WO2010083696A1 - 密封装置和阀 - Google Patents

密封装置和阀 Download PDF

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Publication number
WO2010083696A1
WO2010083696A1 PCT/CN2009/074914 CN2009074914W WO2010083696A1 WO 2010083696 A1 WO2010083696 A1 WO 2010083696A1 CN 2009074914 W CN2009074914 W CN 2009074914W WO 2010083696 A1 WO2010083696 A1 WO 2010083696A1
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WO
WIPO (PCT)
Prior art keywords
guide ring
component
sealing device
shoulder
ring
Prior art date
Application number
PCT/CN2009/074914
Other languages
English (en)
French (fr)
Inventor
王欣
赵斌
黄丙元
贺嘉
Original Assignee
丹佛斯（天津）有限公司
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Application filed by 丹佛斯（天津）有限公司 filed Critical 丹佛斯（天津）有限公司
Publication of WO2010083696A1 publication Critical patent/WO2010083696A1/zh

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Classifications

    • 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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
    • F16K5/06—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having spherical surfaces; Packings therefor
    • F16K5/0647—Spindles or actuating means
    • 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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
    • F16K5/06—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having spherical surfaces; Packings therefor
    • F16K5/0663—Packings
    • F16K5/0694—Spindle sealings

Definitions

  • the present invention relates to a sealing device and a valve using the same. Background technique
  • the ball valve 100 includes a ball 10 as an opening and closing member disposed in the valve chamber, and a valve stem 3 for driving the rotation of the ball, the valve stem 3 being made of brass or stainless steel.
  • the ball is formed with a recess 11 and a through hole 12, and one end of the stem 3 is formed with a shank 32 adapted to fit into the recess 11 and inserted into the recess.
  • valve stem main body portion 31 is mounted in a hole 21 defined by the overhanging sleeve 20 extending from the ball valve body, and is provided in the annular groove 33 formed in the valve stem main body portion.
  • the 0-ring 1 achieves a seal between the stem body portion and the inner wall of the overhanging sleeve.
  • the ball valve further includes two guide rings 2 made of RPTFE (i.e., polytetrafluoroethylene (Teflon) to which carbon fiber, glass fiber or molybdenum disulfide is added) and made of stainless steel.
  • the spacer 4 is disposed at both axial ends of the valve stem main body portion 31, wherein the lower guide ring 2 is disposed between the lower shoulder 35 of the stem main body portion and the annular flange 40, the annular projection
  • the rim 40 is formed between the ball valve chamber and the overhang sleeve; and the upper guide ring 2 is disposed between the upper shoulder 36 of the stem body portion and the spacer 4.
  • the guide ring 2 serves to reduce the frictional resistance of the valve stem when it is rotated and to ensure the centering of the valve stem in the bore 21 of the overhanging sleeve, and the gasket 4 is used to fix the valve stem in the overhanging sleeve.
  • the overhanging sleeve is formed at an end facing away from the valve cavity with a wall thickness reducing extension portion 22. In the assembled state, the extension portion is bent inwardly and pressed against the gasket 4, thereby the valve stem Together with the guide ring 2 is fixed in place.
  • an external thread is formed on the overhanging sleeve, and the ball valve is additionally provided with a bonnet 5 made of brass, and the bonnet 5 is formed with an internal thread, thereby connecting the bonnet 5 to the overhanging sleeve by means of a screw connection.
  • a bonnet seal 6 is disposed between the overhanging sleeve and the bonnet 5 for sealing between the two. Thereby an additional sealing protection of the ball valve is achieved by means of the bonnet.
  • the 0-ring is made of CR rubber because of CR Rubber is compatible with a wide range of refrigerants and lubricants; and an O-ring is used to seal the ball valve.
  • the use of a 0-ring between the relatively moving valve stem 3 and the overhanging sleeve 20 does not achieve a satisfactory sealing effect, since the wear amount of the 0-ring is not compensated after wear, resulting in a reduced sealing effect. . Therefore, the O-ring is suitable for use as a static sealing element and not as a dynamic sealing element.
  • the use of the O-ring as the sealing member has a drawback that the sealing effect gradually decreases over time, which may cause leakage of the fluid, and The amount of external leakage of the fluid is an important criterion for measuring the quality of the seal structure.
  • the guide ring 2 has almost no elasticity and does not have a sealing function, and does not automatically ensure the centering of the valve stem in the hole 21 of the overhanging sleeve. Summary of the invention
  • Another object of the present invention is to provide a sealing device that enables automatic centering of two relatively moving parts while ensuring a good seal between two opposing moving parts.
  • a sealing device comprising: a first member, the first member being formed with a hole;
  • the second component being mounted in the aperture of the first component and rotatable relative to the first component, and the second component being formed with two first shoulders axially spaced apart from each other and a second shoulder, and having at least one annular groove between the first shoulder and the second shoulder on an outer circumferential surface thereof; an O-ring, the O-ring being disposed at the second component Said in the ring groove;
  • first stop member and a second stop member a first stop member and a second stop member, the first stop member and the second stop member being integrally formed with the first member or fixed relative to the first member;
  • second component is axially positioned relative to the first component by the first stop and the second stop, the first guide ring being located at the first shoulder and the first stop Between the pieces, and the second guiding ring is located between the second shoulder and the second stop,
  • An annular surface of the first shoulder is a frustoconical surface, and an axial end surface of the first guide ring opposite to the first shoulder is formed to be a frustoconical surface of the first shoulder An adapted frustoconical surface such that the first guide ring tends to slide radially outward when subjected to axial pressure;
  • the first guide ring is made of a material having an elastic and sealing function, and in the assembled state of the sealing device, the first guide ring is subjected to axial pressure and generates a predetermined amount of compression.
  • the annular surface of the second shoulder is a frustoconical surface
  • the axial end surface of the second guide ring opposite to the second shoulder is formed as a truncated cone with the second shoulder
  • the frustoconical surface of the shaped surface is adapted such that the second guide ring tends to slide radially outward when subjected to axial pressure.
  • the second guide ring is made of a material having an elastic and sealing function, and in the assembled state of the sealing device, the second guide ring is subjected to axial pressure and generates a predetermined amount of compression.
  • the second member is formed on its outer peripheral surface with two ring grooves between the first shoulder and the second shoulder, and each ring groove is provided with an O-ring.
  • the O-ring is made of CR rubber.
  • the first guide ring is made of PTFE.
  • the second guide ring is made of PTFE.
  • one of the first stop and the second stop comprises a spacer
  • the first component comprises an axial extension of the wall thickness reduction, in the assembled state of the sealing device
  • the axial extension is bent radially inwardly and pressed against the spacer to fix the gasket;
  • the other of the first and second stops is A flange projecting radially inwardly of the first member is formed.
  • the sealing device further comprises a cap, the cap is formed with an internal thread, and the first member is formed with an external thread, the cap is connected to the first component by means of a screw connection, and the seal is arranged Between the cap and the first component.
  • the first guide ring and/or the second guide ring are slidable radially outward when subjected to axial pressure.
  • a valve comprising:
  • valve body a valve body, the valve body defining a valve cavity
  • An opening and closing member disposed in the valve cavity
  • valve stem operatively coupled to the opening and closing member and configured to rotate the opening and closing member; a sealing device according to the first aspect of the invention
  • valve body includes an overhanging sleeve extending from the valve body, the overhanging sleeve serving as the first component and the mast serving as the second component.
  • the valve is a ball valve.
  • the double effect of static sealing and dynamic sealing is realized with a simple structure, and the static sealing and the dynamic sealing are designed independently of each other, prolonging the life of the dynamic sealing and the static sealing and the cost is low.
  • automatic alignment of the two relatively moving parts is achieved while ensuring a good seal between the two relatively moving parts.
  • Figure 1 is a perspective cross-sectional view showing a conventional ball valve applied to a refrigeration system
  • Figure 2 is a partial cross-sectional view showing the sealing structure of the ball valve of Figure 1;
  • Figure 3A is a partially enlarged axial cross-sectional view showing the O-ring shear caused by the presence of a pressure difference across the O-ring;
  • Figure 3B is a cross-sectional view of the O-ring showing the O-ring Damage caused by cutting;
  • Figure 4 is a view similar to Figure 2, showing a sealing structure according to the present invention by way of a ball valve;
  • Figure 5A is an axial cross-sectional view of the valve stem of the present invention with an O-ring and a guide ring according to the present invention
  • Figure 5B is a partial enlarged view of a portion A of Figure 5A;
  • Figure 6 is a partial cross-sectional view of the sealing structure of the present invention, illustrating the sealing principle of the guide ring of the present invention
  • Figure 7 is an axial cross-sectional view showing a guide ring in accordance with the present invention. detailed description
  • the sealing structure of the present invention will be described in detail below by taking a refrigerating ball valve as an example, and the ball valve can be used, for example, in a refrigeration and air conditioning system.
  • the embodiments of the present invention are merely illustrative, and are merely illustrative of the principles of the invention and are not intended to limit the invention.
  • the sealing structure of the present invention is not limited to use with ball valves, but can be used in other types of valves such as butterfly valves, plug valves, and the like, and can be used in any situation where a similar dynamic seal is desired.
  • structural components similar to those of the prior art will be given the same reference numerals, and the description thereof will be simplified.
  • the member associated with the sealing structure of the present invention includes: a valve stem 3 made of, for example, brass or stainless steel, and an annular groove 33 formed in the valve stem main body portion 31, for example An O-ring 1 made of CR rubber, a gasket 4 made of, for example, stainless steel, and an overhanging sleeve 20 and the like.
  • the components associated with the additional seal protection include a bonnet 5 made of, for example, brass, a bonnet seal 6 made of, for example, PTFE, disposed between the overhang sleeve 20 and the bonnet 5.
  • a bonnet 5 made of, for example, brass
  • a bonnet seal 6 made of, for example, PTFE
  • the overhanging sleeve 20 is formed with an external thread
  • the bonnet 5 is formed with an internal thread
  • the bonnet 5 is connected to the overhanging sleeve 20 by means of a screw.
  • the sealing structure according to the present invention further includes two guide rings 2, which are respectively disposed at axial ends of the valve stem main body portion 31, wherein the lower guide ring 2 is disposed at the lower shoulder 35 of the valve stem main body portion and Between the annular flanges 40, the annular flange 40 is formed between the ball valve chamber and the overhanging sleeve 20 and serves as a stopper; and the upper guide ring 2 is disposed on the upper portion 36 of the stem body portion and the spacer 4 Between the spacers 4 serves as another stop.
  • the guide ring 2 can achieve the following functions: 1) reducing the frictional resistance when the valve stem is rotated; 2) ensuring automatic centering of the valve stem in the hole 21 of the overhanging sleeve; 3) achieving a sealing function. Therefore, the guide ring 2 is preferably made of a material which is resistant to abrasion, has a small coefficient of friction, has a sealing function, and is elastically deformed under pressure. Thereby, the guide ring 2 can reduce the frictional resistance when the valve stem is rotated and achieve a dynamic seal.
  • Materials that can be used to make the guide ring 2 include PTFE, rubber, carbon fiber, asbestos, graphite, ceramic fibers, and other materials suitable for this purpose, with PTFE being a preferred material for the manufacture of the guide ring 2.
  • valve stem body portion is formed with two annular recesses 33 for mounting an O-ring. It should be noted that the valve stem main body portion may also be formed with only one annular groove or two or more annular grooves.
  • the annular surface of the upper shoulder 36 of the stem body portion is not perpendicular to the stem axis, which is a frustoconical surface forming an acute angle ⁇ ⁇ between the plane perpendicular to the stem axis; in other words, the valve
  • the annular surface of the upper shoulder 36 of the rod body portion is inclined downward from the radially inner side to the radially outer side in the drawing.
  • the annular surface of the lower shoulder 35 of the stem body portion is not perpendicular to the stem axis, which is a frustoconical surface forming an acute angle ⁇ ⁇ between the plane perpendicular to the stem axis;
  • the annular surface of the lower shoulder 35 of the stem main body portion is upward from the radially inner side to the radially outer side in the drawing. Tilt.
  • FIG. 7 is an axial cross-sectional view of the guide ring 2.
  • an axial end face 25 of the guide ring 2 is not perpendicular to the axis of the guide ring 1, but forms an acute angle ⁇ 2 or ⁇ 2 between the planes perpendicular to the axis of the guide ring 1.
  • the values of ⁇ and ⁇ 2 are substantially equal to each other, and the values of ⁇ 1 and ⁇ 2 are substantially equal to each other.
  • ⁇ ( ⁇ 1 and ⁇ 2) and ⁇ ( ⁇ 1 and ⁇ 2) can be designed to be substantially equal to each other; but ⁇ ( ⁇ and ⁇ 2) and ⁇ ( ⁇ ) can also be used according to different design requirements.
  • ⁇ and ⁇ 2) are designed such that: ⁇ ( ⁇ and ⁇ 2) and ⁇ ( ⁇ ⁇ and ⁇ 2) are not equal to each other.
  • the range of the angle ⁇ or ⁇ is not particularly limited in terms of ensuring the automatic centering of the valve stem in the hole 21 of the overhanging sleeve.
  • a reliable dynamic sealing effect is achieved, and the range of the angle ⁇ or ⁇ is subject to a certain value.
  • Limitation, theoretically ⁇ or ⁇ should be at least greater than the friction angle, i.e., the self-locking angle, which is well known to those skilled in the art and therefore will not be described in further detail herein.
  • the friction angle or self-locking angle varies depending on the coefficient of friction of the friction pair material. Therefore, when the material used to manufacture the guide ring and the valve stem is different, the friction angle or the self-locking angle will also be different; correspondingly, it is used to ensure that the guide ring can be along the shoulder of the valve stem main body when subjected to axial pressure.
  • the angle ⁇ or ⁇ of the annular surface sliding radially outward will also vary.
  • the value of the angle ⁇ or ⁇ can be selected according to the size of the compression space of the guide ring and the axial initial compression amount of the guide ring. Therefore, in terms of the fact that the guide ring can slide radially outward to achieve a reliable dynamic sealing effect, the range of the angle ⁇ or ⁇ is not particularly limited, but needs to be larger than the friction angle or the self-locking angle.
  • the inclined end surface 25 of the upper guide ring 2 and the annular surface of the upper shoulder 36 of the valve stem main body portion abut each other, and the inclined end surface 25 of the lower guide ring 1 and the stem main body portion
  • the annular surfaces of the lower shoulders 35 abut each other.
  • FIG. Figure 6 is a partial cross-sectional view of the sealing structure of the present invention illustrating the sealing principle of the guide ring of the present invention.
  • the spacer 4 is pressed against the spacer 4 by bending the extension 22 of the overhanging sleeve inwardly; at the same time, the extension of the overhanging sleeve
  • the pressure F1 acts on the spacer 4
  • the spacer 4 transmits the pressure to the upper guide ring 1 to receive the axial force F2; similarly, the lower guide
  • the ring 1 also receives the effect of axial forces.
  • both the upper and lower guide rings 2 are axially compressed such that the inclined end faces of the guide ring 2 are respectively pressed against the annular surfaces of the upper and lower shoulders 36 and 35 of the valve stem main body portion;
  • the upper and lower guide rings 1 slide radially outwardly along the annular surfaces of the upper and lower shoulders 36 and 35 of the stem body portion, respectively, such that the radially outer surface of the guide ring 2 is pressed against the overhanging sleeve.
  • Inner wall thus, two sealing surfaces are formed at the radially outer surface and the inclined end surface of the guide ring 2 (see also Fig. 5B), achieving a seal between the valve stem and the inner wall of the overhanging sleeve.
  • the initial compression amount H of the guide ring 2 can be determined according to the actual application, or can be determined experimentally.
  • the amount of wear is the initial amount of compression of the guide ring and/or the guide ring 2 is relatively It is compensated by the radial outward movement of the valve stem, thus achieving a reliable dynamic sealing effect.
  • the sealing structure of the present invention As described above, with the sealing structure of the present invention, a good dynamic sealing effect is achieved on the one hand and a valve stem in the hole 21 of the overhanging sleeve, on the other hand, by utilizing the beveling properties of the shoulder and the guiding ring. Automatic alignment. Moreover, according to the present invention, the amount of pre-compression of the guide ring can be controllably adjusted, thereby adjusting the operational life of the dynamic seal.
  • the sealing effect can be adaptively adjusted as the pressure of the fluid in the pressurized fluid system changes.
  • the upper guide ring 2 is further compressed.
  • the inclined end face of the upper guide ring 2 is pressed more tightly against the annular surface of the upper shoulder 36 of the valve stem main body portion, and the radially outer surface of the guide ring 2 is pressed more tightly against the overhanging sleeve.
  • the inner wall, and thus the guide ring 2 provides a proportional leakage protection with respect to fluid pressure.
  • the guide ring 2 having the structure of the present invention is disposed at both axial ends of the valve stem main body, as an alternative, or only in an axial direction of the stem main body portion.
  • a guide ring 2 having the structure of the present invention is disposed at the end.
  • the sealing structure also includes a bonnet 5 and a bonnet seal 6 to provide additional sealing protection.
  • this additional sealing protection is not required and can be selected according to the actual application.
  • annular surfaces of the upper and lower shoulders 35, 36 of the stem body portion are formed at angles ol and ⁇ 1 with respect to a plane perpendicular to the axis of the valve stem, and similarly, the axial end faces of the guide ring 2 are opposed to
  • the angle o 2 or ⁇ 2 formed between the planes perpendicular to the axis of the guide ring is not limited to a specific value, but may be selected according to practical applications as long as the intended function as described above can be achieved.
  • angles ⁇ ⁇ and/or ⁇ 2 and ⁇ ⁇ and/or ⁇ 2 are designed to be able to move radially outward relative to the valve stem when the guide ring is subjected to axial pressure, this is not the preferred solution. Required.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Devices (AREA)
  • Details Of Valves (AREA)

Description

密封装置和阀 技术领域
本发明涉及一种密封装置以及釆用该密封装置的阀。 背景技术
在彼此之间存在相对运动， 比如相对转动或相对线性移动或者同时存在 相对转动和相对线性移动，的两个部件之间， 实现可靠密封一直是一个难点。 传统的设计是将静态密封和动态密封由一个密封部件， 例如 0形环， 承担， 图 1示出了釆用该种 0形环的球阀 100。
如图 1和 1所示， 球阀 100包括设置于阀腔中的、 作为启闭件的球体 10 以及用以驱动球体转动的阀杆 3 , 该阀杆 3由黄铜或不锈钢制成。 球体上形 成有凹槽 11和贯穿孔 12 , 而阀杆 3的一端形成有与凹槽 11相适配并插装于 该凹槽中的柄部 32。
如图 1所示， 阀杆主体部 31装设于自球阀主体延伸出的外伸套筒 20所 限定的孔 21中， 并借助于装设于阀杆主体部上形成的环形槽 33中的 0形环 1实现阀杆主体部与外伸套筒内壁之间的密封。
此外， 如图 2所示， 球阀还包括两个由 RPTFE (即添加有碳纤维、 玻璃 纤维或二硫化钼等的聚四氟乙烯（特氟隆））制成的导向环 2以及由不锈钢制 成的垫片 4 , 两个导向环 1分别设置在阀杆主体部 31的轴向两端， 其中下部 导向环 2设置在阀杆主体部下部台肩 35与环形凸缘 40之间， 该环形凸缘 40 形成在球阀阀腔与外伸套筒之间； 而上部导向环 2设置在阀杆主体部上部台 肩 36与垫片 4之间。导向环 2用以降低阀杆转动时的摩擦阻力并确保阀杆于 外伸套筒的孔 21中的对中， 而垫片 4用以将阀杆固定于外伸套筒中。 如图 1 所示， 外伸套筒于背离阀腔的一端形成有壁厚减薄的延伸部 22 , 在组装状态 下， 延伸部向内弯折并压靠于垫片 4 , 从而将阀杆连同导向环 2固定就位。
另外， 外伸套筒上形成有外螺紋， 且球阀另外设置有由黄铜制成的阀帽 5 , 而阀帽 5上形成有内螺紋，从而借助于螺紋连接将阀帽 5连接在外伸套筒 上。 如图 2所示， 阀帽密封件 6设置在外伸套筒与阀帽 5之间， 用以实现两 者之间的密封。 从而借助于阀帽， 实现球阀的附加密封保护。
在这种传统的用于制冷系统的球阀中， 0形环由 CR橡胶制成， 因为 CR 橡胶可以与多种制冷剂和润滑油相兼容； 且 0形环被用来实现球阀的密封。 然而 ,在相对运动的阀杆 3与外伸套筒 20之间釆用 0形环并不能实现令 人满意的密封效果， 因为 0形环磨损后， 其磨损量不能得到补偿， 导致密封 效果下降。 因此， 0形环适于用作静态密封元件， 而不宜作为动态密封元件。
此外， 对于用于压力流体系统中的球阀而言， 由于 0形环两侧存在较大 压差， 容易造成 0圈发生剪切。 请参见图 3A和 3B, 其分别示出了 0形环两 侧存在压差的情况下造成的 0形环剪切以及 0形环因剪切而造成的损坏。 在 0形环发生剪切损坏的情况下， 会严重影响其密封效果。
因此， 在相对运动的部件之间以及在用于传送压力流体的阀中， 釆用 0 形环作为密封元件存在有随着时间的推移密封效果逐渐下降的缺陷， 从而可 能导致流体的泄漏，而流体的外部泄漏量是衡量密封结构质量好坏的重要标 准。 此外， 导向环 2几乎没有弹性而不具有密封功能， 且不能自动确保阀杆 于外伸套筒的孔 21中的对中。 发明内容
如上所述， 在传统技术中， 在诸如用于制冷系统的球阀中， 静态、 动态 密封均由 0形环来承担， 这势必造成密封模式寿命减小、 成本加大。 因此， 业内存在对成本低、密封寿命长、适用于静态和动态密封的密封结构的需求。
因此， 本发明的目的是提供一种密封装置， 其能够实现静态密封和动态 密封双重效果。
本发明的另一目的是提供一种密封装置， 其能够在确保两个相对运动部 件之间的良好密封的同时， 实现两个相对运动部件的自动对中。
为实现上述目的， 根据本发明第一方面， 提供了一种密封装置， 包括： 第一部件， 该第一部件形成有孔；
第二部件， 该第二部件装设于第一部件的所述孔中并可相对于所述第一 部件转动，且该第二部件形成有两个轴向彼此间隔开的第一轴肩和第二轴肩， 并在其外周面上形成有位于所述第一轴肩和第二轴肩之间的至少一个环槽； 0形环， 该 0形环设置在所述第二部件的所述环槽中；
第一导向环以及第二导向环； 以及
第一止挡件和第二止挡件， 所述第一止挡件和第二止挡件或是与所述第 一部件一体形成或是相对于所述第一部件保持固定； 其中， 所述第二部件利用所述第一止挡件和第二止挡件相对于所述第一 部件轴向定位， 所述第一导向环位于所述第一轴肩与第一止挡件之间， 而所 述第二导向环位于所述第二轴肩与第二止挡件之间，
所述第一轴肩的环形表面是截锥形表面， 而所述第一导向环的与所述第 一轴肩相对的轴向端面形成为与所述第一轴肩的截锥形表面相适配的截锥形 表面， 使得所述第一导向环在承受轴向压力时倾向于径向向外滑动；
其中， 所述第一导向环由具有弹性和密封功能的材料制成， 在所述密封 装置的组装状态下， 所述第一导向环承受轴向压力并产生预定的压缩量。
优选地， 所述第二轴肩的环形表面是截锥形表面， 而所述第二导向环的 与所述第二轴肩相对的轴向端面形成为与所述第二轴肩的截锥形表面相适配 的截锥形表面，使得所述第二导向环在承受轴向压力时倾向于径向向外滑动。
优选地， 所述第二导向环由具有弹性和密封功能的材料制成， 在所述密 封装置的组装状态下， 所述第二导向环承受轴向压力并产生预定的压缩量。
优选地， 所述第二部件在其外周面上形成有位于所述第一轴肩和第二轴 肩之间的两个环槽， 每个环槽设置有一个 0形环。
优选地， 所述 0形环由 CR橡胶制成。
优选地， 所述第一导向环由 PTFE制成。
优选地， 所述第二导向环由 PTFE制成。
优选地， 所述第一止挡件和第二止挡件中的一个止挡件包括垫片， 而所 述第一部件包括壁厚减薄的轴向延伸部， 在密封装置的组装状态下， 该轴向 延伸部径向向内弯折并压靠于所述垫片将所述垫片固定； 所述第一止挡件和 第二止挡件中的另一个止挡件由从所述第一部件径向向内伸出的突缘形成。
优选地， 所述密封装置还包括帽， 该帽上形成有内螺紋， 而所述第一部 件上形成有外螺紋， 所述帽借助于螺紋连接连接于所述第一部件， 且密封件 设置在所述帽与所述第一部件之间。
优选地， 所述第一导向环以及 /或者述第二导向环在承受轴向压力时能 够径向向外滑动。
根据本发明另一方面， 提供了一种阀， 包括：
阀体， 该阀体限定一阀腔；
设置在所述阀腔中的启闭件；
阀杆， 与所述启闭件操作连接并用以转动所述启闭件； 以及 根据本发明第一方面的密封装置；
其中所述阀体包括自阀体延伸出的外伸套筒， 该外伸套筒用作所述第一 部件， 而所述阃杆用作所述第二部件。
优选地， 所述阀是球阀。
釆用本发明的技术方案， 以简单的结构实现了静态密封和动态密封的双 重效果， 且静态密封和动态密封彼此相对独立设计， 延长了动态密封和静态 密封的寿命且成本低。 同时， 釆用本发明技术方案， 在确保两个相对运动部 件之间的良好密封的同时， 实现了两个相对运动部件的自动对中。
此外， 釆用本发明的技术方案， 实现了相对于流体压力的成比例的泄漏 防护。 附图说明
下面结合附图和实施例对本发明作进一步详细说明， 其中
图 1是透视剖视图， 示出了传统的应用于制冷系统中的球阀；
图 2是局部剖面视图， 示出了图 1中的球阀的密封结构；
图 3A是局部放大轴向剖面视图， 示出了 0形环两侧存在压差的情况下 造成的 0形环剪切； 图 3B是 0形环的截面视图， 示出了 0形环因剪切而造成 的损坏；
图 4是类似于图 2的视图， 以球阀为例示出了根据本发明的密封结构； 图 5A是本发明阀杆的轴向剖面视图， 其上装设有 0形环和根据本发明 的导向环； 图 5B是图 5A中部分 A的局部放大视图；
图 6是本发明密封结构的局部剖面视图，其图示了本发明导向环的密 封原理； 以及
图 7是轴向剖面视图， 示出了根据本发明的导向环。 具体实施方式
下面以制冷球阀为例对本发明的密封结构进行详细的说明， 该球阀可用 于例如制冷和空调系统。在此，应当指出， 本发明的实施例仅仅是例示性的， 其仅只用于说明本发明的原理而非限制本发明。 对本领域技术人员显而易见 的是， 本发明密封结构不限于用于球阀， 也可以用于诸如蝶阀、 旋塞阀等其 他类型的阀中， 而且还可以用于任何需要实现类似动态密封的场合。 在下面的描述中， 与现有技术相类似的结构部件将赋予相同的附图标 记， 且其描述将予以简略。
首先参见图 4 , 其示出了根据本发明的密封结构。 如图 4所示， 本发明 的与密封结构相关联的部件包括： 由例如黄铜或不锈钢制成的阀杆 3、 装设 于阀杆主体部 31上形成的环形槽 33中的、 由例如 CR橡胶制成的 0形环 1、 由例如不锈钢制成的垫片 4以及外伸套筒 20等。
与附加密封保护相关联的部件包括由例如黄铜制成的阀帽 5、 设置在外 伸套筒 20与阀帽 5之间的、 由例如 PTFE制成的阀帽密封件 6。 类似地， 外 伸套筒 20上形成有外螺紋， 而阀帽 5上形成有内螺紋， 阀帽 5借助于螺紋连 接在外伸套筒 20上。
根据本发明的密封结构， 还包括两个导向环 2 , 两个导向环 2分别设置 在阀杆主体部 31的轴向两端，其中下部导向环 2设置在阀杆主体部下部台肩 35与环形凸缘 40之间， 该环形凸缘 40形成在球阀阀腔与外伸套筒 20之间 并用作止挡件；而上部导向环 2设置在阀杆主体部上部台肩 36与垫片 4之间， 该垫片 4用作另一止挡件。
根据本发明，导向环 2可实现下述功能： 1 )降低阀杆转动时的摩擦阻力； 2 )确保阀杆于外伸套筒的孔 21中的自动对中； 3 )实现密封功能。 因此， 导 向环 2宜釆用耐磨损、 摩擦系数小、 具有密封功能且在压力作用下产生弹性 变形的材料制成。 从而， 导向环 2可以降低阀杆转动时的摩擦阻力并实现动 态密封。 可用于制造导向环 2的材料包括 PTFE、橡胶、碳纤维、石棉、石墨、 陶瓷纤维以及其他适于此目的的材料，其中 PTFE是用于制造导向环 2的较为 优选的材料。
如图 4-6详细所示， 根据本发明， 阀杆主体部形成有两个环形凹槽 33 , 用以装设 0形环。需要说明的是， 阀杆主体部也可以只形成有一个环形凹槽， 或形成有两个以上的环形凹槽。
阀杆主体部的上部台肩 36的环形表面不与阀杆轴线相垂直，其为一截锥 形表面， 与和阀杆轴线相垂直的平面之间形成一锐角 α ΐ ; 换句话说， 阀杆主 体部的上部台肩 36的环形表面在附图中自径向内侧到径向外侧向下倾斜。
类似地， 阀杆主体部的下部台肩 35的环形表面不与阀杆轴线相垂直，其 为一截锥形表面，与和阀杆轴线相垂直的平面之间形成一锐角 β ΐ ;换句话说， 阀杆主体部的下部台肩 35 的环形表面在附图中自径向内侧到径向外侧向上 倾斜。
请参见图 7, 其是导向环 2的轴向剖面视图。 如图 7所示， 导向环 2的 一轴向端面 25不与导向环 1的轴线相垂直，而是与和导向环 1轴线相垂直的 平面之间形成一锐角 α 2或 β 2。
优选地， αΐ与 α2取值彼此基本相等， β 1与 β 2取值彼此基本相等。 考虑到加工误差等因素，也可以将角度 α 2设计为稍大于 α 1,例如 α 2= α 1+2 。 ； 以及类似地， 可以将角度 β 2设计为稍大于 β ΐ, 例如 β 2= β 1+2° 。 在 一般情况下， 可以将 α ( α1与 α2)与 β ( β 1与 β 2)设计为取值彼此基本 相等； 但也可以根据设计的不同要求， 将 α ( αΐ与 α2)与 β ( β ΐ与 β 2) 设计为： α ( αΐ与 α2)与 β ( β ΐ与 β 2)取值彼此不等。
就确保阀杆于外伸套筒的孔 21中的自动对中而言，角度 α或 β的取值范 围并不受到特别的限制。 但为了确保导向环在受到轴向压力作用时， 能够沿 阀杆主体部台肩的环形表面径向向外滑动进而实现可靠的动态密封效果， 角 度 α或 β的取值范围就要受到一定的限制， 理论上 α或 β至少应大于摩擦角 即自锁角， 这一点是业内人士所熟知的， 因此这里不做进一步详细的说明。
此外， 如业内人士所熟知的， 摩擦角或自锁角因摩擦副材料的摩擦系数 的不同而不同。 因此， 当用以制造导向环和阀杆的材料不同时， 摩擦角或自 锁角也会不同； 相应地， 用于确保导向环在受到轴向压力作用时能够沿阀杆 主体部台肩的环形表面径向向外滑动的角度 α或 β的取值范围也会不同。 此 夕卜， 角度 α或 β的取值可以根据导向环压缩空间的大小以及导向环的轴向初 始压缩量进行选定。 因此， 就导向环能够径向向外滑动以实现可靠的动态密 封效果而言， 角度 α或 β的取值范围并没有特别的限制， 但需大于摩擦角或 自锁角。
请参见图 4, 在组装状态下， 上部导向环 2的倾斜端面 25与阀杆主体部 的上部台肩 36的环形表面彼此贴合， 而下部导向环 1的倾斜端面 25与阀杆 主体部的下部台肩 35的环形表面彼此贴合。 在外伸套筒的延伸部 22向内弯 折并压靠于垫片 4时， 上部和下部导向环 2受到轴向压缩， 使得上部导向环 2的倾斜端面靠压于阀杆主体部的上部台肩 36的环形表面，并使得下部导向 环 2的倾斜端面靠压于阀杆主体部的下部台肩 35的环形表面。
下面参照图 6详细说明由导向环 1实现的动态密封原理和效果。 图 6是 本发明密封结构的局部剖面视图， 其图示了本发明导向环的密封原理。 如图 6详细所示，通过将外伸套筒的延伸部 22向内弯折而压靠于垫片 4 , 使得垫片 4相对于外伸套筒保持固定； 同时，在外伸套筒的延伸部 22向内弯 折并压靠于垫片 4时，压力 F1作用于垫片 4上， 而垫片 4又将压力传递到上 部导向环 1使之承受轴向力 F2;类似地，下部导向环 1也承受轴向力的作用。 由于该轴向力， 一方面， 上部和下部导向环 2均受到轴向压缩， 使得导向环 2的倾斜端面分别压靠于阀杆主体部的上部和下部台肩 36和 35的环形表面； 另一方面， 上部和下部导向环 1分别沿阀杆主体部的上部和下部台肩 36和 35的环形表面径向向外滑动，使得导向环 2的径向外表面压靠于外伸套筒的 内壁。 于是， 在导向环 2的径向外表面与倾斜端面处形成两个密封表面 （另 请参见图 5B ), 实现了阀杆与外伸套筒内壁之间的密封。
在组装状态下， 导向环 2的初始压缩量 H可根据实际应用场合确定， 或 者另外可通过实验加以确定。
在操作期间， 当由于阀杆 3在外伸套筒的孔中的旋转， 导向环 2的轴向 表面或径向表面产生磨损时，磨损量由导向环的初始压缩量以及 /或者导向环 2相对于阀杆的径向外移来补偿， 因此获得了可靠的动态密封效果。
此外， 由于上部和下部导向环的密封作用， 降低了 0形环轴向两侧的压 力差， 由此避免或减小了 0形环剪切的发生， 进而提高了 0形环的寿命并从 而改善了静态密封效果。
如上所述， 釆用本发明的密封结构， 通过利用轴肩以及导向环的斜面属 性， 一方面实现了良好的动态密封效果， 另一方面确保了阀杆于外伸套筒的 孔 21中的自动对中。且根据本发明， 可对导向环预压缩量进行可控调节， 由 此来调整动态密封的运作寿命。
此外， 釆用本发明的密封结构， 密封效果可以随着压力流体系统中流体 压力的变化而进行自适应调节。 如图 4所示， 当流体压力变大时， 上部导向 环 2进一步受到压缩。 作为其结果， 上部导向环 2的倾斜端面更紧密地压靠 于阀杆主体部的上部台肩 36的环形表面，以及导向环 2的径向外表面更紧密 地压靠于外伸套筒的内壁， 从而导向环 2能够相对于流体压力提供成比例的 泄漏防护。
此外， 由于上部和下部导向环的密封作用， 降低了 0形环轴向两侧的压 力差， 由此辅助静态密封性能。 因此， 在不增加成本的情况下， 可提高动态 密封性能和静态密封性能两者， 同时提高了密封的运作寿命。 以上结合附图和实施例对本发明进行了说明， 但本领域技术人员应当理 解， 上述实施例仅是例示性的而非限制性的， 在不背离本发明的精神和范围 的条件下， 可对上述实施例作出种种改进。
在上面的实施例中， 具有本发明结构的导向环 2设置在阀杆主体部的轴 向两端处， 作为一种可供选择的方案， 也可仅在在阀杆主体部的一个轴向端 处设置具有本发明结构的导向环 2。
此外， 在上面的实施例中， 密封结构还包括阀帽 5以及阀帽密封件 6以 提供附加密封保护。 但该附加密封保护并非是必须的， 其可以根据实际应用 场合进行选用。
此外， 阀杆主体部的上部和下部台肩 35、 36的环形表面相对于与阀杆轴 线相垂直的平面所形成的角度 o l与 β 1 , 以及类似地， 导向环 2的轴向端面 相对于与导向环轴线相垂直的平面之间所形成的角度 o 2或 β 2 ,不局限于某 一特定的数值， 而是可以根据实际应用场合选用， 只要能够实现如上所述的 预期功能即可。
此外， 虽然角度 α ΐ以及 /或者 α 2与 β ΐ以及 /或者 β 2设计成当导向环 受到轴向压力时能够相对于阀杆径向向外移动是优选的方案， 但这不是实现 发明目的所必需的。

Claims

权利要求
1. 一种密封装置， 包括：
第一部件， 该第一部件形成有孔；
第二部件， 该第二部件装设于第一部件的所述孔中并可相对于所述第一 部件转动，且该第二部件形成有两个轴向彼此间隔开的第一轴肩和第二轴肩， 并在其外周面上形成有位于所述第一轴肩和第二轴肩之间的至少一个环槽； 0形环， 该 0形环设置在所述第二部件的所述环槽中；
第一导向环以及第二导向环； 以及
第一止挡件和第二止挡件， 所述第一止挡件和第二止挡件或是与所述第 一部件一体形成或是相对于所述第一部件保持固定；
其中， 所述第二部件利用所述第一止挡件和第二止挡件相对于所述第一 部件轴向定位， 所述第一导向环位于所述第一轴肩与第一止挡件之间， 而所 述第二导向环位于所述第二轴肩与第二止挡件之间，
其特征在于，
所述第一轴肩的环形表面是截锥形表面， 而所述第一导向环的与所述第 一轴肩相对的轴向端面形成为与所述第一轴肩的截锥形表面相适配的截锥形 表面， 使得所述第一导向环在承受轴向压力时倾向于径向向外滑动；
其中， 所述第一导向环由具有弹性和密封功能的材料制成， 在所述密封 装置的组装状态下， 所述第一导向环承受轴向压力并产生预定的压缩量。
2. 如权利要求 1 所述的密封装置， 其特征在于， 所述第二轴肩的环形 表面是截锥形表面， 而所述第二导向环的与所述第二轴肩相对的轴向端面形 成为与所述第二轴肩的截锥形表面相适配的截锥形表面， 使得所述第二导向 环在承受轴向压力时倾向于径向向外滑动。
3. 如权利要求 2 所述的密封装置， 其特征在于， 所述第二导向环由具 有弹性和密封功能的材料制成， 在所述密封装置的组装状态下， 所述第二导 向环承受轴向压力并产生预定的压缩量。
4. 如权利要求 1-3 中任何一项所述的密封装置， 其特征在于， 所述第 二部件在其外周面上形成有位于所述第一轴肩和第二轴肩之间的两个环槽， 每个环槽设置有一个 0形环。
5. 如权利要求 4所述的密封装置， 其特征在于， 所述 0形环由 CR橡胶 制成。
6. 如权利要求 1所述的密封装置，其特征在于，所述第一导向环由 PTFE 制成。
7. 如权利要求 3所述的密封装置，其特征在于，所述第二导向环由 PTFE 制成。
8. 如权利要求 1-3 中任何一项所述的密封装置， 其特征在于， 所述第 一止挡件和第二止挡件中的一个止挡件包括垫片， 而所述第一部件包括壁厚 减薄的轴向延伸部， 在密封装置的组装状态下， 该轴向延伸部径向向内弯折 并压靠于所述垫片将所述垫片固定； 所述第一止挡件和第二止挡件中的另一 个止挡件由从所述第一部件径向向内伸出的突缘形成。
9. 如权利要求 1-3 中任何一项所述的密封装置， 其特征在于， 还包括 帽， 该帽上形成有内螺紋， 而所述第一部件上形成有外螺紋， 所述帽借助于 螺紋连接连接于所述第一部件，且密封件设置在所述帽与所述第一部件之间。
10. 如权利要求 1-3中任何一项所述的密封装置， 其特征在于， 所述第 一导向环在承受轴向压力时能够径向向外滑动。
11. 如权利要求 3所述的密封装置， 其特征在于， 所述第二导向环在承 受轴向压力时能够径向向外滑动。
12. 如权利要求 1或 3所述的密封装置， 其特征在于， 所述第一导向环 和所述第二导向环在承受轴向压力时能够径向向外滑动。
1 3. 一种阀， 包括：
阀体， 该阀体限定一阀腔；
设置在所述阀腔中的启闭件；
阀杆， 与所述启闭件操作连接并用以转动所述启闭件； 以及
如权利要求 1-12中任何一项所述的密封装置；
其中所述阀体包括自阀体延伸出的外伸套筒， 该外伸套筒用作所述第一 部件， 而所述阃杆用作所述第二部件。
14. 如权利要求 1 3所述的阀， 其特征在于， 所述阀是球阀。
PCT/CN2009/074914 2009-01-22 2009-11-12 密封装置和阀 WO2010083696A1 (zh)

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