TW201719060A - Seal member - Google Patents
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- TW201719060A TW201719060A TW105133027A TW105133027A TW201719060A TW 201719060 A TW201719060 A TW 201719060A TW 105133027 A TW105133027 A TW 105133027A TW 105133027 A TW105133027 A TW 105133027A TW 201719060 A TW201719060 A TW 201719060A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
- F16J15/3232—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Sealing With Elastic Sealing Lips (AREA)
- Sealing Devices (AREA)
- Actuator (AREA)
- Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
Abstract
Description
本發明係關於一種密封構造，尤其關於使用在油空壓機器等之桿(活塞桿)與缸體之滑動間隙之密封構件之構造。The present invention relates to a sealing structure, and more particularly to a configuration of a sealing member used in a sliding gap between a rod (piston rod) of an oil air compressor or the like and a cylinder block.
例如，於油壓機器之缸體與桿(活塞桿)之滑動間隙，為防止被導入至油室之作動油洩漏(作動油自高壓側朝低壓側洩漏)、且順暢實現桿之往復運動，而採用將密封構件嵌入至設置於缸體之密封槽之密封構造。此種密封構造係揭示於日本專利特開2005-337440號公報(專利文獻1)、日本專利特開2014-214769(專利文獻2)等。 [先前技術文獻] [專利文獻] [專利文獻1]日本專利特開2005-337440號公報 [專利文獻2]日本專利特開2014-214769號公報For example, in the sliding gap between the cylinder of the hydraulic machine and the rod (piston rod), in order to prevent leakage of the oil introduced into the oil chamber (the operating oil leaks from the high pressure side to the low pressure side), and smoothly reciprocate the rod, Further, a sealing structure in which the sealing member is fitted into the seal groove provided in the cylinder block is employed. Such a sealing structure is disclosed in Japanese Laid-Open Patent Publication No. 2005-337440 (Patent Document 1), JP-A-2014-214769 (Patent Document 2), and the like. [PRIOR ART DOCUMENT] [Patent Document 1] Japanese Patent Laid-Open Publication No. JP-A-2005-337749
[發明所欲解決之問題] 近年來，為進一步提高密封構造之密封性能，對密封構件之改善日益不斷地進行。 本發明係為解決上述課題而完成者，其目的在於提供一種可更為提高密封構造之密封性能之密封構件。 [解決問題之技術手段] 基於本發明之密封構件係於油空壓機器之缸體與桿之滑動間隙區中劃分高壓側與低壓側，收納於沿上述桿之外周面之周向設置成環狀之密封槽之內部，且封堵上述缸體與上述桿之滑動間隙者，且具備以下之構成。 本發明之密封構件包含位於低壓側之底座部與位於高壓側之唇部，且上述底座部具有位於上述桿側之第1側面、與上述第1側面對向之第2側面、及位於高壓側之第3側面；上述唇部具有朝上述桿側擴展之第1唇部、及朝與上述桿側相反之側擴展之第2唇部；於上述底座部之第1側面及上述第3側面相交之區域，設置彎曲面及斜面；上述彎曲面係以與上述第1側面及上述斜面相接之方式設置，上述斜面係以與上述第3側面相交之方式設置。 於另一形態中，上述彎曲面及上述斜面朝上述第3側面之投影長度為0.3 mm以上且2 mm以下，上述彎曲面之半徑為2 mm以上且15 mm以下，上述斜面相對於上述第3側面之傾斜角度為30°～80°。 [發明之效果] 根據本發明，可提供一種可更為提高密封構造之密封性之密封構造。[Problems to be Solved by the Invention] In recent years, in order to further improve the sealing performance of the sealing structure, the improvement of the sealing member has been progressing increasingly. The present invention has been made to solve the above problems, and an object thereof is to provide a sealing member which can further improve sealing performance of a sealing structure. [Means for Solving the Problem] The sealing member according to the present invention is divided into a high pressure side and a low pressure side in a sliding gap region between a cylinder and a rod of an oil air compressor, and is housed in a circumferential direction along the outer circumferential surface of the rod. The inside of the seal groove is formed, and the sliding gap between the cylinder and the rod is blocked, and the following configuration is provided. The sealing member of the present invention includes a base portion on the low pressure side and a lip portion on the high pressure side, and the base portion has a first side surface on the rod side, a second side surface facing the first side surface, and a high pressure side a third side surface; the lip portion has a first lip portion that expands toward the rod side, and a second lip portion that expands toward a side opposite to the rod side; and the first side surface and the third side surface of the base portion intersect The curved surface and the inclined surface are provided in the region, and the curved surface is provided in contact with the first side surface and the inclined surface, and the inclined surface is provided to intersect the third side surface. In another aspect, a projection length of the curved surface and the inclined surface toward the third side surface is 0.3 mm or more and 2 mm or less, and a radius of the curved surface is 2 mm or more and 15 mm or less, and the inclined surface is opposite to the third surface. The angle of inclination of the side is 30° to 80°. [Effects of the Invention] According to the present invention, it is possible to provide a sealing structure which can further improve the sealing property of the sealing structure.
就基於本發明之實施形態之密封構件及使用該密封構件之構造，以下參照圖式進行說明。於以下所說明之實施形態中，於言及個數、量等之情形時，除有特別記載之情形外，本發明之範圍未必限定於該個數、量等。對相同之構件、相當之零件標註相同之參照序號，而有不予重複說明之情形。以下，作為油空壓機器之一例，以油壓缸為例，但並非限定於油壓缸，可廣泛應用於油空壓機器。 (密封構造) 參照圖1，對本實施形態之密封構造進行說明。圖1係表示實施形態之油壓缸所採用之密封構造之剖視圖。圖1中，為便於說明，缸體1及桿(活塞桿)2以虛線表示。圖1所示之密封構造係伴隨與桿2之壓接及桿2之往復運動(圖1中之上下方向)而變形，但為明晰理解密封構造，而圖示有未對密封構造施加壓力之狀態。 沿桿2之外周面之周向設置有環狀之第1密封槽10G。於該第1密封槽10G，收納有封堵缸體1與桿2之滑動間隙之第1密封構件10。 於較第1密封槽10G更靠高壓側，設置有第2密封槽20G，其沿桿2之外周面之周向設置成環狀。於圖示中，於上方側設置有高壓之油壓室。於第2密封槽20G，收納有封堵缸體1與桿2之滑動間隙之第2密封構件20。 (第1密封構件10) 參照圖2及圖3，就本實施形態之第1密封構件10進行說明。圖2係表示第1密封構件10之構造之立體圖，圖3係圖2中之III線箭頭剖視圖。 第1密封構件10整體具有環狀之形態，由胺基甲酸酯樹脂等合成樹脂、天然橡膠、合成橡膠、或氟橡膠而一體成型。第1密封構件10之於高壓側具有開放側之剖面形狀，具有大致U字形狀。 更具體而言，於圖3所示之剖視圖中，第1密封構件10具備位於低壓側之底座部10h、及位於高壓側之唇部10r。底座部10h包含位於桿2側之第1側面101、與第1側面101對向之第2側面102、及位於高壓側之第3側面103。 唇部10r包含朝桿2側擴展之第1唇部10b、及朝與桿2側相反之側擴展之第2唇部10c。由第1唇部10b及第2唇部10c形成大致U字形狀。 進而，於自底座部10h觀察時為桿2側之低壓側、且底座部10h之第1側面101及第3側面103相交之區域，設有彎曲面110及斜面120。彎曲面110係以與第1側面101及斜面120相接之方式設置，斜面120係以與第3側面103相交之方式設置。 若將彎曲面110及斜面120朝第3側面103之投影長度設為「a」、將彎曲面110之半徑設為「R」、將斜面120之相對於第3側面103之傾斜角度設為「θ」，則為要獲得第1密封構件10對於桿2之更良好之密封性，較佳為投影長度「a」為0.3 mm以上2 mm以下，彎曲面110之半徑「R」為2 mm以上15 mm以下，斜面120相對於第3側面103之傾斜角度「θ」為30°～80°。關於此點，將於後述之實施例進行說明。 再次參照圖1，於自第1密封構件10觀察時，將桿2自低壓側朝高壓側移動之情形稱作「拉步驟」，將桿2自高壓側朝低壓側移動之情形稱作「推步驟」。 參照圖4至圖6，對第1密封構件10之密封狀態進行說明。圖4係表示「拉步驟」之密封狀態之局部放大模式圖，圖5A係表示安裝時之第1密封構件10之密封壓狀態之圖，圖5B係表示安裝時之第1密封構件10之接觸寬度與接觸面壓之關係之圖，圖6A係表示壓力負載時之第1密封構件10之密封壓狀態之圖，圖6B係表示壓力負載時之第1密封構件10之接觸寬度與接觸面壓之關係之圖。另，圖5A、圖6A中P1～P10表示內壓之分佈，表示內壓自P1朝P10減小。 如圖4及圖5A所示，藉由具有第1唇部10b朝桿2側擴展之形態，且於第1密封構件10之底座部10h之第1側面101及第3側面103相交之區域，設置彎曲面110及斜面120，即使於安裝時，底座部10h對桿2仍為非接觸狀態，故於「拉步驟」時，可使油OL易於流回缸體1之內部。 由圖5B之表示安裝時之第1密封構件10之接觸寬度與接觸面壓之關係之圖亦可明瞭，在底座部10h之第1側面101及第3側面103相交之區域，因未接觸到桿2，故於區域R1中未產生峰值面壓。另一方面，由於第1唇部10b與第2唇部10c被第1密封槽10G與桿2相夾而大幅變形，故基於其反作用力，而於區域P2(由(A)中之P9所示之區域)發生由接觸引起之峰值面壓。 接著，即使於圖6A及圖6B之壓力負載時，藉由於底座部10h之第1側面101及第3側面103相交之區域設置彎曲面110及斜面120，而未於區域R1中發生峰值面壓，即使接觸寬度移動，但接觸面壓仍可保持平緩狀態。其結果，朝向缸體1內部之油可較少阻力地回流，藉由使用第1密封構件10之密封構造，油吸入特性提高，而可進一步提高密封性。 另一方面，圖7顯示關聯技術之第1密封構件10X之剖視圖。其係相當於圖2中之III-III線箭頭剖視之圖。唇部10r之第1唇部10b及第2唇部10c之形狀與本實施形態之第1密封構件10相同。該第1密封構件10X係於第1側面101及第3側面103相交之區域僅設置斜面150而未設置彎曲面。 參照圖8至圖10B，對關聯技術之第1密封構件10X之密封狀態進行說明。圖8係表示「拉步驟」之密封狀態之局部放大模式圖，圖9A係表示安裝時之第1密封構件10X之密封壓狀態之圖，圖9B係表示安裝時之第1密封構件10X之接觸寬度與接觸面壓之關係之圖，圖10A係表示壓力負載時之第1密封構件10X之密封壓狀態之圖，圖10B係表示壓力負載時之第1密封構件10X之接觸寬度與接觸面壓之關係之圖。另，圖9A、圖10A中P1～P10表示內壓之分佈，表示內壓自P1朝P10減小。 如圖8及圖9A所示，第1密封構件10X係未於第1密封構件10X之底座部10h設置彎曲面而僅設有斜面150。其結果，於安裝時，底座部10h對桿2成為接觸狀態，如圖9B所示，於區域R3形成峰值面壓。再者，即使於圖10A及圖10B之壓力負載時，因於底座部10h之第1側面101及第3側面103相交之區域僅有斜面150，故於區域R4發生更大之峰值面壓。結果導致於拉步驟時，油吸入特性變差而成為油洩漏之要因之一。 於圖11中，對比說明實施形態之第1密封構件10與關聯技術之第1密封構件10X之洩漏量。圖11係表示實施形態之第1密封構件10與關聯技術之第1密封構件10X之滑動距離及洩漏量之關係之圖。 第1密封構件10及第1密封構件10X皆使用胺基甲酸酯樹脂等之合成樹脂(硬度：硬度計A90、抗拉強度Mpa44.0、伸展性500%、壓縮永久變形40%、壓縮永久變形試驗之條件8)(80°C-70 h)：日本華爾卡工業股份有限公司製；產品編號R5590))。 第1密封構件10係R=2 mm、θ=60°、a=0.6 mm。第1密封構件10X未設置彎曲面，斜面150係R=0 mm、θ=45°、a=0.5 mm(所謂C面=0. 5mm)。 測定中，對任一者僅安裝第1密封構件而測定來自缸體1之油之外部洩漏量。將其結果示於圖11。可確認，本實施形態之第1密封構件10與關聯技術之第1密封構件10X相比具有良好之密封性。 (實施例) 圖12及圖13顯示本實施形態之第1密封構件10之變化例之構造。圖12顯示將「a」設為較大之第1密封構件10A之形狀，圖13顯示將「θ」設為較大之第1密封構件10B之情形。 進而，於圖14至圖16B中，作為具體之實施例1至實施例3，示出壓力負載時之接觸寬度與接觸面壓之關係。實施例1之第1密封構件10具有R=15、θ=80°、a=0.3之形狀，實施例2之第1密封構件10具有R=2、θ=30°、a=2之形狀，實施例3之第1密封構件10具有R=0.5、θ=30°、a=2之形狀。於各圖A中，P1～P10表示內壓之分佈，表示內壓自P1朝P10減小。 圖14A及圖14B所示之實施例1之情形，因於接觸寬度之全域中皆未發生峰值面壓而呈現良好之面壓，故可確認具有優良之密封性。 圖15A及圖15B所示之實施例2之情形，與上述實施例1相比，於接觸寬度之全域皆未發生峰值面壓而呈現更良好之面壓，故可確認具有優良之密封性。 圖16A及圖16B所示之實施例3之情形，與上述實施例1相比，於接觸寬度約1 mm附近之區域發生微小之峰值面壓，故雖與實施例1相比並非良好，但與圖10A及圖10B所示之關聯技術相比為良好，故可確認整體上具有良好之密封性。 根據以上之實施例，於底座部10h之第1側面101及第3側面103相交之區域，設置彎曲面110及斜面120，且彎曲面110係以與第1側面及斜面120相接之方式設置，斜面120係以與第3側面103相交之方式設置。藉此，本實施形態之第1密封構件具有良好之密封性。 進而，將彎曲面110及斜面120朝第3側面103之投影長度「a」設為0.3 mm以上2 mm以下，將彎曲面110之半徑「R」設為2 mm以上15 mm以下，且將斜面120相對於第3側面103之傾斜角度「θ」設為30°～80°，可獲得更理想之密封性。 以上，已對實施形態及實施例進行說明，但應理解，此次所揭示之實施形態就其所有方面皆為例示而非限制者。本發明之範圍係由申請專利範圍揭示，意在包含與申請專利範圍為均等含義及範圍內之所有變更。The sealing member according to the embodiment of the present invention and the structure using the sealing member will be described below with reference to the drawings. In the embodiments described below, the scope of the present invention is not necessarily limited to the number, the amount, and the like, unless otherwise stated. The same components and equivalent components are denoted by the same reference numerals, and the description will not be repeated. Hereinafter, as an example of the oil air compressor, the hydraulic cylinder is exemplified, but the hydraulic cylinder is not limited to the hydraulic cylinder, and can be widely applied to an oil air compressor. (Sealing Structure) A sealing structure of the present embodiment will be described with reference to Fig. 1 . Fig. 1 is a cross-sectional view showing a sealing structure used in a hydraulic cylinder according to an embodiment. In Fig. 1, the cylinder 1 and the rod (piston rod) 2 are indicated by broken lines for convenience of explanation. The sealing structure shown in Fig. 1 is deformed by the pressure contact with the rod 2 and the reciprocating motion of the rod 2 (the upper and lower directions in Fig. 1), but the sealing structure is clearly understood, and the pressure is not applied to the sealing structure. status. An annular first seal groove 10G is provided along the circumferential direction of the outer peripheral surface of the rod 2. The first sealing member 10 that blocks the sliding gap between the cylinder 1 and the rod 2 is housed in the first seal groove 10G. The second seal groove 20G is provided on the high pressure side of the first seal groove 10G, and is provided in a ring shape along the circumferential direction of the outer peripheral surface of the rod 2. In the drawing, a high pressure hydraulic chamber is provided on the upper side. The second sealing member 20 that blocks the sliding gap between the cylinder 1 and the rod 2 is housed in the second seal groove 20G. (First Sealing Member 10) The first sealing member 10 of the present embodiment will be described with reference to Figs. 2 and 3 . Fig. 2 is a perspective view showing the structure of the first sealing member 10, and Fig. 3 is a cross-sectional view taken along line III of Fig. 2; The first sealing member 10 has an annular shape as a whole, and is integrally molded from a synthetic resin such as a urethane resin, natural rubber, synthetic rubber, or fluororubber. The first sealing member 10 has a cross-sectional shape on the open side on the high pressure side, and has a substantially U-shape. More specifically, in the cross-sectional view shown in FIG. 3, the first sealing member 10 includes a base portion 10h on the low pressure side and a lip portion 10r on the high pressure side. The base portion 10h includes a first side surface 101 on the side of the rod 2, a second side surface 102 facing the first side surface 101, and a third side surface 103 on the high pressure side. The lip portion 10r includes a first lip portion 10b that expands toward the rod 2 side, and a second lip portion 10c that expands toward the side opposite to the rod 2 side. The first lip portion 10b and the second lip portion 10c are formed in a substantially U shape. Further, a curved surface 110 and a sloped surface 120 are provided in a region where the low pressure side of the rod 2 is viewed from the base portion 10h and the first side surface 101 and the third side surface 103 of the base portion 10h intersect. The curved surface 110 is provided in contact with the first side surface 101 and the inclined surface 120, and the inclined surface 120 is provided to intersect the third side surface 103. The projection length of the curved surface 110 and the inclined surface 120 toward the third side surface 103 is "a", the radius of the curved surface 110 is "R", and the inclination angle of the inclined surface 120 with respect to the third side surface 103 is " θ" is to obtain a better sealing property of the first sealing member 10 with respect to the rod 2. It is preferable that the projection length "a" is 0.3 mm or more and 2 mm or less, and the radius "R" of the curved surface 110 is 2 mm or more. 15 mm or less, the inclination angle "θ" of the slope 120 with respect to the third side surface 103 is 30° to 80°. In this regard, an embodiment to be described later will be described. Referring again to FIG. 1, when the first sealing member 10 is viewed from the first sealing member 10, the case where the rod 2 is moved from the low pressure side to the high pressure side is referred to as a "pull step", and the case where the rod 2 is moved from the high pressure side to the low pressure side is referred to as "pushing". step". The sealing state of the first sealing member 10 will be described with reference to Figs. 4 to 6 . Fig. 4 is a partially enlarged schematic view showing a sealed state of the "pull step", Fig. 5A is a view showing a state of sealing pressure of the first sealing member 10 at the time of mounting, and Fig. 5B is a view showing contact of the first sealing member 10 at the time of mounting. FIG. 6A is a view showing a state of a sealing pressure of the first sealing member 10 at the time of a pressure load, and FIG. 6B is a view showing a contact width and a contact surface pressure of the first sealing member 10 at the time of a pressure load. The map of the relationship. In addition, in FIGS. 5A and 6A, P1 to P10 indicate the distribution of the internal pressure, and the internal pressure is decreased from P1 toward P10. As shown in FIG. 4 and FIG. 5A, the first lip portion 10b is expanded toward the rod 2 side, and the first side surface 101 and the third side surface 103 of the base portion 10h of the first sealing member 10 intersect each other. Since the curved surface 110 and the inclined surface 120 are provided, even if the base portion 10h is in a non-contact state with respect to the rod 2 at the time of attachment, the oil OL can be easily returned to the inside of the cylinder 1 during the "pull step". FIG. 5B is a view showing the relationship between the contact width of the first sealing member 10 and the contact surface pressure at the time of mounting, and the area where the first side surface 101 and the third side surface 103 of the base portion 10h intersect is not contacted. Since the rod 2 is so, no peak surface pressure is generated in the region R1. On the other hand, since the first lip portion 10b and the second lip portion 10c are largely deformed by being sandwiched by the first seal groove 10G and the rod 2, the reaction force is applied to the region P2 (by P9 in (A) The area shown is the peak surface pressure caused by the contact. Then, even in the case of the pressure load of FIGS. 6A and 6B, the curved surface 110 and the inclined surface 120 are provided in the region where the first side surface 101 and the third side surface 103 of the base portion 10h intersect, and the peak surface pressure does not occur in the region R1. Even if the contact width moves, the contact surface pressure can be kept flat. As a result, the oil toward the inside of the cylinder 1 can be reflowed with less resistance, and by using the sealing structure of the first sealing member 10, the oil suction characteristics are improved, and the sealing property can be further improved. On the other hand, Fig. 7 shows a cross-sectional view of the first sealing member 10X of the related art. This is equivalent to the cross-sectional view of the arrow III-III in Fig. 2 . The shape of the first lip portion 10b and the second lip portion 10c of the lip portion 10r is the same as that of the first sealing member 10 of the present embodiment. In the first sealing member 10X, only the inclined surface 150 is provided in a region where the first side surface 101 and the third side surface 103 intersect, and no curved surface is provided. The sealing state of the first sealing member 10X of the related art will be described with reference to Figs. 8 to 10B. Fig. 8 is a partially enlarged schematic view showing a sealed state of the "pull step", Fig. 9A is a view showing a state of sealing pressure of the first sealing member 10X at the time of mounting, and Fig. 9B is a view showing contact of the first sealing member 10X at the time of mounting. FIG. 10A is a view showing a state of a sealing pressure of the first sealing member 10X at the time of a pressure load, and FIG. 10B is a view showing a contact width and a contact surface pressure of the first sealing member 10X at the time of a pressure load. The map of the relationship. Further, in Figs. 9A and 10A, P1 to P10 indicate the distribution of the internal pressure, and the internal pressure is decreased from P1 toward P10. As shown in FIG. 8 and FIG. 9A, the first sealing member 10X is not provided with a curved surface in the base portion 10h of the first sealing member 10X, and only the inclined surface 150 is provided. As a result, at the time of mounting, the base portion 10h is brought into contact with the rod 2, and as shown in Fig. 9B, a peak surface pressure is formed in the region R3. Further, even in the pressure load of FIGS. 10A and 10B, since the region where the first side surface 101 and the third side surface 103 of the base portion 10h intersect has only the slope 150, a larger peak surface pressure is generated in the region R4. As a result, the oil suction characteristics are deteriorated during the drawing step and become one of the causes of oil leakage. In Fig. 11, the leakage amount of the first sealing member 10 of the embodiment and the first sealing member 10X of the related art will be described in comparison. Fig. 11 is a view showing the relationship between the sliding distance and the amount of leakage of the first sealing member 10 of the embodiment and the first sealing member 10X of the related art. A synthetic resin such as a urethane resin is used for each of the first sealing member 10 and the first sealing member 10X (hardness: hardness meter A90, tensile strength Mpa44.0, stretchability 500%, compression set 40%, compression permanent) Conditions for deformation test 8) (80 ° C - 70 h): manufactured by Japan Walka Industrial Co., Ltd.; product number R5590)). The first sealing member 10 is R = 2 mm, θ = 60°, and a = 0.6 mm. The first sealing member 10X is not provided with a curved surface, and the inclined surface 150 is R = 0 mm, θ = 45°, and a = 0.5 mm (so-called C-face = 0.5 mm). In the measurement, only the first sealing member was attached to either one, and the amount of external leakage of the oil from the cylinder 1 was measured. The result is shown in Fig. 11. It has been confirmed that the first sealing member 10 of the present embodiment has a good sealing property as compared with the first sealing member 10X of the related art. (Embodiment) Figs. 12 and 13 show the structure of a modification of the first sealing member 10 of the present embodiment. Fig. 12 shows the shape of the first sealing member 10A in which "a" is made larger, and Fig. 13 shows the case where the first sealing member 10B in which "θ" is made larger. Further, in FIGS. 14 to 16B, as a specific example 1 to 3, the relationship between the contact width at the time of pressure load and the contact surface pressure is shown. The first sealing member 10 of the first embodiment has a shape of R=15, θ=80°, and a=0.3, and the first sealing member 10 of the second embodiment has a shape of R=2, θ=30°, and a=2. The first sealing member 10 of the third embodiment has a shape of R = 0.5, θ = 30°, and a = 2. In each of the graphs A, P1 to P10 indicate the distribution of the internal pressure, indicating that the internal pressure decreases from P1 toward P10. In the case of the first embodiment shown in Figs. 14A and 14B, since the peak surface pressure did not occur in the entire contact width and a good surface pressure was exhibited, it was confirmed that the sealing property was excellent. In the case of the second embodiment shown in Figs. 15A and 15B, compared with the above-described first embodiment, no peak surface pressure occurred in the entire contact width and a more favorable surface pressure was exhibited, so that it was confirmed that the sealing property was excellent. In the case of the third embodiment shown in Figs. 16A and 16B, since a slight peak surface pressure is generated in a region near the contact width of about 1 mm as compared with the first embodiment, it is not good as compared with the first embodiment. Compared with the related art shown in Figs. 10A and 10B, it was confirmed that the sealing property was good as a whole. According to the above embodiment, the curved surface 110 and the inclined surface 120 are provided in a region where the first side surface 101 and the third side surface 103 of the base portion 10h intersect, and the curved surface 110 is provided so as to be in contact with the first side surface and the inclined surface 120. The slope 120 is provided to intersect the third side surface 103. Thereby, the first sealing member of the present embodiment has a good sealing property. Further, the projection length "a" of the curved surface 110 and the inclined surface 120 toward the third side surface 103 is 0.3 mm or more and 2 mm or less, and the radius "R" of the curved surface 110 is set to 2 mm or more and 15 mm or less, and the inclined surface is formed. The inclination angle "θ" of the 120 with respect to the third side surface 103 is set to 30° to 80°, and a more preferable sealing property can be obtained. The embodiments and examples are described above, but it should be understood that the embodiments disclosed herein are illustrative and not restrictive. The scope of the present invention is intended to be embraced by the appended claims
1‧‧‧缸體
2‧‧‧桿
10‧‧‧第1密封構件
10A‧‧‧第1密封構件
10B‧‧‧第1密封構件
10G‧‧‧第1密封槽
10X‧‧‧第1密封構件
10b‧‧‧第1唇部
10c‧‧‧第2唇部
10h‧‧‧底座部
10r‧‧‧唇部
20‧‧‧第2密封構件
20G‧‧‧第2密封槽
101‧‧‧第1側面
102‧‧‧第2側面
103‧‧‧第3側面
110‧‧‧彎曲面
120‧‧‧斜面
150‧‧‧斜面
a‧‧‧彎曲面及斜面朝第3側面之投影長度
OL‧‧‧油
P1～P9‧‧‧區域
R‧‧‧彎曲面之半徑
θ‧‧‧斜面相對於第3側面之傾斜角度1‧‧‧Cylinder
2‧‧‧ pole
10‧‧‧1st sealing member
10A‧‧‧1st sealing member
10B‧‧‧1st sealing member
10G‧‧‧1st sealing groove
10X‧‧‧1st sealing member
10b‧‧‧1st lip
10c‧‧‧2nd lip
10h‧‧‧Base section
10r‧‧‧Lip
20‧‧‧2nd sealing member
20G‧‧‧2nd sealing groove
101‧‧‧1st side
102‧‧‧2nd side
103‧‧‧3rd side
110‧‧‧ curved surface
120‧‧‧Bevel
150‧‧‧Bevel
a‧‧‧The projected length of the curved surface and the inclined surface toward the third side
OL‧‧‧Oil
P1～P9‧‧‧ area
R‧‧‧The radius of the curved surface θ‧‧‧The angle of inclination of the slope relative to the third side
圖1係表示實施形態之油壓機器所採用之密封構造之剖視圖。 圖2係表示實施形態之第1密封構件之構造之立體圖。 圖3係圖2中之III線箭頭剖視圖。 圖4係表示實施形態之第1密封構件之密封狀態之局部放大模式圖。 圖5A係表示實施形態之安裝時之第1密封構件之密封壓狀態之圖。 圖5B係表示實施形態之安裝時之第1密封構件之接觸寬度與接觸面壓之關係之圖。 圖6A係表示實施形態之壓力負載時之第1密封構件之密封壓狀態之圖。 圖6B係表示實施形態之壓力負載時之第1密封構件之接觸寬度與接觸面壓之關係之圖。 圖7係表示關聯技術之第1密封構件之構造之剖視圖。 圖8係表示關聯技術之第1密封構件之密封狀態之局部放大模式圖。 圖9A係表示關聯技術之安裝時之第1密封構件之密封壓狀態之圖。 圖9B係表示關聯技術之安裝時之接觸寬度與接觸面壓之關係之圖。 圖10A係表示關聯技術之壓力負載時之第1密封構件之密封壓狀態之圖。 圖10B係表示關聯技術之壓力負載時之接觸寬度與接觸面壓之關係之圖。 圖11係表示實施形態及關聯技術之滑動距離及洩漏量之關係之圖。 圖12係表示實施形態之第1密封構件之變化例之剖視圖。 圖13係表示實施形態之第1密封構件之另一變化例之剖視圖。 圖14A係表示實施例1之壓力負載時(R=15、θ=80°、a=0.3)之密封壓狀態之圖。 圖14B係表示實施例1之壓力負載時之接觸寬度與接觸面壓之關係之圖。 圖15A係表示實施例2之壓力負載時之(R=2、θ=30°、a=2)之密封壓狀態之圖。 圖15B係表示實施例2之壓力負載時之接觸寬度與接觸面壓之關係之圖。 圖16A係表示實施例3之壓力負載時(R=0.5、θ=30°、a=2)之密封壓狀態之圖。 圖16B係表示實施例3之壓力負載時之接觸寬度與接觸面壓之關係之圖。Fig. 1 is a cross-sectional view showing a sealing structure used in a hydraulic machine according to an embodiment. Fig. 2 is a perspective view showing the structure of a first sealing member in the embodiment. Figure 3 is a cross-sectional view taken along line III of Figure 2; Fig. 4 is a partially enlarged schematic view showing a sealed state of the first sealing member in the embodiment. Fig. 5A is a view showing a state of a sealing pressure of a first sealing member at the time of mounting in the embodiment. Fig. 5B is a view showing the relationship between the contact width of the first sealing member and the contact surface pressure at the time of mounting in the embodiment. Fig. 6A is a view showing a state of a sealing pressure of a first sealing member in a pressure load according to an embodiment; Fig. 6B is a view showing the relationship between the contact width of the first sealing member and the contact surface pressure in the pressure load of the embodiment. Fig. 7 is a cross-sectional view showing the structure of a first sealing member of the related art. Fig. 8 is a partially enlarged schematic view showing a sealed state of a first sealing member of the related art. Fig. 9A is a view showing a state of a sealing pressure of a first sealing member at the time of attachment of the related art. Fig. 9B is a view showing the relationship between the contact width and the contact surface pressure at the time of mounting of the related art. Fig. 10A is a view showing a state of a sealing pressure of a first sealing member in a pressure load according to the related art. Fig. 10B is a view showing the relationship between the contact width and the contact surface pressure in the pressure load of the related art. Fig. 11 is a view showing the relationship between the sliding distance and the amount of leakage in the embodiment and the related art. Fig. 12 is a cross-sectional view showing a modification of the first sealing member of the embodiment. Fig. 13 is a cross-sectional view showing another modification of the first sealing member of the embodiment. Fig. 14A is a view showing a state of a sealing pressure at the time of pressure load (R = 15, θ = 80°, a = 0.3) in the first embodiment. Fig. 14B is a view showing the relationship between the contact width and the contact surface pressure in the pressure load of the first embodiment. Fig. 15A is a view showing a state of a sealing pressure (R = 2, θ = 30°, a = 2) at the time of pressure load in the second embodiment. Fig. 15B is a view showing the relationship between the contact width and the contact surface pressure in the pressure load of the second embodiment. Fig. 16A is a view showing a state of a sealing pressure in a pressure load (R = 0.5, θ = 30°, a = 2) in the third embodiment. Fig. 16B is a view showing the relationship between the contact width and the contact surface pressure in the pressure load of the third embodiment.
10‧‧‧第1密封構件 10‧‧‧1st sealing member
10b‧‧‧第1唇部 10b‧‧‧1st lip
10c‧‧‧第2唇部 10c‧‧‧2nd lip
10h‧‧‧底座部 10h‧‧‧Base section
10r‧‧‧底座部 10r‧‧‧Base Department
101‧‧‧第1側面 101‧‧‧1st side
102‧‧‧第2側面 102‧‧‧2nd side
103‧‧‧第3側面 103‧‧‧3rd side
110‧‧‧彎曲面 110‧‧‧ curved surface
120‧‧‧斜面 120‧‧‧Bevel
a‧‧‧彎曲面及斜面對第3側面之投影長度 a‧‧‧The projected length of the curved side and the oblique side facing the third side
R‧‧‧彎曲面之半徑 Radius of the R‧‧‧ curved surface
θ‧‧‧斜面相對於第3側面之傾斜角度 Angle of inclination of the θ‧‧‧ slope relative to the third side
Claims (2)
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP??2015-226690 | 2015-11-19 | ||
| JP2015226690A JP6655365B2 (en) | 2015-11-19 | 2015-11-19 | Seal member |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| TW201719060A true TW201719060A (en) | 2017-06-01 |
| TWI696775B TWI696775B (en) | 2020-06-21 |
Family
ID=58718096
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| TW105133027A TWI696775B (en) | 2015-11-19 | 2016-10-13 | Sealing member |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JP6655365B2 (en) |
| KR (1) | KR102439898B1 (en) |
| CN (1) | CN108291648B (en) |
| TW (1) | TWI696775B (en) |
| WO (1) | WO2017086044A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| TWI780178B (en) * | 2017-08-02 | 2022-10-11 | 日商華爾卡股份有限公司 | Metal gasket |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JP2024044407A (en) * | 2022-09-21 | 2024-04-02 | 株式会社東京精密 | Retract mechanism and dimension measuring device equipped with same |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2408777A1 (en) * | 1977-11-15 | 1979-06-08 | Dba | SEALING CUP FOR PRESSURE GENERATORS |
| US4687212A (en) * | 1986-12-16 | 1987-08-18 | Baraw Corporation | Seal assembly with stabilizing ribs |
| JPH11303863A (en) * | 1998-04-15 | 1999-11-02 | Nippon Seiko Kk | Shell type roller bearing |
| JP4699594B2 (en) * | 2000-10-10 | 2011-06-15 | カヤバ工業株式会社 | Fluid pressure packing |
| JP2005337440A (en) | 2004-05-28 | 2005-12-08 | Kayaba Ind Co Ltd | Sealing structure and sealing structure of hydraulic cylinder |
| EP1767838A4 (en) * | 2004-06-07 | 2007-10-10 | Freudenberg Carl Kg | Sealing system |
| US8840115B2 (en) * | 2007-03-09 | 2014-09-23 | Freudenberg-Nok General Partnership | Wide range temperature and pressure hydraulic cylinder sealing system |
| JP2008267449A (en) * | 2007-04-18 | 2008-11-06 | Nok Corp | Backup ring |
| JP2008309278A (en) * | 2007-06-15 | 2008-12-25 | Nsk Ltd | Bearing unit |
| CN201461935U (en) * | 2009-07-30 | 2010-05-12 | 南方天合底盘系统有限公司 | High-intensity sealing leather collar |
| CN201606486U (en) * | 2009-12-29 | 2010-10-13 | 深圳市富洋密封件有限公司 | Y-shaped thermoplastic polyurethane hydraulic sealing ring structure |
| CN201836388U (en) * | 2010-11-04 | 2011-05-18 | 上海麦特密封件有限公司 | Y-shaped seal ring |
| CN101994837B (en) * | 2010-11-15 | 2013-04-03 | 徐州工程学院 | Anti-friction sealing ring |
| CN103123001A (en) * | 2011-11-19 | 2013-05-29 | 李虎林 | Combined seal for shaft |
| CN102563080A (en) * | 2012-01-05 | 2012-07-11 | 上海大学 | Y-shaped rubber dynamic sealing ring with long and short lips for unilateral sealing and sectional vulcanization process for sealing ring |
| JP2014214769A (en) | 2013-04-23 | 2014-11-17 | 日本バルカー工業株式会社 | Seal structure |
| CN103994228A (en) * | 2014-05-13 | 2014-08-20 | 嘉兴新中南汽车零部件有限公司 | Angular lip-shaped rubber sealing ring |
-
2015
- 2015-11-19 JP JP2015226690A patent/JP6655365B2/en active Active
-
2016
- 2016-10-05 CN CN201680067739.1A patent/CN108291648B/en active Active
- 2016-10-05 WO PCT/JP2016/079587 patent/WO2017086044A1/en active Application Filing
- 2016-10-05 KR KR1020187016112A patent/KR102439898B1/en active IP Right Grant
- 2016-10-13 TW TW105133027A patent/TWI696775B/en active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| TWI780178B (en) * | 2017-08-02 | 2022-10-11 | 日商華爾卡股份有限公司 | Metal gasket |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2017086044A1 (en) | 2017-05-26 |
| CN108291648B (en) | 2020-09-22 |
| TWI696775B (en) | 2020-06-21 |
| KR102439898B1 (en) | 2022-09-02 |
| CN108291648A (en) | 2018-07-17 |
| JP6655365B2 (en) | 2020-02-26 |
| JP2017096332A (en) | 2017-06-01 |
| KR20180081766A (en) | 2018-07-17 |
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