WO2011075954A1 - 暗杆闸阀 - Google Patents

暗杆闸阀 Download PDF

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Publication number
WO2011075954A1
WO2011075954A1 PCT/CN2010/002142 CN2010002142W WO2011075954A1 WO 2011075954 A1 WO2011075954 A1 WO 2011075954A1 CN 2010002142 W CN2010002142 W CN 2010002142W WO 2011075954 A1 WO2011075954 A1 WO 2011075954A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
gate valve
transmission
stem
cover
Prior art date
Application number
PCT/CN2010/002142
Other languages
English (en)
French (fr)
Inventor
爱尔登·塔克
章莹
蒲昌烈
Original Assignee
泰科龙(上海)管道有限公司
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 泰科龙(上海)管道有限公司 filed Critical 泰科龙(上海)管道有限公司
Priority to AU2010335907A priority Critical patent/AU2010335907B2/en
Priority to SG2012046983A priority patent/SG181923A1/en
Priority to EP20100838520 priority patent/EP2518376A4/en
Priority to NZ601404A priority patent/NZ601404A/en
Priority to RU2012131572/06A priority patent/RU2510475C1/ru
Publication of WO2011075954A1 publication Critical patent/WO2011075954A1/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
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/02—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor
    • F16K3/0254—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor being operated by particular 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
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/02—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor
    • F16K3/0263—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor using particular material or covering 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
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/02—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor
    • F16K3/12—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with wedge-shaped arrangements of sealing faces
    • 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
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/28—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with resilient valve members
    • 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
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/30—Details
    • F16K3/316—Guiding of the slide
    • 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
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/44—Mechanical actuating means
    • F16K31/50—Mechanical actuating means with screw-spindle or internally threaded actuating means
    • F16K31/508—Mechanical actuating means with screw-spindle or internally threaded actuating means the actuating element being rotatable, non-rising, and driving a non-rotatable axially-sliding element
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D9/00—Couplings with safety member for disconnecting, e.g. breaking or melting member
    • F16D9/06—Couplings with safety member for disconnecting, e.g. breaking or melting member by breaking due to shear stress
    • F16D9/08—Couplings with safety member for disconnecting, e.g. breaking or melting member by breaking due to shear stress over a single area encircling the axis of rotation, e.g. shear necks on shafts

Definitions

  • the present invention relates to a dark rod gate valve for use in a pipe network system. Background technique
  • Gate valves are widely used valves in pipe network systems and are often referred to as gate valves and gate valves.
  • the closing member i.e., the flap
  • the valve stem In the gate valve, the closing member (i.e., the flap) is moved by the valve stem in a direction perpendicular to the center line of the valve seat to cut and open the flow of the medium in the pipe.
  • Gate valves are generally suitable for applications where the valve flap is fully open or fully closed without frequent opening and closing.
  • the characteristics of the gate valve are: full fluid resistance is small; opening and closing effort (excluding special conditions such as sealing surface biting); can be used in the case of two-way flow of the shield, no directionality; the sealing surface is not easily eroded when fully open
  • the short construction length is not only suitable for small valves, but also for large valves.
  • the gate valve can be divided into two types according to the sealing type of the valve seat: one is a metal sealing gate valve, wherein the valve seat sealing pair is a metal sealing jaw; the other is an elastic sealing gate valve, wherein the outer layer of the valve flap is covered with an elastic body such as rubber. .
  • the gate valves of the current network system especially the alarm valves in medium and low-pressure pipe network systems such as buildings and domestic water, are more elastically sealed.
  • the position of the valve stem according to the thread of the valve stem can also be divided into two types: one is a dark rod gate valve, wherein the transmission thread pair is at the lower end of the valve stem, the valve stem can only rotate and cannot be lifted; the other is a lift gate valve, wherein The drive thread pair is at the upper end of the valve stem, and the valve stem can only move up and down but cannot rotate.
  • the gate valve 100 includes a valve body 102, a valve cover 103 fixed to the valve body 102 by screws 110, a valve stem 104, a valve flap 105, and a transmission cap.
  • the valve stem 104 is relatively rotatably mounted in the valve cover 103 by a planar sliding bearing 109 such that the valve stem 104 can only rotate about a vertical centerline and cannot move vertically.
  • an O-ring seal 108 is placed directly on the valve stem 104.
  • the valve nut 107 is threadedly coupled to the valve stem 104 at the lower end of the valve stem 104.
  • the valve nut 107 is mated with the valve flap 105.
  • the shape of the valve flap 105 is adapted to the shape of the inner cavity of the valve body 102 to open and close the gate valve 100.
  • the exterior of the flap 105 will generally be encapsulated, i.e., a layer of elastomer (e.g., rubber layer 111) of a certain thickness is applied to achieve an elastic seal of the valve flap to the flow medium.
  • a drive cap (not shown) is mated to the upper end 106 of the valve stem 104 for operating the gate valve 100.
  • the valve stem 104 is driven to rotate, so that the valve nut 107 and the valve flap 105 move up and down along the valve stem 104 to open and close the gate valve 100.
  • This conventional elastic sealing gate valve mainly has the following problems.
  • the sliding friction coefficient is large.
  • the coefficient of sliding friction is 0.1-0.15. This results in a large sealing and operating torque, easy deformation and destruction of related parts, short fatigue life, and difficulty in assembly of the gate valve.
  • the operator may apply excessive torque, causing damage to the internal parts of the valve due to excessive load.
  • the existing valve flap rubber generally uses a rubber skin with a certain thickness to position the inner rough valve casting.
  • the flexible rubber will have a large deviation when the force is unevenly applied, so that the thickness of the rubber is not uniform.
  • the portion where the thickness is thin is liable to be broken during use, and the internal gate valve member is exposed to the medium to be corroded.
  • the operating torque is also high.
  • An object of the present invention is to solve the above problems and to provide a gate valve having a small operating torque, a reliable seal, a long service life, and a single assembly, which can effectively protect internal components of the valve when the operating torque is excessive.
  • a dark rod gate valve comprising a valve body, a valve cover connected to the valve body, a valve stem, a valve flap and a transmission, the upper end of the valve stem being coupled to a transmission, the valve stem The lower end is connected to the valve flap, wherein the valve stem is rotatably supported in the valve cover by a rolling bearing.
  • a rolling bearing having a low friction coefficient is used instead of the currently used planar sliding friction structural member, and since the rolling friction coefficient is small (the friction coefficient ranges from 0.002 to 0.004), the friction and the operating torque of the valve can be effectively reduced and extended. The life of moving parts, thus extending the life of the product.
  • the rolling bearing also has the function of axial positioning and support.
  • the transmission device includes a transmission cap for applying an operating torque by a user, a connection sleeve for connecting with the valve stem, and a safety block connecting the transmission cap and the connection sleeve, the safety block
  • the connection between the drive cap and the connecting sleeve is broken when subjected to a torque greater than a predetermined torque.
  • the safety block includes an upper portion connected to the transmission cap, a lower portion connected to the coupling sleeve, and an intermediate portion connecting the upper portion and the lower portion, the intermediate portion having a cross-sectional area smaller than a cross section of the upper portion and the lower portion area.
  • the over-torque transmission of the present invention when the operating torque exceeds the safety value, the breakage is broken. Therefore, it is possible to prevent excessive operating torque from being continuously transmitted to the components inside the gate valve, and the internal components of the valve can be effectively protected. Moreover, since it is not necessary to replace the gate valve, it is only necessary to replace the damaged safety block, thereby reducing the maintenance cost.
  • the valve flap comprises a valve casting, a guiding shoe and an encapsulating layer, the guiding shoe being fitted in a KJ groove of the valve casting to be in the process of sealing the valve flap Ganoderma casting positioning.
  • the valve flap according to the invention is encapsulated by the precisely positioned guiding shoes, and the rubberized positioning is accurate, and the thickness of the rubberized layer can be effectively controlled to meet the design requirements, and the thickness is uniform, thereby realizing the designed operating torque and increasing the fatigue life.
  • the gate valve further includes a shaft cover mounted above the valve cover, and a plurality of combined seals are disposed between the shaft cover and the valve stem.
  • the seal may include an O-ring and a PTFE (polytetrafluoroethylene) damper.
  • a multi-pass seal is formed by using an O-ring and a PTFE damper in combination.
  • the PTFE material has a self-lubricating effect, so it can reduce the wear of the O-ring and prolong the service life of the entire sealing pair.
  • valve body and the valve cover and the valve cover and the shaft cover are connected by a hexagon socket countersunk screw.
  • the hexagon socket countersunk head screw used in the gate valve according to the present invention allows the valve cover and the shaft cover to be better positioned automatically due to the cooperation of the tapered surface of the head and the tapered surface of the connected member. Thereby, the connected components can be better and more effectively centered without assembly adjustments, reducing assembly time and cost.
  • the gate valve according to the present invention has the following advantages: (1) Since the rolling bearing is used, the operating torque is relatively small when the same sealing pressure is required; (2) When the operating torque is excessive, the transmission The breakage of the safety block in the block can effectively protect the components in the gate valve; (3) The valve can be positioned accurately, the thickness of the rubber is uniform, and there is no defect such as iron, the seal is reliable, and the service life is long; (4) The operating torque is low. The valve disc has uniform thickness. Under the same working pressure, the fatigue life is better and the valve life is prolonged. (5) Multi-channel self-lubricating seal design, the seal is more reliable and durable; (6) The countersunk head is used. The connecting screw has a good alignment effect and is easy to assemble. DRAWINGS
  • Figure 1 is a schematic cross-sectional view of a conventional elastic sealing dark rod gate valve
  • Figure 2 is an assembled perspective view of a gate valve in accordance with the present invention
  • FIG. 3 is an exploded perspective view of a gate valve in accordance with the present invention.
  • Figure 4 is a cross-sectional view of a gate valve in accordance with the present invention.
  • Figure 4A is an enlarged cross-sectional view of a portion E of Figure 4
  • Figure 5A is an enlarged cross-sectional view of the portion of the rolling bearing of Figure 4;
  • Figure 5B is an exploded perspective view of the rolling bearing portion
  • Figure 6A is an assembled sectional view of the over-torque safety device of the gate valve according to the present invention
  • Figure 6B is an assembled perspective view of the over-torque safety device, wherein the over-torque safety device is cut in half to show its internal structure
  • Figure 6C is an exploded perspective view of the overtorque safety device
  • Figure 6D is a perspective view of the safety block in the overtorque safety device
  • Figure 7 is a schematic illustration of a valve flap of a gate valve in accordance with the present invention.
  • Figure 7A is a plan sectional view of the valve flap of Figure 7 taken along line A - A of Figure 7B;
  • Figure 7B is a cross-sectional view of the valve flap taken along line B - B of Figure 7A;
  • Figure 7C is a perspective view of the guide shoe in the valve flap
  • FIGS. 8A, 8B are schematic views showing the encapsulation of the valve flap using an overmold mold, wherein Fig. 8A shows the state before the flap casting is placed in the mold, and Fig. 8B shows the state after the flap casting is placed in the mold status;
  • Figure 9 is an enlarged cross-sectional view showing the valve stem sealing pair of the gate valve shown in Figure 4.
  • Figure 10A is an enlarged cross-sectional view showing the connecting screw of the gate valve shown in Figure 4;
  • Fig. 10B is a partial perspective view showing the position of the connecting screw shown in Fig. 10A. detailed description
  • the gate valve 1 As shown in Fig. 2 - 4, the gate valve 1 according to the present invention comprises a valve body 2, a valve cover 3 connected to the valve body 2 by a connecting screw 10, a shaft cover 8 connected to the valve cover 3 via a connecting screw 10, and a valve Rod 4, disc nut 7, disc 5 and transmission 6.
  • valve stem 4 is rotatably supported by the rolling bearing 14 and the corresponding bushing 15 In the inner bore of the bonnet 3, the valve stem 4 is only rotatable about the vertical centerline Z and cannot be moved vertically.
  • the upper end of the valve stem 4 is fitted with the transmission 6 so that the operator can rotate the valve stem 4 by rotating the transmission 6.
  • the outer surface of the lower end of the valve stem 4 is externally threaded to be threadedly coupled to the internal thread of the disc nut 7, so that when the valve stem 4 is rotated, the disc nut 7 can be moved up and down along the valve stem 4.
  • the lower portion of the disc nut 7 is provided with a flange which can be snapped into the groove 523 (shown in Fig.
  • a water stop pad 12 is provided between the valve cover 3 and the valve body 2 to prevent the medium from seeping out.
  • a sealing jaw 17 is arranged between the valve stem 4 and the valve cover 3;
  • a shaft cover 8 made of stainless steel is fixedly mounted above the valve cover 3;
  • a plurality of combined valve stem sealing pairs 16 are disposed between the shaft cover 8 and the valve stem 4.
  • a dust damper 18 is installed in the groove in the upper portion of the shaft cover 8 to prevent dust from being added to the bonnet and the inside of the valve body.
  • the structure for supporting the valve stem in the gate valve is generally a flat sliding bearing structure, and the motion pair is a valve stem (commonly used carbon steel or stainless steel) and a planar bearing (a commonly used material is a copper alloy). Its sliding friction coefficient is generally
  • a structure in which the valve stem 4 is supported by the rolling bearing 14 is employed. Specifically, at the top of the valve cover 3, the rolling bearing 14 is mounted between the upper and lower bushings 15, and the high-strength balls of the rolling bearing 14 are accommodated in the grooves provided on the surface of the valve stem 4.
  • the motion pair is the valve stem 4 and the roller
  • the bearing 14 is so that its rolling friction coefficient is equivalent to that of a deep groove ball bearing, which is only 0.002-0.004.
  • the specific contact between the rolling bearing 14 and the valve stem 4 is the high-strength ball of the rolling bearing 14 and the groove in the valve stem 4, the contact form is a line contact, and the force and reaction force between the motion pair are also in line contact manner. transfer.
  • the precision-processed stem groove and the diameter of the high-strength ball are grouped and managed to control the movement gap between each other to ensure the safety of the valve.
  • the precision-machined stem grooves can be grouped and sorted by R angle. For example, when the design valve stem groove radius is R3.000 and the ball diameter is 6.000 (radius basic size is R3.000), the grouping is performed with a deviation of 0.01 mm.
  • the stem can be divided into three groups: stem A (R2.990-3.000), stem B (R3.000-3.010) and stem C (R3.010-3.020).
  • the balls can be divided into three groups: Ball A (radius R2.980-R2.990), Ball B (half diameter R2.990-3.000) and Ball C (radius R3.000-3.010).
  • valve stem and the ball are assembled in groups, that is, the valve stem A and the ball A, the valve stem B and the ball B, the valve stem C and the ball C are assembled, thereby ensuring the matching precision of the motion pair required for the safe operation of the gate valve.
  • the movement pair materials of the valve stem and the ball can be reasonably selected according to different usage requirements.
  • the stem can be made of high carbon steel, SUS431 or other premium stainless steel.
  • Balls can be made of S440C, high chrome steel, bronze, ceramic or carbide. The material can also be processed to meet specific requirements for hardness and wear resistance.
  • the valve stem can be shielded, and hard chrome can be plated in the stem of the stem and polished or shot blasted.
  • over-torque protection transmission 6 (Figs. 6A - 6D) which will be described in detail below, it is effectively ensured that the rolling bearing motion pair is not damaged by an excessive operation load.
  • the casting size of the valve body cavity and the valve flap With uniform thickness of the rubber coating, Make sure that the actual operating torque of the gate valve is not too high due to the poor fit of the sealing components.
  • the upper limit value of the quality acceptance standard is set, and the safe service life of the rolling bearing motion pair is also ensured.
  • the prior art flat sliding bearing is replaced by the above specially designed rolling bearing, which effectively reduces the friction coefficient between the valve stem 4 and the rolling bearing 14, thereby greatly reducing the operating torque, and also improving the valve stem 4 and the rolling bearing 14
  • the service life of the sports officer This can be seen from the comparison test below.
  • test results are as follows.
  • the transmission 6 in the gate valve according to the present invention will now be described with reference to Figs. 6A - 6D.
  • the drive cap installed at the upper end of the valve stem is generally used to operate the gate valve, so that the working parts often damage the components inside the gate valve due to excessive operating torque applied to the transmission cap, and thus the entire gate valve has to be replaced.
  • the transmission 6 is employed to ensure that a safe operating torque is applied to the gate valve 1.
  • the transmission 6 includes a transmission cap 62, a safety block 64 and a coupling sleeve 65, and the transmission cap 62 and the coupling sleeve 65 are joined together by a safety block 64.
  • the interior of the sleeve 65 has an inner bore of a non-circular cross section (e.g., rectangular) to match the non-circular cross-sectional shape of the upper end of the stem 4.
  • the safety block 4 includes an upper portion 641, a lower portion 642, and an intermediate portion 643 that connects the upper and lower portions. Both the upper portion 641 and the lower portion 642 preferably have a non-circular cross section, such as a rectangular shape.
  • the intermediate portion 643 may be a groove having a cross-sectional area that is smaller than the cross-sectional area of the upper portion 641 and the lower portion 642 such that the minimum section bearing capacity of the intermediate portion 643 is less than the required safety torque.
  • the intermediate portion 643 breaks and breaks to ensure that excessive torque is not transmitted to the valve stem 4 and related components through the safety block 64.
  • the upper portion 641 of the safety block 64 is engaged with the transmission cap 62, and the lower portion 642 is engaged with the coupling sleeve 65, thereby connecting the transmission cap 62, the safety block 64 and the connection sleeve 65 into an integral assembly to be fitted to the valve stem.
  • the upper end of 4. The screw 63 is then passed through the through holes in the drive cap 62, the safety block 64 and the connecting sleeve 65 to be locked into the holes in the upper end of the valve stem 4. Finally, the protective rubber stopper 61 is plugged into the through hole above the transmission cap 62 to prevent dust or the like from entering the transmission 6.
  • the existing valve flap encapsulation process generally uses a rubber skin of a certain thickness to position the inner rough valve casting.
  • the flexible rubber is displaced when the force is uneven, and a large deviation occurs, so that the thickness of the rubber is not uniform. This has a detrimental effect on the sealing and the sealing operation torque of the alarm valve.
  • one of the main decisive factors under the same pressure condition is the percentage of the rubber compression deformation in the sealing sub-area between the valve seat and the valve flap of the valve body cavity.
  • the rubber seal on the sides of the disc is designed to have a thickness of 5 mm and a compressive deformation of 1.5 mm at a pressure of 16 bar.
  • the rubber seal compression still needs 1.5mm to meet the sealing requirements.
  • the gate valve In order to accurately position the valve insert casting during the valve flap encapsulation process, the gate valve according to the present invention employs a unique valve flap and corresponding encapsulation process as described below.
  • Figures 7, 7A and 7B show the valve flap 5 after encapsulation.
  • the flap 5 includes a flap casting 52, a guide shoe 53 (Fig. 7C), and an encapsulation layer 51. Only two guide shoes 53 are shown in the drawings, but the number and position thereof are not limited thereto, and may be set according to practical applications as long as the valve casting can be positioned.
  • concave grooves are provided on both sides of the valve casting 52 The groove 521 receives the guide shoe 53.
  • the guide shoe 53 and the recess 521 are both generally U-shaped and match each other. It should be noted that the guide shoe 53 and the recess 521 may have other mutually matching shapes.
  • the guide shoe 53 can be formed of any material suitable for sealing the flap, preferably injection molded from plastic.
  • the guide shoe 53 has a bottom surface 532 that engages with the engagement surface of the groove 521 of the cleat casting 52 and a positioning surface 531 that engages with the positioning table 503 (see Figs. 8A, 8B) of the overmold mold 501 during the encapsulation process.
  • the thickness of the guide shoe 53 can be determined according to the thickness of the rubberized layer to be encapsulated.
  • the positioning surface 531 is not lower than (preferably higher than) the outer surface 511 of the encapsulated rubber layer 51 such that the positioning surface 531 is flush with or slightly protrudes from the outer surface 511 of the rubber layer 51.
  • the positioning surface 531 will be in contact with the coating applied inside the valve body 2.
  • the guiding shoe 53 is preferably injection molded from plastic, not only the flap 5 can be sealed, but also the sliding friction coefficient between the positioning surface 531 of the guiding shoe 53 and the inner coating of the valve body 2 is smaller than that of the outer surface 511 of the rubber layer 51. The coefficient of friction between the internal coatings of the valve body 2. Thus, the operating torque is reduced by reducing the friction.
  • FIG. 8A Before the encapsulation, the positioning table 503 on both sides of the overmold 501 is separated, and the mandrel 502 is positioned at the center of the cavity 504. Then, the guide shoes 53 are fitted into the grooves 521 on both sides of the flap casting 52. As shown in FIG. 8B, the valve casting 52 and the guide shoes 53 which are embedded and firmly fitted on both sides are put into the cavity 504, and the positioning table 503 in the cavity 504 is directly positioned on the two guiding shoes 53. Positioning surface 531.
  • the multi-combined valve stem seal pair 16 includes an assembly of an O-ring 161 (2-way) and a PTFE retaining ring 162 (2-way), and is fitted into the shaft cover 8 The inner hole is in the groove.
  • the shaft cover 8 is made of high quality stainless steel and the internal grooves are precision machined to ensure the seal groove size.
  • the O-type 161 161 and PTFE ⁇ 162 can automatically adjust the seal gap in the groove of the shaft cover 8 according to the sealing pressure, making the sealing performance more reliable. Due to the good self-lubricating properties of the PTFE material, the entire sealing pair 16 is not subject to rust damage, thus extending the service life of the sealing pair 16.
  • the gate valve 1 uses a unique inner hexagonal countersunk screw as a connecting screw 10 to connect the valve body 2 and the valve cover 3 and to connect the valve cover 3 and the shaft cover 8.
  • a unique inner hexagonal countersunk screw as a connecting screw 10 to connect the valve body 2 and the valve cover 3 and to connect the valve cover 3 and the shaft cover 8.
  • the upper portion of the connecting hole of the valve cover 3 has a certain taper which cooperates with the hexagonal taper surface of the connecting screw 10.
  • the valve body 2 and the valve cover 3 and the valve cover 3 and the shaft cover 8 are automatically centered, so that the valve body 2, the valve cover 3 and the shaft cover 8 of the gate valve 1 can be well aligned. Ensure the accuracy of the fit between each other. It also facilitates assembly and eliminates the need for assembly adjustments.

Description

暗杆闸阀 技术领域
本发明涉及一种在管网系统中使用的暗杆闸阀。 背景技术
闸阀是管网系统中广泛使用的一种阀门，也常称之为闸板阀、 闸门阀。 在闸阀中， 通过阀杆带动关闭件 （即， 阀瓣） 沿与阀座 中心线垂直的方向移动来切断和开通管道内的介质流动。 闸阀通 常适用于要保持阀瓣全开或全闭而不需要经常启闭的工况。 闸阀 的特点在于： 全开流体阻力小； 启闭省力 （不包括密封面咬住等 特殊情况）； 可以在介盾双向流动的情况下使用， 没有方向性； 全 开时密封面不易受到冲蚀； 结构长度短， 不仅适合做尺寸小的阀 门， 而且适合做尺寸大的阀门。
闸阀根据阀座的密封型式可以分为两种： 一种是金属密封闸 阀， 其中阀座密封副为金属密封圏； 另一种是弹性密封闸阀， 其 中阀瓣外层包覆有橡胶等弹性体。 随着技术的发展， 目前管网系 统的闸阀， 尤其是楼宇、 生活用水等中低压管网系统中的闹阀， 更多地采用弹性密封的型式。 另外， 闸阔按照阀杆螺紋的位置也 可以分为两种： 一种是暗杆闸阀， 其中传动螺纹副在阀杆下端， 阀杆只能旋转无法升降； 另一种是升杆闸阀， 其中传动螺紋副在 阀杆上端， 阀杆只能上下移动但无法旋转。
下面参照图 1所示的一种传统弹性密封暗杆闸阀 100描述闸 阀的结构和操作。 如图 1所示， 闸阀 100包括阀体 102、 通过螺 钉 110固定到阀体 102上的阀盖 103、 阀杆 104、 阀瓣 105和传动 帽。阀杆 104通过平面滑动轴承 109可相对旋转地安装在阀盖 103 中， 使得阀杆 104仅能够绕竖直中心线旋转， 而不能竖直移动。 为实现阀杆 104与阀盖 103之间的密封， 直接在阀杆 104上开槽 放置 O形密封圏 108。阀瓣螺母 107在阀杆 104的下端与阀杆 104 螺紋连接， 该阀瓣螺母 107与阀瓣 105配合连接。 阀瓣 105的形 状与阀体 102内腔的形状相适应以启闭闸阀 100。 阀瓣 105的外 部一般会包胶， 即包上一定厚度的弹性体层 （例如橡胶层 111 ) 以实现阀瓣对流动介质的弹性密封。
传动帽 （未示出） 配合安装在阀杆 104的上端 106处， 用于 操作闸阀 100。 在工作时， 通过转动传动帽， 驱动阀杆 104转动， 使得阀瓣螺母 107和阀瓣 105—起沿着阀杆 104上下移动， 实现 闸阀 100的启闭。
这种传统的弹性密封闸阀主要存在以下问题。
由于采用平面滑动轴承， 滑动摩擦系数大。 例如， 运动副为 钢与铜时的滑动摩擦系数为 0.1-0.15。 这导致密封和操作扭矩大， 相关零件容易变形和破坏， 疲劳寿命短， 而且使得闸阀的装配困 难。
在使用上述常规传动帽的情况下， 操作人员可能会加栽过大 的扭矩， 导致阀门内部零件因承受过高的负荷而受到破坏。
现有的阀瓣包胶一般采用垫一定厚度的橡胶皮来定位内部的 粗糙的阀瓣铸件。 但是柔性的橡胶在受力不均勾时会产生较大偏 差， 使得包胶厚度不均匀。 这样， 厚度偏薄的地方在使用过程中 容易破损， 使内部的闸阀部件暴露在介质中而受到腐蚀。 另外， 由于橡胶层厚度不均勾， 还会导致操作扭矩偏高。 发明内容
本发明的目的是解决上述问题而提供一种操作扭矩小、 密封 可靠、 使用寿命长且装配筒单的闸阀， 其能够在操作扭矩过大时 有效保护阀门内部零部件。 根据本发明， 提供了一种暗杆闸阀， 其包括阀体、 连接到阀 体上的阀盖、 阀杆、 阀瓣和传动装置， 所述阀杆的上端与传动装 置连接， 所述阀杆的下端与阀瓣连接， 其中所述阀杆通过滚动轴 承可相对转动地支撑在所述阀盖中。
根据本发明， 采用了低摩擦系数的滚动轴承代替目前一般采 用的平面滑动摩擦结构件， 由于滚动摩擦系数小 （摩擦系数范围 为 0.002-0.004 )， 能够有效地减小摩擦和阀门的操作扭矩， 延长 运动部件的寿命， 从而延长产品的使用寿命。 同时滚动轴承还具 有轴向定位和支撑的功能。
优选地， 所述传动装置包括用于由用户施加操作扭矩的传动 帽、 用于与所述阀杆连接的连接套、 以及连接所述传动帽和所述 连接套的保险块， 所述保险块在承受大于预定扭矩的扭矩时断开 所述传动帽和所述连接套之间的连接。 其中， 保险块包括与所述 传动帽相连的上部、 与所述连接套相连的下部以及连接上部和下 部的中间部， 所述中间部的横截面面积小于所述上部和所述下部 的横截面面积。
根据本发明的这种超扭矩保险传动装置， 当操作扭矩超过安 全值时， 就会断裂破坏。 因此， 可以防止过大的操作扭矩继续传 递到闸阀内部的零部件上， 能够有效保护阀门的内部零部件。 并 且， 由于无需更换闸阀而只需更换破坏的保险块， 从而减少了维 修成本。
优选地， 所述阀瓣包括阀瓣铸件、 导向鞋和包胶层， 所述导 向鞋配合安装在所述阀瓣铸件的 KJ槽中， 以在所述阀瓣包胶的过 程中对所述岡瓣铸件定位。
根据本发明的阀瓣利用精确定位的导向鞋进行包胶， 包胶定 位准， 能有效控制包胶层厚度满足设计要求， 确保厚度均匀， 从 而实现设计的操作扭矩， 增加疲劳寿命。 优选地， 所述闸阀还包括安装在所述阀盖上方的轴盖， 在所 述轴盖与所述阀杆之间设有多道组合的密封件。 该密封件可以包 括 O型圏和 PTFE (聚四氟乙烯）挡圏。
在根据本发明的闸阀中，通过组合使用 O型圏与 PTFE挡圏， 形成多道密封。 另外， PTFE 材料具有自润滑作用， 所以能够减 少 O型圏的磨损， 延长整个密封副的使用寿命。
优选地， 通过内六角沉头螺钉连接所述阀体与所述阀盖以及 所述阀盖与所述轴盖。 根据本发明的闸阀中所采用的内六角沉头 螺钉由于头部的锥度面与所连接部件的锥度面的配合， 使阀盖、 轴盖能够更好地自动定位。 从而， 使所连接部件能够更好、 更有 效地对中， 而无需装配调整， 减少了装配时间和成本。
如上所述， 根据本发明的闸阀具有以下优点： （1 ) 由于采用 了滚动轴承， 在要求达到相同的密封压力奈件下， 操作扭矩相对 较小； （2 ) 当操作扭矩过大时， 传动装置中的保险块断裂破坏， 能够有效保护闸阀内的部件； （3 ) 阀瓣包胶定位精确， 包胶厚度 均匀、 无露铁等缺陷， 密封可靠， 使用寿命长； （4 ) 因操作扭矩 低， 阀瓣厚度均匀一致， 相同工作压力条件下， 疲劳寿命较好， 延长了阀门的使用时间； （5 ) 多道自润滑密封设计， 密封更为可 靠， 长久耐用； （6 )釆用沉头的连接螺钉， 对中效果好， 装配简 单。 附图说明
图 1是现有的弹性密封暗杆闸阀的示意性剖视图；
图 2是根据本发明的闸阀的装配立体图；
图 3是根据本发明的闸阀的分解立体图；
图 4是根据本发明的闸阀的剖视图；
图 4A是图 4中部分 E的放大剖视图； 图 5A是图 4中滚动轴承部分的放大剖视图；
图 5B是该滚动轴承部分的分解立体图；
图 6A是根据本发明的闸阀的超扭矩保险装置的装配剖视图； 图 6B是该超扭矩保险装置的装配立体图， 其中该超扭矩保 险装置被剖去一半以示出其内部结构；
图 6C是该超扭矩保险装置的分解立体图；
图 6D是该超扭矩保险装置中的保险块的立体图；
图 7是根据本发明的闸阀的阀瓣的示意图；
图 7A是图 7中的阀瓣沿图 7B中的 A - A线的俯视剖视图； 图 7B是该阀瓣沿图 7A中的 B - B线的剖视图；
图 7C是该阀瓣中的导向鞋的立体图；
图 8A、 8B是示出使用包胶模具对阀瓣包胶的示意图， 其中 图 8A示出将阀瓣铸件放入模具中之前的状态，而图 8B示出将阀 瓣铸件放入模具中之后的状态；
图 9是图 4所示闸阀的阀杆密封副的放大剖视图；
图 10A是图 4所示闸阀的连接螺钉的放大剖视图；
图 10B是示出图 10A所示连接螺钉位置的局部立体图。 具体实施方式
下面结合附图， 进一步详细说明根据本发明的闸阀的具体实 施方式。 应注意， 下面虽然主要结合一种弹性密封的暗杆闸阀来 描述本发明的特征， 但除非明确说明， 本发明的特征也适用于升 杆闸阀或金属密封的闸阀。
如图 2 - 4所示， 根据本发明的闸阀 1包括阀体 2、 通过连接 螺钉 10连接到阀体 2上的阀盖 3、通过连接螺钉 10连接到阀盖 3 上的轴盖 8、 阀杆 4、 阀瓣螺母 7、 阀瓣 5和传动装置 6。
阀杆 4通过滚动轴承 14和相应的轴套 15可相对转动地支撑 在阀盖 3的内孔中， 使得阀杆 4仅能够绕竖直中心线 Z旋转， 而 不能竖直移动。 阀杆 4的上端与传动装置 6配合安装， 使得操作 人员可以通过转动传动装置 6来使阀杆 4转动。 阀杆 4的下端的 外表面设有外螺紋， 以与阀瓣螺母 7的内螺纹螺纹连接， 从而当 阀杆 4在转动时， 阀瓣螺母 7可以沿着阀杆 4上下移动。 如图 3 所示， 阀瓣螺母 7的下部设有凸缘， 该凸缘可以卡入阀瓣 5上部 的凹槽 523 (如图 7所示） 中， 以使阀瓣螺母 7和阀瓣 5成为一 体。 这样， 当阀瓣螺母 7沿着阀杆 4上下移动时， 阀瓣 5随着阀 瓣螺母 7—起运动以打开或关闭闸阀 1。 当阀瓣 5向上移动时， 打开闸阀 1，实现介质的流通； 当阀瓣 5向下移动时，关闭闸阀 1， 截止介质的流动。
在阀盖 3与阀体 2之间设有止水垫圏 12以防止介质渗出。为 实现阀杆 4与阀盖 3的密封： 在轴套 15下方， 在阀杆 4和阀盖 3 之间设有密封圏 17; 在阀盖 3上方固定安装有由不锈钢制成的轴 盖 8， 在轴盖 8与阀杆 4之间设有多道组合的阀杆密封副 16。 在 轴盖 8上部的凹槽中安装有防尘圏 18， 以防止灰尘加入阀盖和阀 体内部。 滚动轴承
如以上参照图 1所述， 目前闸阀中用于支撑阀杆的结构通常 采用平面滑动轴承结构， 运动副为阀杆（常用材料为碳钢或者不 锈钢）与平面轴承（常用材料为铜合金）， 其滑动摩擦系数一般为
0.1-0.15。 如图 5A和 5B所示， 在根据本发明的闸阀中， 为了减 小摩擦系数和操作扭矩， 同时还确保一定的安全系数， 采用了用 滚动轴承 14来支撑阀杆 4的结构。 具体地， 在阀盖 3的顶部处， 滚动轴承 14安装在上下两个轴套 15之间，滚动轴承 14的高强度 滚珠容纳在阀杆 4的表面上所设的沟槽中。 运动副为阀杆 4与滚 动轴承 14， 这样其滚动摩擦系数相当于深沟球轴承， 仅仅为 0.002-0.004。
滚动轴承 14与阀杆 4之间具体进行接触的是滚动轴承 14的 高强度滚珠与阀杆 4中的沟槽， 其接触形式为线接触， 运动副之 间的作用力与反作用力也以线接触的方式传递。 为了确保运动副 的使用寿命满足设计及相关阀门安全标准的要求， 还将精密加工 的阀杆沟槽与高强度滚珠的直径进行分组配对管理， 以将彼此之 间的运动间隙控制在确保阀门安全工作所需的范围之内。
具体地， 可以将已精密加工的阀杆沟槽按 R角进行尺寸分组 筛选配对。 例如， 当设计阀杆沟槽半径基本尺寸为 R3.000, 滚珠 直径基本尺寸为 6.000 (半径基本尺寸为 R3.000 ) 时， 以偏差 0.01mm 进行分组筛选。 阀杆可以分为三组： 阀杆 A ( R2.990-3.000 )，阀杆 B( R3.000-3.010 )和阀杆 C( R3.010-3.020 )。 滚珠可以分为三组： 滚珠 A (半径 R2.980-R2.990 )， 滚珠 B (半 径 R2.990-3.000 ) 和滚珠 C (半径 R3.000-3.010 )。 然后将阀杆与 滚珠按分组配对装配， 即阀杆 A和滚珠 A、 阀杆 B和滚珠 B、 阀 杆 C和滚珠 C进行装配，从而确保闸阀的安全工作所需的运动副 的配合精度。
另外， 还可以根据不同的使用要求， 合理选用阀杆与滚珠的 运动副材料。 例如， 阀杆可以采用优碳钢、 SUS431 或者其它优 质不锈钢材料。 滚珠可以采用 S440C、 高铬钢、 青铜、 陶瓷或硬 质合金等材料。 还可以对材料进行一定的工艺处理以使其硬度和 耐磨性满足特定要求。 例如阀杆可以进行调盾处理， 可以在阀杆 沟槽处镀硬铬并进行抛光处理或喷丸处理。
另外， 通过下面将详细描述的超扭矩保护传动装置 6 (图 6A - 6D ), 有效地确保了滚动轴承运动副不会因过大的操作负荷而 受到破坏。通过控制阀体内腔铸造尺寸以及包胶厚度均匀的阀瓣， 确保闸阀的实际操作扭矩不会因密封零部件的配合尺寸超差而导 致偏高。 而且， 在实际生产中， 通过实际测定每台产品的操作扭 矩值， 设定质量猃收标准的上限值， 也确保了滚动轴承运动副的 安全使用寿命。
将现有技术中的平面滑动轴承用上述特别设计的滚动轴承替 换，有效地减少了阀杆 4与滚动轴承 14之间的摩擦系数，从而大 幅度减小操作扭矩，也提高了阀杆 4与滚动轴承 14运动副的使用 寿命。 这从下面的对比测试可以知道。
对于一种暗杆闸阀， 在其它零部件（阀体 2、 阀瓣 5、 阀盖 3 等）及测试条件（测试压力、 测试仪表、 测试人员）都相同的情 况下， 仅仅将平面滑动轴承更换为滚动轴承 14， 进行扭矩对比测 试， 其测试结果如下。
表 1 暗杆闸阀扭矩对比测试
Figure imgf000010_0001
从上表可以看出， 采用滚动轴承可以减少约 43%的操作扭 矩。 传动装置
下面参照图 6A - 6D描述根据本发明的闸阀中的传动装置 6。 在传统的闸阀中， 一般直接使用安装在阀杆上端的传动帽来操作 闸阀， 这样在工作时常由于在传动帽上施加过大的操作扭矩而损 坏闸阀内部的零部件， 从而不得不更换整个闸阀。 在根据本发明 的闸阀 1中， 则采用了传动装置 6来确保安全的操作扭矩施加在 闸阀 1上。
传动装置 6包括传动帽 62、 保险块 64和连接套 65， 传动帽 62和连接套 65通过保险块 64连接在一起。 连接套 65的内部具 有非圓形横截面 （例如， 矩形） 的内孔， 以与阀杆 4上端的非圆 形横截面形状相配合。 保险块 4包括上部 641、 下部 642以及连 接上部和下部的中间部 643。 上部 641和下部 642都优选具有非 圆形横截面， 例如矩形。 中间部 643可以是沟槽， 其横截面面积 小于上部 641和下部 642的横截面面积， 以使得中间部 643的最 小断面承栽能力小于所需安全扭矩。 这样， 当施加在保险块 64 上的扭矩超过安全扭矩时， 中间部 643会断裂破坏， 以保证过大 的扭矩不会通过保险块 64传递到阀杆 4和相关零部件。
在装配时， 使保险块 64的上部 641与传动帽 62配合， 下部 642与连接套 65配合， 从而将传动帽 62、 保险块 64和连接套 65 三者连接成一体的组件配合安装到阀杆 4的上端。 然后将螺钉 63 穿过传动帽 62、 保险块 64和连接套 65中的通孔而锁紧到阀杆 4 上端的孔中。 最后， 将防护橡胶塞 61塞住传动帽 62上方的通孔 以防止灰尘等进入传动装置 6。
在操作时， 当操作机构 （T型操作杆等等）作用于传动帽 62 时， 操作扭矩经传动帽 62、 保险块 64、 连接套 65而传递到阀杆 4上， 带动阀杆 4旋转。 当操作扭矩超过保险块 64的中间部 643 的最小断面承载能力时，保险块 64就失效或者断裂破坏，使扭矩 无法传递到阀杆 4， 从而有效保护闸阀 1及其内部的零部件。 当 保险块 64被过大的操作扭矩破坏时，仅需要在闸阀 1外部容易地 更换传动装置 6，而无需更换整个闸阀 1，大大节省了时间和成本。 阀瓣包胶
现有的阀瓣包胶工艺一般采用垫一定厚度的橡胶皮来定位内 部的粗糙的阀瓣铸件。 但是柔性的橡胶在受力不均 时会移位而 产生较大偏差， 使得包胶厚度不均匀。 这会对密封以及闹阀的密 封操作扭矩产生不利的影响。
对于闸阀的密封操作扭矩， 在相同的压力条件下， 其主要的 决定因素之一就是阀体内腔的阀座与阀瓣之间密封副区域内橡胶 压缩变形量的百分比。 例如， 假设阀瓣两侧的密封区域的橡胶设 计厚度为 5mm，且压力为 16bar时的压缩变形量为 1.5mm。根据 理论设计与实际验证， 在阀瓣两侧包胶厚度一致的情况下， 其压 缩百分比为 1.5/5=30%。 如果阀瓣在包胶过程中因受力不均匀而 产生偏移 lmm， 则阀瓣两侧密封区域的实际厚度就为 4mm 和 6mm。 在 16bar的相同压力条件下， 橡胶的密封压缩量还是需要 1.5mm才能满足密封要求。 这样的压缩量对于厚度为 4mm的一 侧的压缩百分比为 1.5/4=37.5%。 这就导致必须施加更大的力或 扭矩来达到满足实际密封要求的 37.5%的压缩百分比， 从而使得 操作扭矩增大。
为了在阀瓣包胶过程中对阀瓣铸件进行精确定位， 根据本发 明的闸阀采用了如下所述的独特的阀瓣和相应的包胶工艺。 图 7、 7A和 7B示出包胶后的阀瓣 5。 阀瓣 5包括阀瓣铸件 52、 导向鞋 53 (图 7C ) 和包胶层 51。 图中仅示出了两个导向鞋 53， 但其数 量和位置并不受此限制， 而可以根据实际应用设置， 只要能够对 阀瓣铸件进行定位就可以。相应地，在阀瓣铸件 52的两侧设有凹 槽 521以接纳导向鞋 53。 如图所示， 导向鞋 53和凹槽 521都呈 大体 U形且相互匹配。 应注意导向鞋 53和凹槽 521可以具有其 他任意相互匹配的形状。导向鞋 53可以由适于密封阀瓣的任意材 料形成， 优选用塑料注塑成型。
导向鞋 53具有与阀瓣铸件 52的凹槽 521的接合表面接合的 底面 532和在包胶过程中与包胶模具 501的定位台 503 (参见图 8A、 8B )接合的定位面 531。 导向鞋 53的厚度可以根据待包胶 的包胶层的厚度确定。
该定位面 531不低于（优选地高于）包胶后的包胶层 51的外 表面 511， 使得定位面 531与包胶层 51的外表面 511齐平或相对 于其稍稍突出。这样，在将包胶后的阀瓣 5装配到闸阀 1中之后， 该定位面 531将与阀体 2内部所涂覆的涂层接触。 由于导向鞋 53 优选用塑料注塑成型， 不仅可以密封阀瓣 5， 而且导向鞋 53的定 位面 531与阀体 2内部涂层之间的滑动摩擦系数也小于包胶层 51 的外表面 511直接与阀体 2内部涂层之间的摩擦系数。 于是通过 减少摩擦力而减少了操作扭矩。
下面参照图 8A和 8B描述根据本发明的阀瓣 5的包胶过程。 如图 8A所示， 在包胶前， 分开包胶模具 501两侧的定位台 503， 将芯棒 502在模腔 504中心定位。 然后，将导向鞋 53嵌入阀瓣铸 件 52两侧的凹槽 521内。 如图 8B所示， 将阀瓣铸件 52和两侧 嵌入且牢固配合的导向鞋 53—起放入模腔 504中， 并使模腔 504 中的定位台 503直接定位在两块导向鞋 53的定位面 531上。这样 使阀瓣铸件 52和导向鞋 53都不会产生移动， 从而确保在包胶过 程中精确定位。 因此， 保证了包胶层 51的厚度均 ， 满足设计厚 度要求。 阀杆密封 如上参照图 1所述， 现有闸阀中一般直接在阀杆上开槽放置
O形密封圈。 如图 9所示， 在根据本发明的闸阀中， 多道组合的 阀杆密封副 16包括 O型圏 161 ( 2道）和 PTFE挡圈 162 ( 2道） 的组件， 并装入轴盖 8的内孔沟槽中。 轴盖 8采用优质不锈钢制 成， 并且内部沟槽采用精密加工， 以确保密封沟槽尺寸。 O型圏 161与 PTFE挡圏 162能够在轴盖 8的沟槽内根据密封压力大小 自动调整密封间隙， 使得密封性能更为可靠。 由于 PTFE材料具 有良好的自润滑性能，整个密封副 16不会受到锈蚀破坏，这样就 延长了密封副 16的使用寿命。 自定位装配
如图 10A和 10B所示，根据本发明的闸阀 1采用独特的内六 角沉头螺钉作为连接螺钉 10来连接阀体 2与阀盖 3以及连接阀盖 3与轴盖 8。 例如， 对于阀体 2与阀盖 3的连接， 阀盖 3的连接孔 的上部具有一定的锥度，该锥度与连接螺钉 10的内六角锥度面相 互配合。 这样， 在装配过程中， 实现阀体 2与阀盖 3以及阀盖 3 与轴盖 8的自动对中，从而使得闸阀 1的阀体 2、 阀盖 3和轴盖 8 能够很好地对齐，确保相互之间的配合精度。 同时也方便了装配， 无需进行装配调节。
本发明不受上述实施例限制， 并且在没有脱离本发明的精神和 范围的前提下可以进行多种改变和修改。

Claims

权 利 要 求 书
1. 一种暗杆闸阀， 包括阀体、 连接到阀体上的阀盖、 阀杆、 阀瓣和传动装置， 所述阀杆的上端与传动装置连接， 所述阀杆的 下端与阀瓣连接，
其特征在于， 所述阀杆通过滚动轴承可相对转动地支撑在所 述阀盖中。
2. 根据权利要求 1 所述的暗杆闸阀， 其特征在于， 所述阀 杆和所述滚动轴承按照尺寸公差范围分组配对来进行装配。
3. 根据权利要求 1 所述的暗杆闸阀， 其特征在于， 所述阀 杆由不锈钢制成， 所述滚动轴承的滚珠由以下材料中至少之一制 成： 高硬度金属、 陶瓷或合金。
4. 一种暗杆闸阀， 包括阀体、 连接到阀体上的阀盖、 阀杆、 阀瓣和传动装置， 所述阀杆的上端与传动装置连接， 所述阀杆的 下端与阀瓣连接，
其特征在于， 所述传动装置包括用于由用户施加操作扭矩的 传动帽、 用于与所述阀杆连接的连接套、 以及连接所述传动帽和 所述连接套的保险块， 所述保险块在承受大于预定扭矩的扭矩时 断开所述传动帽和所述连接套之间的连接。
5. 根据权利要求 4 所述的暗杆闸阀， 其特征在于， 所述保 险块包括与所述传动帽相连的上部、 与所述连接套相连的下部以 及连接上部和下部的中间部， 所述中间部的横截面面积小于所述 上部和所述下部的横截面面积。
6. 根据权利要求 4 所述的暗杆闸阀， 其特征在于， 所述连 接套的下端具有非圆形横截面的内孔， 以与所述阀杆上端的非圆 形横截面形状相配合。
7. 根据权利要求 5 所述的暗杆间阀， 其特征在于， 所述保 险块的上部和下部都具有非圆形横截面， 以分别与所述传动帽的 下端和所述连接套的上端的非圆形横截面内孔相配合。
8. 根据权利要求 4 所述的暗杆闸阀， 其特征在于， 紧固件 穿过所述传动帽、 所述保险块和所述连接套中的通孔而将所述传 动装置紧固到所述阀杆。
9. 一种暗杆闸阀， 包括阀体、 连接到阀体上的阀盖、 岡杆、 阀瓣和传动装置， 所述阀杆的上端与传动装置连接， 所述阀杆的 下端与阀瓣连接，
其特征在于， 所述阀瓣包括阀瓣铸件、 导向鞋和包胶层， 所 述导向鞋配合安装在所述阀瓣铸件的凹槽中， 以在所述阀瓣包胶 的过程中对所述阀瓣铸件定位。
10. 根据权利要求 9所述的暗杆闸阀， 其特征在于， 所述导 向鞋具有大体 U形。
11. 根据权利要求 9所述的暗杆闸阀， 其特征在于， 所述导 向鞋用塑料注塑成型。
12. 根据权利要求 9所述的暗杆闸阀， 其特征在于， 所述导 向鞋具有与所述凹槽接合的底面和在包胶过程中与包胶模具的定 位装置接合的定位面。
13. 根据权利要求 12 所述的暗杆闸阀， 其特征在于， 相对 于所述底面， 所述定位面不低于所述包胶层在所述导向鞋附近的 外表面。
14. 根据权利要求 1 - 13中任一项所述的暗杆闸阀， 其特征 在于， 所述闸阀还包括安装在所述阀盖上方的轴盖， 在所述轴盖 与所述阀杆之间设有多道组合的密封件。
15. 根据权利要求 14 所述的暗杆闸阀， 其特征在于， 所述 密封件包括 O型圈和聚四氟乙烯挡圏。
16. 根据权利要求 1 - 13中任一项所述的暗杆闹阀， 其特征 在于， 通过内六角沉头螺钉连接所述阀体与所述阀盖， 所述阀盖 中用于接纳所述内六角沉头螺钉的孔的一部分具有锥度， 以与所 述内六角沉头螺钉的锥度面相互配合。
17. 根据权利要求 1 - 13中任一项所述的暗杆闸阀， 其特征 在于， 所述闸阀还包括安装在所述阀盖上方的轴盖， 通过内六角 沉头螺钉连接所述阀盖与所述轴盖， 所述轴盖中用于接纳所述内 六角沉头螺钉的孔的一部分具有锥度， 以与所述内六角沉头螺钉 的锥度面相互配合。
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103470799A (zh) * 2013-09-13 2013-12-25 河北宝信钢铁集团有限公司 闸阀
CN109707865A (zh) * 2019-01-29 2019-05-03 中国石化销售有限公司华南分公司 一种四阀瓣式无摩擦球阀

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102328460A (zh) * 2011-08-26 2012-01-25 昆山皇田汽车配件工业有限公司 一种机械零部件的包胶结构
CN102588623A (zh) * 2012-02-10 2012-07-18 北京竺港阀业有限公司 一种暗杆闸阀阀杆与阀盖滚珠式连接结构及其实施方案
CN102829200A (zh) * 2012-09-13 2012-12-19 许宏伟 一种橡胶闸阀
JP6101472B2 (ja) * 2012-11-07 2017-03-22 前澤工業株式会社 ソフトシール仕切弁
CN103867739B (zh) * 2014-04-02 2016-03-02 天津市永拓机械有限公司 一种直通式楔型闸阀
CN104191178A (zh) * 2014-09-10 2014-12-10 芜湖市金贸流体科技股份有限公司 一种硬密封闸阀阀体的加工方法
CN106872111B (zh) * 2017-03-31 2023-09-08 桂林电子科技大学 一种符合工业工程学的水龙头渗漏质量检测装置
DE102017107892A1 (de) * 2017-04-12 2018-10-18 AUMA Drives GmbH Schließvorrichtung
CN108757970A (zh) * 2018-07-10 2018-11-06 川北真空科技(北京)有限公司 一种小型双密封插板阀
CN109084079A (zh) * 2018-09-29 2018-12-25 天津包博特密封科技有限公司 一种高密封性搅拌料斗闸板
US11371309B2 (en) 2019-01-08 2022-06-28 Schlumberger Technology Corporation Blowout preventer with a threaded ram
US11174958B2 (en) 2019-01-24 2021-11-16 Jet Oilfield Services, LLC Gate valve and method of repairing same
DE102019001115A1 (de) * 2019-02-15 2020-08-20 Vat Holding Ag Torventil mit Kulissenführung
US11499644B2 (en) 2020-08-25 2022-11-15 Emerson Automation Solutions Final Control US LP Sealing assembly for a knife gate valve
US11300213B1 (en) 2021-02-19 2022-04-12 Emerson Automation Solutions Final Control US LP Floating yoke connection

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2424335Y (zh) * 2000-04-17 2001-03-21 大庆石油管理局第二机械厂 防盗井口专用闸阀
CN2637842Y (zh) * 2003-08-04 2004-09-01 贾春林 高温高压阀座、阀盖密封装置
US7255328B2 (en) * 2004-08-27 2007-08-14 Vetco Gray Inc. Low friction coatings for dynamically engaging load bearing surfaces
CN201121722Y (zh) * 2007-11-28 2008-09-24 陈瑞达 一种新型闸阀
CN201593622U (zh) * 2009-12-24 2010-09-29 泰科龙(上海)管道有限公司 暗杆闸阀

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE640710C (de) * 1936-01-11 1937-01-12 Fried Krupp Grusonwerk Akt Ges Brechbolzen
US2674436A (en) * 1948-12-27 1954-04-06 Oil Ct Tool Company Valve
US3662778A (en) * 1971-01-05 1972-05-16 Mueller Co Gate valve structure
US3734458A (en) * 1971-05-11 1973-05-22 Kerotest Mfg Corp Gate valve
US4436283A (en) * 1982-04-29 1984-03-13 Shore John H Gate valve
DE3345133A1 (de) * 1983-12-14 1985-09-26 Bopp & Reuther Gmbh, 6800 Mannheim Absperrkeil fuer absperrschieber
BE898637A (fr) * 1984-01-09 1984-05-02 Tipton Robert George Jr Vanne-porte
DE3428485A1 (de) * 1984-08-02 1986-02-20 Bopp & Reuther Gmbh, 6800 Mannheim Absperrkeil fuer absperrschieber
US4651973A (en) * 1984-08-13 1987-03-24 Oliver John P Gate valves
US4765591A (en) * 1986-06-16 1988-08-23 Bodnar Thomas R Gate valves
RU2020347C1 (ru) * 1991-05-07 1994-09-30 Атрушкевич Аркадий Анисимович Шиберная задвижка
US5201872A (en) * 1992-01-27 1993-04-13 Superior Oilfield Products, Inc. Gate valve improvement
GB2291491B (en) * 1992-09-18 1996-09-11 Biwater Valves Valve stem protection arrangement
RU2111399C1 (ru) * 1996-01-10 1998-05-20 Акционерная компания "Корвет" Шиберная задвижка
GB0018222D0 (en) * 2000-07-26 2000-09-13 Market Linc Holdings Ltd Valves
UA78335C2 (uk) * 2002-06-27 2007-03-15 Е. Хоул Арматуренверке Гмбх Запірна арматура
US20090057598A1 (en) * 2007-08-31 2009-03-05 Siam Cast Iron Works Co., Ltd. Resilient Wedge Gate Valve

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2424335Y (zh) * 2000-04-17 2001-03-21 大庆石油管理局第二机械厂 防盗井口专用闸阀
CN2637842Y (zh) * 2003-08-04 2004-09-01 贾春林 高温高压阀座、阀盖密封装置
US7255328B2 (en) * 2004-08-27 2007-08-14 Vetco Gray Inc. Low friction coatings for dynamically engaging load bearing surfaces
CN201121722Y (zh) * 2007-11-28 2008-09-24 陈瑞达 一种新型闸阀
CN201593622U (zh) * 2009-12-24 2010-09-29 泰科龙(上海)管道有限公司 暗杆闸阀

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103470799A (zh) * 2013-09-13 2013-12-25 河北宝信钢铁集团有限公司 闸阀
CN109707865A (zh) * 2019-01-29 2019-05-03 中国石化销售有限公司华南分公司 一种四阀瓣式无摩擦球阀
CN109707865B (zh) * 2019-01-29 2023-10-20 中国石油化工股份有限公司 一种四阀瓣式无摩擦球阀

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RU2510475C1 (ru) 2014-03-27
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MY161046A (en) 2017-04-14
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CN102109044A (zh) 2011-06-29
SG181923A1 (en) 2012-08-30
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