WO2017086044A1 - Seal member - Google Patents

Seal member Download PDF

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Publication number
WO2017086044A1
WO2017086044A1 PCT/JP2016/079587 JP2016079587W WO2017086044A1 WO 2017086044 A1 WO2017086044 A1 WO 2017086044A1 JP 2016079587 W JP2016079587 W JP 2016079587W WO 2017086044 A1 WO2017086044 A1 WO 2017086044A1
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WO
WIPO (PCT)
Prior art keywords
seal member
rod
pressure
seal
lip portion
Prior art date
Application number
PCT/JP2016/079587
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French (fr)
Japanese (ja)
Inventor
純一 山下
謙一 高橋
彰 上田
Original Assignee
日本バルカー工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Application filed by 日本バルカー工業株式会社 filed Critical 日本バルカー工業株式会社
Priority to CN201680067739.1A priority Critical patent/CN108291648B/en
Priority to KR1020187016112A priority patent/KR102439898B1/en
Publication of WO2017086044A1 publication Critical patent/WO2017086044A1/en

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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
    • 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

Definitions

  • the present invention relates to a seal structure, and more particularly to a structure of a seal member used in a sliding gap between a rod (piston rod) and a cylinder in a hydraulic / pneumatic device or the like.
  • the sealing member is improved every day.
  • the present invention has been made to solve the above-described problems, and it is an object of the present invention to provide a sealing member that can further enhance the sealing performance of the sealing structure.
  • the high pressure side and the low pressure side are partitioned in the sliding gap between the cylinder and the rod in the hydraulic / pneumatic equipment, and the sealing groove is provided annularly along the circumferential direction of the outer peripheral surface of the rod Is a sealing member that closes the sliding gap between the cylinder and the rod, and has the following configuration.
  • a curved surface and an inclined surface are provided in a region where the first side surface and the third side surface of the heel portion intersect, and the curved surface is provided so as to be in contact with the first side surface and the inclined surface, The slope is provided so as to intersect with the third side surface.
  • the projection length of the curved surface and the slope on the third side surface is 0.3 mm or more and 2 mm or less, the radius of the curved surface is 2 mm or more and 15 mm or less, The inclination angle with respect to the third side surface is 30 ° to 80 °.
  • FIG. 3 is a cross-sectional view taken along line III in FIG. 2.
  • FIG. It is a figure which shows the relationship between the contact width at the time of the pressure load of Example 2, and a contact surface pressure.
  • FIG. It is a figure which shows the relationship between the contact width at the time of the pressure load of Example 3, and a contact surface pressure.
  • FIG. 1 is a cross-sectional view showing a seal structure employed in the hydraulic cylinder in the embodiment.
  • a cylinder 1 and a rod (piston rod) 2 are shown by broken lines for convenience of explanation.
  • the seal structure shown in FIG. 1 is deformed with the pressure contact with the rod 2 and the reciprocating motion of the rod 2 (vertical direction in FIG. 1).
  • pressure is applied to the seal structure. The state is not shown.
  • An annular first seal groove 10G is provided along the circumferential direction of the outer peripheral surface of the rod 2.
  • the first seal groove 10 ⁇ / b> G accommodates a first seal member 10 that closes the sliding gap between the cylinder 1 and the rod 2.
  • the second seal groove 20G is provided in an annular shape along the circumferential direction of the outer peripheral surface of the rod 2 and on the high pressure side of the first seal groove 10G.
  • a high-pressure hydraulic chamber is provided on the upper side.
  • a second seal member 20 that closes a sliding gap between the cylinder 1 and the rod 2 is accommodated in the second seal groove 20G.
  • FIG. 2 is a perspective view showing the structure of the first seal member 10
  • FIG. 3 is a cross-sectional view taken along line III in FIG.
  • the first seal member 10 has an annular shape as a whole, and is integrally formed of synthetic resin such as urethane resin, natural rubber, synthetic rubber, or fluororubber.
  • the first seal member 10 has a substantially U-shaped cross section having an open side on the high pressure side.
  • the heel portion 10h includes a heel portion 10h located on the low pressure side and a lip portion 10r located on the high pressure side in the sectional view shown in FIG.
  • the heel portion 10h includes a first side face 101 located on the rod 2 side, a second side face 102 located opposite to the first side face 101, and a third side face 103 located 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 form a substantially U shape.
  • a curved surface 110 and an inclined surface 120 are provided in a region where the first side surface 101 and the third side surface 103 of the heel portion 10h intersect, which is the low pressure side on the rod 2 side when viewed from the heel portion 10h. .
  • the curved surface 110 is provided so as to be in contact with the first side surface 101 and the inclined surface 120, and the inclined surface 120 is provided so as to intersect with the third side surface 103.
  • the projected length of the curved surface 110 and the inclined surface 120 onto 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 “ ⁇ ”.
  • the projection length “a” is 0.3 mm or more and 2 mm or less
  • the radius “R” of the curved surface 110 is 2 mm or more and 15 mm or less.
  • the inclination angle “ ⁇ ” of the inclined surface 120 with respect to the third side surface 103 is preferably 30 ° to 80 °. This point will be described in an embodiment described later.
  • FIG. 4 is a partially enlarged schematic diagram showing a sealing state in the “pulling step”
  • FIG. 5A is a diagram showing a sealing pressure state of the first seal member 10 at the time of mounting
  • FIG. 5B is a first sealing member at the time of mounting
  • FIG. 6A is a diagram showing a seal pressure state of the first seal member 10 when pressure is applied
  • FIG. 6B is a diagram showing a relationship between the contact width and the contact surface pressure of FIG. It is a figure which shows the relationship between a contact width and a contact surface pressure.
  • P1 to P10 indicate internal pressure distributions, indicating that the internal pressure decreases from P1 to P10.
  • the first lip portion 10 b has a form that expands toward the rod 2 side, and the region where the first side surface 101 and the third side surface 103 of the heel portion 10 h of the first seal member 10 intersect with each other. Further, by providing the curved surface 110 and the inclined surface 120, the heel portion 10h is in a non-contact state with the rod 2 even at the time of wearing, and the oil OL can be easily introduced into the cylinder 1 during the “pulling process”. It is possible to return to
  • the curved surface 110 and the inclined surface 120 are provided in the region R1 in the region where the first side surface 101 and the third side surface 103 of the heel portion 10h intersect. Even if the contact width moves, the contact surface pressure can be kept smooth without generating the peak surface pressure. As a result, it is possible to reduce the resistance of oil to the inside of the cylinder 1 and to improve the oil suction characteristic by the seal structure using the first seal member 10 and to further improve the sealing performance.
  • FIG. 7 shows a cross-sectional view of the first seal member 10X in the related art.
  • FIG. 3 is a view corresponding to a cross section taken along line III-III in FIG. 2.
  • the shapes of the first lip portion 10b and the second lip portion 10c of the lip portion 10r are the same as those of the first seal member 10 of the present embodiment.
  • the slope 150 is provided in the region where the first side surface 101 and the third side surface 103 intersect, and no curved surface is provided.
  • FIG. 8 is a partially enlarged schematic view showing a seal state in the “pulling step”
  • FIG. 9A is a view showing a seal pressure state of the first seal member 10X at the time of mounting
  • FIG. 9B is a first seal member at the time of mounting.
  • 10A is a diagram showing the relationship between the contact width of 10X and the contact surface pressure
  • FIG. 10A is a diagram showing the seal pressure state of the first seal member 10X at the time of pressure load
  • FIG. 10B is the diagram of the first seal member 10X at the time of pressure load. It is a figure which shows the relationship between a contact width and a contact surface pressure.
  • P1 to P10 indicate the distribution of internal pressure, and the internal pressure decreases from P1 to P10.
  • the heel portion 10h of the first seal member 10X is not provided with a curved surface, and only the inclined surface 150 is provided.
  • the heel portion 10h comes into contact with the rod 2, and a peak surface pressure is formed in the region R3 as shown in FIG. 9B.
  • a peak surface pressure is present in the region R4.
  • the oil suction characteristic was poor, which was one factor in causing oil leakage.
  • FIG. 11 explains the amount of leakage between the first seal member 10 of the embodiment and the first seal member 10X of the related art.
  • FIG. 11 is a diagram illustrating the relationship between the sliding distance and the leakage amount between the first seal member 10 of the embodiment and the first seal member 10X of the related art.
  • Both the first seal member 10 and the first seal member 10X are synthetic resins such as urethane resin (hardness durometer A90, tensile strength Mpa 44.0, elongation 500%, compression set 40%, compression set test conditions. 8) (80 ° C.-70 h): Nippon Valqua Industries, Ltd., product number R5590)).
  • urethane resin hardness durometer A90, tensile strength Mpa 44.0, elongation 500%, compression set 40%, compression set test conditions. 8 (80 ° C.-70 h): Nippon Valqua Industries, Ltd., product number R5590)).
  • Example 12 and 13 show a structure of a modified example of the first seal member 10 in the present embodiment.
  • FIG. 12 shows the shape of the first seal member 10A having a relatively large “a”
  • FIG. 13 shows the case of the first seal member 10B having a relatively large “ ⁇ ”.
  • FIGS. 14A to 16B show the relationship between the contact width and the contact surface pressure at the time of pressure loading, as specific examples 1 to 3.
  • A 2
  • P1 to P10 indicate the distribution of the internal pressure, and the internal pressure decreases from P1 to P10.
  • Example 1 shown in FIG. 14A and FIG. 14B, no peak surface pressure is generated in the entire contact width, and good surface pressure is shown. I was able to confirm.
  • Example 2 shown in FIG. 15A and FIG. 15B compared to Example 1 above, no peak surface pressure is generated in the entire contact width, and a better surface pressure is shown. It was confirmed that it had excellent sealing performance.
  • Example 3 compared to Example 1 above, a minute peak surface pressure is generated in a region where the contact width is about 1 mm. Although it is not good at all, it is better than the related technology shown in FIG. 10A and FIG. 10B, so that it has been confirmed that it has a good sealing performance as a whole.
  • 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 heel portion 10h intersect, and the curved surface 110 includes the first side surface and the inclined surface 120.
  • the inclined surface 120 is provided so as to intersect the third side surface 103.
  • the projection length “a” of the curved surface 110 and the inclined surface 120 onto the third side surface 103 is set to 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.
  • the inclination angle “ ⁇ ” with respect to the third side surface 103 is set to 30 ° to 80 °, it is possible to obtain more preferable sealing performance.

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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

This seal member (10) is configured so that a curved surface (110) and a sloped surface (120) will be provided in the region where a first side surface (101) of a heel section (10h) and a third side surface (103) thereof intersect, the curved surface (110) being provided so as to be in contact with the first side surface (101) and the sloped surface (120), the sloped surface (120) being provided so as to intersect the third side surface (103).

Description

シール部材Seal member
　本発明は、シール構造に関し、特に、油空圧機器などにおけるロッド（ピストンロッド）とシリンダとの摺動隙間に用いられるシール部材の構造に関する。 The present invention relates to a seal structure, and more particularly to a structure of a seal member used in a sliding gap between a rod (piston rod) and a cylinder in a hydraulic / pneumatic device or the like.
　たとえば、油圧機器におけるシリンダとロッド（ピストンロッド）との摺動隙間には、油室に導入される作動油の漏れ（高圧側から低圧側への作動油の漏れ）を防止するとともに、ロッドの往復運動を円滑に実現するために、シリンダに設けられたシール溝にシール部材が嵌め入れられるシール構造が採用されている。このようなシール構造は、特開２００５－３３７４４０号公報（特許文献１）、特開２０１４－２１４７６９（特許文献２）等に開示されている。 For example, in a sliding gap between a cylinder and a rod (piston rod) in hydraulic equipment, hydraulic oil introduced into the oil chamber is prevented from leaking (leakage of hydraulic oil from the high pressure side to the low pressure side) and the rod In order to smoothly realize the reciprocating motion, a seal structure in which a seal member is fitted into a seal groove provided in the cylinder is employed. Such a sealing structure is disclosed in Japanese Patent Application Laid-Open No. 2005-337440 (Patent Document 1), Japanese Patent Application Laid-Open No. 2014-214769 (Patent Document 2), and the like.
特開２００５－３３７４４０号公報JP 2005-337440 A 特開２０１４－２１４７６９号公報JP 2014-214769 A
　近年、シール構造によるシール性能をより高めるため、シール部材の改善が日々行なわれている。 In recent years, in order to further improve the sealing performance by the sealing structure, the sealing member is improved every day.
　この発明は、上記課題を解決するためになされたものであり、シール構造によるシール性能をより高めることを可能とする、シール部材を提供することにある。 The present invention has been made to solve the above-described problems, and it is an object of the present invention to provide a sealing member that can further enhance the sealing performance of the sealing structure.
　この発明に基づいたシール部材においては、油空圧機器におけるシリンダとロッドとの摺動隙間において高圧側と低圧側と仕切り、上記ロッドの外周面の周方向に沿って環状に設けられたシール溝の内部に収容されて、上記シリンダと上記ロッドとの摺動隙間を塞ぐシール部材であって、以下の構成を備える。 In the sealing member according to the present invention, the high pressure side and the low pressure side are partitioned in the sliding gap between the cylinder and the rod in the hydraulic / pneumatic equipment, and the sealing groove is provided annularly along the circumferential direction of the outer peripheral surface of the rod Is a sealing member that closes the sliding gap between the cylinder and the rod, and has the following configuration.
　低圧側に位置するヒール部と、高圧側に位置するリップ部と、を含み、上記ヒール部は、上記ロッド側に位置する第１側面、上記第１側面に対向位置する第２側面、および、高圧側に位置する第３側面を有し、上記リップ部は、上記ロッド側に向けて拡がる第１リップ部、および、上記ロッド側とは反対側に向けて拡がる第２リップ部を有し、上記ヒール部の第１側面および上記第３側面が交わる領域には、湾曲面、および、斜面が設けられ、上記湾曲面は、上記第１側面および上記斜面に対して接するように設けられ、上記斜面は上記第３側面と交わるように設けられている。 A heel portion located on the low pressure side; and a lip portion located on the high pressure side, wherein the heel portion is a first side surface located on the rod side, a second side surface opposed to the first side surface, and A third side surface located on the high-pressure side, the lip portion has a first lip portion that expands toward the rod side, and a second lip portion that expands toward the side opposite to the rod side; A curved surface and an inclined surface are provided in a region where the first side surface and the third side surface of the heel portion intersect, and the curved surface is provided so as to be in contact with the first side surface and the inclined surface, The slope is provided so as to intersect with the third side surface.
　他の形態においては、上記湾曲面および上記斜面の上記第３側面への投影長さは、０．３ｍｍ以上２ｍｍ以下であり、上記湾曲面の半径は、２ｍｍ以上１５ｍｍ以下であり、上記斜面の上記第３側面に対する傾斜角度は、３０°から８０°である。 In another embodiment, the projection length of the curved surface and the slope on the third side surface is 0.3 mm or more and 2 mm or less, the radius of the curved surface is 2 mm or more and 15 mm or less, The inclination angle with respect to the third side surface is 30 ° to 80 °.
　本発明によれば、シール構造によるシール性能をより高めることを可能とする、シール構造を提供することが可能になる。 According to the present invention, it is possible to provide a seal structure that can further enhance the sealing performance of the seal structure.
実施の形態の油圧機器に採用されるシール構造を示す断面図である。It is sectional drawing which shows the seal structure employ | adopted as the hydraulic equipment of embodiment. 実施の形態の第１シール部材の構造を示す斜視図である。It is a perspective view which shows the structure of the 1st seal member of embodiment. 図２中のＩＩＩ線矢視断面図である。FIG. 3 is a cross-sectional view taken along line III in FIG. 2. 実施の形態における第１シール部材のシール状態を示す部分拡大模式図である。It is a partial expansion schematic diagram which shows the sealing state of the 1st seal member in embodiment. 実施の形態の装着時における第１シール部材のシール圧状態を示す図である。It is a figure which shows the seal pressure state of the 1st seal member at the time of mounting | wearing of embodiment. 実施の形態の装着時における第１シール部材の接触幅と接触面圧との関係を示す図である。It is a figure which shows the relationship between the contact width of a 1st seal member at the time of mounting | wearing of embodiment, and a contact surface pressure. 実施の形態の圧力負荷時における第１シール部材のシール圧状態を示す図である。It is a figure which shows the seal pressure state of the 1st seal member at the time of the pressure load of embodiment. 実施の形態の圧力負荷時における第１シール部材の接触幅と接触面圧との関係を示す図である。It is a figure which shows the relationship between the contact width of a 1st seal member at the time of the pressure load of embodiment, and a contact surface pressure. 関連技術における第１シール部材の構造を示す断面図である。It is sectional drawing which shows the structure of the 1st seal member in related technology. 関連技術における第１シール部材のシール状態を示す部分拡大模式図である。It is a partial expansion schematic diagram which shows the sealing state of the 1st seal member in related technology. 関連技術の装着時における第１シール部材におけるシール圧状態を示す図である。It is a figure which shows the seal pressure state in the 1st seal member at the time of mounting | wearing of related technology. 関連技術の装着時における接触幅と接触面圧との関係を示す図である。It is a figure which shows the relationship between the contact width at the time of mounting | wearing of related technology, and contact surface pressure. 関連技術の圧力負荷時における第１シール部材におけるシール圧状態を示す図である。It is a figure which shows the seal pressure state in the 1st seal member at the time of the pressure load of related technology. 関連技術の圧力負荷時における接触幅と接触面圧との関係を示す図である。It is a figure which shows the relationship between the contact width at the time of the pressure load of related technology, and a contact surface pressure. 実施の形態および関連技術の摺動距離および漏れ量の関係を示す図である。It is a figure which shows the relationship of sliding distance and leakage amount of embodiment and related technology. 実施の形態の第１シール部材の変形例を示す断面図である。It is sectional drawing which shows the modification of the 1st seal member of embodiment. 実施の形態の第１シール部材の他の変形例を示す断面図である。It is sectional drawing which shows the other modification of the 1st seal member of embodiment. 実施例１の圧力負荷時における、（Ｒ＝１５、θ＝８０°、ａ＝０．３）のシール圧状態を示す図である。It is a figure which shows the seal pressure state of (R = 15, (theta) = 80 degrees, a = 0.3) at the time of the pressure load of Example 1. FIG. 実施例１の圧力負荷時における接触幅と接触面圧との関係を示す図である。It is a figure which shows the relationship between the contact width at the time of the pressure load of Example 1, and a contact surface pressure. 実施例２の圧力負荷時における、（Ｒ＝２、θ＝３０°、ａ＝２）のシール圧状態を示す図である。It is a figure which shows the seal pressure state of (R = 2, (theta) = 30 degrees, a = 2) at the time of the pressure load of Example 2. FIG. 実施例２の圧力負荷時における接触幅と接触面圧との関係を示す図である。It is a figure which shows the relationship between the contact width at the time of the pressure load of Example 2, and a contact surface pressure. 実施例３の圧力負荷時における、（Ｒ＝０．５、θ＝３０°、ａ＝２）のシール圧状態を示す図である。It is a figure which shows the seal pressure state of (R = 0.5, (theta) = 30 degrees, a = 2) at the time of the pressure load of Example 3. FIG. 実施例３の圧力負荷時における接触幅と接触面圧との関係を示す図である。It is a figure which shows the relationship between the contact width at the time of the pressure load of Example 3, and a contact surface pressure.
　本発明に基づいた実施の形態におけるシール部材およびそのシール部材を用いたシール構造について、以下、図を参照しながら説明する。以下に説明する実施の形態において、個数、量などに言及する場合、特に記載がある場合を除き、本発明の範囲は必ずしもその個数、量などに限定されない。同一の部品、相当部品に対しては、同一の参照番号を付し、重複する説明は繰り返さない場合がある。以下では、油空圧機器の一例として油圧シリンダを挙げているが、油圧シリンダに限定されず、広く油空圧機器に適用することが可能である。 The seal member and the seal structure using the seal member in the embodiment based on the present invention will be described below with reference to the drawings. In the embodiments described below, when referring to the number, amount, and the like, the scope of the present invention is not necessarily limited to the number, amount, and the like unless otherwise specified. The same parts and corresponding parts are denoted by the same reference numerals, and redundant description may not be repeated. In the following, a hydraulic cylinder is cited as an example of a hydraulic / pneumatic device, but the present invention is not limited to a hydraulic cylinder, and can be widely applied to a hydraulic / pneumatic device.
　（シール構造）
　図１を参照して、本実施の形態におけるシール構造について説明する。図１は、実施の形態における油圧シリンダに採用されるシール構造を示す断面図である。図１中において、シリンダ１およびロッド（ピストンロッド）２は、説明の便宜上破線で図示している。図１に示すシール構造は、ロッド２との圧接およびロッド２の往復運動（図１中の上下方向）にともなって変形するが、シール構造を明確に理解するため、シール構造には圧力が加わっていない状態を図示している。 (Seal structure)
With reference to FIG. 1, the seal structure in this Embodiment is demonstrated. FIG. 1 is a cross-sectional view showing a seal structure employed in the hydraulic cylinder in the embodiment. In FIG. 1, a cylinder 1 and a rod (piston rod) 2 are shown by broken lines for convenience of explanation. The seal structure shown in FIG. 1 is deformed with the pressure contact with the rod 2 and the reciprocating motion of the rod 2 (vertical direction in FIG. 1). However, in order to clearly understand the seal structure, pressure is applied to the seal structure. The state is not shown.
　ロッド２の外周面の周方向に沿って環状の第１シール溝１０Ｇが設けられている。この第１シール溝１０Ｇには、シリンダ１とロッド２との摺動隙間を塞ぐ第１シール部材１０が収容されている。 An annular first seal groove 10G is provided along the circumferential direction of the outer peripheral surface of the rod 2. The first seal groove 10 </ b> G accommodates a first seal member 10 that closes the sliding gap between the cylinder 1 and the rod 2.
　ロッド２の外周面の周方向に沿って環状に設けられ、第１シール溝１０Ｇよりも高圧側に、第２シール溝２０Ｇが設けられている。図示において、上方側に高圧の油圧室が設けられている。第２シール溝２０Ｇには、シリンダ１とロッド２との摺動隙間を塞ぐ第２シール部材２０が収容されている。 The second seal groove 20G is provided in an annular shape along the circumferential direction of the outer peripheral surface of the rod 2 and on the high pressure side of the first seal groove 10G. In the drawing, a high-pressure hydraulic chamber is provided on the upper side. A second seal member 20 that closes a sliding gap between the cylinder 1 and the rod 2 is accommodated in the second seal groove 20G.
　（第１シール部材１０）
　図２および図３を参照して、本実施の形態における第１シール部材１０について説明する。図２は、第１シール部材１０の構造を示す斜視図、図３は、図２中のＩＩＩ線矢視断面図である。 (First seal member 10)
With reference to FIG. 2 and FIG. 3, the 1st seal member 10 in this Embodiment is demonstrated. 2 is a perspective view showing the structure of the first seal member 10, and FIG. 3 is a cross-sectional view taken along line III in FIG.
　第１シール部材１０は、全体として環状の形態を有し、ウレタン樹脂等の合成樹脂、天然ゴム、合成ゴム、または、フッ素ゴムにより一体成型されている。第１シール部材１０は、高圧側に開放側を有する断面形状が略Ｕ字形状を有している。 The first seal member 10 has an annular shape as a whole, and is integrally formed of synthetic resin such as urethane resin, natural rubber, synthetic rubber, or fluororubber. The first seal member 10 has a substantially U-shaped cross section having an open side on the high pressure side.
　より具体的には、図３に示す断面視において、低圧側に位置するヒール部１０ｈと、高圧側に位置するリップ部１０ｒとを備えている。ヒール部１０ｈは、ロッド２側に位置する第１側面１０１、第１側面１０１に対向位置する第２側面１０２、および、高圧側に位置する第３側面１０３を含む。 More specifically, it includes a heel portion 10h located on the low pressure side and a lip portion 10r located on the high pressure side in the sectional view shown in FIG. The heel portion 10h includes a first side face 101 located on the rod 2 side, a second side face 102 located opposite to the first side face 101, and a third side face 103 located on the high pressure side.
　リップ部１０ｒは、ロッド２側に向けて拡がる第１リップ部１０ｂ、および、ロッド２側とは反対側に向けて拡がる第２リップ部１０ｃを含む。第１リップ部１０ｂおよび第２リップ部１０ｃにより略Ｕ字形状を形成している。 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 form a substantially U shape.
　さらに、ヒール部１０ｈから見てロッド２側の低圧側である、ヒール部１０ｈの第１側面１０１および第３側面１０３が交わる領域には、湾曲面１１０、および、斜面１２０とが設けられている。湾曲面１１０は、第１側面１０１および斜面１２０に対して接するように設けられ、斜面１２０は第３側面１０３と交わるように設けられている。 Further, a curved surface 110 and an inclined surface 120 are provided in a region where the first side surface 101 and the third side surface 103 of the heel portion 10h intersect, which is the low pressure side on the rod 2 side when viewed from the heel portion 10h. . The curved surface 110 is provided so as to be in contact with the first side surface 101 and the inclined surface 120, and the inclined surface 120 is provided so as to intersect with the third side surface 103.
　湾曲面１１０および斜面１２０の第３側面１０３への投影長さを、「ａ」とし、湾曲面１１０の半径を「Ｒ」とし、斜面１２０の第３側面１０３に対する傾斜角度を「θ」とすると、第１シール部材１０におけるロッド２に対するより良好な密閉性を得るには、投影長さ「ａ」は、０．３ｍｍ以上２ｍｍ以下、湾曲面１１０の半径「Ｒ」は、２ｍｍ以上１５ｍｍ以下、斜面１２０の第３側面１０３に対する傾斜角度「θ」は、３０°から８０°であると良い。この点については、後述の実施例で説明する。 The projected length of the curved surface 110 and the inclined surface 120 onto 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”. In order to obtain better sealing performance with respect to the rod 2 in the first seal member 10, 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 and 15 mm or less. The inclination angle “θ” of the inclined surface 120 with respect to the third side surface 103 is preferably 30 ° to 80 °. This point will be described in an embodiment described later.
　再び、図１を参照して、第１シール部材１０から見た場合には、ロッド２が低圧側から高圧側に向けて移動する場合は、「引き工程」と呼ばれ、ロッド２が高圧側から低圧側に向けて移動する場合は、「押し工程」と呼ばれる。 Referring again to FIG. 1, when viewed from the first seal member 10, when the rod 2 moves from the low pressure side toward the high pressure side, this is called a “pulling step”, and the rod 2 is moved to the high pressure side. When moving from a low pressure side to a low pressure side, this is called a “pushing process”.
　図４から図６を参照して、第１シール部材１０のシール状態について説明する。図４は、「引き工程」における、シール状態を示す部分拡大模式図、図５Ａは、装着時における第１シール部材１０のシール圧状態を示す図、図５Ｂは、装着時における第１シール部材１０の接触幅と接触面圧との関係を示す図、図６Ａは、圧力負荷時における第１シール部材１０のシール圧状態を示す図、図６Ｂは、圧力負荷時における第１シール部材１０の接触幅と接触面圧との関係を示す図である。なお、図５Ａ、図６Ａ中においてＰ１～Ｐ１０は内圧の分布を示し、Ｐ１からＰ１０に向けて内圧が小さくなることを示している。 The sealing state of the first seal member 10 will be described with reference to FIGS. FIG. 4 is a partially enlarged schematic diagram showing a sealing state in the “pulling step”, FIG. 5A is a diagram showing a sealing pressure state of the first seal member 10 at the time of mounting, and FIG. 5B is a first sealing member at the time of mounting. FIG. 6A is a diagram showing a seal pressure state of the first seal member 10 when pressure is applied, and FIG. 6B is a diagram showing a relationship between the contact width and the contact surface pressure of FIG. It is a figure which shows the relationship between a contact width and a contact surface pressure. In FIG. 5A and FIG. 6A, P1 to P10 indicate internal pressure distributions, indicating that the internal pressure decreases from P1 to P10.
　図４および図５Ａに示すように、第１リップ部１０ｂがロッド２側に向けて拡がる形態を有するとともに、第１シール部材１０のヒール部１０ｈの第１側面１０１および第３側面１０３が交わる領域に、湾曲面１１０、および、斜面１２０とを設けることで、装着時においてもヒール部１０ｈは、ロッド２に対して非接触状態となり、「引き工程」時には、油ＯＬをシリンダ１の内部に容易に戻すことを可能とする。 As shown in FIG. 4 and FIG. 5A, the first lip portion 10 b has a form that expands toward the rod 2 side, and the region where the first side surface 101 and the third side surface 103 of the heel portion 10 h of the first seal member 10 intersect with each other. Further, by providing the curved surface 110 and the inclined surface 120, the heel portion 10h is in a non-contact state with the rod 2 even at the time of wearing, and the oil OL can be easily introduced into the cylinder 1 during the “pulling process”. It is possible to return to
　図５Ｂの装着時における第１シール部材１０の接触幅と接触面圧との関係を示す図からも明らかなように、ヒール部１０ｈの第１側面１０１および第３側面１０３が交わる領域においては、ロッド２に接触しないことから領域Ｒ１においてピーク面圧は発生していない。一方、第１リップ部１０ｂと第２リップ部１０ｃとは、第１シール溝１０Ｇとロッド２とにより挟み込まれ大きく変形することから、その反力に基づき、領域Ｐ２（（Ａ）中のＰ９で示す領域）において接触によるピーク面圧が発生している。 As is apparent from the diagram showing the relationship between the contact width of the first seal member 10 and the contact surface pressure during the mounting of FIG. 5B, in the region where the first side surface 101 and the third side surface 103 of the heel portion 10h intersect, Since it does not contact the rod 2, 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 sandwiched between the first seal groove 10G and the rod 2 and greatly deformed, based on the reaction force, the region P2 (P9 in (A)) In the region shown), the peak surface pressure due to contact is generated.
　次に、図６Ａおよび図６Ｂにおける圧力負荷時においても、ヒール部１０ｈの第１側面１０１および第３側面１０３が交わる領域において、湾曲面１１０、および、斜面１２０とを設けることで、領域Ｒ１にピーク面圧が発生することなく、接触幅が移動しても接触面圧は滑らかな状態を保つことを可能としている。その結果、シリンダ１内部への油を抵抗が少なく戻すことが可能となり、第１シール部材１０を用いたシール構造により油の吸い込み特性が向上しシール性能をより高めることを可能とする。 Next, even during the pressure load in FIGS. 6A and 6B, the curved surface 110 and the inclined surface 120 are provided in the region R1 in the region where the first side surface 101 and the third side surface 103 of the heel portion 10h intersect. Even if the contact width moves, the contact surface pressure can be kept smooth without generating the peak surface pressure. As a result, it is possible to reduce the resistance of oil to the inside of the cylinder 1 and to improve the oil suction characteristic by the seal structure using the first seal member 10 and to further improve the sealing performance.
　一方、図７に、関連技術における第１シール部材１０Ｘの断面図を示す。図２中のＩＩＩ－ＩＩＩ線矢視断面に相当する図である。リップ部１０ｒの第１リップ部１０ｂおよび第２リップ部１０ｃの形状は、本実施の形態の第１シール部材１０と同じである。この第１シール部材１０Ｘは、第１側面１０１および第３側面１０３が交わる領域には、斜面１５０のみが設けられ、湾曲面は設けられていない。 On the other hand, FIG. 7 shows a cross-sectional view of the first seal member 10X in the related art. FIG. 3 is a view corresponding to a cross section taken along line III-III in FIG. 2. The shapes of the first lip portion 10b and the second lip portion 10c of the lip portion 10r are the same as those of the first seal member 10 of the present embodiment. In the first seal member 10X, only the slope 150 is provided in the region where the first side surface 101 and the third side surface 103 intersect, and no curved surface is provided.
　図８から図１０Ｂを参照して、関連技術の第１シール部材１０Ｘのシール状態について説明する。図８は、「引き工程」における、シール状態を示す部分拡大模式図、図９Ａは、装着時における第１シール部材１０Ｘのシール圧状態を示す図、図９Ｂは、装着時における第１シール部材１０Ｘの接触幅と接触面圧との関係を示す図、図１０Ａは、圧力負荷時における第１シール部材１０Ｘのシール圧状態を示す図、図１０Ｂは、圧力負荷時における第１シール部材１０Ｘの接触幅と接触面圧との関係を示す図である。なお、図９Ａ、図１０Ａ中においてＰ１～Ｐ１０は内圧の分布を示し、Ｐ１からＰ１０に向けて内圧が小さくなることを示している。 8 to 10B, the seal state of the related art first seal member 10X will be described. FIG. 8 is a partially enlarged schematic view showing a seal state in the “pulling step”, FIG. 9A is a view showing a seal pressure state of the first seal member 10X at the time of mounting, and FIG. 9B is a first seal member at the time of mounting. 10A is a diagram showing the relationship between the contact width of 10X and the contact surface pressure, FIG. 10A is a diagram showing the seal pressure state of the first seal member 10X at the time of pressure load, and FIG. 10B is the diagram of the first seal member 10X at the time of pressure load. It is a figure which shows the relationship between a contact width and a contact surface pressure. In FIGS. 9A and 10A, P1 to P10 indicate the distribution of internal pressure, and the internal pressure decreases from P1 to P10.
　図８および図９Ａに示すように、第１シール部材１０Ｘは、第１シール部材１０Ｘのヒール部１０ｈには、湾曲面は設けられておらず、斜面１５０のみが設けられいてる。その結果、装着時において、ヒール部１０ｈは、ロッド２に対して接触状態となり、図９Ｂに示すように領域Ｒ３にピーク面圧が形成される。また、図１０Ａおよび図１０Ｂにおける圧力負荷時においても、ヒール部１０ｈの第１側面１０１および第３側面１０３が交わる領域においては、斜面１５０のみであることから、領域Ｒ４においてさらに大きなピーク面圧が発生する。その結果、引き工程時において、油の吸い込み特性が悪く油漏れの原因の一要素となっていた。 As shown in FIGS. 8 and 9A, in the first seal member 10X, the heel portion 10h of the first seal member 10X is not provided with a curved surface, and only the inclined surface 150 is provided. As a result, at the time of mounting, the heel portion 10h comes into contact with the rod 2, and a peak surface pressure is formed in the region R3 as shown in FIG. 9B. Further, even when the pressure is applied in FIGS. 10A and 10B, since the region where the first side surface 101 and the third side surface 103 of the heel portion 10h intersect is only the slope 150, a larger peak surface pressure is present in the region R4. appear. As a result, during the drawing process, the oil suction characteristic was poor, which was one factor in causing oil leakage.
　図１１に、実施の形態の第１シール部材１０と関連技術の第１シール部材１０Ｘとの漏れ量を対比して説明する。図１１は、実施の形態の第１シール部材１０と関連技術の第１シール部材１０Ｘとの、摺動距離および漏れ量の関係を示す図である。 FIG. 11 explains the amount of leakage between the first seal member 10 of the embodiment and the first seal member 10X of the related art. FIG. 11 is a diagram illustrating the relationship between the sliding distance and the leakage amount between the first seal member 10 of the embodiment and the first seal member 10X of the related art.
　第１シール部材１０および第１シール部材１０Ｘはいずれも、ウレタン樹脂等の合成樹脂（硬さデュロメータＡ９０、引張強さＭｐａ４４．０、伸び５００％、圧縮永久歪４０％、圧縮永久歪試験の条件８）（８０℃－７０ｈ）：日本バルカー工業株式会社製、製品番号Ｒ５５９０））を用いた。 Both the first seal member 10 and the first seal member 10X are synthetic resins such as urethane resin (hardness durometer A90, tensile strength Mpa 44.0, elongation 500%, compression set 40%, compression set test conditions. 8) (80 ° C.-70 h): Nippon Valqua Industries, Ltd., product number R5590)).
　第１シール部材１０は、Ｒ＝２ｍｍ、θ＝６０°、ａ＝０．６ｍｍである。第１シール部材１０Ｘは、湾曲面は設けられておらず、斜面１５０は、Ｒ＝０ｍｍ、θ＝４５°、ａ＝０．５ｍｍである（いわゆるＣ面＝０．５ｍｍ）。 The first seal member 10 has 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 has R = 0 mm, θ = 45 °, and a = 0.5 mm (so-called C surface = 0.5 mm).
　測定においては、いずれも第１シール部材のみを装着し、シリンダ１からの油の外部漏れ量を測定した。その結果を、図１１に示す。本実施の形態における第１シール部材１０は、関連技術における第１シール部材１０Ｘに比較して良好な密封性能を有することが確認できた。 In the measurement, only the first seal member was attached, and the amount of external leakage of oil from the cylinder 1 was measured. The result is shown in FIG. It has been confirmed that the first seal member 10 in the present embodiment has better sealing performance than the first seal member 10X in the related art.
　（実施例）
　図１２および図１３に、本実施の形態における第１シール部材１０の変形例の構造を示す。図１２は、「ａ」を比較的大きく設けた第１シール部材１０Ａの場合の形状を示し、図１３は「θ」を比較的大きく設けた第１シール部材１０Ｂの場合を示す。 (Example)
12 and 13 show a structure of a modified example of the first seal member 10 in the present embodiment. FIG. 12 shows the shape of the first seal member 10A having a relatively large “a”, and FIG. 13 shows the case of the first seal member 10B having a relatively large “θ”.
　さらに、図１４Ａから図１６Ｂに、具体的な実施例１から実施例３として、圧力負荷時における接触幅と接触面圧との関係を示す。実施例１における第１シール部材１０は、Ｒ＝１５、θ＝８０°、ａ＝０．３の形状を有し、実施例２における第１シール部材１０は、Ｒ＝２、θ＝３０°、ａ＝２の形状を有し、実施例３における第１シール部材１０は、Ｒ＝０．５、θ＝３０°、ａ＝２の形状を有している。各図Ａにおいては、Ｐ１～Ｐ１０は内圧の分布を示し、Ｐ１からＰ１０に向けて内圧が小さくなることを示している。 Further, FIGS. 14A to 16B show the relationship between the contact width and the contact surface pressure at the time of pressure loading, as specific examples 1 to 3. FIG. The first seal member 10 in Example 1 has a shape of R = 15, θ = 80 °, and a = 0.3, and the first seal member 10 in Example 2 has R = 2 and θ = 30 °. , A = 2, and the first seal member 10 in Example 3 has a shape of R = 0.5, θ = 30 °, and a = 2. In each figure A, P1 to P10 indicate the distribution of the internal pressure, and the internal pressure decreases from P1 to P10.
　図１４Ａおよび図１４Ｂに示す実施例１の場合は、接触幅の全域においてピーク面圧は発生しておらず、良好な面圧が示されていることから、優良なシール性能を有していることが確認できた。 In the case of Example 1 shown in FIG. 14A and FIG. 14B, no peak surface pressure is generated in the entire contact width, and good surface pressure is shown. I was able to confirm.
　図１５Ａおよび図１５Ｂに示す実施例２の場合は、上記実施例１に比べて、接触幅の全域においてピーク面圧は発生しておらず、より良好な面圧が示されていることから、優良なシール性能を有していることが確認できた。 In the case of Example 2 shown in FIG. 15A and FIG. 15B, compared to Example 1 above, no peak surface pressure is generated in the entire contact width, and a better surface pressure is shown. It was confirmed that it had excellent sealing performance.
　図１６Ａおよび図１６Ｂに示す実施例３の場合は、上記実施例１に比べて、接触幅が約１ｍｍ近傍の領域において、微小なピーク面圧が発生していることから、実施例１に比べては良好でないものの、図１０Ａおよび図１０Ｂに示した関連技術に比べると良好であることから、全体としては、良好なシール性能を有していることが確認できた。 In the case of Example 3 shown in FIGS. 16A and 16B, compared to Example 1 above, a minute peak surface pressure is generated in a region where the contact width is about 1 mm. Although it is not good at all, it is better than the related technology shown in FIG. 10A and FIG. 10B, so that it has been confirmed that it has a good sealing performance as a whole.
　以上の実施例によれば、ヒール部１０ｈの第１側面１０１および第３側面１０３が交わる領域には、湾曲面１１０、および、斜面１２０が設けられ、湾曲面１１０は、第１側面および斜面１２０に対して接するように設けられ、斜面１２０は第３側面１０３と交わるように設けられている。これにより、本実施の形態における第１シール部材は、良好な密封性能を有している。 According to the above embodiment, 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 heel portion 10h intersect, and the curved surface 110 includes the first side surface and the inclined surface 120. The inclined surface 120 is provided so as to intersect the third side surface 103. Thereby, the 1st sealing member in this Embodiment has favorable sealing performance.
　さらに、湾曲面１１０および斜面１２０の第３側面１０３への投影長さ「ａ」を、０．３ｍｍ以上２ｍｍ以下とし、湾曲面１１０の半径「Ｒ」を、２ｍｍ以上１５ｍｍ以下として、斜面１２０の第３側面１０３に対する傾斜角度「θ」を、３０°から８０°にすることで、より好ましい密封性能を得ることを可能としている。 Further, the projection length “a” of the curved surface 110 and the inclined surface 120 onto the third side surface 103 is set to 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. By setting the inclination angle “θ” with respect to the third side surface 103 to 30 ° to 80 °, it is possible to obtain more preferable sealing performance.
　以上、実施の形態および実施例について説明したが、今回開示された実施の形態は全ての点で例示であって制限的なものではないと考えられるべきである。本発明の範囲は請求の範囲によって示され、請求の範囲と均等の意味および範囲内での全ての変更が含まれることが意図される。 Although the embodiments and examples have been described above, the embodiments disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.
１　シリンダ、２　ロッド、１０，１０Ａ，１０Ｂ　第１シール部材、１０Ｇ　第１シール溝、１０ｈ　ヒール部、１０ｒ　リップ部、２０　第２シール部材、２０Ｇ　第２シール溝、１０１　第１側面、１０２　第２側面、１０３　第３側面、１０ｂ　第１リップ部、１０ｃ　第２リップ部、１１０　湾曲面、１２０　斜面。 1 cylinder, 2 rod, 10, 10A, 10B first seal member, 10G first seal groove, 10h heel portion, 10r lip portion, 20 second seal member, 20G second seal groove, 101 first side surface, 102 second Side surface, 103 3rd side surface, 10b 1st lip part, 10c 2nd lip part, 110 curved surface, 120 slope.

Claims (2)

  1. 　油空圧機器におけるシリンダとロッドとの摺動隙間において高圧側と低圧側と仕切り、前記ロッドの外周面の周方向に沿って環状に設けられたシール溝の内部に収容されて、前記シリンダと前記ロッドとの摺動隙間を塞ぐシール部材であって、
    　低圧側に位置するヒール部と、
    　高圧側に位置するリップ部と、含み、
    　前記ヒール部は、
    　前記ロッド側に位置する第１側面、前記第１側面に対向位置する第２側面、および、高圧側に位置する第３側面を有し、
    　前記リップ部は、
    　前記ロッド側に向けて拡がる第１リップ部、および、前記ロッド側とは反対側に向けて拡がる第２リップ部を有し、
    　前記ヒール部の第１側面および前記第３側面が交わる領域には、湾曲面、および、斜面が設けられ、
    　前記湾曲面は、前記第１側面および前記斜面に対して接するように設けられ、
    　前記斜面は、前記第３側面と交わるように設けられている、シール部材。     In the sliding gap between the cylinder and the rod in the hydraulic / pneumatic equipment, the high pressure side and the low pressure side are partitioned, and housed in an annular seal groove provided along the circumferential direction of the outer peripheral surface of the rod, A sealing member for closing a sliding gap with the rod,
    A heel portion located on the low pressure side;
    Including a lip portion located on the high pressure side,
    The heel part is
    A first side located on the rod side, a second side located opposite the first side, and a third side located on the high pressure side,
    The lip portion is
    A first lip portion that expands toward the rod side, and a second lip portion that expands toward the opposite side of the rod side,
    A curved surface and a slope are provided in a region where the first side surface and the third side surface of the heel portion intersect,
    The curved surface is provided so as to contact the first side surface and the inclined surface,
    The slope is a seal member provided so as to intersect with the third side surface.
  2. 　前記湾曲面および前記斜面の前記第３側面への投影長さは、０．３ｍｍ以上２ｍｍ以下であり、
    　前記湾曲面の半径は、２ｍｍ以上１５ｍｍ以下であり、
    　前記斜面の前記第３側面に対する傾斜角度、３０°から８０°である、請求項１に記載のシール部材。     The projection length of the curved surface and the inclined surface onto the third side surface is 0.3 mm or more and 2 mm or less,
    The radius of the curved surface is 2 mm or more and 15 mm or less,
    The sealing member according to claim 1, wherein an inclination angle of the inclined surface with respect to the third side surface is 30 ° to 80 °.
PCT/JP2016/079587 2015-11-19 2016-10-05 Seal member WO2017086044A1 (en)

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KR20180081766A (en) 2018-07-17

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