201217604 六、發明說明： 【發明所屬之技術領域】 本發明的實施形態，係關於一種藉由懸掛裝置防振支 撐水槽的洗衣機。 【先前技術】 以往，例如滾筒式洗衣機中，具備可在內部的旋轉的 滾筒的水槽，在筐體的底部藉由複數個懸掛裝置被彈性支 撐，並藉由該複數個懸掛裝置發揮降低伴隨著滾筒的旋轉 的振動的衰減功能。 而且，作爲懸掛裝置已知有使用例如藉由磁場的強度 使黏度改變的磁性黏性流體（MR流體）（例如參閱專利 文獻1 )。 磁性黏性流體由於是藉由磁場產生電路賦予磁場的方 式可控制流體的黏度，而作爲洗衣機的懸掛裝置被採用， 並對於隨著水槽的振動上下動（往復動）的軸件，使磁性 黏性流體接觸，藉由其黏性作爲抑制軸件的上下動的抵抗 發揮功能，進而使水槽的振動振幅衰減。 並可提供一種，藉由該衰減作用（阻尼器作用），迅 速使運轉時的振動衰減的低振動、低噪音的洗衣機。 [先行技術文獻] [專利文獻] [專利文獻1]日本特開2006 - 57766號公報 201217604 【發明內容】 [發明所欲解決之課題] 然而，由僅使用上述的磁性黏性流體的所謂流體阻尼 器手段構成的懸掛裝置中，要正確地可變控制對應其振動 振幅的大小的黏度並不容易。 又，在磁場產生電路等成爲不能通電的異常時，由於 衰減作用變的極微的小，所以具有引起異常振動等的不穩 定原因。 於此，提供一種除了流體阻尼器手段之外，設置經常 發揮衰減作用的摩擦阻尼器手段，謀求阻尼力的穩定化的 洗衣機。 [解決課題用的手段] 根據本實施形態的洗衣機，係一種在筐體內防震支撐 配設可在內部旋轉的洗滌槽的水槽的懸掛裝置的洗衣機， 其特徵爲：前述懸掛裝置是具備有：流體阻尼器手段與摩 擦阻尼器手段的構成，前述流體阻尼器手段具有：隨著前 述水槽的振動在筒狀的汽缸內往復動的軸件；以及被收容 在前述汽缸內，藉由電能量的施加改變黏性的功能性流體 ，該功能性流體的黏性，是構成以抵抗前述軸件的往復動 的方式發揮功能，進而使前述水槽的振動衰減，前述摩擦 阻尼器手段是經由前述流體阻尼器手段與前述軸件呈串聯 配置，振動時與前述軸件的往復動滑動抵接而發生摩擦力 ，該摩擦力是構成以抵抗前述軸件的往復動的方式發揮功 201217604 能，進而使前述水槽的振動衰減。 【實施方式】 [實施發明用的形態] (第1實施形態） 以下，參閱圖1至圖3，針對適用於滾筒式洗衣機的 第1實施形態進行說明。 首先，針對圖3所示的滾筒式洗衣機（以下僅稱爲洗 衣機）的整體構造進行說明。在形成外殻的箱狀的筐體1 的前面部（圖示右側）大致中央部，形成有洗滌物出入口 2，並設有開閉該洗滌物出入口 2的門扇3。 又，在筐體1的前面部的上部設有操作面板4,在其 裏側設有運轉控制用的控制裝置5。 在筐體1的內部配設有水槽6。該水槽6是以軸向作 爲前後而形成橫軸圓筒狀，筐體1的底板la上，藉由左 右一對（僅一方圖示）的懸掛裝置7(詳細容後敘述）以 朝前上方傾斜的狀態被彈性支撐。 在水槽6的背面部安裝有馬達8。該馬達8是例如由 直流的無刷馬達構成者，且爲外轉子形，並經由軸承托架 9將安裝在其轉子8a的中心部的未圖示的旋轉軸插到水 槽6的內部，而與後述的滾筒1〇的背面部的中央部連結 〇 滾筒10是作爲收容被配設在水槽6內部的洗滌物的 洗滌槽發揮功gg ’且是形成以其軸向作爲前後的橫軸圓筒 201217604 狀者，且如前述，與馬達8的旋轉軸連結被支撐成朝與水 槽6呈同軸狀的向前上方傾斜的狀態。 其結果，滾筒10是藉由馬達8直接被旋轉，而在橫 軸周圍旋轉，馬達8是作爲使滾筒10旋轉的滾筒驅動裝 置發揮功能。 又，在滾筒1 〇的周側部（胴部），在全區域形成有 許多可通水、通風的小孔1 1，而相對於此，水槽6基本 上爲無孔狀，並形成可貯水的構成。 該等滾筒10及水槽6皆在前面部具有開口部12、13 ，其中在水槽6的開口部13與洗滌物出入口 2之間，安 裝有環狀的波紋管14。 藉此，洗滌物出入口 2是形成經由：波紋管14、水 槽6的開口部1 3、及滾筒1 0的開口部1 2與滾筒10的內 部聯繫的形態。 在貯水可能的水槽6的最低部位’途在途中經由排水 閥1 5連接排水管1 6 ’而形成可朝機外進行排水。從該水 槽6的背面側跨到上方及前方配設有乾燥單元 該乾燥單元17是由具備有送風裝置19、加熱裝置20 、及未圖示的除濕手段等的循環導管18所構成’對從水 槽6內所排出的空氣中的水分進行除濕’接著進行加熱’ 所謂生成乾燥風，進行返回到水槽6內的返復循環’而使 被旋轉驅動的滾筒1〇內的洗滌物乾燥。 於此，針對前述的懸掛裝置7的具體構造進行說明。 除了圖3也參閱表示圖2的懸掛裝置7單體構造的縱剖視 -8- 201217604 圖進行說明。 懸掛裝置7,作爲其槪略構造是具備有··安裝在具有 筐體1的底板la的安裝板21側的圓筒狀的汽缸22;安 裝在具有水槽6的安裝板23側的軸件24 ;以及被安裝在 軸件24與汽缸22間的線圈彈簧25之構造。 該懸掛裝置7的具體的安裝構造，是在汽缸22的下 端部安裝汽缸連結部22a，並隔著橡膠等的彈性襯板26 以螺帽27將該連結部22a鎖緊在底板la的安裝板21， 藉此，將汽缸22安裝在底板1 a側的安裝板2 1。 另一方面，軸件24是由：由被插入到汽缸22的內部 (詳細容後敘述）的磁性構件構成的軸件主部24a :以及 由一體連結在其上端部的磁性構件構成的軸件連結部24b 所構成，並隔著橡膠等的彈性襯板28等以螺帽29將該軸 件連結部24b鎖緊在水槽6的安裝板23，而構成使軸件 24追隨水槽6的振動在上下方向等形成一體的振動的連 結構造。 此外，線圈彈簧2 5的安裝構造的詳細容後敘述，於 此槪述時，如圖2所示，在汽缸22的上端部支撐線圈彈 簧25的下端部，上端部被止擋在被配置在軸件24的上部 的圓板狀的彈簧支承板3 0，而以蓄積著彈發力的狀態被 安裝。 亦即，線圈彈簧25是以從汽缸22朝上方彈推軸件 24，亦即，朝汽缸22的外方以拉出的方式彈推的狀態被 張設。 -9- 201217604 接著，也參閱圖1的放大剖面圖針對汽缸22的內部 構造及其槪略構造進行說明。 在汽缸22內，將軸件24支承成可在直線上往復動（ 上下動）的軸承手段，在上、下部分開並以固定的方式被 設置，並且作成在其上、下部分開的軸承手段的中間部位 ，收容後述的功能性流體3 6及作爲磁場產生手段發揮功 能的線圈捲線軸單元3 7等的構造。 於此，首先，針對被設在上部側的軸承手段進行說明 時，藉由壓入或鉚接手段將中空筒狀的上部軸承盒31安 裝在汽缸22的開口上端部，將例如由燒結含油金屬構成 的軸承32以壓入狀態嵌合固定在其上部軸承盒31內部， 而可滑動地軸支軸件24的上半部側。 此外，雖設有在上部軸承盒31的上部呈一體突設的 彈簧承部48，可是關於該詳細容後敘述。 而相對於此，針對被配置在下部側的軸承手段進行說 明時（參閱圖2)，下部側軸承手段是位在汽缸22的上 下方向的大致中間部，並藉由壓入或鉚接手段固定性的安 裝中空筒狀的下部軸承盒33。 在軸承盒33的中空內部，是與前述同樣將由燒結含 油金屬構成的軸承32以壓入狀態予以嵌合固定。 此結果，被插到汽缸22內的軸件24是藉由位在汽缸 22的上端部及中間部（下部）的軸承手段，被支撐成可 以直線在上下方向往復作動。 可是’如前述，在安裝了線圈彈簧2 5的狀態下，由201217604 VI. Description of the Invention: [Technical Field of the Invention] An embodiment of the present invention relates to a washing machine for supporting a water tank by a suspension device. [Prior Art] Conventionally, for example, a drum type washing machine includes a water tank that can rotate inside, and is elastically supported by a plurality of suspension devices at the bottom of the casing, and is reduced by the plurality of suspension devices. The attenuation function of the vibration of the rotation of the drum. Further, as the suspension device, a magnetic viscous fluid (MR fluid) which changes viscosity by, for example, the strength of a magnetic field is known (for example, see Patent Document 1). The magnetic viscous fluid can control the viscosity of the fluid by the magnetic field generating circuit to impart a magnetic field, and is used as a suspension device of the washing machine, and magnetically viscous for the shaft member that moves up and down (reciprocating) with the vibration of the water tank. The contact of the fluid fluid functions as a function of suppressing the up and down movement of the shaft member, thereby attenuating the vibration amplitude of the water tank. It is also possible to provide a low-vibration, low-noise washing machine which rapidly attenuates vibration during operation by the damping action (damper action). [PRIOR ART DOCUMENT] [Patent Document 1] [Patent Document 1] JP-A-2006-57766 (2012) The present invention provides a so-called fluid damping using only the above-described magnetic viscous fluid. In the suspension device constituted by the means, it is not easy to accurately control the viscosity corresponding to the magnitude of the vibration amplitude. Further, when an abnormality in which the magnetic field generating circuit or the like is not energized, the attenuation action becomes extremely small, and therefore there is a cause of instability such as abnormal vibration. Here, there is provided a washing machine which is provided with a friction damper means which often exhibits a damping effect in addition to the fluid damper means, and which stabilizes the damping force. [Means for Solving the Problem] The washing machine according to the present embodiment is a washing machine that is provided with a suspension device for supporting a water tank of a washing tub that can be rotated inside, and is characterized in that the suspension device is provided with a fluid. a damper means and a friction damper means, the fluid damper means having a shaft member that reciprocates in a cylindrical cylinder in accordance with vibration of the water tank; and is housed in the cylinder, by application of electric energy a functional fluid that changes viscosity, and the viscosity of the functional fluid is configured to function to resist reciprocation of the shaft member, thereby attenuating vibration of the water tank, and the friction damper means is via the fluid damper The means is disposed in series with the shaft member, and a frictional force is generated in contact with the reciprocating sliding movement of the shaft member during vibration, and the frictional force is configured to perform the work of resisting the reciprocating motion of the shaft member, thereby enabling the water tank Vibration attenuation. [Embodiment] [Embodiment for Carrying Out the Invention] (First Embodiment) Hereinafter, a first embodiment applied to a drum type washing machine will be described with reference to Figs. 1 to 3 . First, the overall structure of the drum type washing machine (hereinafter simply referred to as a washing machine) shown in Fig. 3 will be described. A laundry doorway 2 is formed in a substantially central portion of a front portion (right side of the drawing) of the box-shaped casing 1 forming the outer casing, and a door leaf 3 for opening and closing the laundry doorway 2 is provided. Further, an operation panel 4 is provided on the upper portion of the front portion of the casing 1, and a control device 5 for operation control is provided on the inner side. A water tank 6 is disposed inside the casing 1. The water tank 6 is formed in a horizontal axis in the axial direction as a front-rear direction, and the bottom plate 1a of the casing 1 is attached to the front and the upper by a pair of right and left (only one of them) suspension devices 7 (described in detail). The inclined state is elastically supported. A motor 8 is attached to the back surface of the water tank 6. The motor 8 is formed of, for example, a DC brushless motor, and has an outer rotor shape, and a rotating shaft (not shown) attached to a central portion of the rotor 8a is inserted into the water tank 6 via a bearing bracket 9. The cymbal 10 is connected to the center of the back surface of the drum 1 后 which will be described later. The cymbal cylinder 10 functions as a washing tank that accommodates the laundry disposed inside the water tank 6 and is formed as a horizontal axis cylinder with its axial direction as the front and rear. As described above, in the case of 201217604, the rotation shaft of the motor 8 is coupled to be supported in a state of being inclined upward and upward in a coaxial shape with the water tank 6. As a result, the drum 10 is rotated by the motor 8 and rotated around the horizontal axis, and the motor 8 functions as a drum driving device that rotates the drum 10. Further, in the circumferential side portion (the crotch portion) of the drum 1 ,, a plurality of water-permeable and ventilating small holes 1 1 are formed in the entire area, whereas the water tank 6 is substantially non-porous and forms a water-storable water. Composition. Each of the drum 10 and the water tank 6 has openings 12, 13 at the front portion thereof, and an annular bellows 14 is fitted between the opening portion 13 of the water tank 6 and the laundry inlet and outlet 2. Thereby, the laundry inlet/outlet 2 is formed by the bellows 14, the opening portion 13 of the water tank 6, and the opening portion 1 2 of the drum 10 in contact with the inner portion of the drum 10. The drain pipe 16 is connected to the drain portion 1 5 via the drain valve 15 in the middle of the lowest portion of the water tank 6 where the water storage is possible, so that drainage can be performed outside the machine. A drying unit is disposed from the back side of the water tank 6 to the upper side and the front side. The drying unit 17 is constituted by a circulation duct 18 including a blower 19, a heating device 20, and a dehumidifying means (not shown). The moisture in the air discharged from the water tank 6 is dehumidified and then heated. The dry air is generated, and the returning loop is returned to the inside of the water tank 6 to dry the laundry in the drum 1 that is rotationally driven. Here, the specific structure of the suspension device 7 described above will be described. In addition to Fig. 3, a longitudinal sectional view -8-201217604 showing a single structure of the suspension device 7 of Fig. 2 will be described. The suspension device 7 is provided with a cylindrical cylinder 22 attached to the mounting plate 21 side of the bottom plate 1a of the casing 1 as a schematic structure thereof, and a shaft member 24 attached to the mounting plate 23 side having the water tank 6. And the configuration of the coil spring 25 mounted between the shaft member 24 and the cylinder 22. The specific mounting structure of the suspension device 7 is such that the cylinder connecting portion 22a is attached to the lower end portion of the cylinder 22, and the connecting portion 22a is locked to the mounting plate of the bottom plate la by the elastic lining 26 of rubber or the like with the nut 27 interposed therebetween. 21, whereby the cylinder 22 is mounted on the mounting plate 21 on the side of the bottom plate 1a. On the other hand, the shaft member 24 is composed of a shaft main portion 24a composed of a magnetic member inserted into the inside of the cylinder 22 (described later in detail): and a shaft member composed of a magnetic member integrally coupled to the upper end portion thereof. The connecting portion 24b is configured to lock the shaft connecting portion 24b to the mounting plate 23 of the water tank 6 with a nut 29 via an elastic lining plate 28 such as rubber, and the like, so that the shaft member 24 follows the vibration of the water tank 6. An integrated vibration connection structure is formed in the vertical direction or the like. In addition, the mounting structure of the coil spring 25 will be described later in detail. As will be described later, as shown in FIG. 2, the lower end portion of the coil spring 25 is supported at the upper end portion of the cylinder 22, and the upper end portion is stopped at the end. The disk-shaped spring supporting plate 30 of the upper portion of the shaft member 24 is attached in a state in which the spring force is accumulated. In other words, the coil spring 25 is in a state in which the shaft member 24 is pushed upward from the cylinder 22, that is, in a state of being pulled outward toward the outside of the cylinder 22. -9- 201217604 Next, the internal structure of the cylinder 22 and its schematic structure will be described with reference to the enlarged cross-sectional view of Fig. 1 . In the cylinder 22, the shaft member 24 is supported as a bearing means capable of reciprocating (up and down) in a straight line, which is separated and fixed in the upper and lower portions, and is formed as a bearing which is separated at the upper and lower portions thereof. The intermediate portion of the means accommodates a functional fluid 36 to be described later, a coil bobbin unit 37 that functions as a magnetic field generating means, and the like. First, when the bearing means provided on the upper side is described, the hollow cylindrical upper bearing cartridge 31 is attached to the upper end of the opening of the cylinder 22 by press fitting or caulking means, for example, made of sintered oil-containing metal. The bearing 32 is fitted and fixed inside the upper bearing housing 31 in a press-fit state, and slidably supports the upper half side of the shaft member 24. Further, although the spring receiving portion 48 integrally formed on the upper portion of the upper bearing housing 31 is provided, the details will be described later. On the other hand, when the bearing means disposed on the lower side is described (see FIG. 2), the lower-side bearing means is located at a substantially intermediate portion in the vertical direction of the cylinder 22, and is fixed by press-fitting or riveting means. A hollow cylindrical lower bearing housing 33 is mounted. In the hollow interior of the bearing housing 33, the bearing 32 made of a sintered oil-containing metal is fitted and fixed in a pressed state as described above. As a result, the shaft member 24 inserted into the cylinder 22 is supported by the bearing means positioned at the upper end portion and the intermediate portion (lower portion) of the cylinder 22 so as to be reciprocally movable in the vertical direction. However, as described above, in the state in which the coil spring 25 is mounted,
Cc -10· 201217604 於軸件22是位在朝上方（外方）被彈推的狀態，所以設 在軸件22的下端部的擋環34與下部軸承盒33衝撞，亦 即軸件22以朝上方防止脫落的狀態被收容。 此外，比下部軸承盒33更位在下面的汽缸22內，形 成有考慮到軸件22的下降衝程的大小的空洞3 5。 於此，針對被收容在上、下部軸承盒3 1、3 3間的功 能性流體3 6及作爲磁場產生手段發揮功能的線圏捲線軸 單元3 7等的構造進行說明。 首先，針對線圈捲線軸單元37的構造進行敘述時， 線圈捲線軸單元3 7是在圓筒狀的捲線軸3 8捲裝產生磁場 (magnetic fi el )的線圈39，例如在本實施形態，是作成 上下兩段捲裝的上線圈39a、下線圈39b的構造。 如此，構成在配置有位在捲裝有線圈39的捲線軸38 的上部、下部、及其中間的各軛40、42、及41的狀態下 ，作成樹脂鑄模（鑄模部47 )的一體構成的線圈捲線軸 單元37。 將該線圈捲線軸單元37的鑄模部47的外周面側嵌合 在汽缸22的內周面，而被安裝收容在汽缸22內。 此外，被安裝的線圈捲線軸單元3 7的筒狀中空部， 是在被插入的軸件24的外周面之間形成環狀的狹小的空 隙G。 又，在位在線圈捲線軸單元3 7的上端部的上部軛40 的上面側，環狀的流體密封43壓入其外周圍的剛性部分 並予以固定，使唇狀的內周圍與軸件24的外周面緊貼而 -11 - 201217604 形成封閉的構造。 又，在位於下端部的下部軛41的下面側，壓入固定 有上述同樣的流體密封43，而與軸件24的外周面緊貼並 予以封閉。 因此，空隙G是以各流體密封43封閉其上下端部， 而在整體形成筒狀的空間，並且，各流體密封43是以個 別的上、下部軸承盒31、3 3從外方側挾持的方式被支撐 ，而以確實防止脫落的狀態被安裝。 又，如圖2所示，利用中間軛42，經由安裝在汽缸 22的墊圏45，將從串連連接的上、下線圈39a、39b分別 拉出的導線44導出到外部，並與未圖示的驅動電路連接 〇 在導線44覆蓋保護用的管子46。 而且’在上述構成的空隙G內塡充有功能性流體36 (圖1、2中’以塗白的狀態表示）。此外，被形成在軸 件2 4與線圈捲線軸單元3 7之間的空隙G，雖是形成筒狀 的空間’尤其是與各軛4 0、4 1、4 2對應的間隙被形成最 狹小’並且藉由配置在上下部的流體密封4 3作成功能性 流體36不爲洩漏的封閉構成。 於此’針對功能性流體3 6的特性等進行敘述。功能 性流體3 6是控制從外部所施加的物理量，使黏性等的流 變性的性質功能性的改變的流體，具體而言，作爲藉由電 能量的施加使黏性改變的流體，例如相當於依據磁場（ magnetic field )的強度使黏性特性改變的磁性黏性流體 -12- 201217604 (MR流體），或依據電場（electric field)的強度使黏 性特性改變的電黏性流體（ER流體）等。 這之中，前者的磁性黏性流體（MR流體）是例如使 鐵、羰基鐵等的強磁性粒子在油中分散者，施加磁場時強 磁性粒子形成鎖狀的群組，而具有具有外觀上的黏度上昇 的特性。以下，進行在本實施形態，採用上述磁性黏性流 體作爲功能性流體3 6時的作用說明等。 依據通過導線44流到線圈3 9的電流値產生磁場的磁 場產生手段的線圏捲線軸單元3 7，是可控制作爲功能性 流體3 6的磁性黏性流體的黏性。 其產生的磁場，由於是依據電流値可以改變，所以可 容易可變控制磁性黏性流體的黏性。 接著，針對先前槪述的線圈彈簧25的特別是下端部 的安裝構造進行詳細的敘述。 亦即，如圖1、2所示，在本實施形態，利用位在汽 缸22的上端部的上部軸承盒3 1，設置在其上面側呈一體 突出形成的彈簧承部48。 該彈簧承部48是具有形成徑小筒狀的筒狀部48a。 因此，該彈簧承部48被形成在比汽缸22的上端部更突出 的位置。 在該筒狀部48a的基部與上部軸承盒31的邊界部分 ，由不同徑所形成的段差部49，在該段差部49，從下方 支撐線圈彈簧2 5的下端部。 於此，線圈彈簧25的下端部相對於彈簧承部48的筒 -13- 201217604 狀部48a的外周基部不會自由移動的方式，嵌合線圈彈簧 25，且隨著愈往筒狀部48a的上部愈鬆的嵌合，亦即形成 滑動嵌合的形態，確實支撐線圈彈簧25的下端部。 此外，將線圈彈簧2 5滑動結合在筒狀部4 8 a的形態 ，是也可將筒狀部48a形成尖錐狀，或也可作成線圏彈簧 2 5的內徑慢慢放大的形狀。 又，筒狀部48a的長度（高度尺寸），是設成比線圈 彈簧25的緊貼長度形成的更小。這是因爲筒狀部48a的 上端部不會與彈簧支承板3 0抵接，可有效發揮到線圈彈 簧25的最大限度的壓縮狀態的功能。 再者，如圖1所示，在彈簧承部48的內部，形成比 插穿到中心的軸件24更徑大的圓形狀的外周，且有形成 具有相當於筒狀部48a的長度（高度）的深度的凹處50 〇 在該凹處50內，藉由從上方壓入兩個圓環狀的密封 構件51的方式嵌合，並且以上下相對的狀態進行配置， 在其兩者的對向間形成有由環狀的間隙構成的溝狀部5 2 〇 各密封構件51爲放入彈簧的油封，且具有複數個例 如兩條的唇狀5 1 a、5 1 b，其內側的唇狀5 1 a是經由彈簧 5 1c與軸件24緊貼，尤其作爲密封用唇狀發揮功能。又 ，外側的唇狀5 1 b主要作爲粉塵用唇作爲防止粉塵侵入發 揮功能，可是，皆與被插入內部的軸件24緊貼’發揮以 液密封閉的功能。Cc -10· 201217604 The shaft member 22 is in a state of being pushed upward (outside), so that the retaining ring 34 provided at the lower end portion of the shaft member 22 collides with the lower bearing cartridge 33, that is, the shaft member 22 is The state in which it is prevented from falling upward is accommodated. Further, the lower bearing housing 33 is positioned in the lower cylinder 22, and a cavity 35 is formed in consideration of the magnitude of the descending stroke of the shaft member 22. Here, the structure of the functional fluid 3 6 accommodated between the upper and lower bearing cartridges 3 1 and 3 3 and the coil bobbin unit 3 7 functioning as a magnetic field generating means will be described. First, when the structure of the coil bobbin unit 37 is described, the coil bobbin unit 37 is a coil 39 that generates a magnetic field (magnetic fi el ) in a cylindrical bobbin 38. For example, in the present embodiment, The upper coil 39a and the lower coil 39b of the upper and lower windings are constructed. In this manner, the resin dies (molding portions 47) are integrally formed in a state in which the yokes 40, 42, and 41 are disposed in the upper portion, the lower portion, and the intermediate portion of the bobbin 38 on which the coil 39 is wound. Coil bobbin unit 37. The outer peripheral surface side of the mold portion 47 of the coil bobbin unit 37 is fitted to the inner peripheral surface of the cylinder 22, and is housed and housed in the cylinder 22. Further, the cylindrical hollow portion of the coil bobbin unit 37 to be mounted is a narrow gap G formed in an annular shape between the outer peripheral surfaces of the inserted shaft members 24. Further, at the upper surface side of the upper yoke 40 at the upper end portion of the coil bobbin unit 37, the annular fluid seal 43 is pressed into the rigid portion of the outer periphery thereof and fixed, so that the inner periphery of the lip and the shaft member 24 are fixed. The outer peripheral surface is close to the -11 - 201217604 to form a closed structure. Further, the same fluid seal 43 as described above is press-fitted and fixed to the lower surface side of the lower yoke 41 located at the lower end portion, and is in close contact with and closed to the outer peripheral surface of the shaft member 24. Therefore, the gap G is a space in which the upper and lower end portions are closed by the respective fluid seals 43, and the cylindrical space is integrally formed, and each of the fluid seals 43 is held by the outer upper and lower bearing boxes 31, 33 from the outer side. The mode is supported, and is installed in a state of being surely prevented from coming off. Further, as shown in FIG. 2, the intermediate yoke 42 is used to guide the lead wires 44 that are respectively pulled out from the series-connected upper and lower coils 39a and 39b via the pad 45 attached to the cylinder 22, and is not shown. The illustrated drive circuit is connected to the conductor 44 for covering the conductor 46. Further, the functional fluid 36 is filled in the gap G having the above configuration (indicated by the whitened state in Figs. 1 and 2). Further, the gap G formed between the shaft member 24 and the coil bobbin unit 3 7 is formed into a cylindrical space, in particular, the gap corresponding to each of the yokes 40, 4 1 and 4 2 is formed to be the narrowest. 'And by the fluid seal 4 disposed in the upper and lower portions, the functional fluid 36 is configured to be closed without leakage. Here, the characteristics and the like of the functional fluid 36 will be described. The functional fluid 36 is a fluid that changes the physical quantity applied from the outside and functionally changes the properties of rheology such as viscosity, and specifically, a fluid that changes viscosity as a result of application of electric energy, for example, A magnetic viscous fluid -12-201217604 (MR fluid) that changes viscosity characteristics according to the strength of a magnetic field, or an viscous fluid (ER fluid) that changes viscosity characteristics according to the strength of an electric field )Wait. Among them, the magnetic viscous fluid (MR fluid) of the former is, for example, a ferromagnetic particle such as iron or carbonyl iron which is dispersed in oil. When a magnetic field is applied, the ferromagnetic particles form a lock-like group, and have a appearance. The characteristic of the viscosity rise. Hereinafter, the operation and the like when the above-described magnetic viscous fluid is used as the functional fluid 36 will be described in the present embodiment. The bobbin bobbin unit 37, which is a magnetic field generating means for generating a magnetic field by the current flowing through the wire 44 to the coil 39, is a viscosity which can control the magnetic viscous fluid as the functional fluid 36. The magnetic field generated by the magnetic field can be changed variably according to the current, so that the viscosity of the magnetic viscous fluid can be easily controlled. Next, the attachment structure of the coil spring 25, which will be described in detail, in particular, the lower end portion will be described in detail. That is, as shown in Figs. 1 and 2, in the present embodiment, the upper bearing housing 31 is positioned on the upper end portion of the cylinder 22, and a spring receiving portion 48 integrally formed on the upper surface side thereof is provided. The spring receiving portion 48 has a tubular portion 48a having a small cylindrical shape. Therefore, the spring receiving portion 48 is formed at a position more protruding than the upper end portion of the cylinder 22. At a boundary portion between the base portion of the tubular portion 48a and the upper bearing cartridge 31, a step portion 49 formed of a different diameter supports the lower end portion of the coil spring 25 from the lower portion. Here, the lower end portion of the coil spring 25 is fitted with the coil spring 25 so as not to move freely with respect to the outer peripheral base portion of the cylinder-13-201217604 portion 48a of the spring receiving portion 48, and as it goes to the cylindrical portion 48a The looser upper portion fits, that is, the form in which the sliding fit is formed, and the lower end portion of the coil spring 25 is surely supported. Further, in a form in which the coil spring 25 is slidably coupled to the tubular portion 48a, the tubular portion 48a may be formed in a tapered shape, or the inner diameter of the coil spring 25 may be gradually enlarged. Further, the length (height size) of the tubular portion 48a is set to be smaller than the contact length of the coil spring 25. This is because the upper end portion of the tubular portion 48a does not abut against the spring supporting plate 30, and the function of maximizing the compression state of the coil spring 25 can be effectively exhibited. Further, as shown in FIG. 1, in the inside of the spring receiving portion 48, a circular outer circumference which is larger than the shaft member 24 inserted through the center is formed, and a length corresponding to the cylindrical portion 48a is formed (height). The recess 50 in the depth of the recess 50 is fitted in the recess 50 by pressing the two annular sealing members 51 from above, and is disposed in the upper and lower opposite states, in the pair of the two A groove portion 5 2 formed of an annular gap is formed therebetween. Each sealing member 51 is an oil seal that is placed in a spring, and has a plurality of, for example, two lips 5 1 a, 5 1 b, and an inner lip thereof. The shape 51 1 a is in close contact with the shaft member 24 via the spring 5 1c, and particularly functions as a lip for sealing. Further, the outer lip shape 5 1 b functions mainly as a dust-proof lip as a dust intrusion prevention function, but both of them are in close contact with the shaft member 24 inserted therein to function as a liquid-tight seal.
Cc- -14- 201217604 藉由這之中的上下相對的內側的各唇狀51a、51a在 軸件24周圍形成有前述溝狀部52，並且，作爲其前端側 (中心側）的軸件24側形成有預定寬幅（上下方向）的 開放的間隙。 然後，在本實施形態，在該溝狀部52塡充半固體狀 的潤滑油5 3 (圖1中以虛線陰影線表示）。因此，溝狀 部5 2作爲潤滑油積存部發揮功能，並且，潤滑油5 3與軸 件24的外周面經常以預定寬幅形成面接觸。 此外，形成半固體狀的潤滑油53的硬度，是採用具 有JIS (日本工業規格）分類0號〜3號的稠度（是指糊狀 物質的硬度、軟度、流動性等的意思的用語）的尿素系潤 滑油。 並且，藉由上述構成構成懸掛裝置7，懸掛裝置7是 以左右一對被安裝在水槽6與筐體1的底板ia之間，而 構成在筐體1的底板la上彈性支撐水槽6。 接著，敘述上述構成的洗衣機的作用。 在具備本實施形態的橫軸周圍的滾筒1 0的洗衣機， 在洗衣、洗清、脫水、及乾燥的各行程，控制裝置5分別 以適當的旋轉速度驅動控制滾筒1 0的方式執行運轉。 而且’滚筒10因被收容在滾筒10內的洗滌物造成不 平衡負載等的原因而振動，被彈性支撐的水槽6以上下方 向爲主體進行振動。 與該水槽6的上下振動互動，在懸掛裝置7，經由一 體連結在水槽6的軸件2 4，使線圏彈簧2 5伸縮，軸件2 4 -15- 201217604 在汽缸22內朝上下方向振動（往復作動）° 線圈彈簧25是藉由其伸縮作用吸收振動’並有效果 地阻止往筐體1 (底板1 a )側的振動傳達。 另—方面，在汽缸22內，由於在被形成在圓筒狀的 線圈捲線軸單元3 7的中空部與軸件2 4的外周面之間的空 隙G，塡充有功能性流體3 6 (於此爲磁性黏性流體）’ 所以功能性流體3 6的黏性作爲相對於軸件2 4的上下方向 的往復作動的摩擦抵抗發揮功能，而形成迅速使水槽6的 振動振幅衰減的作用。 而且，在旋轉驅動滾筒1〇的運轉時’對線圈39通電 產生磁場。藉此，在上下呈兩段配置的各線圈39a、39b 的周圍形成磁路，其中尤其是磁束密度高的各軛40、41 、4 2與軸件2 4之間，在空隙G之中成爲狹小的間隙。 因此，對功能性流體3 6賦予磁場時，該部位的磁性 黏性流體的黏度急速提高，對於軸件24的上下方向的往 復作動的摩擦抵抗增大，結果，迅速使水槽6的振動振幅 衰減。 如此，將捲線軸3 8 ;線圈3 9 ;軛40、41、42等一體 化的捲線軸線圈單元3 7，是作爲磁場產生手段發揮功能 〇 又，接收到該磁場產生手段所產生的磁場的功能性流 體36，提昇其黏度，並發揮作爲對軸件24的往復作動抵 抗的機能，而獲得振動的衰減作用，即構成所謂在本實施 形態所說的流體阻尼器手段者，尤其對於在高速旋轉滾筒Cc - -14 - 201217604 The groove portion 52 is formed around the shaft member 24 by the lip portions 51a, 51a on the upper and lower sides of the upper and lower sides, and the shaft member 24 as the front end side (center side) thereof The side is formed with an open gap of a predetermined width (up and down direction). Then, in the present embodiment, the groove portion 52 is filled with a semi-solid lubricating oil 5 3 (indicated by a broken line in Fig. 1). Therefore, the groove portion 52 functions as a lubricating oil reservoir, and the lubricating oil 53 and the outer peripheral surface of the shaft member 24 are often brought into surface contact with a predetermined width. In addition, the hardness of the semi-solid lubricating oil 53 is a viscosity having a consistency of the JIS (Japanese Industrial Standards) classification No. 0 to No. 3 (meaning the hardness, softness, fluidity, etc. of the pasty substance). Urea-based lubricants. Further, the suspension device 7 is configured by the above-described configuration, and the suspension device 7 is attached between the water tank 6 and the bottom plate ia of the casing 1 in a pair of right and left, and the water tank 6 is elastically supported on the bottom plate 1a of the casing 1. Next, the action of the washing machine having the above configuration will be described. In the washing machine including the drum 10 around the horizontal axis of the present embodiment, the control device 5 performs the operation of driving the control drum 10 at an appropriate rotational speed for each stroke of washing, washing, dehydrating, and drying. Further, the drum 10 vibrates due to an unbalanced load or the like caused by the laundry contained in the drum 10, and the water tank 6 that is elastically supported vibrates in the lower direction. The upper and lower vibrations of the water tank 6 interact with each other, and the suspension member 7 is integrally coupled to the shaft member 24 of the water tank 6 to expand and contract the coil spring 25, and the shaft member 2 4 -15 - 201217604 vibrates in the cylinder 22 in the up and down direction. (Reciprocating operation) The coil spring 25 absorbs vibration by its expansion and contraction and effectively prevents vibration from being transmitted to the casing 1 (base plate 1 a ) side. On the other hand, in the cylinder 22, since the gap G formed between the hollow portion of the cylindrical coil bobbin unit 37 and the outer peripheral surface of the shaft member 24 is filled with the functional fluid 3 6 ( Here, it is a magnetic viscous fluid). Therefore, the viscosity of the functional fluid 36 functions as a frictional resistance against the reciprocating action of the vertical direction of the shaft member 24, and forms a function of rapidly attenuating the vibration amplitude of the water tank 6. Further, when the rotation of the drum 1 is operated, the coil 39 is energized to generate a magnetic field. Thereby, a magnetic circuit is formed around each of the coils 39a and 39b arranged in two stages, in which, among the yokes 40, 41, and 42 having a high magnetic flux density, and the shaft member 24, in the gap G, Small gaps. Therefore, when a magnetic field is applied to the functional fluid 36, the viscosity of the magnetic viscous fluid at the portion is rapidly increased, and the frictional resistance against the reciprocating motion of the shaft member 24 in the vertical direction is increased, and as a result, the vibration amplitude of the water tank 6 is rapidly attenuated. . In this manner, the bobbin 3 8 ; the coil 3 9 ; the yoke 40 , 41 , 42 and the like are integrated as the magnetic field generating means, and receive the magnetic field generated by the magnetic field generating means. The functional fluid 36 lifts its viscosity and exerts its function as a resistance to the reciprocating action of the shaft member 24, thereby obtaining the damping effect of the vibration, that is, the so-called fluid damper means in the present embodiment, especially at a high speed. Rotating drum
-16- 201217604 ι〇的脫水運轉時所產生的大幅的振動振幅，可發揮有效 的衰減作用。 相對於此，活用彈簧承部48的筒狀部48a，由於相 當於收納在其中空內部的高黏度的硬度的半固體狀的潤滑 油5 3，經常處於與軸件24接觸的狀態，所以，可獲得隨 著軸件24的往復作動的預定的摩擦力，而形成經由軸件 24使水槽6的振動衰減的作用，即作爲所謂在本實施形 態所說的摩擦阻尼器手段發揮功能。 因此，摩擦阻尼器手段，是適合經常發揮與流體阻尼 器手段不同，但實質上不變的機械性一定的摩擦力。此外 ，此時的摩擦力嚴格來說雖是藉由作爲潤滑油53的洩漏 防止與潤滑油5 3的貯留部發揮功能的唇狀5 1 a或唇狀 5 1 b對軸件24的接觸壓作爲摩擦力輔助性的加強，可是 在本實施形態，是以潤滑油53所爲的摩擦作用爲主體進 行說明。 又，爲了構成摩擦阻尼器手段雖活用彈簧承部48, 可是其筒狀部48a防止線圈彈簧25的大幅的傾倒或彎曲 具有效果。 該筒狀部48a，比汽缸22的上端部更位於外方（上 方），因此，密封構件51或潤滑油5 3雖位在汽缸22外 ，可是，由於滑動接合在筒狀部48 a的外周的線圈彈簧 25，在與本來必要的有效長度的一部分重複（重疊）的範 圍可構成摩擦阻尼器手段，所以，不會發生爲了設置阻尼 器手段，必須將具備流體阻尼器手段的懸掛裝置7的全長 -17- 201217604 構成的更長等的不理想的情況。 倂用使用功能性流體3 6的流體阻尼器手段、與使用 具有半固體狀的硬度的潤滑油53的摩擦阻尼器手段，可 更進一步有效作爲也包含線圈彈簧2 5的防振作用的洗衣 機的防振用的懸掛裝置7發揮功能。 其中，作爲摩擦阻尼器手段，如上述，經常發揮一定 的衰減作用（阻尼器作用），且由於可確保，因此，可期 待懸掛裝置7所爲的衰減作用的穩定化。 又，本來在作爲懸掛裝置7的主力的流體阻尼器手段 ，即使有例如因捲線軸線圈單元3 7的故障而不能通電， 或無法馬上對應振動等有效發揮功能時，由於也可藉由最 小限度摩擦阻尼器手段所爲的衰減作用有效地發揮功能， 所以作爲洗衣機的懸掛裝置7，可貢獻對振動的安全性或 穩定化。 如以上說明，根據第1實施形態所示的洗衣機，是防 振支撐在內部具有旋轉滾筒1 0的水槽6的懸掛裝置7， 且懸掛裝置7是具備有：流體阻尼器手段與摩擦阻尼器手 段的構造。 流體阻尼器手段是具有：隨著水槽6的振動，在筒狀 的汽缸22內往復作動的軸件24 ;以及被收容在汽缸22 內，藉由電能量的施加，使黏性改變的功能性流體3 6 ( 在本實施形態爲磁性黏性流體），該功能性流體3 6的黏 性，是以抵抗軸件24的往復作動的方式發揮功能，而使 水槽6的振動衰減。 -18- 201217604 另一方面，摩擦阻尼器手段，是構成對於流體阻尼器 手段，經由軸件22成串聯配置，振動時，與軸件22的往 復作動滑動抵接產生摩擦力，該摩擦力是以抵抗軸件22 的往復作動的方式發揮功能，使水槽6的振動衰減。 根據這樣的構成的懸掛裝置7，可提供藉由主體的流 體阻尼器手段迅速使水槽6的振動衰減之低振動、低噪音 的洗衣機。例如，由於可改變控制功能性流體3 6的黏度 ，所以依據振動振幅的大小的控制、或滾筒式洗衣機的行 程別的控制等可以執行適當的衰減控制。 除了該流體阻尼器手段，具備補助性功能的摩擦阻尼 器手段，由於可經常藉由大致一定的摩擦力獲得衰減作用 ，所以結果可使懸掛裝置7所爲的衰減作用穩定化。 再者，即使主體的流體阻尼器手段因某種原因而不能 適當發揮功能時，可獲得最低限度的摩擦阻尼器手段所爲 的衰減作用，並可期待可迴避到達異常振動或異常運轉爲 止等的實用的效果。 又，懸掛裝置7具備由從汽缸22朝外方拉出的方向 彈推軸件24的線圈彈簧25，對於在水槽6側所發生的振 動，使線圈彈簧3 5伸縮，使振動不會傳達到筐體1側。 摩擦阻尼器手段是位在支撐該線圈彈簧25的一端的 汽缸22的外端部，並配置在以線圏彈簧25圍繞周圍的範 圍。亦即，摩擦阻尼器手段，是位在作爲線圈彈簧25需 要的有效長的範圍內，且設置在與線圈彈簧25的一部分 重疊的位置，所以不需加大（增長）具有流體阻尼器手段 -19- 201217604 的懸掛裝置7，可添加摩擦阻尼器手段，所以製作及組裝 上有利。 更具體而言’在汽缸22的外端部設置嵌合支撐線圏 彈簧2 5的一端的筒狀的彈簧承部4 8，作爲彈簧承部4 8 的筒狀長度的筒狀部48a，是形成的比線圏彈簧25的緊 貼長度更小。 藉此，筒狀部48a的上端部不會與彈簧支承板30抵 接而可以伸縮，這是因爲作爲防振用線圈彈簧2 5壓縮到 最大限度的壓縮狀態爲止可使線圈彈簧25有效地發揮功 能。 此外，彈簧承部48在本實施形態，雖是藉由與上部 軸承盒31 —體成形的方式設置，而容易進行製作或組立 ，可是也可將該等以不同構件進行組裝構成。 而且，摩擦阻尼器手段所產生的摩擦力，是作可藉由 與軸件24滑動抵接的兩個密封構件5 1與半固體狀的潤滑 油53可獲得的構造。 因此，可抑制大的摩擦音或不舒服的摩擦音的發生， 並與流體阻尼器手段一起達成懸掛裝置7的靜音化。作爲 潤滑油53，表示其硬度的稠度，JIS分類0號~3號的尿 素系潤滑油可獲的所期望的衰減作用。 又，在本實施形態，作爲潤滑油積存部，將兩個密封 構件51在上下呈相對向的配置，在其間以環狀形成在軸 件24側開放的溝狀部52，並作成在該溝狀部52塡充有 潤滑油53的構成。 -20- 201217604 被充塡的潤滑油53，是藉由上下配置的密封構件51 不會漏出到外部並可確實被保持，且與軸件24滑動抵接 ，可長期間發揮一定的摩擦力。 此時，也可作爲兼具在流體阻尼器手段採用的流體密 封43。例如，尤其如圖1所示，被配置在上部軛40的上 部的流體密封43，防止從下方往上方的功能性流體36的 洩漏。 於此，以下部側的密封構件5 1代用流體密封43，也 可採用上部（外方側）的1個密封構件51的構造。 在該構造，形成在上部的密封構件51與軸承32之間 形成有潤滑油積存部的形態，例如即使潤滑油5 3從軸承 3 2朝下方漏出時，也可以流體密封43確實予以封閉。 又，在本實施形態，雖然軸承32是設在密封構件51 的內方（下部側），可是也可配置在密封構件51的外方側 (上端）。此時，採用被配置在上部的流體密封43取代 下部側的1個密封構件5 1，而具有可在其兩者間容易形 成適當的空間所形成的潤滑油積存部的優點。 此外，在本實施形態，雖以適用滾筒式洗衣機進行敘 述，但並不限於此，也可適用例如具有兼具可在縱軸周圍 旋轉的脫水槽的洗滌槽，且在其縱軸具備有底筒狀的水槽 之所謂縱型的洗衣機。 又，懸掛裝置7是將軸件24側安裝在水槽6，將汽 缸22側配設筐體1側，所以可抑制在導出導線44的汽缸 2 2側產生的振動的點上是有利的，可是也可作成將汽缸 -21 - 201217604 22側安裝在水槽6的相反配置’並且只要汽缸22與軸件 24爲相對的往復作動的關係即可。 (第2實施形態） 相對於上述，圖4爲表示第2實施形態的相當於圖i 的圖，相對於在第1實施形態，利用半固體狀的潤滑油 5 3作爲摩擦阻尼器手段，在該第2實施形態，在使用固 體狀的彈性摩擦體5 4作爲摩擦阻尼器手段的點上有所不 同，除此之外，實質上爲共通的構造。 以下，在與第1實施形態同一部分標示同一符號並省 略說明，且針對不同點進行說明。 亦即，如圖4所示，作成在彈簧承部4 8的筒狀部 48a的內方設有圓筒狀的彈性摩擦體54，且該彈性摩擦體 與軸件24滑動抵接。作爲該彈性摩擦體54，最好是例如 具有自己潤滑性（耐磨耗性）及高彈性的胺甲酸乙酯狀的 彈性體，或耐磨耗性優的具有彈性氈等的摩擦構件。 其他，只要可獲得所期望的摩擦力即可’例如也可採 用作爲在第1實施形態所示的密封構件51的置入有彈簧 的油封，此時，藉由彈簧51c所爲的彈簧力的調整、或藉 由滑動接合的複數個唇狀的調整’可獲得對於軸件24的 適當的摩擦力。 如此，由於具備有固體狀的彈性摩擦體5 4作爲補助 功能的摩擦阻尼器手段’可獲得經常穩定的大致—定的摩 擦力，所以可使懸掛裝置7所爲的衰減作用穩定化’且即 -22- 201217604 使流體阻尼器手段因任何的原因而無法適當發揮功能時’ 也可獲得最低限度彈性摩擦體54所爲的衰減作用等’並 可期待與上述第1實施形態同樣的作用效果。 此外，作爲懸掛裝置7，雖已針對軸件24與功能性 流體3 6之間的摩擦抵抗的實施形態作例示，可是並不限 於此，例如相對於塡充在汽缸內的功能性流體，使具有複 數個流孔的活塞閥依據振動往復作動，也可作成爲控制通 過流孔的功能性流體的黏性的構成，亦即使用藉由電能量 的施加使黏性改變的功能性流體，相對於依據水槽的振動 往復作動的軸以發揮抵抗力的方式發揮功能，使水槽的振 動衰減的懸掛裝置機構即可。 以上’雖說明了本發明的幾個實施形態，可是該等的 實施形態，是作爲例子提示者，並沒有限定發明的範圍的 意圖。該等新規的實施形態可在其他的各式各樣的形態被 實施’在不脫離發明的要旨的範圍，可進行各種的的省略 '置換 '變更。該等的實施形態或其變形，是包含在發明 的範圍或要旨，並且，包含在申請專利範圍的範圍所記載 的發明與其均等的範圍。 【圖式簡單說明】 [圖1]表示放大第1實施形態的懸掛裝置的—部的縱 剖視圖 [H 2]表示懸掛裝置單體的構造的縱剖視圖 [圖3]表示適用滾筒式洗衣機的洗衣機整體構造的槪 -23- 201217604 要的縱剖視圖 [圖4]表示第2實施形態的相當於圖1的圖 【主要元件符號說明】 1 :筐體 6 :水槽 7 :懸掛裝置 10 :滾筒（洗漉槽） 22 :汽缸 24 :軸件 2 5 :線圈彈簧 3 6 :功能性流體（流體阻尼器手段） 3 7 :線圈捲線軸單元（磁場產生手段） 3 9 :線圈 43 :流體密封 48 :彈簧承部 48a :筒狀部 5 1 :密封構件 5 2 :溝狀部（潤滑油積存部） 5 3 :潤滑油（摩擦阻尼器手段） 54 :彈性摩擦體（摩擦阻尼器手段） -24--16- 201217604 The large vibration amplitude generated during the dehydration operation of ι〇 can exert an effective attenuation effect. On the other hand, the cylindrical portion 48a of the spring-loaded portion 48 is often in contact with the shaft member 24 because it corresponds to the semi-solid lubricating oil 53 having a high-viscosity hardness accommodated in the hollow portion thereof. The predetermined frictional force with the reciprocation of the shaft member 24 is obtained, and the vibration of the water tank 6 is attenuated via the shaft member 24, that is, the friction damper means as described in the present embodiment. Therefore, the friction damper means is a frictional force which is suitable for constantly exhibiting a mechanical property different from that of the fluid damper means, but which is substantially constant. Further, the frictional force at this time is strictly a contact pressure of the lip shape 51 1 or the lip shape 51 1 to the shaft member 24 which functions as a leakage preventing portion of the lubricating oil 53 and functions as a storage portion of the lubricating oil 5 3 . In the present embodiment, the frictional action of the lubricating oil 53 is mainly described as the main component of the frictional force. Further, in order to constitute the friction damper means, the spring receiving portion 48 is used, but the cylindrical portion 48a has an effect of preventing the coil spring 25 from being largely tilted or bent. The tubular portion 48a is located further outward than the upper end portion of the cylinder 22, and therefore, the sealing member 51 or the lubricating oil 53 is located outside the cylinder 22, but is slidably engaged on the outer circumference of the cylindrical portion 48a. The coil spring 25 can be configured to overlap (overlap) with a portion of the effective length that is originally necessary to constitute the friction damper means. Therefore, it is not necessary to provide the suspension device 7 having the fluid damper means for providing the damper means. The full length -17- 201217604 constitutes a longer and less desirable situation. The fluid damper means using the functional fluid 36 and the friction damper means using the lubricating oil 53 having a semi-solid hardness can be further effectively used as a washing machine which also includes the vibration-proof action of the coil spring 25. The suspension device 7 for vibration prevention functions. Among them, as the friction damper means, as described above, a certain damping effect (damper action) is often exerted, and since it can be secured, the damping effect by the suspension device 7 can be stabilized. In addition, the fluid damper means, which is the main force of the suspension device 7, can be used as a function of the failure of the bobbin coil unit 37, for example, or if the function of the coil yoke unit 37 is not effective, or the function can be effectively performed in response to vibration or the like. Since the damping action by the friction damper means functions effectively, the suspension device 7 of the washing machine can contribute to the safety or stabilization of the vibration. As described above, the washing machine according to the first embodiment is a suspension device 7 that supports the water tank 6 having the rotary drum 10 therein, and the suspension device 7 is provided with a fluid damper means and a friction damper means. Construction. The fluid damper means has a shaft member 24 that reciprocates in the cylindrical cylinder 22 in accordance with the vibration of the water tank 6, and a function of changing the viscosity by the application of electric energy in the cylinder 22. The fluid 3 6 (in the present embodiment is a magnetic viscous fluid), the viscous property of the functional fluid 36 functions to resist the reciprocation of the shaft member 24, and the vibration of the water tank 6 is attenuated. -18-201217604 On the other hand, the friction damper means is configured such that the fluid damper means is arranged in series via the shaft member 22, and when vibrating, the frictional force is generated by the reciprocating sliding contact with the shaft member 22, and the frictional force is The function of the reciprocating action of the shaft member 22 is exerted to attenuate the vibration of the water tank 6. According to the suspension device 7 having such a configuration, it is possible to provide a low-vibration, low-noise washing machine that rapidly attenuates the vibration of the water tank 6 by the fluid damper means of the main body. For example, since the viscosity of the control functional fluid 36 can be changed, appropriate attenuation control can be performed depending on the control of the magnitude of the vibration amplitude, the control of the stroke of the drum type washing machine, and the like. In addition to the fluid damper means, the friction damper means having the auxiliary function can often obtain the damping effect by the substantially constant frictional force, so that the damping effect by the suspension means 7 can be stabilized. Further, even if the fluid damper means of the main body does not function properly for some reason, the attenuation effect by the minimum friction damper means can be obtained, and it is expected that the abnormal vibration or abnormal operation can be avoided. Practical effect. Further, the suspension device 7 includes a coil spring 25 that pushes the shaft member 24 in a direction pulled outward from the cylinder 22, and expands and contracts the coil spring 35 against the vibration generated on the side of the water tank 6, so that the vibration is not transmitted to The side of the casing 1 is. The friction damper means is an outer end portion of the cylinder 22 which is located at one end of the coil spring 25, and is disposed around the circumference of the coil spring 25. That is, the friction damper means is located within a range of effective length required as the coil spring 25, and is disposed at a position overlapping with a part of the coil spring 25, so that it is not necessary to increase (grow) the fluid damper means - The suspension device 7 of 19-201217604 can be added with a friction damper, so it is advantageous in production and assembly. More specifically, the cylindrical spring portion 4 8 that is fitted to one end of the support coil spring 25 is provided at the outer end portion of the cylinder 22 as the cylindrical portion 48a of the cylindrical length of the spring receiving portion 48. The formed length is smaller than the close length of the coil spring 25. Thereby, the upper end portion of the tubular portion 48a can be expanded and contracted without abutting against the spring support plate 30. This is because the coil spring 25 can be effectively utilized as the vibration-proof coil spring 25 is compressed to the maximum compression state. Features. Further, in the present embodiment, the spring receiving portion 48 is easily formed or assembled by being integrally formed with the upper bearing cartridge 31, but may be assembled by using different members. Further, the frictional force generated by the friction damper means is a structure obtainable by the two sealing members 51 and the semi-solid lubricating oil 53 which are slidably abutted against the shaft member 24. Therefore, it is possible to suppress the occurrence of a large rubbing sound or an uncomfortable rubbing sound, and to achieve the quieting of the suspension device 7 together with the fluid damper means. As the lubricating oil 53, the consistency of the hardness is shown, and the desired damping effect of the urea-based lubricating oil of the JIS classification No. 0 to No. 3 can be obtained. Further, in the present embodiment, the two sealing members 51 are disposed to face each other in the vertical direction as the lubricating oil reservoir, and the groove portion 52 opened on the side of the shaft member 24 is formed in a ring shape therebetween, and is formed in the groove. The shape 52 is filled with the lubricating oil 53. -20-201217604 The lubricating oil 53 that is filled is not leaked to the outside by the sealing member 51 disposed above and below, and can be surely held, and is slidably abutted against the shaft member 24, so that a certain frictional force can be exhibited for a long period of time. In this case, it is also possible to use the fluid seal 43 which is also used in the fluid damper means. For example, as shown in Fig. 1, in particular, the fluid seal 43 disposed at the upper portion of the upper yoke 40 prevents leakage of the functional fluid 36 from above to the upper side. Here, the sealing member 51 on the lower side is replaced with the fluid seal 43, and the structure of one sealing member 51 on the upper side (outer side) may be employed. In this configuration, the lubricating oil reservoir is formed between the upper sealing member 51 and the bearing 32. For example, even if the lubricating oil 5 3 leaks downward from the bearing 32, the fluid seal 43 can be surely closed. Further, in the present embodiment, the bearing 32 is provided on the inner side (lower side) of the sealing member 51, and may be disposed on the outer side (upper end) of the sealing member 51. At this time, the fluid seal 43 disposed on the upper portion is used instead of the one seal member 51 on the lower side, and there is an advantage that the lubricating oil reservoir portion which can easily form an appropriate space therebetween can be used. Further, in the present embodiment, the drum type washing machine is applied. However, the present invention is not limited thereto. For example, a washing tub having a dewatering tank that can rotate around the vertical axis can be applied, and the vertical axis has a bottom. A so-called vertical washing machine with a cylindrical sink. Further, since the suspension device 7 is attached to the water tank 6 on the side of the shaft member 24 and disposed on the side of the casing 1 on the side of the cylinder 22, it is advantageous to suppress the vibration generated on the side of the cylinder 2 2 of the lead wire 44, but it is advantageous. It is also possible to provide the cylinder 21 - 201217604 22 side in the opposite arrangement of the water tank 6 and to reciprocate as long as the cylinder 22 and the shaft member 24 are opposed to each other. (Second Embodiment) FIG. 4 is a view corresponding to FIG. 2 in the second embodiment, and the semi-solid lubricating oil 5 3 is used as a friction damper means in the first embodiment. The second embodiment differs in that the solid elastic friction body 54 is used as a friction damper means, and is basically a common structure. In the following, the same portions as those in the first embodiment are denoted by the same reference numerals, and the description thereof will be omitted. That is, as shown in Fig. 4, a cylindrical elastic friction body 54 is formed inside the tubular portion 48a of the spring receiving portion 48, and the elastic friction member is slidably abutted against the shaft member 24. The elastic friction body 54 is preferably, for example, an urethane-like elastomer having self-lubricating property (abrasion resistance) and high elasticity, or a friction member having an elastic felt or the like which is excellent in abrasion resistance. In addition, as long as the desired frictional force can be obtained, for example, an oil seal in which the spring is placed in the sealing member 51 shown in the first embodiment can be used. In this case, the spring force by the spring 51c is used. Appropriate friction for the shaft member 24 can be obtained by adjustment, or by a plurality of lip-shaped adjustments of the sliding engagement. In this way, since the elastic friction body 54 having the solid shape is provided as a friction damper means of the auxiliary function, a constant and constant frictional force can be obtained, so that the damping effect by the suspension device 7 can be stabilized'. -22-201217604 When the fluid damper means cannot function properly for any reason, 'the attenuation effect by the minimum elastic friction body 54 can be obtained, and the same effect as the above-described first embodiment can be expected. Further, although the suspension device 7 has been exemplified as an embodiment of the frictional resistance between the shaft member 24 and the functional fluid 36, it is not limited thereto, and for example, with respect to the functional fluid charged in the cylinder, A piston valve having a plurality of orifices can be reciprocated according to vibration, or can be configured to control the viscosity of a functional fluid passing through the orifice, that is, a functional fluid that changes viscosity by application of electric energy, The suspension mechanism that reciprocates according to the vibration of the water tank functions to exert a resistance and attenuates the vibration of the water tank. The above has described several embodiments of the present invention, and these embodiments are presented as examples, and do not limit the scope of the invention. The embodiments of the new regulations can be implemented in various other forms. Various modifications may be made without departing from the scope of the invention. The invention and its modifications are intended to be included within the scope and spirit of the invention and the scope of the invention described in the scope of the claims. BRIEF DESCRIPTION OF THE DRAWINGS [Fig. 1] is a longitudinal cross-sectional view showing a portion of a suspension device according to a first embodiment. [H 2] is a longitudinal sectional view showing a structure of a single suspension device. Fig. 3 is a view showing a washing machine to which a drum type washing machine is applied.槪-23- 201217604 overall structure view [Fig. 4] shows the diagram corresponding to Fig. 1 of the second embodiment [Description of main components] 1 : Housing 6 : Sink 7 : Suspension device 10 : Roller (washing Groove 22) Cylinder 24: Shaft 2 5 : Coil spring 3 6 : Functional fluid (fluid damper means) 3 7 : Coil bobbin unit (magnetic field generating means) 3 9 : Coil 43 : Fluid seal 48 : Spring Bearing portion 48a: cylindrical portion 5 1 : sealing member 5 2 : groove portion (lubricating oil reservoir) 5 3 : lubricating oil (friction damper means) 54 : elastic friction body (friction damper means) -24-