lower end of the compression coil spring 50, the elastic pipe 51 facing the coarsely wound portion 50a can be reliably positioned and held at that position, and the vibration isolation performance can be stabilized. Can be achieved. The flange 52
Function as a spring pedestal with the receiving member 53, and the compression coil spring 50 is supported in a buffered manner by the flange portion 52, so that no noise is generated at this portion.
【００４６】（第５の実施の形態）図６に示す第５実施
例における防振装置６６は、上記第４実施例に対し、弾
性パイプ５４と圧縮コイルばね５０を受けるばね台座５
５を一体化した構成で、ばね台座５５の構成は弾性パイ
プ５４の下端部に金属板５５ａをインサート成形し強度
補強を施したものである。(Fifth Embodiment) A vibration isolator 66 in a fifth embodiment shown in FIG. 6 is different from the fourth embodiment in that a spring pedestal 5 for receiving an elastic pipe 54 and a compression coil spring 50 is provided.
The spring pedestal 55 has a structure in which a metal plate 55a is insert-molded at the lower end portion of the elastic pipe 54 to reinforce the strength.
【００４７】従って、本実施例構成によれば、上記第４
実施例に比して一層部品点数及び組立工程の簡素化が図
れる他は、同様に弾性パイプ５４の位置決めとその保持
が確実にして防振性能の一層の安定化と、圧縮コイルば
ね５０の粗巻側下端部を緩衝的に支持できる。Therefore, according to the structure of this embodiment, the fourth
Except that the number of parts and the assembling process can be further simplified as compared with the embodiment, similarly, the positioning and holding of the elastic pipe 54 are ensured to further stabilize the vibration isolation performance, and the compression coil spring 50 The lower end on the winding side can be supported in a buffered manner.
【００４８】（第６の実施の形態）図７に示す第６実施
例における防振装置６７は、上記第４実施例とは逆配置
関係に圧縮コイルばね５６の上半部を粗巻部分５６ａ
に、下半部を蜜巻部分５６ｂに構成すると共に、その粗
巻部分５６ａに対峙してダンパ体５７と一体に形成され
た弾性パイプ５８を摩擦摺接可能に被嵌した構成にあ
る。(Sixth Embodiment) In a vibration isolator 67 according to a sixth embodiment shown in FIG. 7, the upper half of the compression coil spring 56 is roughly wound in a reversely arranged relation to the fourth embodiment.
In addition, the lower half portion is configured as a honey wound portion 56b, and an elastic pipe 58 formed integrally with the damper body 57 is opposed to the rough wound portion 56a so as to be slidably contacted.
【００４９】斯かる構成によれば、脱水起動時の大きな
振動発生時には粗巻部分５６ａ及び蜜巻部分５６ｂ共密
着するほどに圧縮され、従って圧縮コイルばね５６全体
が弾性パイプ５８内面と摩擦摺接することとなり、大き
な減衰力を得ることができると共に、粗巻部分５６ａを
設けて見かけ上のばね定数を大きくしているので、減衰
力を大きくするのに有効である。一方、定常時において
は、圧縮コイルばね５６の粗巻部分５６ａはばね定数が
大きいため小刻みな振動には殆ど応動せず、従って弾性
パイプ５８との摩擦摺接も実質的にないため不要な減衰
力や騒音の発生を抑えることができると共に、この小刻
みな振動に対しては蜜巻部分５６ｂが有効に作用して振
動吸収し、総じて起動時及び定常時共に夫々に最適な防
振性能が得られる。According to this configuration, when a large vibration is generated at the start of dehydration, the coarsely wound portion 56a and the finely wound portion 56b are compressed so as to be in close contact with each other, so that the entire compression coil spring 56 frictionally contacts the inner surface of the elastic pipe 58. In other words, a large damping force can be obtained, and since the apparent spring constant is increased by providing the rough winding portion 56a, it is effective to increase the damping force. On the other hand, in the steady state, the coarsely wound portion 56a of the compression coil spring 56 has a large spring constant and hardly responds to small vibrations. Therefore, there is substantially no frictional sliding contact with the elastic pipe 58. In addition to suppressing the generation of force and noise, the honey winding portion 56b effectively acts on this small vibration and absorbs the vibration, and as a whole, the optimum vibration damping performance is obtained both at the start-up and during the steady state. Can be
【００５０】そして、特に本実施例ではダンパ体５７と
弾性パイプ５８とを一体化したので、部品点数及び組立
工程が簡素化することはもとより、圧縮コイルばね５６
の粗巻部分５６ａに対峙して被嵌した弾性パイプ５８の
位置保持が確実にでき、防振性能を安定化できる利点を
有する。In this embodiment, since the damper body 57 and the elastic pipe 58 are integrated, the number of parts and the assembling process can be simplified.
This has the advantage that the position of the elastic pipe 58 fitted and fitted to the rough winding portion 56a can be reliably maintained, and the vibration isolation performance can be stabilized.
【００５１】（第７の実施の形態）図８に示す第７実施
例における防振装置６８は、ダンパケース３８とばね台
座３２との間に鼓形の圧縮コイルばね５９を装着したも
ので、すなわち中央部分を径小部分５９ａとして両端側
に夫々なだらかに拡径する径大部分５９ｂを有してな
り、その径小部分５９ａに相当長の弾性パイプ６０を被
嵌した構成である。この場合、弾性パイプ６０は圧縮コ
イルばね５９の径小部分５９ａに対し、極力接触圧を小
さくするのが望ましく、従って径小部分５９ａの外径形
状に沿う筒形状としても良い。(Seventh Embodiment) A vibration isolator 68 according to a seventh embodiment shown in FIG. 8 has a drum-shaped compression coil spring 59 mounted between a damper case 38 and a spring pedestal 32. That is, the central portion has a small-diameter portion 59a, and has a large-diameter portion 59b that gradually expands at both ends, and an elastic pipe 60 of a considerable length is fitted to the small-diameter portion 59a. In this case, it is desirable that the elastic pipe 60 has as small a contact pressure as possible with respect to the small-diameter portion 59a of the compression coil spring 59. Therefore, the elastic pipe 60 may have a cylindrical shape that conforms to the outer diameter of the small-diameter portion 59a.
【００５２】斯かる構成によれば、脱水起動時の大きな
振動発生時には径小部分５９ａ及び径大部分５９ｂ共密
着するほどに圧縮され、従って径大部分５９ｂが弾性パ
イプ６０内に圧挿された状態で出没して摩擦摺接するこ
ととなり、大きな減衰力を得ることができる。一方、定
常時においては、圧縮コイルばね５９の径大部分５９ａ
の少なくとも大部分は弾性パイプ６０と接触するに至ら
ず、また径小部分５９ａと弾性パイプ６０との接触圧も
極力小さく設定してあるので減衰力は低減し、従って主
に圧縮コイルばね５９全体の伸縮作用にて小刻みな振動
を吸収し、振動伝達や騒音発生を有効に阻止でき、結果
として起動時及び定常時共に夫々に最適な防振性能が得
られる。尚、弾性パイプ６０は接触圧が小さい最も細径
とする径小部分５９ａに被嵌されているため、径大部分
５９ｂ側へ移行することなくその位置に保持できる。According to such a configuration, when a large vibration is generated at the time of starting dehydration, the small-diameter portion 59a and the large-diameter portion 59b are compressed so as to be in close contact with each other, and therefore the large-diameter portion 59b is pressed into the elastic pipe 60. It comes out and comes into frictional sliding contact in this state, and a large damping force can be obtained. On the other hand, in the steady state, the large-diameter portion 59a of the compression coil spring 59
Of the elastic coil 60 does not come into contact with the elastic pipe 60, and the contact pressure between the small-diameter portion 59a and the elastic pipe 60 is set as small as possible, so that the damping force is reduced. By virtue of the expansion and contraction effect of, small vibrations can be absorbed and vibration transmission and noise generation can be effectively prevented. As a result, optimum vibration damping performance can be obtained both at start-up and at steady-state. Since the elastic pipe 60 is fitted to the small diameter portion 59a having the smallest contact pressure and the smallest diameter, the elastic pipe 60 can be held at that position without shifting to the large diameter portion 59b.
【００５３】（第８の実施の形態）図９及び図１０に示
す第８実施例における防振装置６９は、ダンパケース３
８とばね台座３２との間に末広がり形状の圧縮コイルば
ね６１を装着し、その略上半部に相当する径小部分６１
ａにやはり末広がりの筒状弾性パイプ６２を被嵌したも
ので、該弾性パイプ６２と径小部分６１ａとの接触圧は
できるだけ小さくした構成にある。尚、弾性パイプ６２
の上端部は下部支持部材３５の下面に衝止され、上方へ
の抜け止めがなされると共に下方への移動に対しては径
大部分６１ｂによって阻止される。また、弾性パイプ６
２の内端部は、図９のＢ部を拡大して示す図１０から理
解できるように下方に向かって径大となるテーパ部６２
ａを形成している。(Eighth Embodiment) An anti-vibration device 69 according to an eighth embodiment shown in FIGS.
A compression coil spring 61 having a divergent shape is mounted between the spring base 8 and the spring base 32, and a small-diameter portion 61 corresponding to a substantially upper half portion thereof.
Also, a flared cylindrical elastic pipe 62 is fitted over the section a, and the contact pressure between the elastic pipe 62 and the small-diameter portion 61a is made as small as possible. The elastic pipe 62
The upper end of the lower support member 35 is abutted against the lower surface of the lower support member 35, and is prevented from falling out and prevented from moving downward by the large-diameter portion 61b. The elastic pipe 6
The inner end portion 2 has a tapered portion 62 whose diameter increases downward as can be understood from FIG. 10, which is an enlarged view of the portion B in FIG.
a.
【００５４】斯かる構成によれば、脱水起動時の大きな
振動発生時には径小部分６１ａ及び径大部分６１ｂ共密
着するほどに圧縮され、従って径大部分６１ｂが弾性パ
イプ６２内に圧挿された状態で出没して摩擦摺接するこ
ととなり、大きな減衰力を得ることができる。一方、定
常時においては、圧縮コイルばね６１の径大部分６１ｂ
は弾性パイプ６２とは接触するに至らず、また径小部分
６１ａと弾性パイプ６２との接触圧も極力小さく設定し
てあるので減衰力は低減し、従って圧縮コイルばね６１
全体の伸縮作用にて小刻みな振動を吸収し、振動伝達や
騒音発生を有効に阻止でき、結果として起動時及び定常
時共に夫々に最適な防振性能が得られる。According to such a configuration, when a large vibration is generated at the start of dehydration, the small-diameter portion 61a and the large-diameter portion 61b are compressed so that they come into close contact with each other, so that the large-diameter portion 61b is pressed into the elastic pipe 62. It comes out and comes into frictional sliding contact in this state, and a large damping force can be obtained. On the other hand, in the steady state, the large-diameter portion 61b of the compression coil spring 61
Does not come into contact with the elastic pipe 62, and the contact pressure between the small diameter portion 61a and the elastic pipe 62 is set as small as possible, so that the damping force is reduced.
Small vibrations can be absorbed by the entire expansion and contraction action, and vibration transmission and noise generation can be effectively prevented. As a result, optimal vibration damping performance can be obtained both at the time of startup and at the time of steady operation.
【００５５】そして、上記径大部分６１ｂが弾性パイプ
６２に対し出没するところの下端部には末広がりのテー
パ部６２ａを形成しているので、その出没動作が円滑に
でき、これは圧縮コイルばね６１の外径寸法の径変化が
大きい場合ほど有効となる。尚、本実施例における弾性
パイプ６２は、ダンパ体３６と一体に形成することも可
能である。その他、本発明は上記し且つ図面に示した実
施例に限定されるものではなく、要旨を逸脱しない範囲
内にて適宜変更して実施できるものである。Since the large-diameter portion 61b is formed with a divergent taper portion 62a at the lower end where the large-diameter portion 61b protrudes and retracts with respect to the elastic pipe 62, the protruding and retracting operation can be performed smoothly. The effect becomes larger as the change in the outer diameter dimension of the element becomes larger. In addition, the elastic pipe 62 in the present embodiment can be formed integrally with the damper body 36. In addition, the present invention is not limited to the embodiment described above and shown in the drawings, and can be implemented with appropriate modifications without departing from the scope of the invention.
【００５６】[0056]
【発明の効果】本発明は以上説明した通り、脱水起動時
及び定常時の夫々固有の振動形態に応じて減衰力を加減
調整できるようにしたので、起動時の大きな振動に対処
して減衰力を大きく発生する構成でありながら、定常時
の小さな振動に対しては減衰力を低減できるので、減衰
力を大きくしたがために生じ易い振動伝達や騒音発生の
悪影響を有効に抑制できる洗濯機の防振装置を提供でき
る。As described above, according to the present invention, the damping force can be adjusted in accordance with the respective vibration modes at the start of dehydration and at the time of steady state. Although it is a configuration that generates a large amount of vibration, the damping force can be reduced for small vibrations in a steady state, so the washing machine that can effectively suppress the adverse effects of vibration transmission and noise generation that are likely to occur due to the increased damping force An anti-vibration device can be provided.
【図１】本発明の第１実施例の要部を示す縦断側面図FIG. 1 is a longitudinal sectional side view showing a main part of a first embodiment of the present invention.
【図２】洗濯機全体の縦断側面図FIG. 2 is a vertical sectional side view of the entire washing machine.
【図３】本発明の第２実施例の要部を示す縦断側面図FIG. 3 is a longitudinal sectional side view showing a main part of a second embodiment of the present invention.
【図４】本発明の第３実施例の要部を示す縦断側面図FIG. 4 is a longitudinal sectional side view showing a main part of a third embodiment of the present invention.
【図５】本発明の第４実施例の要部を示す縦断側面図FIG. 5 is a longitudinal sectional side view showing a main part of a fourth embodiment of the present invention.
【図６】本発明の第５実施例の要部を示す要部の縦断側
面図FIG. 6 is a longitudinal sectional side view of a main part showing a main part of a fifth embodiment of the present invention.
【図７】本発明の第６実施例の要部を示す縦断側面図FIG. 7 is a longitudinal sectional side view showing a main part of a sixth embodiment of the present invention.
【図８】本発明の第７実施例の要部を示す縦断側面図FIG. 8 is a longitudinal sectional side view showing a main part of a seventh embodiment of the present invention.
【図９】本発明の第８実施例の要部を示す縦断側面図FIG. 9 is a longitudinal sectional side view showing a main part of an eighth embodiment of the present invention.
【図１０】図９のＢ部の拡大図FIG. 10 is an enlarged view of a portion B in FIG. 9;
【図１１】従来構成を示す要部の縦断側面図FIG. 11 is a longitudinal sectional side view of a main part showing a conventional configuration.
【図１２】要部の拡大図FIG. 12 is an enlarged view of a main part.
２１は洗濯機、２２は外箱、２３は外槽（槽体）、２
４，４６及び４７は吊り棒、２４ａはテーパ部、２５，
６３，６４，６５，６６，６７，６８及び６９は防振装
置、３６及び５７はダンパ体、３４，４８，５０，５
６，５９及び６１は圧縮コイルばね、４０，４９，５
１，５４，５８，６０及び６２は弾性パイプを示す。21 is a washing machine, 22 is an outer box, 23 is an outer tub (tank body), 2
4, 46 and 47 are hanging rods, 24a is a tapered part,
63, 64, 65, 66, 67, 68 and 69 are vibration damping devices, 36 and 57 are damper bodies, 34, 48, 50, 5
6,59 and 61 are compression coil springs, 40,49,5
1, 54, 58, 60 and 62 indicate elastic pipes.
Claims (7)
ばねを介して槽体を弾性的に吊持する防振装置におい
て、前記吊り棒に挿通せられ該吊り棒と摺動摩擦接触す
るダンパ体を設け、このダンパ体と前記圧縮コイルばね
とで前記槽体を防振支持すると共に、吊り棒にはダンパ
体と摺動する範囲内にあって下方が径大となるテーパ部
を設けたことを特徴とする洗濯機の防振装置。1. A vibration isolator for elastically suspending a tub body via a hanging rod and a compression coil spring in an outer box of a washing machine, wherein the vibration isolator is inserted through the hanging rod and makes sliding frictional contact with the hanging rod. A damper body is provided, the damper body and the compression coil spring support the tank body in a vibration-proof manner, and the suspension rod is provided with a tapered portion within a range in which the suspension body slides and the diameter of the lower part is large. A vibration isolator for a washing machine.
ばねを介して槽体を弾性的に吊持する防振装置におい
て、前記吊り棒に挿通せられ該吊り棒と摺動摩擦接触す
るダンパ体を設け、このダンパ体と前記圧縮コイルばね
とで前記槽体を防振支持すると共に、吊り棒にはダンパ
体と摺動する範囲のうちの下方部位の表面粗さを摩擦係
数が大となるように加工処理したことを特徴とする洗濯
機の防振装置。2. A vibration isolator for elastically suspending a tub body via a suspension rod and a compression coil spring in an outer box of a washing machine, wherein the vibration absorber is inserted through the suspension rod and makes sliding friction contact with the suspension rod. A damper body is provided, the tank body is vibration-isolated and supported by the damper body and the compression coil spring, and the suspension rod has a large coefficient of friction to determine the surface roughness of the lower portion of the sliding range with the damper body. An anti-vibration device for a washing machine, wherein the anti-vibration device is processed so that
ばねを介して槽体を弾性的に吊持する防振装置におい
て、前記吊り棒に挿通せられ該吊り棒と摺動摩擦接触す
るダンパ体を設け、このダンパ体と前記圧縮コイルばね
とで前記槽体を防振支持すると共に、圧縮コイルばねを
粗巻部分と蜜巻部分とから構成し、この粗巻部分にその
外周面と摺動摩擦接触し且つ粗巻部分相当長の筒状弾性
パイプを被嵌したことを特徴とする洗濯機の防振装置。3. A vibration isolator for elastically suspending a tub body via a hanging rod and a compression coil spring in an outer box of a washing machine, wherein the vibration absorbing device is inserted through the hanging rod and makes sliding frictional contact with the hanging rod. A damper body is provided, the tank body is vibration-isolated and supported by the damper body and the compression coil spring, and the compression coil spring is composed of a coarsely wound part and a finely wound part. A vibration isolator for a washing machine, wherein a cylindrical elastic pipe having sliding friction contact and a length equivalent to a coarsely wound portion is fitted.
し、この粗巻部分に有底円筒状に形成した弾性パイプを
下方から被嵌して、該弾性パイプの内底部を圧縮コイル
ばねの粗巻側端部のばね台座としたことを特徴とする請
求項３記載の洗濯機の防振装置。4. A lower portion of the compression coil spring is a coarsely wound portion, and an elastic pipe formed into a bottomed cylindrical shape is fitted on the coarsely wound portion from below, and an inner bottom portion of the elastic pipe is fitted to the compression coil spring. 4. A vibration isolator for a washing machine according to claim 3, wherein a spring pedestal at the end of the coarse winding is provided.
し、この粗巻部分にダンパー体から筒状に一体に延設し
てなる弾性パイプを上方から被嵌したことを特徴とする
請求項３記載の洗濯機の防振装置。5. The compression coil spring according to claim 1, wherein an upper portion of the compression coil spring is a coarsely wound portion, and an elastic pipe integrally and cylindrically extended from a damper body is fitted to the coarsely wound portion from above. 3. The vibration isolator of the washing machine according to 3.
ばねを介して槽体を弾性的に吊持する防振装置におい
て、前記吊り棒に挿通せられ該吊り棒と摺動摩擦接触す
るダンパ体を設け、このダンパ体と前記圧縮コイルばね
とで前記槽体を防振支持すると共に、圧縮コイルばねの
外径を径大及び径小部分とから構成し、この径小部分に
その外周面と摺動摩擦接触する筒状弾性パイプを被嵌し
たことを特徴とする洗濯機の防振装置。6. A vibration isolator for resiliently suspending a tub body via a suspension rod and a compression coil spring in an outer box of a washing machine, wherein the vibration absorber is inserted through the suspension rod and makes sliding frictional contact with the suspension rod. A damper body is provided, the tank body is vibration-isolated and supported by the damper body and the compression coil spring, and the outer diameter of the compression coil spring is comprised of a large diameter part and a small diameter part. A vibration isolator for a washing machine, wherein a cylindrical elastic pipe that comes into sliding friction contact with a surface is fitted.
端部を末広がりのテーパ状に形成したことを特徴とする
請求項６記載の洗濯機の防振装置。7. The vibration isolator for a washing machine according to claim 6, wherein the inner end portion of the compression coil spring of the elastic pipe on the large diameter side is formed to have a tapered shape diverging.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10286744A JP2000107488A (en) | 1998-10-08 | 1998-10-08 | Device for isolating vibration of washing machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10286744A JP2000107488A (en) | 1998-10-08 | 1998-10-08 | Device for isolating vibration of washing machine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2000107488A true JP2000107488A (en) | 2000-04-18 |
Family
ID=17708476
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10286744A Pending JP2000107488A (en) | 1998-10-08 | 1998-10-08 | Device for isolating vibration of washing machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2000107488A (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002364756A (en) * | 2001-06-08 | 2002-12-18 | Nok Corp | Sealing device |
| JP2008113980A (en) * | 2006-11-08 | 2008-05-22 | Hitachi Appliances Inc | Drum washing machine |
| WO2017114035A1 (en) * | 2015-12-30 | 2017-07-06 | 合肥海尔洗衣机有限公司 | Damping-variable vibration damping device for washing machine and washing machine |
| WO2017114036A1 (en) * | 2015-12-30 | 2017-07-06 | 合肥海尔洗衣机有限公司 | Washing machine variable damping shock absorbing device and washing machine |
| WO2017114037A1 (en) * | 2015-12-30 | 2017-07-06 | 合肥海尔洗衣机有限公司 | Washing machine variable damping shock absorbing device and washing machine |
| JP2018509566A (en) * | 2015-01-23 | 2018-04-05 | 青島海爾滾筒洗衣机有限公司 | Variable damping damper |
| CN108070982A (en) * | 2016-11-10 | 2018-05-25 | 青岛海尔洗衣机有限公司 | A kind of damping device of washing machine and washing machine |
| WO2019007339A1 (en) * | 2017-07-03 | 2019-01-10 | 青岛海尔洗衣机有限公司 | Shock absorption suspension rod assembly for washing machine, and washing machine |
| CN109736050A (en) * | 2019-02-11 | 2019-05-10 | 昌邑市永富弹簧有限公司 | Rotary drum washing machine damping assembly |
| CN113638193A (en) * | 2020-05-11 | 2021-11-12 | 青岛海尔洗衣机有限公司 | Suspender component and washing machine |
-
1998
- 1998-10-08 JP JP10286744A patent/JP2000107488A/en active Pending
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002364756A (en) * | 2001-06-08 | 2002-12-18 | Nok Corp | Sealing device |
| JP2008113980A (en) * | 2006-11-08 | 2008-05-22 | Hitachi Appliances Inc | Drum washing machine |
| JP2018509566A (en) * | 2015-01-23 | 2018-04-05 | 青島海爾滾筒洗衣机有限公司 | Variable damping damper |
| CN106930046A (en) * | 2015-12-30 | 2017-07-07 | 合肥海尔洗衣机有限公司 | A kind of washing machine mutative damp vibration absorber and washing machine |
| WO2017114037A1 (en) * | 2015-12-30 | 2017-07-06 | 合肥海尔洗衣机有限公司 | Washing machine variable damping shock absorbing device and washing machine |
| CN106930045A (en) * | 2015-12-30 | 2017-07-07 | 合肥海尔洗衣机有限公司 | A kind of washing machine mutative damp vibration absorber and washing machine |
| WO2017114036A1 (en) * | 2015-12-30 | 2017-07-06 | 合肥海尔洗衣机有限公司 | Washing machine variable damping shock absorbing device and washing machine |
| CN106930047A (en) * | 2015-12-30 | 2017-07-07 | 合肥海尔洗衣机有限公司 | A kind of washing machine mutative damp vibration absorber and washing machine |
| WO2017114035A1 (en) * | 2015-12-30 | 2017-07-06 | 合肥海尔洗衣机有限公司 | Damping-variable vibration damping device for washing machine and washing machine |
| CN106930046B (en) * | 2015-12-30 | 2020-06-19 | 合肥海尔洗衣机有限公司 | Variable-damping vibration attenuation device of washing machine and washing machine |
| CN108070982A (en) * | 2016-11-10 | 2018-05-25 | 青岛海尔洗衣机有限公司 | A kind of damping device of washing machine and washing machine |
| US11142859B2 (en) | 2016-11-10 | 2021-10-12 | Chongqing Haier Drum Washing Machine Co., Ltd. | Damping device for a washing machine, and washing machine |
| WO2019007339A1 (en) * | 2017-07-03 | 2019-01-10 | 青岛海尔洗衣机有限公司 | Shock absorption suspension rod assembly for washing machine, and washing machine |
| CN109736050A (en) * | 2019-02-11 | 2019-05-10 | 昌邑市永富弹簧有限公司 | Rotary drum washing machine damping assembly |
| CN113638193A (en) * | 2020-05-11 | 2021-11-12 | 青岛海尔洗衣机有限公司 | Suspender component and washing machine |
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