1336753 (1) 九、發明說明 【發明所屬之技術領域】 本發明是關於車輛用的油壓緩衝器。 【先前技術】 在車輛的油壓緩衝器，由於引擎振動等所引起的車體 側的振動，會傳達到在阻尼筒與活塞桿之間所配設的懸吊 φ 線圈彈簧，而使其產生共振情形。特別是由直徑較小的芯 線所構成，具備有節距較小的緊密捲繞部分與較大的疏鬆 捲繞部分的懸吊線圈彈簧，該共振情形，會產生於節距較 小的緊密捲繞部分。該懸吊線圈彈簧的共振振動情形，會 對油壓緩衝器的各部分造成異常的荷重，例如，活塞桿的 螺紋部的的螺頂部會產生振動疲勞破壞，或者鄰接的芯線 彼此接觸，會產生所謂的芯線之間的聲音，而懸吊線圈彈 簧的內周接觸到彈簧導引部的表面也會產生雜音。 φ 彈簧導引部雖然是安裝作爲防止懸吊線圈彈簧彎曲的 構件，可是由於使彈簧導引部接觸於懸吊線圈彈簧的內周 ，而使懸吊線圈彈簧的自由振動部的捲繞數改變，而使懸 吊線圈彈簧的共振點偏移，而能夠抑制其共振振動情形。 作爲採用了彈簧導引部的油壓緩衝器，有記載於日本 實用新案登錄 2596400 (專利文獻】）、日本專利 27 1 0982 (專利文獻2 )的技術。 專利文獻1的油壓緩衝器，在活塞桿的外周上部，且 在懸吊線圈彈簧的內周側，是配設有間隔部1 3，該間隔 -4· i (2) 1336753 部1 3 ’是以：圓筒基部1 3 a、在圓筒基部的外周沿著軸方 向形成的放射狀的複數的肋部13b'以及在肋部與肋部之 間沿著軸方向所形成的槽部所構成。 可是，在專利文獻〗的技術中，有時會由於懸吊線圈 彈簧的內徑尺寸、與間隔部的基部外周的肋部的外徑尺寸 的誤差，而導致讓懸吊線圈彈簧無法插入到間隔部的外周 〇 φ 專利文獻2的油壓緩衝器，是在彈簧導引部49、50 的外周方向隔著間隔的兩處位置，形成兩個細縫部S，其 中一個細縫部S 1是延伸設置到下端部，並且將在外周方 向隔著間隔形成有複數的突條部53 ' 54的構造設置在缸 简的外周。 彈簧導引部49、5 0，會由於細縫部S I所造成的彈性 ，緊貼於避震彈簧47、48的內面部’而產生於避震彈簧 47、48的振動，會被彈簧導引部的彈性而吸收。而藉由 ϋ將彈簧導引部的突條部5 3、5 4形成爲越朝向上端部其直 徑變得越小，則能夠提昇避震彈簧4 7、4 8的安裝性。 可是，當避震彈簧4 7、4 8的節距較小的緊密捲繞部 分是位於彈簧導引部的上端部時’突條部5 3、54的外周 與避震彈簧4 7、4 8的內周之間的間隙會變大’所以彈簧 導引部對於避震彈簧4 7、4 8所產生的振動的吸收性會變 差。 【發明內容】 -5- (3) 1336753 本發明的課題，要提供一種油壓緩衝器’是具備有能 夠同時達到懸吊線圈彈簧的振動吸收性與安裝性的彈簧導 引部。 本發明，在緩衝筒內可自由滑動地插入活塞桿，在緩 衝筒與活塞桿之間，配設著懸吊線圈彈簧，在外周形成有 用來導引懸吊線圏彈簧的內周的複數的肋部的彈簧導引部 ，是同軸地嵌插於懸吊線圈彈簧的車輛用的油壓緩衝器’ φ 形成於上述彈簧導引部的外周的複數的肋部之中的一個肋 部，是形成爲接觸或接近於上述懸吊線圈彈簧的內周，並 且其他肋部是形成爲較該一個肋部更低。 本發明，在緩衝筒內可自由滑動地插入活塞桿，在緩 衝简與活塞桿之間，配設著懸吊線圈彈簧，在外周形成有 用來導引懸吊線圈彈簧的內周的複數的肋部的彈簧導引部 ，是同軸地嵌插於懸吊線圈彈簧的車輛用的油壓緩衝器， 在沿著上述彈簧導引部的外周的小於180度的其中一側的 φ圓周上，形成有：接觸或接近於上述懸吊線圈彈簧的內周 的兩個以上的肋部，並且在沿著該彈簧導引部的外周的另 一側的圓周上’形成有：較該一側圓周上所設置的兩個以 上的肋部更低的肋部。 【實施方式】 油壓緩衝器10，如第1圖所示，例如是中介安裝在 機車的後部車軸側與車體側之間，在車體側所安裝的緩衝 同1 1 ’插入活塞桿1 2，該活塞桿丨2是安裝在車軸側，在 -6- (4) (4)1336753 衝同π的外周部與活塞桿丨2之間中介安裝有懸吊線圈 彈簧】3。 緩衝筒丨】’是一·體地具備有：車體側安裝構件1 4、 上彈簧座1 5。活塞桿1 2是以鎖定螺母1 7固定於車軸側 安裝構件1 6，在車軸側安裝構件】6具備有下彈簧座】8。 懸吊線圈彈簧1 3，是經由上下的彈簧座1 5 ' 1 8，而被中 介女裝在緩衝商1 1與活塞桿1 2之間。 油壓緩衝器〗〇，在緩衝筒11的開口部，是斂縫保持 著：桿導引部21、〇形環22、油封23、端板部24，是在 經過緩衝筒Π的桿導引部2〗、〇形環22、油封23而插 入到緩衝筒1 1的活塞桿】2的前端部，斂縫固定著活塞 25，活塞桿12，是經由活塞25而可自由滑動於緩衝筒π 。活塞25，是將緩衝筒〗〗的內部二分爲上下的油室26 a 、26B’並且具備有用來聯絡兩油室26A、26B的流路27 ’在該流路2 7具備有：當活塞桿1 2伸縮時會產生壓縮側 阻尼力與伸長側阻尼力的活塞閥裝置3 0。 活塞閥裝置30’如第2圖所示，是從活塞桿]2的前 端側開始，依序插入：閥擋塊31、閥彈簧32(第2圖（E ))、開孔閥3 3 (第2圖（B ))、封閉閥3 4 (第2圖（ C ))、閥座35(第2圖（D))、活塞25，將這些構件 固定在活塞桿】2的中間階段部與前端斂縫部之間。活塞 閥裝置30，是具備有用來將流路27聯繫於下油室26B的 阻尼孔2 7 A，並且藉由被閥擋塊3]支承其背面的閥彈簧 32，將開孔閥33、封閉閥34 (封閉閥34是以封閉住開孔 (5) 1336753 閥3 3的小孔3 3 A的方式積疊於開孔閥3 3 )緊壓於活塞 25的端面及閥座35’朝向封閉流路27的方向彈壓。油壓 緩衝器1 0 ’在壓縮側行程’是藉由將開孔閥3 3、封閉閥 3 4推開來產生壓縮側阻尼力。而在伸長側行程’在活塞 桿1 2的低速區域，是藉由阻尼孔2 7 A的流路阻力來產生 伸長側阻尼力，在活塞桿〗2的中高速區域’是藉由封閉 閥3 4的移位來將開孔閥3 3的小孔3 3 A打開’藉由其流 φ 路阻力來產生伸長側阻尼力。 油壓緩衝器10，在最壓縮時，會使插裝於活塞桿12 的基端部的擋塊橡膠3 6抵接於緩衝筒1 1的端面，來限制 其最壓縮行程，當最伸長時，會使被支承於桿導引部21 的回彈彈簧3 7抵接於活塞2 5的閥擋塊3 1，來限制其最 伸長行程。 藉此，在油壓緩衝器1 〇，會以懸吊線圈彈簧1 3的彈 力，來吸收車輛從路面所受到的衝擊力，以設置在活塞 φ 2 5的活塞閥裝置3 0所產生的阻尼力，來抑制懸吊線圏彈 簧1 3吸收衝擊力時所伴隨產生的伸縮振動。 油壓緩衝器1 〇，以如下述的方式，具有彈簧導引部 40 〇 彈簧導引部40，如第1圖所示，是作成大致圓筒狀 ，是嵌裝在緩衝筒Π的圓筒狀的外周，而背面被支承於 上彈簧座1 5。彈簧導引部40，如第3圖所示，在其基端 部具備有用來讓懸吊線圈彈簧1 3的上端部安置定位的鍔 部4 1 ’並且在外周形成有：嵌插著懸吊線圈彈簧1 3，用 -8- (6) 1336753 來導引該懸吊線圈彈簧】3的內周的複數的肋部42 °複數 的肋部4 2 ’是在沿著彈簧導引部4 0的外周的圓周上等間 隔地形成。彈簧導引部40 ’在緩衝筒1 1的外周’是與懸 吊線圈彈簧1 3同軸地嵌插，藉由肋部42的沿著彈簧導引 部直徑方向的半徑方向外面部，來導引懸吊線圈彈簧13 的內周，則能夠防止懸吊線圈彈簧1 3彎曲而接觸於緩衝 筒I 1的外周的情形。在彈簧導引部40的軸方向且在位於 φ 鍔部4 1的相反側的肋部4 2的前端側外面部，是倒角形成 有懸吊線圈彈簧I 3的嵌插用導引面4 3。 彈簧導引部40，如第3圖、第4圖（A)所示，在本 實施例，總共具有四個肋部42，其中一個肋部42A的沿 著彈簧導引部直徑方向的半徑方向高度，是形成爲接觸或 接近於懸吊線圈彈簧1 3的內周，並且將其他三個肋部 4 2B的半徑方向高度形成爲比肋部42A更低。 這裡的較高的肋部42A與較低的肋部42B的高度的 ϋ差異h，是設定爲大於：懸吊線圈彈簧1 3的內周半徑尺 寸rl的製造誤差的最小値、與彈簧導引部40的較低的肋 部42B的半徑尺寸r2的製造誤差的最大値的兩者的差異 〇 第3圖（A)以兩點虛線來顯示懸吊線圈彈簧1 3，第 4圖（A )以實線來顯示懸吊線圈彈簧]3。 藉由本實施例可達到以下的作用效果。 (a )將彈簧導引部40的外周所形成的複數的肋部 42其中的一個肋部42A，形成爲接觸或接近於懸吊線圈 (7) 1336753 彈簧1 3的內周’並且將其他肋部42B形成爲較該一個肋 部42 A更低，所以當在彈簧導引部4 0的外周安裝懸吊線 圈彈簧13時，會由於較高的肋部42A與較低的肋部42B 的高度的差異’而能使懸吊線圈彈簧1 3朝直徑方向偏心 或移動。於是，如果將較高的肋部42A與較低的肋部42B 的高度的差異h，是設定爲大於：懸吊線圈彈簧13的內 周半徑尺寸的製造誤差的最小値' 與彈簧導引部40的較 鲁低的肋部42B的半徑尺寸的製造誤差的最大値的兩者的差 異的話，則懸吊線圈彈簧1 3的安裝性會很優異。 在將懸吊線圈彈簧〗3安裝於彈簧導引部4 〇的外周側 之後，由於車體側的振動而振動的懸吊線圈彈簧1 3，會 接觸於彈簧導引部4 0的較高的肋部4 2 A，使懸吊線圈彈 簧1 3的自由振動部（彈簧1 3的沒有接觸於肋部4】a的 較長的部分）的捲繞數改變’來抑制懸吊線圈彈簧I 3的 共振振動情形。 # ( b )複數的肋部42 ’是在沿著彈簧導引部40的外 周的圓周上’等間隔地形成，所以能夠在圓周上均勻地限 制懸吊線圈彈簧]3的彎曲情形。 第4圖（B)〜（D) ’是顯示彈簧導引部40的變形 例的彈簧導引部50〜70。彈簧導引部5〇〜7〇，具有與彈 簧導引部4〇同樣的鍔部4 1、肋部42，是將複數的肋部 42 ’等間隔地形成在沿著這些彈簧導引部50〜70的外周 的圓周上。 70 彈簧導引部50〜70，在沿著這些彈簧導引部5〇〜 -10 * (8) 1336753 •接觸 部42A 的圓周 上的肋 的肋部 形成爲 他的肋 中一側 與彈簧 含於懸 圍內。 較低的 心移動 較高的 彈簧導 低的肋 三個較 的外周的小於U 0度的其中一側的圓周上，形成有 或接近於懸吊線圈彈簧1 3的內周的兩個以上的肋 ’並且在沿著彈簧導引部5 0〜7 0的外周的另一側 上’是形成有：較設置於該一側的圓周上的兩個以 部42Α更低的肋部42Β。也就是說，將兩個以上 42Α的沿著彈簧導引部直徑方向的半徑方向高度， 接觸或接近於懸吊線圈彈簧1 3的內周，並且將其 • 部42Β的半徑方向高度形成爲較肋部42Α更低。 這裡的在沿著彈簧導引部50〜70的外周的其 的圓周上所形成的肋部42A，在懸吊線圈彈簧1 3 導引部50〜70互相偏心移動的狀態，是形成在包 吊線圈彈簧1 3的內周的其中一側的I 80度內的範 此時，懸吊線圈彈簧1 3，是以較高的肋部4 2 A與 肋部4 2B的半徑方向高度的差異h而朝直徑方向偏1336753 (1) Description of the Invention [Technical Field of the Invention] The present invention relates to a hydraulic shock absorber for a vehicle. [Prior Art] In the hydraulic shock absorber of the vehicle, the vibration of the vehicle body side due to engine vibration or the like is transmitted to the suspended φ coil spring disposed between the damper cylinder and the piston rod, thereby generating Resonance situation. In particular, it is composed of a core wire having a small diameter, and is provided with a suspension coil spring having a tightly wound portion with a small pitch and a large loosely wound portion. This resonance occurs in a tight roll with a small pitch. Around the part. The resonant vibration of the suspension coil spring causes an abnormal load on each part of the oil pressure damper. For example, the screw top of the threaded portion of the piston rod may cause vibration fatigue damage, or the adjacent core wires may contact each other, which may occur. The so-called sound between the core wires, and the inner circumference of the suspension coil spring contacts the surface of the spring guide portion to generate noise. Although the φ spring guide is attached as a member for preventing the suspension coil spring from being bent, the number of windings of the free vibration portion of the suspension coil spring is changed by bringing the spring guide portion into contact with the inner circumference of the suspension coil spring. The resonance point of the suspension coil spring is shifted, and the resonance vibration condition can be suppressed. As a hydraulic damper using a spring guide portion, there is a technique described in Japanese Utility Model Publication No. 2596400 (Patent Literature) and Japanese Patent No. 27 1 0982 (Patent Document 2). In the hydraulic damper of Patent Document 1, a spacer portion 13 is disposed on the outer peripheral side of the piston rod and on the inner peripheral side of the suspension coil spring, and the interval is -4 (i) 1336753 portion 1 3 ' The cylindrical base portion 13 3 a, a radial plurality of rib portions 13 b ′ formed along the axial direction on the outer circumference of the cylindrical base portion, and a groove portion formed along the axial direction between the rib portion and the rib portion Composition. However, in the technique of the patent document, the suspension coil spring cannot be inserted into the interval due to an error in the inner diameter dimension of the suspension coil spring and the outer diameter dimension of the rib portion on the outer circumference of the base portion of the spacer portion. The outer peripheral 〇 φ of the hydraulic damper of Patent Document 2 is formed at two positions spaced apart from each other in the outer circumferential direction of the spring guiding portions 49 and 50, and two slit portions S are formed, and one slit portion S 1 is extended. To the lower end portion, a structure in which a plurality of ridge portions 53' 54 are formed at intervals in the outer circumferential direction is provided on the outer circumference of the cylinder block. The spring guides 49, 50 are caused by the elasticity of the slit portion SI, and are in contact with the inner surface portion ' of the suspension springs 47, 48, and are generated by the vibration of the suspension springs 47, 48, and are guided by the spring guide portion. The elasticity is absorbed. On the other hand, the ridge portions 5 3 and 5 4 of the spring guide portion are formed such that the smaller the diameter toward the upper end portion, the better the mountability of the suspension springs 4 7 and 48 can be improved. However, when the tightly wound portion where the pitch of the suspension springs 47, 48 is small is located at the upper end portion of the spring guide portion, the outer circumference of the ridge portion 5 3, 54 and the suspension springs 4 7 , 4 8 The gap between the inner circumferences becomes large. Therefore, the absorbability of the spring guides to the vibration generated by the suspension springs 4 7 and 48 is deteriorated. [5] (3) 1336753 An object of the present invention is to provide a hydraulic shock absorber which is provided with a spring guide portion capable of simultaneously achieving vibration absorption and mountability of a suspension coil spring. According to the present invention, the piston rod is slidably inserted into the buffer cylinder, and a suspension coil spring is disposed between the buffer cylinder and the piston rod, and a plurality of ribs for guiding the inner circumference of the suspension coil spring are formed on the outer circumference. The spring guide portion of the portion is a hydraulic damper φ coaxially inserted into the suspension coil spring, and φ is formed in one of a plurality of ribs formed on the outer circumference of the spring guide portion. To contact or approximate the inner circumference of the suspension coil spring described above, and the other ribs are formed lower than the one rib. According to the present invention, the piston rod is slidably inserted into the buffer cylinder, and a suspension coil spring is disposed between the buffer and the piston rod, and a plurality of ribs for guiding the inner circumference of the suspension coil spring are formed on the outer circumference. The spring guide portion of the portion is a hydraulic shock absorber for the vehicle that is coaxially inserted into the suspension coil spring, and is formed on the φ circumference of one side of less than 180 degrees along the outer circumference of the spring guide portion. There are two or more ribs that are in contact with or close to the inner circumference of the above-mentioned suspension coil spring, and are formed on the circumference of the other side along the outer circumference of the spring guide portion: on the circumference of the one side Two or more ribs are provided with lower ribs. [Embodiment] As shown in Fig. 1, the hydraulic damper 10 is interposed, for example, between the rear axle side of the locomotive and the vehicle body side, and the buffer installed on the vehicle body side is the same as the 1 1 'inserted piston rod 1 2. The piston rod 丨 2 is mounted on the axle side, and a suspension coil spring is interposed between the outer circumference of the -6-(4) (4) 1336753 and the piston rod 丨2. The buffer cartridge ’] is integrally provided with a vehicle body side mounting member 14 and an upper spring seat 15 . The piston rod 1 2 is fixed to the axle-side mounting member 16 by a lock nut 17 , and the axle-side mounting member 6 is provided with a lower spring seat 8 . The suspension coil spring 13 is connected between the buffer 1 1 and the piston rod 12 via the upper and lower spring seats 1 5 ' 1 8 . The hydraulic damper 〇 is held in the opening portion of the buffer cylinder 11 by the caulking: the rod guiding portion 21, the 〇 ring 22, the oil seal 23, and the end plate portion 24 are guided by the rod passing through the buffer cylinder The second portion, the ring 22 and the oil seal 23 are inserted into the front end portion of the piston rod 2 of the buffer cylinder 1 1 , and the piston 25 is caulked, and the piston rod 12 is slidably slidable in the buffer cylinder via the piston 25 . The piston 25 divides the inside of the buffer cylinder into upper and lower oil chambers 26a and 26B' and is provided with a flow path 27' for contacting the two oil chambers 26A and 26B. The flow path 27 is provided with a piston rod. 1 2 A piston valve device 30 that generates a compression side damping force and an expansion side damping force when expanding and contracting. As shown in Fig. 2, the piston valve device 30' is inserted from the front end side of the piston rod 2, and is sequentially inserted: the valve stopper 31, the valve spring 32 (Fig. 2 (E)), and the opening valve 3 3 ( Fig. 2 (B)), closing valve 3 4 (Fig. 2 (C)), valve seat 35 (Fig. 2 (D)), and piston 25, these members are fixed to the intermediate stage of the piston rod 2 Between the front ends of the joints. The piston valve device 30 is provided with a orifice 27 7 A for communicating the flow path 27 to the lower oil chamber 26B, and the valve 30 is closed by the valve spring 32 supported by the valve block 3]. The valve 34 (the closing valve 34 is stacked on the opening valve 3 3 in such a manner as to close the opening (5) 1336753, the small hole 3 3 A of the valve 3 3 ) is pressed against the end face of the piston 25 and the valve seat 35' faces the closed The direction of the flow path 27 is biased. The hydraulic damper 10' in the compression side stroke is generated by pushing the opening valve 3 3 and the closing valve 34 to generate a compression side damping force. On the extension side stroke 'in the low speed region of the piston rod 12, the expansion side damping force is generated by the flow path resistance of the orifice 27 7 A, and the middle speed region of the piston rod 2 is closed by the closing valve 3 The displacement of 4 opens the small hole 3 3 A of the opening valve 3 3 to generate the elongation side damping force by its flow φ path resistance. When the hydraulic damper 10 is most compressed, the stopper rubber 36 inserted into the proximal end portion of the piston rod 12 abuts against the end surface of the buffer cylinder 11 to limit its maximum compression stroke, when it is most elongated. The rebound spring 37 supported by the rod guide 21 abuts against the valve stop 31 of the piston 25 to limit its maximum elongation stroke. Thereby, in the hydraulic damper 1 〇, the impact force of the vehicle from the road surface is absorbed by the elastic force of the suspension coil spring 13 to set the damping generated by the piston valve device 30 of the piston φ 25 . The force is used to suppress the stretching vibration accompanying the suspension wire spring 13 when the impact force is absorbed. The hydraulic shock absorber 1 has a spring guide portion 40 and a spring guide portion 40 as shown in the first embodiment, and is formed into a substantially cylindrical shape as shown in Fig. 1 and is a cylinder fitted in the buffer cylinder. The outer periphery of the shape is supported by the upper spring seat 15 . As shown in Fig. 3, the spring guide portion 40 is provided at its base end portion with a flange portion 4 1 ' for positioning the upper end portion of the suspension coil spring 13 and is formed with an overhang on the outer circumference. The coil spring 13 is guided by -8-(6) 1336753 to guide the plurality of ribs 42 of the inner circumference of the suspension coil spring 3; the plurality of ribs 4 2 ' are along the spring guide 40 The circumference of the outer circumference is formed at equal intervals. The spring guide portion 40' is inserted coaxially with the suspension coil spring 13 at the outer circumference of the buffer cylinder 1 1 and guided by the radially outer portion of the rib portion 42 along the diameter direction of the spring guide portion. By suspending the inner circumference of the coil spring 13, it is possible to prevent the suspension coil spring 13 from being bent and coming into contact with the outer circumference of the buffer cylinder I1. In the axial direction of the spring guide portion 40 and on the front end side outer surface portion of the rib portion 42 located on the opposite side of the φ 锷 portion 41, the insertion guide surface 4 in which the suspension coil spring I 3 is chamfered is formed. 3. The spring guiding portion 40, as shown in Fig. 3 and Fig. 4(A), has a total of four ribs 42 in the present embodiment, one of which has a radial direction along the diameter direction of the spring guiding portion. The height is formed to contact or approach the inner circumference of the suspension coil spring 13 and the radial heights of the other three ribs 4 2B are formed to be lower than the rib 42A. Here, the ϋ difference h of the height of the higher rib 42A and the lower rib 42B is set to be larger than: the minimum manufacturing error of the inner peripheral radius dimension rl of the suspension coil spring 13 and the spring guide The difference between the maximum 値 of the manufacturing error of the radius dimension r2 of the lower rib 42B of the portion 40. FIG. 3(A) shows the suspension coil spring 13 with a two-dot dotted line, FIG. 4(A) The suspension coil spring]3 is displayed in a solid line. The following effects can be achieved by the present embodiment. (a) one of the plurality of ribs 42 formed by the outer circumference of the spring guiding portion 40 is formed to be in contact with or close to the inner circumference of the suspension coil (7) 1336753 spring 13 and other ribs The portion 42B is formed lower than the one rib 42 A, so when the suspension coil spring 13 is attached to the outer circumference of the spring guiding portion 40, the height of the higher rib 42A and the lower rib 42B may be due to The difference 'can make the suspension coil spring 13 eccentric or move in the diameter direction. Thus, if the difference h between the heights of the higher ribs 42A and the lower ribs 42B is set to be larger than: the minimum manufacturing error of the inner peripheral radius dimension of the suspension coil spring 13 and the spring guide portion The difference in the maximum 値 of the manufacturing error of the radius dimension of the relatively low rib 42B of 40 is excellent in the mountability of the suspension coil spring 13 . After the suspension coil spring 3 is attached to the outer peripheral side of the spring guide portion 4, the suspension coil spring 13 vibrating due to the vibration of the vehicle body side is in contact with the higher of the spring guide portion 40. The rib portion 4 2 A changes the number of windings of the free vibration portion of the suspension coil spring 13 (the longer portion of the spring 13 that is not in contact with the rib portion 4 a) to suppress the suspension coil spring I 3 Resonant vibration situation. # (b) The plurality of ribs 42' are formed at equal intervals along the circumference of the outer circumference of the spring guiding portion 40, so that the bending of the suspension coil springs 3 can be uniformly restricted on the circumference. 4(B) to (D)' are spring guide portions 50 to 70 which show a modified example of the spring guide portion 40. The spring guides 5 〇 to 7 〇 have the same ridges 4 1 and ribs 42 as the spring guides 4 , , and the plurality of ribs 42 ′ are formed at equal intervals along the spring guides 50 . ~70 on the circumference of the outer circumference. 70 spring guides 50 to 70, along the ribs of the ribs on the circumference of the contact portion 42A along the spring guides 5 〇 10 - 10 * (8) 1336 753. Within the suspension. The lower core moves the higher spring-guided lower ribs on the circumference of one of the three outer circumferences less than U 0 degrees, forming two or more of the inner circumference of the suspension coil spring 13 The rib 'and the other side along the outer circumference of the spring guides 50 to 70 are formed with two ribs 42 以 lower than the portion 42 较 on the circumference provided on the one side. That is, the heights of the two or more 42 turns in the radial direction along the diameter direction of the spring guide are brought into contact with or close to the inner circumference of the suspension coil spring 13 and the height in the radial direction of the portion 42 is formed as The ribs 42 are lower. Here, the rib portion 42A formed on the circumference of the outer circumference of the spring guiding portions 50 to 70 is formed in the state in which the suspension coil springs 13 are guided to move eccentrically with each other. At a time of I 80 degrees on one side of the inner circumference of the coil spring 13 , the suspension coil spring 13 is a difference in the height of the radial direction between the higher rib 4 2 A and the rib 4 2B. Diameter in the diameter direction
第4圖（B)的彈簧導引部50，是具備有兩個 肋部42A與兩個較低的肋部42B，第4圖（C )的 引部60，是具備有兩個較高的肋部42A與一個較 部42B，第4圖（D )的彈簧導引部70，是具備有 高的肋部42A與三個較低的肋部42B， 藉由本實施例則可達到以下的作用效果。 (a )在沿著彈簧導引部50〜70的外周的小於1 80度 的其中一側的圓周上，形成有：接觸或接近於懸吊線圈彈 簧1 3的內周的兩個以上的肋部42A，並且在沿著該彈簧 (9) 1336753 導引部5 0〜7 0的外周的另一側的圓周上，是形成有：較 設置於該一側的圓周上的肋部4 2 Α更低的肋部4 2 Β，所以 當將懸吊線圈彈簧1 3安裝於彈簧導引部50〜70的外周時 ，能夠以較高的肋部42A與較低的肋部42B的高度的差 異，來使懸吊線圈彈簧1 3朝直徑方向偏心或移動。於是 ，如果將較高的肋部42A與較低的肋部42B的高度的差 異，是設定爲大於：懸吊線圈彈簧1 3的內周半徑尺寸的 φ 製造誤差的最小値、與彈簧導引部50〜70的較低的肋部 42B的半徑尺寸的製造誤差的最大値的兩者的差異的話， 則懸吊線圈彈簧1 3的安裝性會很優異。 在將懸吊線圈彈簧1 3安裝於彈簧導引部50〜70的外 周側之後，由於車體側的振動而振動的懸吊線圈彈簧13 ，會接觸於彈簧導引部50〜70的較高的肋部42A，使懸 吊線圈彈簧丨3的自由振動部（彈簧1 3的沒有接觸於肋部 42 A的較長的部分）的捲繞數改變，來抑制懸吊線圈彈簧 φ 1 3的共振振動情形。 (b)由於複數的肋部4 2，是在沿著彈簧導引部5 0〜 7 0的外周的圓周上等間隔地形成，所以可以在圓周上均 勻地限制懸吊線圈彈簧1 3的彎曲情形。 以上，藉由圖面來詳細敘述了本發明的實施例’本發 明的具體構造並不限於該實施例，本發明也包含’在不脫 離本發明的主旨的範圍的設計變更。 【圖式簡單說明】 -12- (10) (10)1336753 第1圖是顯示油壓緩衝器的半剖面圖。 第2圖是顯示活塞閥裝置，（A)是剖面圖，（B) 是顯示開孔閥的俯視圖，（C )是顯示封閉閥的俯視圖， (D )是顯示閥座的俯視圖，（E )是顯示閥彈簧的剖面 圖。 第3圖是顯示閥導引部，（A )是俯視圖，（B )是 沿著（A )的B - B線的剖面圖。 第4圖是顯示彈簧導引部，（A )是顯示第3圖的彈 簧導引部的示意圖，（B )〜（D )是顯示變形例的彈簧 導引部的示意圖。 【主要元件符號說明】 1 〇 :油壓緩衝器 1 1 :緩衝筒 1 2 :活塞桿 1 3 :懸吊線圈彈簧 1 4 :車體側安裝構件 1 5 :上彈簧座 1 6 :車軸側安裝構件 I 7 :鎖定螺母 1 8 :下彈簧座 21 :桿導引部 2 2 : Ο形環 2 3 :油封 -13- (11)1336753 24 :端板部 25 :活塞 26A :上油室 26B :下油室 2 7 :流路 2 7 A :阻尼孔The spring guiding portion 50 of Fig. 4(B) is provided with two ribs 42A and two lower ribs 42B, and the guiding portion 60 of Fig. 4(C) is provided with two higher ones. The rib portion 42A and the one portion 42B, and the spring guiding portion 70 of the fourth drawing (D) are provided with a high rib portion 42A and three lower rib portions 42B, and the following effects can be achieved by the present embodiment. effect. (a) On the circumference of one side of less than 180 degrees along the outer circumference of the spring guiding portions 50 to 70, two or more ribs which are in contact with or close to the inner circumference of the suspension coil spring 13 are formed. The portion 42A, and on the circumference of the other side along the outer circumference of the guide portion 50 to 70 of the spring (9) 1336753, is formed with a rib 4 2 which is disposed on the circumference of the one side. Since the lower rib portion 4 2 Β, when the suspension coil spring 13 is attached to the outer circumference of the spring guiding portions 50 to 70, the difference between the height of the higher rib portion 42A and the lower rib portion 42B can be obtained. To make the suspension coil spring 13 eccentric or move in the diameter direction. Thus, if the difference between the heights of the higher ribs 42A and the lower ribs 42B is set to be larger than: the minimum radius of the manufacturing error of the inner peripheral radius of the suspension coil spring 13 is φ, and the spring guide When the difference between the maximum 値 of the manufacturing error of the radius of the lower rib 42B of the portions 50 to 70 is small, the mounting property of the suspension coil spring 13 is excellent. After the suspension coil springs 13 are attached to the outer circumferential sides of the spring guiding portions 50 to 70, the suspension coil springs 13 vibrating due to the vibration of the vehicle body side are in contact with the spring guiding portions 50 to 70. The rib 42A changes the number of windings of the free vibration portion of the suspension coil spring 3 (the longer portion of the spring 13 that does not contact the rib 42 A) to suppress the suspension coil spring φ 1 3 Resonance vibration situation. (b) Since the plurality of ribs 4 2 are formed at equal intervals along the circumference of the outer circumference of the spring guiding portions 50 to 70, the bending of the suspension coil spring 13 can be uniformly restricted on the circumference. situation. The embodiment of the present invention has been described in detail by the drawings. The specific structure of the present invention is not limited to the embodiment, and the present invention also includes the design changes without departing from the scope of the invention. [Simple description of the drawing] -12- (10) (10) 13367573 Figure 1 is a half cross-sectional view showing the hydraulic buffer. Fig. 2 is a view showing a piston valve device, (A) is a sectional view, (B) is a plan view showing the opening valve, (C) is a plan view showing the closing valve, and (D) is a plan view showing the valve seat, (E) It is a sectional view showing the valve spring. Fig. 3 is a view showing a valve guide portion, (A) is a plan view, and (B) is a cross-sectional view taken along line B - B of (A). Fig. 4 is a view showing a spring guiding portion, (A) is a schematic view showing a spring guiding portion of Fig. 3, and (B) to (D) are schematic views showing a spring guiding portion of a modified example. [Description of main component symbols] 1 〇: Hydraulic buffer 1 1 : Buffer cylinder 1 2 : Piston rod 1 3 : Suspension coil spring 1 4 : Body side mounting member 1 5 : Upper spring seat 1 6 : Axle side mounting Member I 7 : Lock nut 18 8 : Lower spring seat 21 : Rod guide 2 2 : Cylinder ring 2 3 : Oil seal-13 - (11) 13367753 24: End plate portion 25: Piston 26A: Oiling chamber 26B: Lower oil chamber 2 7 : Flow path 2 7 A : Damping hole
3 0 :活塞閥裝置 3 1 :閥擋塊 3 2 :閥彈簧 3 3 :開孔閥 3 4 :封閉閥 3 5 :閥座 3 6 :擋塊橡膠 3 7 :回彈彈簧 40 :彈簧導引部3 0 : Piston valve device 3 1 : Valve stop 3 2 : Valve spring 3 3 : Opening valve 3 4 : Closed valve 3 5 : Seat 3 6 : Stop rubber 3 7 : Rebound spring 40 : Spring guide unit
4 1 :鍔部 4 2 :肋部 43 :嵌插用導引面 -144 1 : 锷 4 2 : rib 43 : Inserting guide surface -14