1360616 九、發明說明 【發明所屬之技術領域】 本發明爲車輛等之煞車配管中用於管材連接部的擴口 連結構造。 【先前技術】 該種擴口型管接頭，是利用擴張管材末端的管接頭， φ且在煞車之類的油壓回路中，廣泛運用於油壓機器與管材 之間的連接。該種擴口型管接頭的傳統例如第6圖所示。 在第6圖中，圖號10是表示於末端加工形成擴口部 的金屬製管材，圖號11則表示連接對象的油壓機器本 體。在該本體11開口形成有作爲連接埠之前端呈錐形的 螺絲孔（以下簡稱爲錐形螺絲孔）12，且錐形螺絲孔12 通往油路14»圖號14爲形成於管材10前端的擴口部。圖 號1 5則是本體1 1側呈錐狀的密封面。 • 在管材10外嵌有擴口螺帽17。在錐形螺絲孔12形成 有：可供擴口螺帽17之公螺紋螺合的母螺紋。因此，形 成可藉由鎖緊擴口螺帽17，而使管材10的擴口部14壓接 於密封面1 5。 管材1〇的擴口部14，是利用將末端擴張成圓錐狀的 擴口加工所形成。該擴口部14，其擴口密封面14a是壓接 於所配合的密封面15而形成有效的密封。該種單擴口型 之擴口部14的規格，是依據ISO的標準。本出願人在特 許文獻1中，揭示一種ISO型之擴口連結構造的改良》 -5- 136, 月日修(更)正替換頁:丨 在擴口連結構造中，除了單擴口型之外，還具有如第 7圖所示之JASO標準的雙重擴口型的擴口部20。該雙重 擴口型的擴口部20，是執行兩次擴口加工的產物。 [專利文獻1]日本特開2005-2 14254號公報 【發明內容】 [發明欲解決之課題] 由於ISO型的擴口連結構造是形成：按壓擴口部14 而緊密貼著於密封面15的構造，故將因爲擴口螺帽17的 鎖緊方式而使密封性能有所不同。一旦擴口螺帽17未鎖 緊，將使壓接於密封面15的密封面壓降低，而導致密封 性能不足。相反地，一旦以過量的扭矩來鎖緊擴口螺帽 17，將如第8圖所示，使擴口部14壓潰而產生大量變 形，導致擴口密封面14a從密封面15脫離而使密封面壓 下降。特別是當利用不易控制扭矩的氣動工具來旋鎖擴口 螺帽時，將因爲過量扭矩而形成過度鎖緊，其結果多半是 招致密封性能下降。 在ISO型的擴口連結構造中，除了擴口螺帽17之過 度鎖緊的問題以外，當利用擴口螺帽17使擴口部14壓接 於密封面15時，由於擴口部14是面接觸於密封面，因此 原本就具有難以確保高密封面壓的問題。 不僅如此，當鎖緊擴口螺帽17後，有時管材1〇將因 爲某些原因而略微轉動。在該場合中，擴口螺帽17是與 管材10 —起轉動，長時間下來將衍生出擴口螺帽17鬆 -6- 1360616 --------- .· 年日修 ---—」 弛、密封性能下降的問題。 有鑑於此’本發明的目的是提供一種管材的擴口連結 構造，該管材的擴口連結構造可解決前述傳統技術所具有 的問題點，並可防止當以過量的扭矩鎖緊擴口螺帽、或管 0 材傾斜***時之局部面壓下降的情形，且能確保更高密封 面壓" 此外’本發明的另一個目的是提供一種管材的擴口連 ^ 結構造，該管材的擴口連結構造不易使管材與擴口螺帽一 起轉動，可防止長時間下來密封性能的下降。 [解決問題之手段] 爲達成前述的目的，本發明是在金屬製管材的末端形 成擴口部，並將管材末端***配合構件的錐形螺絲孔，再 藉由將擴口螺帽旋鎖入前述錐形螺絲孔，而使前述擴口部 按壓於前述錐形螺絲孔底面之密封面的管材的擴口連結構 φ 造，其特徵爲：用來密封前述錐形螺絲孔底面的密封面之 前述擴口部的密封面、與被擴口螺帽前端所按壓之前述擴 口部背面的被按壓面，兩者的中心都是在與前述管材之軸 心相同的軸上，並配置在具有大致相同半徑的圓上，當前 述管材的外徑爲〇!( mm)、前述擴口部的最大外徑爲D2 (mm)、前述擴口部之前端的内徑爲D3( mm)時，前述 擴口部爲ISO型，且 (D,-1.2)^D3^〇.8 D2 136 此外，前述擴口部的密封面是形成球面。 此外，特徵爲：當前述球面的球半徑爲r時’ R2 D"2 根據本發明，可防止當以過量的扭矩鎖緊擴口螺帽 時、或管材傾斜地***時之局部性的面壓下降，並可確保 更高的密封面壓。 此外，使得管材與擴口螺帽很難一起轉動，可防止因 擴口螺帽緩緩地鬆弛所引發之長時間的密封性能下降。 【實施方式】 以下，針對本發明之管材的擴口連結構造的實施形 態，參考圖面進行說明》 第1實施形態 第1圖，是顯示本發明第1實施形態之擴口連結構造 的剖面圖。在該第1圖中，圖號10爲金屬製的管材，圖 號11爲連接對象的油壓機器本體。該本體11形成有錐形 螺絲孔12，而該錐形螺絲孔1 2連通於油路1 4。在錐形螺 絲孔12的底面，形成有呈錐狀的密封面15。在管材10外 嵌著擴口螺帽17，該擴口螺帽17是形成：螺令於形成在 錐形螺絲孔1 2的母螺紋》 -8 - 1360616[Technical Field] The present invention relates to a flared connection structure for a pipe joint portion of a brake pipe for a vehicle or the like. [Prior Art] This type of flared pipe joint is a pipe joint that expands the end of the pipe, and is widely used in a hydraulic circuit such as a brake to connect the hydraulic machine to the pipe. A conventional example of such a flared pipe joint is shown in Fig. 6. In Fig. 6, reference numeral 10 denotes a metal pipe material which is formed at the end to form a flared portion, and Fig. 11 shows a hydraulic machine body to be connected. A screw hole (hereinafter simply referred to as a tapered screw hole) 12 which is tapered at a front end of the connecting body is formed in the opening of the body 11, and a tapered screw hole 12 leads to the oil passage 14. FIG. 14 is formed at the front end of the pipe 10. The flared part. Figure 15 is a sealing surface having a tapered shape on the body 1 1 side. • A flared nut 17 is fitted over the tube 10. The tapered screw hole 12 is formed with a female thread for screwing the male screw of the flared nut 17. Therefore, the flared portion 14 of the pipe 10 can be crimped to the sealing surface 15 by locking the flared nut 17. The flared portion 14 of the tube 1 is formed by a flared process in which the tip is expanded into a conical shape. The flared portion 14 has a flared sealing surface 14a that is crimped to the mating sealing surface 15 to form an effective seal. The specifications of the flared portion 14 of the single flare type are in accordance with the ISO standard. In the patent document 1, the present applicant discloses an improvement of the ISO type flare connection structure -5-136, the monthly repair (more) replacement page: 丨 in the flare connection structure, except for the single flare type In addition, there is a double flared flared portion 20 of the JASO standard as shown in Fig. 7. The double flared flared portion 20 is a product that performs two flare processes. [Problem to be Solved by the Invention] The ISO-type flared connection structure is formed by pressing the flared portion 14 and closely adhering to the sealing surface 15 The construction will result in different sealing performance due to the locking manner of the flared nut 17. Once the flared nut 17 is unlocked, the sealing surface pressure crimped to the sealing surface 15 will be lowered, resulting in insufficient sealing performance. Conversely, once the flared nut 17 is locked with an excessive torque, as shown in Fig. 8, the flared portion 14 is crushed to cause a large amount of deformation, causing the flared sealing surface 14a to be detached from the sealing surface 15 The sealing surface pressure drops. In particular, when a pneumatic tool that does not easily control the torque is used to lock the flared nut, excessive locking is caused by excessive torque, and as a result, the sealing performance is likely to be degraded. In the ISO-type flared connection structure, in addition to the problem of excessive locking of the flared nut 17, when the flared portion 14 is crimped to the sealing surface 15 by the flared nut 17, the flared portion 14 is Since the surface is in contact with the sealing surface, there is a problem that it is difficult to ensure a high sealing surface pressure. Moreover, when the flared nut 17 is locked, sometimes the tube 1 turns slightly rotated for some reason. In this case, the flared nut 17 rotates with the pipe 10, and the flared nut 17 is derived for a long time. 6- 1360616 ---------. --" Relaxation and sealing performance degradation problems. In view of the above, an object of the present invention is to provide a flared joint structure of a pipe which can solve the problems of the prior art described above and can prevent the flared nut from being locked with excessive torque. Or the case where the partial pressure of the material is lowered when the material is obliquely inserted, and the higher sealing surface pressure can be ensured. Further, another object of the present invention is to provide a flared structure of the pipe, which is flared. The joint structure is not easy to rotate the pipe together with the flared nut, thereby preventing a decrease in sealing performance over a long period of time. [Means for Solving the Problem] In order to achieve the above object, the present invention forms a flared portion at the end of a metal pipe, and inserts the end of the pipe into a tapered screw hole of the fitting member, and then locks the flared nut into the screw hole. a taper screw hole, wherein the flared portion is pressed against the flared joint structure φ of the pipe surface of the bottom surface of the tapered screw hole, and is characterized in that: a sealing surface for sealing the bottom surface of the tapered screw hole The sealing surface of the flared portion and the pressed surface of the back surface of the flared portion pressed by the tip end of the flared nut are both disposed on the same axis as the axial center of the pipe, and are disposed In the circle having substantially the same radius, when the outer diameter of the pipe is 〇! (mm), the maximum outer diameter of the flared portion is D2 (mm), and the inner diameter of the front end of the flared portion is D3 (mm), the foregoing The flared portion is of the ISO type, and (D, -1.2)^D3^〇.8 D2 136 Further, the sealing surface of the flared portion is formed into a spherical surface. Further, it is characterized in that when the spherical radius of the spherical surface is r, 'R2 D" 2 according to the present invention, it is possible to prevent localized partial pressure drop when the flared nut is locked with excessive torque or when the pipe is obliquely inserted. And can ensure a higher sealing surface pressure. In addition, it is difficult to rotate the pipe and the flared nut together, and the long-term sealing performance degradation caused by the slow relaxation of the flared nut can be prevented. [Embodiment] Hereinafter, an embodiment of a flared connection structure of a pipe according to the present invention will be described with reference to the drawings. First Embodiment FIG. 1 is a cross-sectional view showing a flare connection structure according to a first embodiment of the present invention. . In the first drawing, reference numeral 10 is a metal pipe material, and reference numeral 11 is a hydraulic machine body to be connected. The body 11 is formed with a tapered screw hole 12, and the tapered screw hole 12 is connected to the oil passage 14. A tapered sealing surface 15 is formed on the bottom surface of the tapered screw hole 12. A flared nut 17 is embedded in the pipe 10, and the flared nut 17 is formed by a female thread formed in the tapered screw hole 12 -8 - 1360616
〇年。7月％日敝)i替換頁I 在管材ίο的末端，是藉由擴口加工而形成有圓錐狀 的擴口部30»在本實施形態中，擴口部30基本上是以不 具反折形狀之單擴口型的擴口部爲基礎，並附加以下的特 徵》 管材10的擴口部30是由以下的3個部分所形成：前 端部31;和第1曲折部32，該第1曲折部32是連接於該 前端部31;及第2曲折部33»在第1圖中’ 爲管材1〇 φ 的外徑。D2爲擴口部30的最大外徑’ D3爲前端部31的 内徑。 在擴口部30，於前端部31的外側面’從前端起以特 定的S所標示的圓環狀區域形成密封面。另外’在第1曲 折部32的背面，以寬度S’所標示的圓環狀區域則成爲接 觸於擴口螺帽17前端並形成按壓的被按壓面。接著，密 封面S的區域與被按壓面S’的區域，彼此的中心均位在與 管材10之軸心L相同的軸上，並配置在具有大致相同之 Φ 半徑的圓上。也就是說，擴口部30的密封面S，其中心 位於管材10的軸心L且配置在半徑爲R的圓上，而位在 被擴口螺帽17前端所按壓之擴口部3〇背面的被按壓面 S ’’也同樣是中心位於管材丨〇的軸心l且配置在半徑爲 R的圓上。 密封面S與被按壓面S，呈現具有一定寬度的環狀形 狀，幾乎是相當於以管材1 〇之軸心L作爲軸心的圓錐台 的側面。所謂「密封面S與被按壓面s，，各自的中心均位 在與管材10之軸心L相同的軸上，並配置在大致與半徑 -9- 1360616——--—Ί 年01月^°日修(更)正替換^ 1 , τ- —--i-------- R相等的圓上」是指：密封面S之寬度的中心部與被按壓 面S’之寬度的中心部是分別配置在大致等於半徑R的圓 上。此外，文中所述的「大致相同」是指：密封面S的寬 度範圍與被按壓面S’的寬度範圍在半徑方向上重疊，最好 是上述寬度範圍重疊5 0%以上。 再者，在密封面S的寬度與被按壓面S’的寬度遠低於 半徑R的場合中，幾乎可忽略密封面S的寬度與被按壓面 S’的寬度，密封面S與被按壓面S’的形狀是近似於圓環， 在該場合中上述兩者均是位在同一半徑R的圓上。 接下來，針對構成上述構造之本實施形態的作用及效 果進行說明。 在第1圖中，是將管材10的末端***配合構件也就 是指油壓機器本體11的錐形螺絲孔12。當擴口螺帽17旋 鎖入錐形螺絲孔12時，擴口螺帽17的前端將抵接於擴口 部30的背面。當更進一步旋鎖擴口螺帽17時，擴口部30 的密封面S將按壓錐形螺絲孔12底面的密封面15，而形 成有效地密封。 根據本實施形態，由於是具有「密封面S與被按壓面 S’各自的中心是位在與管材10之軸心L相同的軸上且配 置在大致與半徑R相等的圓上」的構造，故由擴口螺帽 17所作用的按壓力將不會分散地，集中作用於直接將擴口 部30的密封面S壓接於密封面15的壓接作用，如此一 來，可確保高密封面壓。因此，即使是使用氣動工具等不 易管理扭矩的工具來鎖緊擴口螺帽17，也能確實地獲得充 -10- 1360616 ~〇年忙日細正替換l1 分的密封性能。 此外，由於具有「密封面s與被按壓面s’各自的中心 是位在與管材10之軸心L相同的軸上且配置在大致與半 徑R相等的圓上J的構造，因此使作用於被按壓面S’之 力量中的絕大部分作用於密封面S，故可集中於密封作 用，而不會產生如第8圖所示因槓桿作用而使擴口部30 大量變形的情形。如此一來，即使在以過量的扭矩過度旋 鎖擴口螺帽17的場合中，由於擴口部30不會形成大量變 形，因此不會有密封面壓下降的情形，可確保高密封性 m ° 在如同本實施形態之單擴口型的擴口連結構造中，根 據實驗的結果及經驗上的評估，倘若管材10的外徑D, (mm)、擴口部30的最大外徑D2.(mm)、擴口部30前 端的内徑D3 ( mm )之間存在以下的關係時： (D,-l .2) ^D3 ^ 0.8 D2 ... ( 1 ) 密封面S的區域及被按壓面的區域S’，其中心是位在 與管材10之軸心L相同的軸上且配置在大致與半徑R相 同的圓上，密纣面S的區域與被按壓面的區域S’可形成重 疊的構造。 其次，第2圖是顯示：以電腦模擬當改變擴口螺帽17 之軸方向的鎖緊力（N)時，密封面壓（N/cm2 )將產生何 種變化的圖表。在第2圖中，是針對符合計算式（1)， -11 - 1360616 ---^ 叫月π日修(更)正替換妄j 且D3=0.6 5D2之尺寸的擴口連結構造進行模擬。該模擬 的結果是以實線來表示。 以虛線所表示的部分，是顯示針對第6圖所示的傳統 型擴口連結構造採用相同的條件執行模擬的結果。在第6 圖所示的傳統型擴口連結構造中，並不符合上述計算式 (1)的條件，且密封面S的區域與被按壓面的區域S’並 未形成重疊關係。 在第2圖中，當鎖緊力（以下稱爲軸力）從零開始增 加時，密封面壓是上昇後急遽下降，並在軸力爲2 OOON左 右時形成最低。該狀況是從線接觸變化成面接觸所衍生的 現象。根據上述的現象，倘若以軸力2000N來鎖緊，應該 可獲得高密封面壓。話雖如此，但在現場作業中以實際的 擴口螺帽所執行的鎖緊步驟，是無法以不滿2000N的軸力 來完成。現場作業中所呈現的結果是意味著：當以2000N 以上鎖緊時密封面壓的變化。因此，當著眼於第2圖中軸 力200 0N以上的範圍時，可由第2圖清楚的得知，相較於 傳統型的擴口構造，本實施形態的擴口構造的密封面壓更 高，具有更優良的密封性能。 第2實施形態 接著’針對本發明之第2實施形態的擴口連結構造， 參考第3圖進行說明。 該第2實施形態，是將本發明用於具有雙重擴口型之 擴口部30的管材的實施形態。雖然擴口部3〇是由：前端 -12- 1360616 ’V了月知日修(¾轉換頁 部31;和連接於該前端部31的第1曲折部32;及第2曲 折部33的3個部分所形成的這點與單擴口型相同，但是 利用執行2次擴口加工，而使前端部31形成180。反折的 形狀。在第2圖中，0!表示管材10的外徑。D2爲擴口部 30的最大外徑，D3則是前端部31的内徑。Leap year. In the embodiment of the pipe ίο, the flared portion 30 is formed by the flaring process. In the present embodiment, the flared portion 30 is substantially non-reflexed. Based on the shape of the single flared flared portion, the following features are added: The flared portion 30 of the pipe 10 is formed by the following three portions: a front end portion 31; and a first meander portion 32, the first The meandering portion 32 is connected to the front end portion 31; and the second meandering portion 33» is the outer diameter of the pipe 1〇φ in Fig. 1 . D2 is the maximum outer diameter 'D3 of the flared portion 30 is the inner diameter of the tip end portion 31. In the flared portion 30, a sealing surface is formed in an annular region indicated by a specific S from the distal end side of the distal end portion 31. Further, the annular region indicated by the width S' on the back surface of the first bent portion 32 serves as a pressed surface that contacts the tip end of the flared nut 17 and forms a press. Next, the region of the cover S and the region of the pressed surface S' are positioned on the same axis as the axis L of the tube 10, and are disposed on a circle having substantially the same Φ radius. That is, the sealing surface S of the flared portion 30 is located at the axis L of the tube 10 and is disposed on a circle having a radius R, and is located at the flared portion of the flared nut 17 at the front end of the flared portion. The pressed surface S'' on the back side is also centered on the axis l of the tube 且 and arranged on a circle having a radius R. The sealing surface S and the pressed surface S have an annular shape having a constant width, and are almost equivalent to the side surface of the truncated cone having the axial center L of the tube 1 作为 as the axis. The "sealing surface S and the pressed surface s" are each positioned on the same axis as the axis L of the tube 10, and are disposed substantially at the radius of -9-1360616----- January 2001 ^ °日修 (more) is replacing ^ 1 , τ- —--i-------- R is equal to the circle” means the width of the center of the sealing surface S and the width of the pressed surface S′ The center portions are respectively disposed on a circle substantially equal to the radius R. Further, "substantially the same" as used herein means that the width of the sealing surface S overlaps the width of the pressed surface S' in the radial direction, and it is preferable that the width range overlaps by 50% or more. Further, in the case where the width of the sealing surface S and the width of the pressed surface S' are much lower than the radius R, the width of the sealing surface S and the width of the pressed surface S', the sealing surface S and the pressed surface are almost negligible. The shape of S' is approximately a ring, in which case both of the above are on a circle of the same radius R. Next, the action and effect of the present embodiment constituting the above configuration will be described. In Fig. 1, the insertion of the end of the pipe 10 into the fitting member means the tapered screw hole 12 of the hydraulic machine body 11. When the flare nut 17 is screwed into the tapered screw hole 12, the front end of the flare nut 17 abuts against the back surface of the flared portion 30. When the flared nut 17 is further twisted, the sealing surface S of the flared portion 30 will press the sealing surface 15 of the bottom surface of the tapered screw hole 12 to form an effective seal. According to the present embodiment, the center of each of the sealing surface S and the pressed surface S' is located on the same axis as the axis L of the tube 10 and is disposed on a circle substantially equal to the radius R. Therefore, the pressing force applied by the flared nut 17 will not be dispersed, and the centrifugal action of directly pressing the sealing surface S of the flared portion 30 against the sealing surface 15 can be ensured, thereby ensuring a high sealing surface. Pressure. Therefore, even if the flaring nut 17 is locked using a tool such as a pneumatic tool that does not easily manage the torque, it is possible to surely obtain the sealing performance of the charging of the first day of the year. In addition, since the center of each of the "sealing surface s and the pressed surface s' is a structure which is located on the same axis as the axis L of the pipe 10 and is disposed on a circle substantially equal to the radius R, it acts on Most of the force of the pressed surface S' acts on the sealing surface S, so that the sealing action can be concentrated without causing a large deformation of the flared portion 30 due to the lever action as shown in Fig. 8. In the case where the flared nut 17 is excessively twisted with an excessive torque, since the flared portion 30 does not undergo a large amount of deformation, there is no possibility that the sealing surface pressure is lowered, and the high sealing property m ° can be ensured. In the flared joint structure of the single flare type as in the present embodiment, based on the experimental results and empirical evaluation, the outer diameter D of the pipe 10, (mm), and the maximum outer diameter D2 of the flared portion 30 ( Mm), when there is the following relationship between the inner diameter D3 (mm) of the front end of the flared portion 30: (D, -l .2) ^D3 ^ 0.8 D2 (1) The area of the sealing surface S is pressed The area S' of the face is centered on the same axis as the axis L of the tube 10 and is disposed substantially the same as the radius R On the circle, the area of the closed surface S and the area S' of the pressed surface may form an overlapping structure. Next, Fig. 2 is a view showing the locking force in the axial direction of the flared nut 17 by computer simulation (N) When the sealing surface pressure (N/cm2) will produce a graph of what kind of change. In the second figure, it is for the calculation formula (1), -11 - 1360616 ---^ called the month π day repair (more) Simulation is performed by replacing the flaring structure of 妄j and D3=0.6 5D2. The result of this simulation is indicated by a solid line. The portion indicated by a broken line shows the conventional flaring for the sixth figure. The result of the simulation is performed under the same conditions in the joint structure. In the conventional flared joint structure shown in Fig. 6, the condition of the above formula (1) is not satisfied, and the area of the seal surface S and the area of the pressed surface are S' does not form an overlapping relationship. In Fig. 2, when the locking force (hereinafter referred to as the axial force) increases from zero, the sealing surface pressure rises sharply and rises, and is formed when the axial force is about 2 OOON. The lowest is the phenomenon that is derived from the change of line contact into surface contact. For example, if the shaft force is locked by 2000N, a high sealing surface pressure should be obtained. Having said that, the locking step performed by the actual flared nut in the field operation cannot be with an axial force of less than 2000N. The result presented in the on-site operation means that the sealing surface pressure changes when locked at 2000N or more. Therefore, when focusing on the range of the axial force of 200 0N or more in Fig. 2, it can be clearly seen from Fig. 2. It is known that the flaring structure of the present embodiment has a higher sealing surface pressure and a more excellent sealing performance than the conventional flaring structure. The second embodiment follows the flaring of the second embodiment of the present invention. The connection structure will be described with reference to Fig. 3. The second embodiment is an embodiment in which the present invention is applied to a pipe having a double flared flared portion 30. The flared portion 3〇 is composed of: the front end -12- 1360616 'V 月 日 修 修 (3⁄4 conversion page portion 31; and the first meandering portion 32 connected to the front end portion 31; and the second meandering portion 33) This point is formed in the same manner as the single flare type, but the front end portion 31 is formed by 180. The shape of the fold is reversed by performing the second flare processing. In Fig. 2, 0! indicates the outer diameter of the pipe 10. D2 is the maximum outer diameter of the flared portion 30, and D3 is the inner diameter of the front end portion 31.
在該雙重擴口型的擴口部30中，密封面s與被按壓 面S’是爲在第3圖中所示的位置。密封面S與被按壓面 S’，各自的中心是位在與管材1〇之軸心L相同的軸上， 且配置在大致與半徑R相等的圓上，而密封面S與被按壓 面S ’在半徑方向上形成重疊的狀態是與第1實施形態相 同。 根據上述的第2實施形態，與第1實施形態相同，即 使在以過量的扭矩來過度鎖緊擴口螺帽17的場合中，也 能確保高度的密封性能。 而在雙重擴口型的場合中，當管材10的外徑Di (mm)、擴口部30的最大外徑D2(mm)、前述擴口部 之前端的内徑D3 ( mm )之間存在以下的關係時： (D 1 - 1 · 〇) ^ D3 ^ 0.8D2 ... ( 2 ) 密封面s的區域與被按壓面S’的區域，其中心是位在 與管材10之軸心L相同的軸上並配置在大致與半徑R相 等的圓上，而可形成密封面S的區域與被按壓面的區域S， 重疊的構造。 -13- 1360616_n ~箄</|月〇日修(更)正替換頁.. 第3實施形態 接著，針對本發明之第3實施形態的擴口連結構造’ 參考第4圖進行說明》 該第4實施形態的擴口連結構造，是更進—步改良第 1實施形態之單擴口型擴口連結構造而成’其擴口部30的 密封面是形成球面的實施形態。在該擴口部30的場合中 是形成：從前端部31的外周面起至第1曲折部32的外周 面爲止，連接成大致相同半徑的球面。 .不僅如此，當中心位於管材1 〇的軸線上之球面的球 半徑爲R時，與管材10的外徑Di之間存在以下的關係： R ^ D,/2 ... ( 3 ) 而在該第3實施形態中，擴口部30之密封面的區域 S與被按壓面的區域S’是與第1實施形態相同，並符合計 算式（1)的關係，也就是說：密封面S的區域與被按壓 面的區域S’的中心是位在與管材1〇之軸心L相同的軸上 且配置在大致與半徑R相同的圓上，而且密封面S的區域 與被按壓面的區域S’可形成重疊的構造。 根據上述的第3實施形態，除了可獲得第1實施形態 的作用效果之外’由於擴口部30的密封面S形成球面， 故即使是線接觸於密封面15的單擴口型擴口部3〇，也可 以藉由每個單位面積之密封力增大的線密封構造，確實地 -14 - 1360616 月》日修(更)正替換;頁i 確保更高的密封面壓。 此外’在末端具有擴口部30之管材10的場合中，當 管材1〇***錐形螺絲孔12時，是對軸芯呈傾斜地***。 在該場合中’當管材10呈傾斜的狀態下鎖緊擴口螺帽17 時’將使擴口部30的密封面s不對稱地接觸於密封面15 (亦即非全面接觸），而具有擴口部30之整個外周無法 形成密封狀態》In the double flared flared portion 30, the sealing surface s and the pressed surface S' are at the positions shown in Fig. 3. The sealing surface S and the pressed surface S' each have a center on the same axis as the axis L of the tube 1〇, and are disposed on a circle substantially equal to the radius R, and the sealing surface S and the pressed surface S The state in which the overlapping in the radial direction is the same as in the first embodiment. According to the second embodiment described above, as in the first embodiment, even when the flare nut 17 is excessively locked with an excessive torque, the high sealing performance can be ensured. In the case of the double flare type, the outer diameter Di (mm) of the pipe 10, the maximum outer diameter D2 (mm) of the flared portion 30, and the inner diameter D3 (mm) of the front end of the flared portion are as follows. When the relationship is: (D 1 - 1 · 〇) ^ D3 ^ 0.8D2 ( 2 ) The area of the sealing surface s and the area of the pressed surface S' are at the same center as the axis L of the tube 10 The shaft is disposed on a circle substantially equal to the radius R, and the region where the sealing surface S is formed and the region S of the pressed surface overlap each other. -13- 1360616_n ~ 箄 </|月〇日修 (more) replacement page.. Third Embodiment Next, the flare connection structure of the third embodiment of the present invention will be described with reference to Fig. 4 In the flared connection structure of the fourth embodiment, the single-flare-type flared connection structure of the first embodiment is further improved. The sealing surface of the flared portion 30 is a spherical surface. In the case of the flared portion 30, a spherical surface having substantially the same radius is formed from the outer peripheral surface of the distal end portion 31 to the outer peripheral surface of the first meandering portion 32. Moreover, when the spherical radius of the spherical surface centered on the axis of the pipe 1 为 is R, there is the following relationship with the outer diameter Di of the pipe 10: R ^ D, /2 ... ( 3 ) In the third embodiment, the region S of the sealing surface of the flared portion 30 and the region S' of the pressed surface are the same as in the first embodiment, and conform to the relationship of the calculation formula (1), that is, the sealing surface S. The center of the region S' of the pressed surface is located on the same axis as the axis L of the tube 1〇 and is disposed on a circle substantially the same as the radius R, and the region of the sealing surface S and the surface to be pressed The area S' can form an overlapping configuration. According to the third embodiment described above, the sealing surface S of the flared portion 30 forms a spherical surface in addition to the effect of the first embodiment. Therefore, even the single-flare-shaped flared portion that is in line contact with the sealing surface 15 is formed. 3〇, it is also possible to replace the line seal structure with an increase in sealing force per unit area, and it is surely replaced by 14- 1360616 (day); page i ensures a higher sealing surface pressure. Further, in the case where the tube 10 having the flared portion 30 is provided at the end, when the tube 1 is inserted into the tapered screw hole 12, the shaft core is inserted obliquely. In this case, 'when the flare nut 17 is locked in a state where the pipe 10 is inclined' will cause the sealing surface s of the flared portion 30 to asymmetrically contact the sealing surface 15 (ie, not in full contact), and have The entire periphery of the flared portion 30 cannot form a sealed state"
但是，根據第3實施形態，由於擴口部30的密封面 S是形成球面，因此很難不規則地抵接於密封面15，故整 個外周可藉由線密封構造而確保高密封面壓》 第4實施形態 第5圖，是顯示本發明第4實施形態之擴口連結構造 的圖。 上述第1〜第3實施形態的擴口連結構造，主要是可 φ 獲得高密封面壓之擴口部的密封構造，但以下所說明的第 4實施形態，是除了第1〜第3實施形態的擴口連結構造 之外，可更進一步防止管材10與擴口螺帽17 —起轉動之 單擴口型的擴口連結構造。 在第5圖中，於密封面15上，藉由沖床加工或滚花 加工等所形成的凹凸部5 0是與錐形螺絲孔1 2同軸地形成 圓環狀。在該場合中，凹凸部50是配置在：作爲密封面 1 5而發揮作用之區域的外側。擴口部3 〇的第1曲折部3 2 是形成抵接於該凹凸部50。擴口部30側的密封面S與凹 -15- I261M6--, ’。^卞日#(更)正替換頁j 凸部50之間的關係是形成：當被按壓於錐形螺絲孔12的 底面時’凹凸部50是位在有效密封的擴口部30側之密封 面S的區域外。換言之，擴口部30之密封面S的區域是 形成於內側，以避免與凹凸部50接觸。而在第5圖中， 雖然凹凸部50是形成在半徑方向上連接有凹凸，但凹凸 亦可連接於圓環狀的圓周方向上。 根據上述的第4實施形態，當鎖入擴口螺帽17時， 擴口部30的密封面S被按壓於錐形螺絲孔12底面的密封 面15，並使密封面S的外側被壓接於凹凸部50而變的緊 密。如此一來，可使出現於擴口部30與密封面15之間的 摩擦係數顯著增加。因此，無論以任何的原因對管材10 作用轉動力，管材也不會轉動，如此一來，可防止因轉動 而造成擴口螺帽17的鬆弛。據此，在旋鎖管材10後，可 長時間維持開始時的密封性能。 造 構 結 S 連 □ 擴 之 態 形 施 實 11 第 明 發 本 示 1 顯 明爲 說.. 單圖 簡 1 式第 圖 的縱剖面圖。 第2圖：是顯示模擬本發明第1實施形態之擴口連結 構造中，當鎖緊力改變時之密封面壓的變化結果的圖表。 第3圖：爲顯示本發明第2實施形態之擴口連結構造 的縱剖面圖。 第4圖：爲顯示本發明第3實施形態之擴口連結構造 的縱剖面圖。 -16- 1360616 ~年1月”日修(更)正替換頁j 第5圖：爲顯示本發明第4實施形態之擴口連結構造 的縱剖面圖。 第6圖：爲傳統擴口連結構造的縱剖面圖。 第7圖：爲雙重擴口型之擴口部的縱剖面圖。 第8圖：爲顯示傳統擴口連結構造之問題點的縱剖面However, according to the third embodiment, since the sealing surface S of the flared portion 30 is formed into a spherical surface, it is difficult to irregularly abut against the sealing surface 15, so that the entire outer circumference can be secured by the wire sealing structure to ensure a high sealing surface pressure. (Fourth embodiment) Fig. 5 is a view showing a flare connection structure according to a fourth embodiment of the present invention. In the flared connection structure of the above-described first to third embodiments, the sealing structure of the flared portion having a high sealing surface pressure can be obtained. However, the fourth embodiment described below is the first to third embodiments. In addition to the flared connection structure, the single flared flared connection structure in which the pipe material 10 and the flare nut 17 rotate together can be further prevented. In Fig. 5, on the sealing surface 15, the uneven portion 50 formed by punching or knurling or the like is formed in an annular shape coaxially with the tapered screw hole 12. In this case, the uneven portion 50 is disposed outside the region that functions as the sealing surface 150. The first meandering portion 3 2 of the flared portion 3 is formed to abut against the uneven portion 50. The sealing surface S on the side of the flared portion 30 is recessed -15-I261M6--, '. ^卞日# (more) replacement page j The relationship between the convex portions 50 is formed such that when pressed against the bottom surface of the tapered screw hole 12, the concave-convex portion 50 is a seal on the flared portion 30 side of the effective seal. Outside the area of the surface S. In other words, the region of the sealing surface S of the flared portion 30 is formed on the inner side to avoid contact with the uneven portion 50. On the other hand, in Fig. 5, although the uneven portion 50 is formed with irregularities formed in the radial direction, the unevenness may be connected to the annular circumferential direction. According to the fourth embodiment described above, when the flared nut 17 is locked, the sealing surface S of the flared portion 30 is pressed against the sealing surface 15 of the bottom surface of the tapered screw hole 12, and the outer side of the sealing surface S is crimped. It becomes denser in the uneven portion 50. As a result, the coefficient of friction occurring between the flared portion 30 and the sealing surface 15 can be significantly increased. Therefore, the tube does not rotate regardless of the rotational force acting on the tube 10 for any reason, so that the slack of the flared nut 17 due to the rotation can be prevented. According to this, after the twisting of the pipe 10, the sealing performance at the beginning can be maintained for a long time. The construction of the knot S □ □ expansion of the state of the implementation of the 11th syllabus 1 shows that: single figure simplification 1 type of the figure of the longitudinal section. Fig. 2 is a graph showing a result of a change in the sealing surface pressure when the locking force is changed in the flared connection structure according to the first embodiment of the present invention. Fig. 3 is a longitudinal sectional view showing a flare connection structure according to a second embodiment of the present invention. Fig. 4 is a longitudinal sectional view showing a flare connection structure according to a third embodiment of the present invention. -16- 1360616 - January of the year "Nearly (more) replacement page j Fig. 5 is a longitudinal cross-sectional view showing the flare connection structure of the fourth embodiment of the present invention. Fig. 6 is a conventional flare connection structure Longitudinal section view. Figure 7: Longitudinal section of the flared portion of the double flare type. Fig. 8: Longitudinal section showing the problem of the conventional flared joint structure
【主要元件符號說明】 I 〇 :管材 II :油壓機器本體 1 2 :錐形螺絲孔[Main component symbol description] I 〇 : Pipe II : Hydraulic machine body 1 2 : Tapered screw hole
1 4 :油路 1 5 :密封面 1 7 :擴口螺帽 30 :擴口部 3 1 :前端部 3 2 :第1曲折部 3 3 :第2曲折部 S :密封面 S’ ：被按壓面 -17-1 4 : Oil passage 1 5 : Sealing surface 1 7 : Flared nut 30 : Flared portion 3 1 : Front end portion 3 2 : First bent portion 3 3 : Second bent portion S : Sealing surface S' : Pressed Face -17-