[go: up one dir, main page]

WO2011134400A1 - 一种双向压力自平衡截止阀 - Google Patents

一种双向压力自平衡截止阀 Download PDF

Info

Publication number
WO2011134400A1
WO2011134400A1 PCT/CN2011/073379 CN2011073379W WO2011134400A1 WO 2011134400 A1 WO2011134400 A1 WO 2011134400A1 CN 2011073379 W CN2011073379 W CN 2011073379W WO 2011134400 A1 WO2011134400 A1 WO 2011134400A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
ring
sealing
balancing
pressure
Prior art date
Application number
PCT/CN2011/073379
Other languages
English (en)
French (fr)
Inventor
周君
Original Assignee
南京理工大学
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.)
Filing date
Publication date
Application filed by 南京理工大学 filed Critical 南京理工大学
Priority to EP11774391.4A priority Critical patent/EP2565500B1/en
Priority to RU2012146416/06A priority patent/RU2559216C2/ru
Priority to US13/515,279 priority patent/US8794592B2/en
Priority to BR112012026754A priority patent/BR112012026754A2/pt
Publication of WO2011134400A1 publication Critical patent/WO2011134400A1/zh

Links

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
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/02—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with screw-spindle
    • F16K1/06—Special arrangements for improving the flow, e.g. special shape of passages or casings
    • F16K1/08—Special arrangements for improving the flow, e.g. special shape of passages or casings in which the spindle is perpendicular to the general direction of flow
    • 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
    • F16J15/18—Sealings between relatively-moving surfaces with stuffing-boxes for elastic or plastic packings
    • F16J15/184—Tightening mechanisms
    • 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
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/02—Construction of housing; Use of materials therefor of lift valves
    • 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
    • F16K39/00—Devices for relieving the pressure on the sealing faces
    • F16K39/02—Devices for relieving the pressure on the sealing faces for lift valves
    • F16K39/022—Devices for relieving the pressure on the sealing faces for lift valves using balancing surfaces
    • 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
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/04—Means in valves for absorbing fluid energy for decreasing pressure or noise level, the throttle being incorporated in the closure member
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7904—Reciprocating valves

Definitions

  • This invention relates to a valve, and more particularly to a two-way pressure self-balancing shut-off valve for use in a high temperature, high pressure or corrosive environment as a conduit for shutting off or switching a bidirectional flow medium.
  • Valves are indispensable important mechanical products in petrochemical, oilfield, metallurgical, thermal power plants and other pressure pipelines. Due to the use of existing valve technology products, it is necessary to overcome the medium pressure on the opening and closing parts to open and close the valve. When the valve is used When high temperature, high pressure and large diameter pipes are used, the medium pressure not only causes the valve to operate very much, but also easily causes damage and leakage of the valve sealing surface.
  • the pressure self-balancing valve can self-balance the pressure of the medium acting on the opening and closing member through the pressure self-balancing principle, thereby fundamentally eliminating the influence of the medium pressure on the valve operating performance, sealing quality and sealing life.
  • the pressure self-balancing valve has become an important way to transform and upgrade existing valve products, and the key technology to realize the pressure self-balancing stop valve is the sealing of the pressure self-balancing structure.
  • the existing sealing technology of the pressure self-balancing structure is usually sealed by a sealing ring of type "0" or "Y", because the sealing of the sealing ring is self-sealing depending on the pressure of the medium itself.
  • the degree of sealing of the ring is independent of the pressure of the medium, and it is also independent of the size of the sealing pre-tightening force when the sealing ring is installed.
  • the degree of sealing does not change with the decrease of the sealing pre-tightening force after the sealing ring wears, so it has a durable and reliable sealing quality. And seal life. Since the seals such as the "0" type and the "Y" type must be made of a high-density elastic material, the materials that can be used for the production of the "0" type, "Y” type seals, etc. are all rubbers that are not resistant to high temperatures. Plastic and other materials. Due to the limitation of the material of the sealing ring, the applicable temperature of the pressure self-balancing stop valve has been limited to below 20 CTC, and it cannot be used for a high-temperature pressure pipe with a large surface area.
  • flexible graphite is a loose, low-density, high-temperature material that operates under high temperature, high pressure or radiation conditions without decomposition, deformation or aging, and is chemically stable. It is commonly used as a sealing filler for high temperature rods. Since flexible graphite is not a high-density sealing material, it is not suitable for making sealing rings of type "0" and "Y".
  • the inventor's patent application in 2003 (CN 2637835Y) is a high-temperature resistant self-balancing shut-off valve.
  • the high-temperature resistant flexible graphite is used as a sealing material in a self-balancing shut-off valve to solve the problem of high temperature resistance of the sealing material.
  • the valve is made of a high-temperature sealing material such as flexible graphite to make a seal ring, and is set by The method of pressing the sealing ring to compensate for the low density problem of the high temperature resistant sealing material realizes the sealing of the sealing ring to the outer circle of the valve disc and the valve body.
  • Liu Wang has disclosed a new type of shut-off valve and disclosed the following technical features (see Fertilizer Industry, No. 2, 1989, page 39, right column, line 11 to 24) Line, new structure stop valve schematic):
  • the valve is provided with packing gland, packing and gasket from top to bottom.
  • the packing gland and the gasket can be used to squeeze the packing by tightening the hand wheel of the valve.
  • the contact surface of the packing gland and the packing is spherical, so that the sealing degree is greatly improved, and the spherical surface can also compensate the wear of the upper part of the packing at any time.
  • the packing is applied to the packing by the packing gland to obtain the sealing of the plug part of the valve head, and the packing head to the valve head is strengthened by using the contact surface of the packing gland and the packing as a spherical surface.
  • the pressing force of the rod portion further improves the sealing of the inner circumference of the packing to the stem portion of the valve head.
  • the sealing of the valve head depends not only on the sealing of the inner circle of the packing on the stem of the valve head, but also on the sealing between the outer circle of the packing and the stuffing box. The wear of the inner circle will inevitably lead to the decrease of the sealing pre-tightening force inside and outside the packing.
  • the object of the present invention is to provide a two-way pressure self-balancing shut-off valve capable of achieving high temperature, high pressure, and corrosion resistance with a long service life in view of the deficiencies of the prior art.
  • the bidirectional pressure self-balancing stop valve of the present invention comprises a valve body, a valve flap, a pressure ring, a valve cover, a valve stem and a balance hole; the valve flap is disposed in a cavity of the valve body; a pressure ring is disposed on the upper portion of the cavity of the valve body by a threaded connection; the valve cover is fixedly coupled with the valve body; the valve stem passes through the valve cover, and a lower end portion thereof is movably coupled to the valve flap; a ring-shaped groove formed between the outer circumference of the valve flap and the pressure ring and the valve body is provided with a composite sealing ring resistant to high temperature or corrosion, and the composite sealing ring includes an upper gasket from top to bottom.
  • upper seal ring, upper spacer ring, blocking ring, lower spacer ring, lower seal ring and lower The upper seal ring and the lower seal ring are made of a high temperature or corrosion resistant sealing material, and the upper gasket, the upper spacer ring, the lower spacer ring and the lower gasket are made of a high temperature or corrosion resistant rigid material.
  • the lower end surface of the upper washer and the upper end surface of the upper spacer are shaped to press the conical surface, the inclined surface or the spherical surface of the upper sealing ring toward the inner direction of the valve flap;
  • the lower end surface of the upper spacer and the upper end surface of the lower spacer are shaped to press a cylindrical surface, a conical surface, a slope surface or a spherical surface of the blocking ring toward the outer surface of the valve;
  • an upper end surface of the lower gasket is shaped to press a conical surface, a slope surface or a spherical surface of the lower seal ring in a valve inner direction.
  • the upper washer and the upper spacer jointly press the upper seal ring inwardly, and obtain a larger sealing pre-tightening force on the inner circular surface of the upper seal ring than the outer circumferential surface; similarly, by tightening
  • the pressure ring causes the lower spacer and the lower gasket to jointly press the lower sealing ring inwardly, and obtains a larger sealing pre-tightening force on the inner circular surface of the lower sealing ring than the outer circumferential surface, by being disposed on the upper and lower spacers A blocking passage between the outer ring surface of the upper seal ring and the outer circumferential surface of the lower seal ring.
  • the high temperature resistant sealing material of the present invention is preferably a flexible graphite material, and the corrosion resistant sealing material is preferably a polytetrafluoroethylene material.
  • the rigid material can be a metal material or a ceramic material, or any other rigid material capable of achieving the object of the invention.
  • the upper gasket and the pressure ring of the present invention can be made as two separate parts, or can be made into the same part, and it is preferable to make two separate parts.
  • the balance hole may be disposed on the valve flap or the valve stem.
  • the blocking ring plays a vital role in the structure of the present invention, and functions to block the medium from continuing downward or upward along the outer circumferential surface of the upper or lower sealing ring, when a blocking ring made of a sealing material such as flexible graphite is used.
  • a blocking ring made of a sealing material such as flexible graphite is used.
  • the cross-sectional shape is an isosceles trapezoid, by setting the angle between the waist and the outer circumference of the valve disc, the shape of the lower end surface of the upper spacer ring and the upper end surface of the lower spacer ring can be conveniently oriented.
  • the pressure self-sealing structure of the bidirectional pressure self-balancing stop valve of the invention makes use of a low density, high temperature resistant or corrosion resistant sealing material, such as flexible graphite, etc. It can obtain pressure self-sealing characteristics similar to "0" type and "Y" type sealing ring, which has long-lasting and reliable sealing quality and sealing life. It fundamentally solves the problem that the pressure self-balancing stop valve can not be used in high temperature medium environment.
  • the technical problem makes the product of the invention suitable for the cutting or opening of the high temperature and high pressure pipelines of the bidirectional flow medium above 650 ° C; at the same time, the corrosion resistant sealing material, such as Teflon, can also obtain the pressure self-sealing.
  • the characteristics are applicable to a variety of corrosive medium environments.
  • the bidirectional pressure self-balancing stop valve of the invention makes the pressure of the medium on the valve disc self-balance, and the valve operation is very easy, which not only reduces the manual labor intensity of the manual valve. And significantly reduce the energy consumption of the auxiliary devices of electric and pneumatic valves, and greatly widened the cut
  • the valve is applied to the large-diameter high-temperature high-pressure pipeline with two-way flow; 3.
  • the invention expands The high-temperature application field of the pressure self-balancing valve can solve the safety in the practical application of the valve.
  • High-pressure valve that must be configured before the high-pressure water pump for water supply to boilers, mines, oil wells, etc. When the water pump is supplied with water, the valve needs to be opened. The water supply pipeline is unobstructed, and when the water pump stops supplying water, it is necessary to close the valve to prevent the backflow of the supplied high-pressure water.
  • the high-temperature and high-pressure steam generated by the multiple boilers are respectively sent to the common mother pipe through the high-pressure valve.
  • pipeline systems such as petrochemical, oilfield, metallurgy or power plants generally have a large number of bi-directional high-temperature and high-pressure pipelines.
  • the invention has passed a large number of two-way high temperature and high pressure sealing performance and reliability experiments, The practical application test of the high temperature and high pressure pipeline shows that the invention has obvious technical advantages compared with the existing valve and has a very broad application prospect.
  • FIG. 1 is a schematic structural view of a bidirectional pressure self-balancing stop valve according to the present invention.
  • Figure 2 is a partial enlarged view of Figure 1.
  • Figure 3 is a schematic view of the pressing force when the upper seal ring is pre-tensioned.
  • Figure 4 is a schematic diagram of the self-sealing force of the upper seal ring against the pressure of the valve flap.
  • the bidirectional pressure self-balancing stop valve of the present invention includes a valve body
  • the first sealing surface 2 sealed with the valve flap 4 is shaped like a flat surface, a conical surface or a spherical surface; the valve flap 4 is disposed in the cavity of the valve body 1; and the lower end surface 35 of the valve flap 4 is provided a second sealing surface 33 sealed with the valve body 1 in the shape of a flat surface, a conical surface or a spherical surface; the pressure ring 16 is disposed on the upper portion of the cavity of the valve body 1 by screwing; the valve cover 17 and The valve body 1 is fixedly coupled; the valve stem 19 passes through the valve cover 17, and the lower end portion thereof is movably coupled to the valve flap 4, and the valve stem 19 can carry the valve flap 4 in the cavity of the valve body 1 Moving, forming the opening or closing of the present
  • the blocking ring 11, the lower spacer 10, the lower sealing ring 8 and the lower gasket 7; the upper sealing ring 13 and the lower sealing ring 8 are made of a sealing material, and different sealing materials can be used as needed, in this embodiment
  • the sealing material used is flexible graphite;
  • the blocking ring 11 is also made of flexible graphite, the section of which is an isosceles trapezoid, and the angle between the waist and the outer circumference of the valve disc is 45 °; 14.
  • the upper spacer 12, the lower spacer 10 and the lower washer 7 are made of a metal material, and cooperate with the outer circle of the valve flap 4; the lower end surface 22 of the upper washer 14 and the upper spacer 12
  • the shape of the upper end surface 25 is a conical surface, a slope surface or a spherical surface that presses the upper seal ring 13 toward the inner direction of the valve flap; the shape of the lower end surface 26 of the upper spacer ring 12 and the upper end surface 28 of the lower spacer ring 10 Squeezing the block to the outside of the valve body a conical, beveled or spherical surface of the ring 11; the lower spacer
  • the lower end surface 29 of the 10 and the upper end surface 32 of the lower gasket 7 are shaped to press the conical surface, the inclined surface or the spherical surface of the lower sealing ring 8 in the valve inner direction.
  • the upper washer 14 and the upper spacer 12 collectively press the upper seal ring 13 inwardly, and the upper spacer ring 12 and the lower spacer ring 10 outwardly press the blocking ring 11, the lower spacer 10 and the lower washer 7
  • the inner sealing ring 8 is pressed inwardly, and a larger sealing pre-tightening force is obtained on the inner circular surface 24 of the upper sealing ring 13 than that of the outer circular surface 23.
  • the force diagram of the upper sealing ring 13 is as shown in FIG.
  • the upper washer 14 and the pressure ring 16 can be made into two separate parts or combined into one part.
  • the working principle of the present invention is as follows: After the shut-off valve of the present invention is coupled with the pressure pipe, when the shut-off valve is in the closed state, the lower end surface of the valve flap and the upper end surface of the valve body are tightly pressed to form a seal under the push of the valve stem.
  • the pressure self-balancing principle of the medium is as follows: If the medium enters from the lower passage, the medium pressure acts on the lower end surface of the valve flap, and is transmitted to the valve body and the bonnet coupling cavity through the balance hole provided on the valve flap or the valve stem.
  • valve flap Acting on the upper end surface of the valve flap, forming a pair of axial forces in opposite directions and canceling each other in the axial direction of the valve flap, thereby realizing the pressure self-balancing of the medium to the valve flap; if the medium enters from the upper passage, the medium pressure acts on Radial forces that cancel each other are formed on the outer circumferential surface of the valve flap, and the pressure self-balancing of the medium to the valve flap is achieved.
  • the pressure medium passes through the valve flap Or the balance hole provided on the valve stem is transmitted to the valve body and the valve cover coupling cavity, and then penetrates into the outer circumferential surface of the upper sealing ring with a small pre-tightening force along the gap between the upper washer and the valve flap, due to the set blocking ring
  • the passage of the medium along the outer circumferential surface of the upper sealing ring is blocked, and the pressure medium penetrating the outer circumferential surface of the upper sealing ring is pressed against the outer circumferential surface of the upper sealing ring, forcing the inner circular surface of the upper sealing ring and
  • the outer circumference of the valve flap is further adhered to form a self-sealing of the pressure of the upper sealing ring against the valve flap.
  • the sealing force of the inner circular surface of the upper sealing ring on the outer circumferential surface of the valve flap is mainly formed by the medium pressure on the outer circumferential surface of the upper sealing ring, and then on the inner circular surface of the upper sealing ring and outside the valve flap
  • the medium is tightly formed on the circle, because the medium adhesion force is the self-sealing force formed by the medium pressure itself, and is more reliable as the medium pressure increases, and the degree of sealing is not only independent of the medium pressure, but also
  • the inner circular surface of the upper sealing ring has nothing to do with the sealing pre-tightening force of the outer circumference of the valve disc, and solves the key technology of the medium pressure self-sealing by using the high temperature resistant material, and also realizes the outer ring surface of the valve disc despite the upper sealing ring.
  • the wear of the inner circular surface may result in a decrease in the sealing pre-tightening force of the present invention, but does not cause a decrease in the degree of sealing of the present invention, and the wear automatic compensation function of the present invention is only used to provide continuous sealing pre-tightening. force. Therefore, the present invention does not achieve sealing by simply arranging the parts and the sealing member, and the present invention only needs to obtain a far distance on the inner circular surface of the upper sealing ring and the outer circumferential surface of the valve flap by appropriately tightening the pressing ring. Less than The pre-tightening force of the pressure can achieve a long-lasting and reliable sealing quality and sealing life.
  • the medium penetrates into the outer circumferential surface of the lower sealing ring with a small pre-tightening force along the gap between the lower gasket and the valve body, and the penetrating groove is blocked by the passage of the medium along the outer circumferential surface of the lower sealing ring.
  • the pressure medium on the outer circumferential surface of the lower sealing ring presses against the outer circumferential surface of the lower sealing ring, forcing the inner circular surface of the lower sealing ring to further adhere to the outer circumference of the valve flap, thereby forming the pressure of the lower sealing ring against the valve flap Self-sealing.
  • Test valve diameter DN100mm, valve pressure PN32.0MPa;
  • Test valve diameter DN100mm, valve pressure PN32.0MPa;

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Valves (AREA)
  • Lift Valve (AREA)
  • Safety Valves (AREA)
  • Sliding Valves (AREA)
  • Taps Or Cocks (AREA)

Description

一种双向压力自平衡截止阀 技术领域
本发明涉及一种阀门， 尤其涉及一种适用于高温、 高压或腐蚀环境下， 作为 截断或接通双向流动介质管道的双向压力自平衡截止阀。
背景技术
阀门是石化、 油田、 冶金、 热电厂等压力管道上不可缺少的重要机械产品， 由于现有阀门技术产品的使用过程中，必须克服启闭件上承受的介质压力才能启 闭阀门， 当阀门用于高温、 高压和大通径管道时， 介质压力不仅造成阀门的操作 力非常大， 也极易造成阀门密封面的损伤和泄漏。
压力自平衡阀能够通过压力自平衡原理，使作用在启闭件上的介质压力自平 衡， 从而从根本上消除介质压力对阀门操作性能、密封质量及密封寿命等方面的 影响。压力自平衡阀已成为现有阀门产品转型升级的重要途径， 而实现压力自平 衡截止阀的关键技术是对压力自平衡结构的密封。现有的压力自平衡结构的密封 技术通常采用 "0"型、 "Y"型等密封圈进行密封， 由于该类密封圈的密封依 赖于介质自身压力对密封圈形成的压力自密封，使得密封圈的密封程度与介质压 力的高低无关， 也与安装密封圈时的密封预紧力的大小无关，其密封程度不随密 封圈磨损后密封预紧力的下降而改变， 因此具有持久可靠的密封质量和密封寿 命。 由于 "0"型、 "Y"型等密封圈必须采用高密度的弹性材料制成， 目前能够 用于制作 "0"型、 "Y"型等密封圈的材料均为不耐高温的橡胶、 塑料等材料。 由于密封圈材料的限制， 迄今压力自平衡截止阀的适用温度仍限制在 20CTC以 下， 无法用于面广量大的高温压力管道。
研究发现， 一些低密度的密封材料具有耐高温、 耐腐蚀的性能。 例如， 柔性 石墨就是一种松散的低密度耐高温材料， 在高温、 高压或辐射条件下工作， 不发 生分解， 变形或老化， 化学性质稳定， 通常用于高温杆件的密封填料。 由于柔性 石墨不是高密度密封材料， 因此不适用于制作 "0"型、 "Y"型等密封圈。 发明 人在 2003年申请的专利 （CN 2637835Y) 可耐高温的压力自平衡截止阀中， 将 耐高温的柔性石墨作为密封材料应用于自平衡截止阀，解决密封材料耐高温的问 题。在该专利中， 阀门采用柔性石墨等耐高温密封材料制作密封圈， 并通过设置 压环压紧密封圈的方法来弥补该类耐高温密封材料的低密度问题，实现密封圈对 阀瓣外圆与阀体之间的密封。但是， 该结构中由于密封结构不具备压力自密封特 性， 密封圈对阀瓣的密封程度完全依赖于压环对密封圈压紧后产生的密封预紧 力，使用过程中其密封程度会随着阀瓣对密封圈的磨损而下降， 因此该专利的密 封寿命还不能满足实际应用要求。
为了提高柔性石墨填料的应用效果， 刘望有曾公开了一种新型结构的截止 阀， 并公开了以下技术特征 （参见化肥工业， 1989年第 2期第 39页右栏第 11 行至第 24行，新结构截止阀示意图）： 阀门中自上而下依次设有填料压盖、填料、 垫片，可以通过旋紧阀门的手轮使得填料压盖和垫片共同挤压填料。填料压盖与 填料的接触面是球面的，使密封度大大提高，球面的作用还能使填料上部的磨损 随时得以补偿。该文章中提到， 是通过设置填料压盖对填料施加压紧力， 来获得 填料对阀头杆部的密封， 并通过采用填料压盖与填料的接触面为球面， 来增强填 料对阀头杆部的压紧力， 从而进一步提高填料内圆对阀头杆部的密封。但实际应 用中， 对阀头的密封， 不仅取决于填料内圆对阀头杆部的密封， 还取决于填料外 圆与填料函之间的密封， 随着使用过程中阀头杆部对填料内圆的磨损， 必然导致 填料内、外圆的密封预紧力随之下降， 当密封预紧力低于介质压力时， 泄漏随即 发生在密封预紧力相对较低的填料的外圆与填料函之间，并沿填料压盖的外圆与 填料函之间流出。该文章中也提到： "填料有的一二个月都不用压紧"， 由此可见 该文中所提到的截止阀不仅密封寿命短，而且必须多次和及时的压紧填料才能保 持对阀头的密封， 该文章中公开的技术方案根本不适用压力自平衡阀的密封环 境。 发明内容
发明目的： 本发明的目的在于针对现有技术的不足， 提供一种使用寿命长 的能够实现耐高温高压、 耐腐蚀的双向压力自平衡截止阀。
技术方案： 本发明所述的双向压力自平衡截止阀， 包括阀体、 阀瓣、 压环、 阀盖、 阀杆和平衡孔； 所述阀瓣设置在所述阀体的腔体内； 所述压环通过螺纹联 接设置在所述阀体的腔体上部； 所述阀盖与所述阀体固定联接； 所述阀杆穿过所 述阀盖，其下端部与所述阀瓣活动联接； 所述阀瓣的外圆与所述压环以及所述阀 体之间构成的环形沟槽内设置有耐高温或耐腐蚀的复合密封圈，所述复合密封圈 自上而下依次包括上垫圈、 上密封圈、 上隔环、 阻断圈、 下隔环、 下密封圈和下 垫圈； 所述上密封圈和下密封圈采用耐高温或耐腐蚀的密封材料制成， 所述上垫 圈、 上隔环、 下隔环和下垫圈采用耐高温或耐腐蚀的刚性材料制成， 与所述阀瓣 的外圆间隙配合；所述上垫圈的下端面和所述上隔环的上端面的形状为向阀瓣内 方向挤压所述上密封圈的圆锥面、斜面或球面； 所述上隔环的下端面和所述下隔 环的上端面的形状为向阀体外方向挤压所述阻断圈的圆柱面、 圆锥面、斜面或球 面；所述下隔环的下端面和所述下垫圈的上端面的形状为向阀瓣内方向挤压所述 下密封圈的圆锥面、 斜面或球面。
通过旋紧压环使得上垫圈和上隔环共同向内挤压上密封圈，并在上密封圈的 内圆表面获得较其外圆表面更大的密封预紧力； 同理，通过旋紧压环使得下隔环 和下垫圈共同向内挤压下密封圈，并在下密封圈的内圆表面获得较其外圆表面更 大的密封预紧力，通过设置在上隔环与下隔环之间的阻断圈， 阻断上密封圈外圆 表面与下密封圈外圆表面的介质通道。
本发明所述耐高温密封材料优选为柔性石墨材料，耐腐蚀密封材料优选为聚 四氟乙烯材料， 随着科技的进步， 越来越多的密封材料被发现、 被合成， 任何具 有耐高温或耐腐蚀或其他的功能的密封材料都能采用本发明结构，实现自密封效 果； 所述刚性材料可以为金属材料或陶瓷材料， 也可以为其他任何能够实现发明 目的的刚性材料。
本发明所述上垫圈和所述压环可以分别制成两个独立的零件，也可以制成同 一个零件， 比较优选为制成两个单独的零件。
所述平衡孔可以设置在所述阀瓣或所述阀杆上。
阻断圈在本发明结构中具有至关重要的作用，起到阻断介质沿上或下密封圈 的外圆表面继续下或上行的作用， 当采用柔性石墨等密封材料制成的阻断圈， 其 截面形状为等腰梯形时，通过设定其腰与阀瓣外圆的夹角， 就能够方便的通过所 述上隔环的下端面和所述下隔环的上端面的形状为向阀体外方向挤压力， 实现 上、 下密封圈之间介质的阻断； 当采用金属材料制成的 "0"型空心密封圈作为 阻断圈时，即可以通过所述上隔环的下端面和所述下隔环的上端面的形状为向阀 体外方向挤压该密封圈， 实现上、 下密封圈之间介质的阻断， 也可以通过将该密 封圈直接设置在阀体与上隔环或下隔环的圆柱体之间， 实现上、下密封圈之间介 质的阻断， 但金属 "0"型空心密封圈的制作成本和安装成本较高。
阻断圈的实现方式可以多种多样，本发明提供两种比较优选的阻断方式， 第 一种为由柔性石墨等密封材料制成的截面为等腰梯形的密封圈，其腰与阀瓣外圆 的夹角为 45 ° ； 第二种为由金属材料制成的 "0"型空心密封圈。
本发明与现有技术相比， 其有益效果是： 1、 本发明双向压力自平衡截止阀 的压力自密封结构， 使得采用低密度、 耐高温或耐腐蚀的密封材料， 比如柔性石 墨等， 也能获得类似于 "0"型、 "Y"型密封圈的压力自密封特性， 使其具有持 久可靠的密封质量和密封寿命，从根本上解决了压力自平衡截止阀迄今无法用于 高温介质环境的技术难题， 使得本发明产品适用于 650°C以上双向流动介质的高 温、高压管道的截断或开启； 同时，采用耐腐蚀的密封材料， 比如聚四氟乙烯等， 也同样可以获得压力自密封特性， 并适用于多种腐蚀性的介质环境； 2、本发明 双向压力自平衡截止阀，使得阀瓣上承受的介质压力自平衡，阀门操作十分轻松， 不仅降低了手动阀门的人工操作劳动强度， 而且显著降低了电动、气动阀门的辅 助装置能耗， 还极大的拓宽了截止阀在双向流动的大通径高温高压管道上的应 用； 3、 采用不同材料制作， 可广泛适用于各种通径的单向或双向流动的高温、 高压及腐蚀性介质管道； 4、 本发明拓展了压力自平衡阀的高温应用领域， 能够 解决阀门实际应用中的安全性， 例如： 向锅炉、矿井、 油井等补水用的高压水泵 前必须配置的高压阀， 当水泵供水时， 需要开启阀门使供水管道通畅， 而当水泵 停止供水时， 又需关闭阀门防止所供高压水的倒流， 又如热电厂的发电过程中， 需将多个锅炉产生的高温高压蒸汽分别通过高压阀门送入共用母管中，当停止部 分锅炉供气时， 同样需要关闭阀门以防止高温高压蒸汽的回流； 实际应用中的石 化、油田、冶金或电厂等管道系统，一般都存在大量的双向流动的高温高压管道， 本发明已通过的大量双向高温高压密封性能及可靠性实验，以及高温高压管道的 实际应用试验表明，本发明与现有阀门相比具有十分明显的技术优势， 具有十分 广阔应用前景。
附图说明
图 1为本发明双向压力自平衡截止阀的结构示意图。
图 2为图 1的局部放大图。
图 3为上密封圈预紧时的受挤压力示意图。
图 4为上密封圈对阀瓣的压力自密封受力示意图。 具体实施方式 下面结合附图，对本发明技术方案进行详细说明，但是本发明的保护范围不 局限于所述实施例。
实施例： 如图 1、 图 2所示， 本发明所述双向压力自平衡截止阀， 包括阀体
1、 阀瓣 4、 压环 16、 阀盖 17、 阀杆 19和平衡孔 21 ; 阀体 1内设有上通道 3、 下通道 34及内通道 36， 在内通道 36的上端面上设有与所述阀瓣 4密封的第一 密封面 2， 其形状为平面、 圆锥面或球面； 所述阀瓣 4设置在所述阀体 1的腔体 内； 阀瓣 4的下端面 35上设有与所述阀体 1密封的第二密封面 33， 其形状为平 面、 圆锥面或球面； 所述压环 16通过螺纹联接设置在所述阀体 1的腔体上部； 所述阀盖 17与所述阀体 1固定联接； 所述阀杆 19穿过所述阀盖 17， 其下端部 与所述阀瓣 4活动联接， 阀杆 19可携带阀瓣 4在阀体 1腔体中作上下移动， 形 成本发明的开启或关闭； 所述平衡孔 21设置在所述阀瓣 4或所述阀杆 19上， 使 置于阀瓣 4下端面 35下方的阀体 1下通道 34与置于阀瓣 4上端面 20上方的阀 体 1、 阀盖 17联接腔 18沟通； 所述阀瓣 4的外圆与所述压环 16以及所述阀体 1 之间构成的环形沟槽内设置有耐高温或耐腐蚀的复合密封圈，所述复合密封圈自 上而下依次包括上垫圈 14、 上密封圈 13、 上隔环 12、 阻断圈 11、 下隔环 10、 下密封圈 8和下垫圈 7; 所述上密封圈 13、 下密封圈 8采用密封材料制成， 可以 根据需要采用不同的密封材料，本实施例为了达到耐高温的目的，采用的密封材 料为柔性石墨； 阻断圈 11也是采用柔性石墨制成， 其截面为等腰梯形， 其腰与 阀瓣外圆的夹角为 45 ° ； 所述上垫圈 14、 上隔环 12、 下隔环 10和下垫圈 7采 用金属材料制成， 与所述阀瓣 4 的外圆间隙配合； 所述上垫圈 14 的下端面 22 和所述上隔环 12的上端面 25的形状为向阀瓣内方向挤压所述上密封圈 13的圆 锥面、 斜面或球面； 所述上隔环 12的下端面 26和所述下隔环 10的上端面 28 的形状为向阀体外方向挤压所述阻断圈 11的圆锥面、 斜面或球面； 所述下隔环
10的下端面 29和所述下垫圈 7的上端面 32的形状为向阀瓣内方向挤压所述下 密封圈 8的圆锥面、 斜面或球面。
通过旋紧压环 16使得上垫圈 14和上隔环 12共同向内挤压上密封圈 13， 上 隔环 12及下隔环 10向外挤压阻断圈 11、 下隔环 10及下垫圈 7向内挤压下密封 圈 8， 并在上密封圈 13的内圆表面 24获得较其外圆表面 23更大的密封预紧力， 上密封圈 13的受力示意图如图 3所示。
同理，在下密封圈 8的内圆表面 31获得较其外圆表面 30更大的密封预紧力， 以及在阻断圈 11的外圆表面 27获得足够的密封阻断力； 通过设置在上隔环 12 与下隔环 10之间的阻断圈 11， 阻断上密封圈 13的外圆表面 23与下密封圈 8的 外圆表面 30的介质通道。
上垫圈 14与压环 16可分别制成两个独立的零件或合制成同一个零件。 本发明的工作原理如下： 本发明的截止阀与压力管道联接后， 当截止阀处于 关闭状态时， 在阀杆的推动下， 阀瓣下端面与阀体内通道上端面贴紧构成密封。 介质的压力自平衡原理为： 若介质从下通道进入时， 介质压力作用在阀瓣的下端 面的同时， 又通过阀瓣或阀杆上所设平衡孔传递至阀体、 阀盖联接腔并作用在阀 瓣的上端面， 沿阀瓣的轴向形成一对方向相反、相互抵消的轴向力， 实现了介质 对阀瓣的压力自平衡； 若介质从上通道进入时， 介质压力作用在阀瓣的外圆表面 上形成相互抵消的径向力， 实现了介质对阀瓣的压力自平衡。本发明处于开启状 态时， 在阀杆的拉动下， 阀瓣被提起直至完全开启阀门。
下面分两种情况来详细说明本发明截止阀密封圈的介质压力自密封原理： 一、 当压力介质从阀体下通道进入时， 介质压力自密封原理如图 4所示： 压力介质通过阀瓣或阀杆上所设平衡孔传递至阀体、 阀盖联接腔， 再沿上垫 圈与阀瓣之间的缝隙渗入预紧力较小的上密封圈的外圆表面，由于设置的阻断圈 阻断了介质沿上密封圈的外圆表面继续下行的通道，渗入上密封圈的外圆表面的 压力介质则对上密封圈的外圆表面形成挤压，迫使上密封圈的内圆表面与阀瓣的 外圆进一步贴紧， 构成上密封圈对阀瓣的压力自密封。
本发明上密封圈的内圆表面对阀瓣的外圆表面的密封力，主要是通过介质压 力在上密封圈的外圆表面形成挤压，进而在上密封圈的内圆表面与阀瓣外圆上形 成介质贴紧力， 由于该介质贴紧力是由介质压力自身形成的自密封力， 并随着介 质压力的升高而愈加可靠，其密封程度不仅与介质压力的高低无关，还与上密封 圈的内圆表面对阀瓣外圆的密封预紧力的大小无关，解决了利用耐高温材料进行 介质压力自密封的关键技术，也实现了尽管阀瓣的外圆表面对上密封圈的内圆表 面的磨损，会导致本发明密封预紧力的下降，但却不会导致本发明密封程度的下 降， 而本发明所具有的磨损自动补偿功能仅用于提供持续不断的密封预紧力。 因 此，本发明不是通过简单的设置零件与密封件进行挤压来实现密封，本发明只需 通过适当旋紧压环，在上密封圈的内圆表面与阀瓣的外圆表面上， 获得远小于介 质压力的密封预紧力， 就能得到持久可靠的密封质量和密封寿命。
二、 当压力介质从阀体上通道进入时， 介质压力自密封原理为：
介质沿下垫圈与阀体之间的缝隙渗入预紧力较小的下密封圈的外圆表面，由 于设置的阻断圈阻断了介质沿下密封圈的外圆表面继续上行的通道，渗入下密封 圈的外圆表面的压力介质则对下密封圈的外圆表面形成挤压，迫使下密封圈的内 圆表面与阀瓣的外圆进一步贴紧， 构成下密封圈对阀瓣的压力自密封。
下面通过进一步的具体实验数据来说明本发明产品稳定的性能：
( 1 ) 以下是本发明的双向压力自平衡截止阀与同参数现有截止阀的性能对
Figure imgf000009_0001
注： 1、 试验阀门： 通径 DN100mm、 阀门压力 PN32.0MPa;
2、 表中现有截止阀数据摘自 《实用阀门设计手册》 机械工业出版社陆 培文主编 2002.9;
(2) 密封及寿命试验
Figure imgf000009_0002
注： 1、 试验阀门： 通径 DN100mm、 阀门压力 PN32.0MPa;
2、于 2008年 10月 21 日通过《国家泵阀产品质量监督检测中心》检测。 如上所述，尽管参照特定的优选实施例已经表示和表述了本发明，但其不得 解释为对本发明自身的限制。在不脱离所附权利要求定义的本发明的精神和范围 前提下， 可对其在形式上和细节上作出各种变化。

Claims

1、 一种双向压力自平衡截止阀， 包括阀体（1 )、 阀瓣 （4)、 压环 （16)、 阀 盖 （17)、 阀杆 （19)和平衡孔 （21 ); 所述阀瓣 （4)设置在所述阀体 （1 ) 的腔 体内； 所述压环 （16) 设置在所述阀体 （1 ) 的腔体上部； 所述阀盖 （17) 与所 述阀体（1 ) 固定联接； 所述阀杆 （19) 穿过所述阀盖（17)， 其下端部与所述阀 瓣 （4) 活动联接； 所述阀瓣 （4) 的外圆与所述压环 （16) 以及所述阀体 （1 ) 之间构成的环形沟槽内设置有耐高温或耐腐蚀的复合密封圈， 其特征在于： 所述 复合密封圈自上而下依次包括上垫圈 （14)、 上密封圈 （13 )、 上隔环 （12)、 阻 断圈 （11 )、 下隔环 （10)、 下密封圈 （8) 和下垫圈 （7); 所述上密封圈 （13 ) 和下密封圈 （8)采用耐高温或耐腐蚀的密封材料制成； 所述上垫圈 （14)、 上隔 环 （12)、 下隔环 （10)和下垫圈 （7)采用耐高温或耐腐蚀的刚性材料制成； 所 述上垫圈 （14) 的下端面（22)和所述上隔环 （12) 的上端面 （25 ) 的形状为向 阀瓣内方向挤压所述上密封圈 （13 ) 的圆锥面、 斜面或球面； 所述上隔环 （12) 的下端面（26)和所述下隔环 （10) 的上端面（28) 的形状为向阀体外方向挤压 所述阻断圈 （11 ) 的圆柱面、 圆锥面、 斜面或球面； 所述下隔环 （10) 的下端面
(29) 和所述下垫圈 （7) 的上端面 （32) 的形状为向阀瓣内方向挤压所述下密 封圈 （8) 的圆锥面、 斜面或球面。
2、 根据权利要求 1所述的双向压力自平衡截止阀， 其特征在于： 所述压环 ( 16) 通过螺纹连接设置在所述阀体 （1 ) 的腔体上部。
3、 根据权利要求 1所述的双向压力自平衡截止阀， 其特征在于： 所述上垫 圈 （14)、 上隔环 （12)、 下隔环 （10)和下垫圈 （7)与所述阀瓣 （4) 的外圆间 隙配合。
4、 根据权利要求 1所述的双向压力自平衡截止阀， 其特征在于： 所述耐高 温的密封材料为柔性石墨； 所述耐腐蚀的密封材料为聚四氟乙烯。
5、 根据权利要求 1所述的双向压力自平衡截止阀， 其特征在于： 所述刚性 材料为金属或陶瓷。
6、 根据权利要求 1所述的双向压力自平衡截止阀， 其特征在于： 所述上垫 圈 （14) 和所述压环 （16) 可合制成同一个零件。
7、 根据权利要求 1所述的双向压力自平衡截止阀， 其特征在于： 所述平衡 孔 （21 ) 设置在所述阀瓣 （4) 或所述阀杆 （19) 上。
8、 根据权利要求 1所述的双向压力自平衡截止阀， 其特征在于： 所述阻断 圈 （11) 由密封材料制成的截面为等腰梯形的密封圈或由金属材料制成的 " 0" 型空心密封圈。
9、 根据权利要求 1所述的双向压力自平衡截止阀， 其特征在于： 所述阀体 (1)上设置有与所述阀瓣（4)贴合密封的第一密封面（2)， 其形状为平面、 圆 锥面或球面。
10、根据权利要求 1所述的双向压力自平衡截止阀， 其特征在于： 所述阀瓣 (4) 上设置有与所述阀体 （1) 贴合密封的第二密封面 （33)， 其形状为平面、 圆锥面或球面。
PCT/CN2011/073379 2010-04-30 2011-04-27 一种双向压力自平衡截止阀 WO2011134400A1 (zh)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP11774391.4A EP2565500B1 (en) 2010-04-30 2011-04-27 Bidirectional pressure self balancing stop valve
RU2012146416/06A RU2559216C2 (ru) 2010-04-30 2011-04-27 Двунаправленный самобалансирующийся запорный клапан давления
US13/515,279 US8794592B2 (en) 2010-04-30 2011-04-27 Bidirectional pressure self-balancing stop valve
BR112012026754A BR112012026754A2 (pt) 2010-04-30 2011-04-27 válvula reguladora com autobalanceamento de pressão bidirecional

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN2010101608302A CN101806363B (zh) 2010-04-30 2010-04-30 一种高温高压双向平衡截止阀
CN201010160830.2 2010-04-30

Publications (1)

Publication Number Publication Date
WO2011134400A1 true WO2011134400A1 (zh) 2011-11-03

Family

ID=42608271

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2011/073379 WO2011134400A1 (zh) 2010-04-30 2011-04-27 一种双向压力自平衡截止阀

Country Status (6)

Country Link
US (1) US8794592B2 (zh)
EP (1) EP2565500B1 (zh)
CN (1) CN101806363B (zh)
BR (1) BR112012026754A2 (zh)
RU (1) RU2559216C2 (zh)
WO (1) WO2011134400A1 (zh)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140197342A1 (en) * 2013-01-17 2014-07-17 Wan-Rong Kung Filler Assembly for a Valve
CN112413139A (zh) * 2020-12-04 2021-02-26 沈阳罗托克调控阀门制造有限公司 一种风洞试验设备用大口径高压液压执行调压减压阀
CN113915367A (zh) * 2021-09-24 2022-01-11 苏州中仪精博流体控制有限公司 一种新型低泄漏球阀

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101806363B (zh) * 2010-04-30 2011-08-10 南京理工大学 一种高温高压双向平衡截止阀
CN103016744B (zh) * 2012-12-08 2016-01-20 中国航天科技集团公司第六研究院第十一研究所 超低温高压动密封结构
CN104141798B (zh) * 2013-10-28 2016-08-17 河南航天液压气动技术有限公司 一种平衡式截止阀
CN103727254B (zh) * 2014-01-26 2016-02-03 周君 一种高温高压自平衡调节阀
CN104712772B (zh) * 2015-01-23 2017-04-05 北京航天试验技术研究所 一种双向密封低流阻截止阀
CN106468370A (zh) * 2015-08-21 2017-03-01 上海电气电站设备有限公司 用于提升式阀门的双层阀盖
CN106195294A (zh) * 2016-09-29 2016-12-07 李岑文达 一种阀门密封面防冲蚀结构
CN106439211B (zh) * 2016-10-12 2024-04-26 诸暨市亿霸电子阀门有限公司 一种电子膨胀阀上的阀杆组件
US10385990B2 (en) * 2017-10-30 2019-08-20 Sun Hydraulics, Llc Pressure-balanced pull-type manual actuation mechanism for a valve
DE102018102251A1 (de) * 2018-02-01 2019-08-01 Samson Aktiengesellschaft Ventilgehäuse-Baukastensystem und Hubventil
CN108374923A (zh) * 2018-04-09 2018-08-07 中南焦作氨阀股份有限公司 一种大压差开启阀门
CN108662170B (zh) * 2018-07-12 2021-05-07 宣达实业集团有限公司 料浆专用阀
CN108708979A (zh) * 2018-08-01 2018-10-26 周君 双向压力自平衡截止阀
CN112749449B (zh) * 2019-10-31 2024-11-12 中核苏阀科技实业股份有限公司 一种压力自紧密封结构的实现方法
CN111486244B (zh) * 2020-05-28 2024-06-28 安徽中烟工业有限责任公司 一种结合平面密封和锥面密封的波纹管阀门
CN114321392B (zh) * 2021-04-22 2025-01-28 南京新视界阀门科技有限公司 一种双向高温高压自平衡截断阀
CN113847428B (zh) * 2021-08-30 2023-01-17 西安近代化学研究所 一种平衡压力密封装置
CN114438389B (zh) * 2022-01-27 2023-06-13 山野控制阀集团有限公司 一种金刚石材料和金刚石复合材料球阀
CN115711162B (zh) * 2022-11-01 2025-04-08 山东齐鲁电机制造有限公司 一种汽轮机紧凑型主汽阀
CN115750797A (zh) * 2022-11-29 2023-03-07 武汉洛特福动力技术有限公司 一种管路用组合阀
CN119664920B (zh) * 2025-02-19 2025-05-13 亿川科技(成都)有限责任公司 一种内置式双向自密封高温高压阀

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5375812A (en) * 1993-12-06 1994-12-27 Abb Vetco Gray Inc. Dynamic metal-to-metal seal
CN1148677A (zh) * 1995-10-24 1997-04-30 陈宝镇 平衡式防内外泄漏柱塞截止阀
CN2438898Y (zh) * 2000-08-16 2001-07-11 孔昭润 盘根填料内压密封阀门
JP2003185024A (ja) * 2001-12-18 2003-07-03 Saginomiya Seisakusho Inc シール構造およびそれを用いた流体制御弁
CN2637835Y (zh) 2003-08-27 2004-09-01 南京理工大学 液、气压力自平衡截止阀
CN201443604U (zh) * 2009-06-29 2010-04-28 王培浩 一种活塞平衡式阀门
CN101806363A (zh) * 2010-04-30 2010-08-18 南京理工大学 一种高温高压双向平衡截止阀

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1502734A (en) * 1923-06-22 1924-07-29 William T Young Valve
US2097943A (en) * 1931-11-25 1937-11-02 Zagorski Johann Valve
GB469473A (en) * 1935-11-23 1937-07-23 Fritz Faudi Improvements in shock-absorbing struts for aircraft undercarriages
US3443789A (en) * 1966-06-27 1969-05-13 Custom Eng & Mfg Corp Plug valve
DE2529641C3 (de) * 1975-07-03 1982-01-21 Fördertechnik Streicher GmbH, 7988 Wangen Hahn mit axial nachstellbarem Kegelküken
US4214730A (en) * 1979-04-11 1980-07-29 Baumann Hans D Chemically inert control valve
US4328974A (en) * 1980-02-19 1982-05-11 White Richard E Stuffing box packing system and method
JPS5769173A (en) * 1980-10-13 1982-04-27 Sekisui Chem Co Ltd Stop valve
RU2047030C1 (ru) * 1992-06-29 1995-10-27 Научно-производственный кооператив "Радиапласт" Уплотнительное устройство
RU2162179C1 (ru) * 2000-05-22 2001-01-20 Общество с ограниченной ответственностью "Ямбурггаздобыча" Клапан запорно-регулирующий
JP4958350B2 (ja) * 2001-09-26 2012-06-20 日本バルカー工業株式会社 グランドパッキンを用いた密封装置
US6719271B2 (en) * 2002-07-18 2004-04-13 Control Components, Inc. Combination face and plug seal
US6851658B2 (en) * 2003-02-04 2005-02-08 Fisher Controls International Inc. Control valve trim and bore seal
RU2250407C2 (ru) * 2003-06-04 2005-04-20 Открытое акционерное общество "НПО "Промавтоматика" Клапан запорно-регулирующий
US6935616B2 (en) * 2003-07-18 2005-08-30 Hans D. Baumann Balanced plug valve
CN2700647Y (zh) * 2004-04-06 2005-05-18 郑州市荥阳通用阀门厂 一种锥塞阀
WO2008007685A1 (ja) * 2006-07-12 2008-01-17 Kitz Corporation 軸封パッキンとバルブ用軸封構造
CN201184441Y (zh) * 2008-04-23 2009-01-21 王法荣 一种钢制制冷阀门

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5375812A (en) * 1993-12-06 1994-12-27 Abb Vetco Gray Inc. Dynamic metal-to-metal seal
CN1148677A (zh) * 1995-10-24 1997-04-30 陈宝镇 平衡式防内外泄漏柱塞截止阀
CN2438898Y (zh) * 2000-08-16 2001-07-11 孔昭润 盘根填料内压密封阀门
JP2003185024A (ja) * 2001-12-18 2003-07-03 Saginomiya Seisakusho Inc シール構造およびそれを用いた流体制御弁
CN2637835Y (zh) 2003-08-27 2004-09-01 南京理工大学 液、气压力自平衡截止阀
CN201443604U (zh) * 2009-06-29 2010-04-28 王培浩 一种活塞平衡式阀门
CN101806363A (zh) * 2010-04-30 2010-08-18 南京理工大学 一种高温高压双向平衡截止阀

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
"Valve Design Manual", 2002, MECHANICAL INDUSTRY PRESS
JOURNAL OF THE CHEMICAL FERTILIZER INDUSTRY, vol. 2, 1989, pages 39

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140197342A1 (en) * 2013-01-17 2014-07-17 Wan-Rong Kung Filler Assembly for a Valve
US9027906B2 (en) * 2013-01-17 2015-05-12 Wan-Rong Kung Filler assembly for a valve
CN112413139A (zh) * 2020-12-04 2021-02-26 沈阳罗托克调控阀门制造有限公司 一种风洞试验设备用大口径高压液压执行调压减压阀
CN113915367A (zh) * 2021-09-24 2022-01-11 苏州中仪精博流体控制有限公司 一种新型低泄漏球阀

Also Published As

Publication number Publication date
RU2559216C2 (ru) 2015-08-10
EP2565500B1 (en) 2017-11-22
US8794592B2 (en) 2014-08-05
US20120305110A1 (en) 2012-12-06
EP2565500A4 (en) 2015-11-18
CN101806363A (zh) 2010-08-18
BR112012026754A2 (pt) 2017-12-19
EP2565500A1 (en) 2013-03-06
RU2012146416A (ru) 2014-05-10
CN101806363B (zh) 2011-08-10

Similar Documents

Publication Publication Date Title
WO2011134400A1 (zh) 一种双向压力自平衡截止阀
CN107084258B (zh) 对夹衬氟球阀
CN102313074B (zh) 高压阀的自动填料密封结构
CN204459183U (zh) 高性能双重密封氯气专用波纹管截止阀
CN206419493U (zh) 一种双重密封截止阀
CN203286121U (zh) 自密封闸阀
CN207212307U (zh) 一种油田注气采油井口节流阀
CN103727254B (zh) 一种高温高压自平衡调节阀
CN204611153U (zh) 一种能够有效降低泄漏率的法兰密封结构
CN204004559U (zh) 一种取样三通阀
CN203730808U (zh) 一种高温高压自平衡调节阀
CN206361185U (zh) 一种低温球阀
CN205639656U (zh) 一种排污疏水阀
CN1329679C (zh) 一种高压容器密封装置
CN104455489A (zh) 一种碟阀联接结构
CN204664441U (zh) 一种高压差双向软密封蝶阀
CN108708979A (zh) 双向压力自平衡截止阀
CN217519237U (zh) 自密封防泄漏高温高压截止阀
CN107269861A (zh) 一种排污疏水阀
CN205689777U (zh) 一种双向密封并且五级泄漏量调节阀
CN202381720U (zh) 一种单向压力自平衡截止阀
WO2018152947A1 (zh) 气动衬氟波纹管单座调节阀
CN212361163U (zh) 旋转补偿器端面密封结构及旋转补偿器
CN204610917U (zh) 锻钢管线软密封平板闸阀
CN205371655U (zh) 超低温蝶阀

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 11774391

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 13515279

Country of ref document: US

WWE Wipo information: entry into national phase

Ref document number: 2417/MUMNP/2012

Country of ref document: IN

REEP Request for entry into the european phase

Ref document number: 2011774391

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 2011774391

Country of ref document: EP

NENP Non-entry into the national phase

Ref country code: DE

WWE Wipo information: entry into national phase

Ref document number: 2012146416

Country of ref document: RU

REG Reference to national code

Ref country code: BR

Ref legal event code: B01A

Ref document number: 112012026754

Country of ref document: BR

REG Reference to national code

Ref country code: BR

Ref legal event code: B01E

Ref document number: 112012026754

Country of ref document: BR

ENP Entry into the national phase

Ref document number: 112012026754

Country of ref document: BR

Kind code of ref document: A2

Effective date: 20121018