WO2016067737A1 - トラニオン型ボールバルブ - Google Patents
トラニオン型ボールバルブ Download PDFInfo
- Publication number
- WO2016067737A1 WO2016067737A1 PCT/JP2015/074234 JP2015074234W WO2016067737A1 WO 2016067737 A1 WO2016067737 A1 WO 2016067737A1 JP 2015074234 W JP2015074234 W JP 2015074234W WO 2016067737 A1 WO2016067737 A1 WO 2016067737A1
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- WO
- WIPO (PCT)
- Prior art keywords
- ball
- seat
- ball seat
- pressure
- trunnion
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- 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
- F16K5/0673—Composite packings
- F16K5/0678—Composite packings in which only one of the components of the composite packing is contacting the plug
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- 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
- F16K5/0689—Packings between housing and plug
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K27/00—Construction of housing; Use of materials therefor
- F16K27/06—Construction of housing; Use of materials therefor of taps or cocks
- F16K27/067—Construction of housing; Use of materials therefor of taps or cocks with spherical plugs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- 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
- F16K5/08—Details
- F16K5/14—Special arrangements for separating the sealing faces or for pressing them together
- F16K5/20—Special arrangements for separating the sealing faces or for pressing them together for plugs with spherical surfaces
- F16K5/201—Special arrangements for separating the sealing faces or for pressing them together for plugs with spherical surfaces with the housing or parts of the housing mechanically pressing the seal against the plug
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- 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
- F16K5/08—Details
- F16K5/14—Special arrangements for separating the sealing faces or for pressing them together
- F16K5/20—Special arrangements for separating the sealing faces or for pressing them together for plugs with spherical surfaces
- F16K5/201—Special arrangements for separating the sealing faces or for pressing them together for plugs with spherical surfaces with the housing or parts of the housing mechanically pressing the seal against the plug
- F16K5/202—Special arrangements for separating the sealing faces or for pressing them together for plugs with spherical surfaces with the housing or parts of the housing mechanically pressing the seal against the plug with conical surfaces
Definitions
- the present invention relates to a trunnion-type ball valve, and more particularly, to a mounting structure of a ball seat and a seat retainer that can exhibit high sealing performance against high-pressure fluid.
- a trunnion type ball valve is known as a valve particularly suitable for a high-pressure fluid, and is usually mounted on a body with a ball seat serving as a valve seat held by a seat retainer, and this ball seat is caused by the elasticity of a coil spring. It is provided in a structure in which fluid is sealed with a primary (upstream side) ball sheet by being ejected in the direction of the valve body and pressing the ball sheet.
- the ball seat is provided in a structure that prevents the ball seat from falling off.
- the seat is provided with a female screw.
- the seal ring is provided with a screw, and the seal ring is attached to the seat via the female screw and the male screw.
- a disc spring is mounted on the back of the seat, and the disc and the seal ring are pressed in the valve body direction by the disc spring.
- the seal ring is brought into pressure contact with the valve body by a compression coil spring mounted on the back side in a state in which the screw thread ends are brought into contact with each other to prevent the loose seal from protruding from the seat.
- the gap on the contact surface with the valve body is prevented.
- a seal member is provided on the inner diameter side of the seal ring, and this seal member prevents the pressure from entering the back side, and the back of the seal ring due to the pop-out of the seal ring due to the back pressure action. Intrusion of pressure is prevented.
- a valve seat holding ring is engaged with the outer periphery on the back side of the valve seat, and a fluid communication groove is provided circumferentially on the engagement surface of the valve seat holding ring.
- the valve seat is pulled back to a normal position by equalizing the pressure difference between the inlet side flow path pressure and the pocket pressure from the fluid communication groove through the fluid communication hole. As a result, the valve seat is prevented from popping out, deforming, or breaking.
- the ball seat 3 is provided in a state in which the ball seat 3 is prevented from falling off from the seat retainer 2, and the ball seat 3 is mounted to the seat retainer 2 in a free state. It has become.
- the ball seat and the valve body in addition to preventing the ball seat from dropping off, it may be required that the ball seat and the valve body can be opened and closed while maintaining high sealing performance.
- the seal surface of the ball seat in addition to preventing the seal ring from popping out, in order to ensure sealing performance, is provided with the same curvature as the seal surface of the valve body.
- the seal surfaces of the ball seat and the valve body are provided so as to be in close contact over the entire circumference.
- the seal surface 6 in the range from the primary side seal portion 4 to the secondary side seal portion 5 formed on the ball seat 3 is the valve on the outer periphery of the ball valve body 7, as in Patent Document 1.
- the ball seat 3 is prevented from falling off, and the spherical shape of the ball valve body 7 and the shape of the sealing surface 6 of the ball seat 3 are provided with the same dimensions.
- the fluid pressure is sealed because the sealing surface 6 is always in surface contact with the valve body sealing surface 8 in the range from the primary side sealing part 4 to the secondary side sealing part 5 from time to time. It has become so.
- Patent Document 4 the ball seat is held in a circumferentially rotatable state by the seat holding portion, and the ball seat is rotated in the circumferential direction along with the rotation of the ball, thereby preventing uneven wear of the ball seat and reducing the sealing performance.
- a ball valve that attempts to prevent this is disclosed.
- the space between the bottom surface of the seat ring and the bottom surface of the seat ring holding groove of the seat holding means is provided so as to be inclined while being inclined toward the ball side as the outer diameter is increased. The pressure deformation when the pressure is applied is absorbed into the space, thereby preventing the position of the seal portion from changing and maintaining the sealing performance.
- a resin material is generally used as a ball seat. In this case, when the fluid pressure becomes high, the ball seat elastically deforms according to the pressure to seal the fluid.
- Patent Document 2 also attempts to prevent the seat packing from popping out.
- the seat packing since the seat packing is press-fitted into the packing liner and integrated, when the seat packing becomes hot, the packing is expanded due to expansion. There is a possibility of jumping out of the liner. Since this sheet packing is provided with a taper in the vicinity of the back surface as a leakage preventing structure and is intended to be integrated with the packing liner by a wedge effect, it is difficult to set the dimensions of the packing liner and the sheet packing. Further, when the sheet packing is press-fitted into the packing liner due to this uneven structure, the assembling operation becomes difficult. There is a possibility of uneven wear without being in position. In order to prevent this, it may be necessary to process the sheet surface after press-fitting. In addition, there is a problem that the seat packing is easily consumed due to the relief of abnormal pressure increase in the cavity.
- the resin ball sheet 3 when high pressure is applied from the flow path side after assembly and at a low pressure, the resin ball sheet 3 is a sheet as shown by the arrow in FIG. It elastically deforms in the direction of opening outward with the contact portion 9 with the retainer 2 as the center.
- the contact portion 9 is on the outer diameter side in FIG. 14 with respect to the primary seal portion 4, so the primary seal portion 4 is centered on the contact portion 9. It moves in the direction approaching the ball valve body 7 by the rotating action that opens to the outside of the ball seat 3. As a result, as shown in FIG.
- the seal between the ball valve body 7 and the ball seat 3 changes from the surface contact from the primary side seal portion 4 to the secondary side seal portion 5 to the line contact on the primary side seal portion 4 side.
- the seal surface pressure of the primary side seal portion 4 is locally increased by this line contact seal, and the ball seat 3 is partially deformed. If the valve is rotated in this state, the primary side seal portion 4 cannot withstand the surface pressure, causing uneven wear, which easily leads to fluid leakage.
- the ball seat 3 is rotated with the contact portion 9 as a base point, and the primary side seal portion 4 serving as a sealing portion is closer to the ball valve body 7 than the secondary side seal portion 5.
- the primary side seal portion 4 serving as a sealing portion is closer to the ball valve body 7 than the secondary side seal portion 5.
- Patent Document 4 tries to prevent uneven wear by rotating in the circumferential direction while preventing the ball sheet from falling off
- Patent Document 5 absorbs the pressure deformation of the seat ring while preventing the ball sheet from falling off. I am trying to prevent the change of the position.
- the ball seat is elastically deformed in the opening direction so that the contact with the ball valve body approaches the line contact from the surface contact, as in the ball valve of FIG.
- uneven wear occurs on the seal surface and the seal performance deteriorates.
- the present invention has been developed in order to solve the conventional problems, and its purpose is to prevent the ball seat from falling off the seat retainer and to avoid abnormal wear of the ball seat while avoiding wear of the ball seat. Reducing the number of parts and simplifying the structure while securing strength to improve workability and assembly, and improve the sealing performance between the ball seat and the valve body even at high pressure to prevent leakage
- Another object of the present invention is to provide a trunnion type ball valve capable of improving the durability of the ball seat.
- a seat retainer in which a ball seat is mounted on one or both of balls having a through hole provided in a body, and the ball is rotated through a stem.
- the ball seat prevents excessive protrusion due to abnormal pressure increase in the cavity when fully closed or fully open in a ball valve that is mounted in a free state and prevents the ball seat from protruding into the mounting groove formed in the seat retainer.
- the seat retainer is moved in the direction opposite to the ball by the self-tightening force using this pressure, and the ball sheet is pushed out to the ball side by excessive pressure flowing into the back surface side of the ball sheet in the mounting groove.
- It is a trunnion type ball valve configured to relieve in a flow path via a communication portion provided between an inner peripheral surface and a mounting groove.
- the engaging portion provided on the inner peripheral opening side of the mounting groove is opposed to the engaging portion provided on the outer peripheral mounting side of the ball seat so as to be able to be locked in the inserting direction.
- This is a trunnion type ball valve in which the ball seat is prevented from popping out of the mounting groove and the ball seat is mounted in the mounting groove in a free state.
- the threaded portion is provided as an engaging portion to be provided in the inner periphery of the mounting groove, and the male threaded portion of the ball seat is screwed into the female threaded portion as the engaging portion, and the rear end side of the male threaded portion
- This is a trunnion type ball valve in which the rear end side of the female threaded portion is provided so as to be able to be locked and the ball seat is prevented from popping out.
- the invention according to claim 4 is a trunnion-type ball valve in which the thread of the inner end of the female thread and the thread of the outer end of the male thread are locked to prevent the ball seat from popping out.
- the invention according to claim 6 is such that the inner diameter dimension of the A portion, which is the fulcrum position of the back seal of the ball seat, is provided closer to the inner diameter than the seal portion of the ball seat, and the ball seat at high pressure opens with the A portion as a fulcrum. It is a trunnion type ball valve that is elastically deformed and seals at least a surface contact state from the outer diameter side to the inner diameter side.
- the invention according to claim 7 is a trunnion-type ball valve in which the positional relationship between the A portion which is a fulcrum position and the sealing portion B and the sealing portion C which are seal portions is A ⁇ C ⁇ B with respect to the inner diameter dimension. is there.
- the invention according to claim 8 is a trunnion-type ball valve in which the sealing portion B maintains a line contact state and the sealing portion C is in a non-contact state with the ball surface when the assembly is initial and the fluid pressure is low. .
- the ball seat seal portion is formed in a spherical surface, and the spherical surface is arranged on the flow axis in the body in the same manner as the center of the ball, and the inner diameter thereof is set. It is a trunnion type ball valve formed with a diameter smaller than the spherical shape of the ball.
- the invention according to claim 11 is a trunnion type ball valve in which a clearance is provided between the inner peripheral surface of the locking portion formed in the mounting groove and the outer peripheral surface side of the ball seat.
- the ball seat is mounted while preventing the ball retainer from popping into the mounting groove of the seat retainer, and the ball seat is prevented from dropping even when a high-pressure fluid flows or the valve is slightly opened.
- High sealing performance can be demonstrated.
- the ball seat is attached to the seat retainer in a free state, even if abnormal pressure rises when fully closed or fully opened, the seat retainer is moved in the opposite direction to the ball by the so-called self-tightening force that uses the pressure in the cavity.
- the excess pressure due to abnormal pressure increase in the cavity is relieved in the flow path through the communication portion between the inner peripheral surface of the ball seat and the mounting groove, so that the ball seat Prevent wear on the contact surface with the ball.
- the relief point at the time of the valve closing seal can be stabilized and the abnormal pressure increase can be surely avoided, and when the valve is closed, the high sealing performance is maintained and the high pressure fluid is prevented from leaking.
- the relief mechanism can be configured with a ball seat and a seat retainer to reduce the number of parts, simplify the internal structure, install the ball seat while ensuring strength without increasing grooves and dents, and improve workability and assembly. Can also be improved.
- the ball seat is mounted on the seat retainer mounting groove in a free state, so that the ball seat is movable relative to the seat retainer when a force in the protruding direction is applied to the ball seat.
- the ball seat can be prevented from popping out by the opposing engaging portion and locking portion.
- the female thread portion is provided as an engaging portion and the male screw portion as a locking portion so as to be able to be locked in the loading direction, it is easy to utilize these screws.
- the ball seat can be attached to the seat retainer, and after screwing, the ball seat can be reliably prevented from popping out by locking the rear end side of the opposing male screw portion and the rear end side of the female screw portion. .
- the seat retainer and the ball seat move in opposite directions due to self-tightening force, and the back of the ball seat is separated from the seat retainer. Furthermore, the abnormal pressure increase can be eliminated by discharging the pressure in the cavity through the relief groove.
- the ball seat is mounted in a free state in the mounting groove while preventing the ball seat from dropping from the seat retainer, and this ball seat is sealed when the fluid pressure is low.
- the outer diameter side of the part is in line contact with the ball, and in the case of high pressure, high pressure fluid is applied to the large-diameter valve by elastically deforming so that the A part is opened as a fulcrum and the seal part is sealed to the ball in a surface contact state. Even when it flows, it is possible to improve the sealing performance between the ball seat and the valve body and reliably prevent leakage.
- the sealing portion B when the fluid pressure is low, the sealing portion B contacts the ball while preventing the sealing portion C from contacting the ball while the A portion which is the fulcrum position is sealed on the back surface.
- the line contact seal by the sealing portion B can prevent leakage while preventing wear of the ball sheet.
- the ball seat When the fluid pressure is high, the ball seat is elastically deformed in the direction to open with respect to the ball around the A portion at the fulcrum position, so that the sealing portion C side contacts the ball and the outer diameter side sealing portion
- Surface contact from B to the inside of the sealing part C on the inner diameter side is a seal part, so that local surface pressure is prevented and uneven wear of the seal part is prevented, and the sealing property is improved and leakage is ensured. Can be prevented.
- the sealing portion B when the fluid pressure is low, the sealing portion B is prevented from coming into contact with the ball to prevent wasteful wear and to secure a sealing property capable of preventing fluid leakage. Can do.
- the ball seat when the fluid pressure is high, the ball seat is elastically deformed so as to open with respect to the ball, and the spherical surface of the seal portion is brought into surface contact with the outer periphery of the ball.
- the sealability can be improved while preventing uneven wear of the part.
- the tenth aspect of the present invention it is possible to elastically deform toward the clearance side without suppressing deformation of the ball sheet at a high pressure to maintain high sealing performance, and to transmit extra stress due to contact of the mounting groove to the ball sheet. By avoiding it, the flexibility can be maintained. On the other hand, by preventing the ball seat from opening too much through the clearance, it is possible to maintain the surface contact seal state at high pressure and prevent leakage.
- the ball seat can be mounted in a free state in a state in which the projection is prevented from protruding from the seat retainer by the engaging portion, and the ball can be elastically deformed so that the ball can be sealed from low pressure to high pressure.
- FIG. 2 is a schematic cross-sectional view taken along FF in FIG.
- FIG. 2 is a sectional view taken along line JJ in FIG. It is the longitudinal cross-sectional view which showed the assembly process of the ball seat.
- It is a partially expanded sectional view which shows the state at the time of abnormal pressure
- FIG. 4 is a partially enlarged cross-sectional view showing a slightly opened state of the ball in a region E in FIG. 3.
- FIG. 1 shows an embodiment of a trunnion type ball valve of the present invention in an opened state
- FIG. 3 shows a cross-sectional view taken along line JJ in FIG. 1, ie, a central cross section of the trunnion type ball valve of the present invention. The figure is shown.
- a ball seat 1 has a body 11, a ball 12, a stem 13, a seat retainer 14, and a ball seat 15, and particularly has a large diameter and a class (nominal pressure). It is suitable for use as a high pressure fluid of about 150 to 2500.
- the body 11 has an annular body 20 and annular caps 21, 21 on both sides, which are made of carbon steel, stainless steel, etc., and are integrated by bolts and nuts 22.
- a ball 12 is rotatably provided via a stem 13 including an upper stem 13 a and a lower stem 13 b, and a seat retainer 14 is disposed on both the balls 12, that is, on the upstream and downstream sides.
- a ball seat 15 is attached to the seat retainer 14.
- the ball 12 is made of stainless steel, and is provided with a through hole 12 a that can communicate with the flow path 23 in the valve body 10.
- the ball sheet 15 and the seat retainer 14 are attached to the upstream and downstream sides of the ball 12, but these may be provided on one or both of the upstream and downstream sides.
- the ball valve body 10 in which the ball seat 15 and the seat retainer 14 are mounted on the upstream and downstream sides either the right side or the left side in the drawing may be the primary side.
- the ball sheet 15 is formed in an annular shape that can be elastically deformed by a resin material such as PTFE (polytetrafluoroethylene), nylon, PEEK (polyetheretherketone), and a sealing surface 25 is provided on the contact side of the ball 12.
- a resin material such as PTFE (polytetrafluoroethylene), nylon, PEEK (polyetheretherketone), and a sealing surface 25 is provided on the contact side of the ball 12.
- An annular inner peripheral surface 27 is provided up to the back surface 15 a side of the ball sheet 15 following the seal surface 25.
- a male screw portion 30 is provided as a locking portion, and this male screw portion 30 is provided up to about half the thickness in the mounting direction of the ball seat 15. .
- At least one relief groove 31 is formed on the inner peripheral surface 27 of the ball seat 15.
- the relief groove 31 is provided from the vicinity of the boundary between the inner peripheral surface 27 and the sealing surface 25 to a back surface 15a side of the ball seat 15 at a predetermined depth.
- the relief groove 31 is formed after the seat retainer 14 is mounted.
- the communication portion 40 provided between the inner peripheral surface 27 side and the outer peripheral surface side (the external thread portion 30 side) of the ball seat 15 is provided to be configurable.
- the relief grooves 31 are desirably provided at a plurality of locations on the inner peripheral surface 27 of the ball seat at equal intervals. Further, the relief groove 31 may be provided in a mounting groove 32, which will be described later, of the seat retainer 14, which faces the inner peripheral surface 27.
- a groove or a hole that can be tightened or removed by a tightening jig may be provided on the outer periphery of the ball seat 15. Easy assembly.
- the seat retainer 14 is formed in a substantially cylindrical shape by a metal material such as carbon steel or stainless steel, and is formed so that the mounting side of the ball seat 15 is slightly expanded, and the ball seat 15 is inserted therein.
- a possible annular mounting groove 32 is provided.
- a female screw portion 33 that can be screwed with the male screw portion 30 is provided as a projecting engagement portion.
- the female thread portion 33 is provided from the opening side to approximately half of the length of the mounting groove 32, and the thread 33a is a thread 30a of the thread portion 30 of the ball seat 15 in the case of the valve body 10 of size 3B.
- a bottomed hole 34 having a diameter larger than the outer diameter of the male screw part 30 is provided behind the female thread part 33, and the depth of the bottomed hole 34 is larger than the length of the male screw part 30.
- the inner diameter of the bottomed hole 34 is slightly larger than the outer diameter of the external thread portion 30.
- the ball screw 15 is inserted into the mounting groove 32 in a state in which the male screw portion 30 is screwed into the female screw portion 33 and the male screw portion 30 is accommodated in the bottomed hole 34. After the male screw portion 30 and the female screw portion 33 are screwed together, the rear end side of the male screw portion 30 and the rear end side of the female screw portion 33 face each other so as to be able to be locked in the loading direction of the male screw portion 30.
- the ball sheet 15 is prevented from jumping out from the mounting groove 32, and the ball sheet 15 is mounted in a free state, that is, in a state of being movable at least in the direction of the flow path center axis O with respect to the mounting groove 32.
- the abnormal pressure increase in the cavity 35 means that the temperature of the fluid rises or the environment in which the valve main body 10 is installed becomes high, so that the body 11 and the ball 12 in the valve main body 10 in the valve closed state.
- the fact that the ball sheet 15 is pushed out to the ball 12 side is not limited to the state in which the position of the ball sheet 15 moves to the ball 12 side, and at least the ball sheet 15 does not follow the sheet retainer 14 and the ball 12 is pressed.
- the screw threads 30a and 33a are preferably fine screws.
- the height of the screw threads can be adjusted while ensuring the number of threads by making the screw length as short as possible.
- the fine screw has a short pitch, it is preferable in the trunnion type ball valve of the present invention in that the number of incomplete threads in the circumferential direction is reduced.
- the depth of the bottomed hole 34 is larger than the length of the external thread portion 30 as described above, so that the thread 30a surely exceeds the region of the thread 33a, and the external thread 30 is in the bottomed hole 34. It is possible to charge until it is accommodated in the housing, and a clearance CL in the loading direction (in the direction of the flow path center axis O in FIG. 1) is provided between the threads 30 and 33a as shown in FIG. Since the inner diameter of the bottomed hole 34 is slightly larger than the outer diameter of the external thread portion 30, a radial gap G is also provided between them, and the ball sheet 15 is formed between the seat retainer 14 and the gap G.
- the clearance CL In the range of the clearance CL, it is possible to advance and retreat in a state where the sliding resistance is small.
- the dimensions such as the clearance CL and the size of the gap G are set in consideration of the environmental temperature at the time of assembly and the temperature difference due to the difference in the assembly location. In the case of this embodiment, it is provided so as to be able to cope with an assembly temperature of a maximum of 40 ° C. in the summer and a minimum of 10 ° C. in the winter.
- the ball sheet 15 is rotated in the direction opposite to the screwing direction, and it is confirmed that the ball sheet 15 does not re-screw or drop off.
- the ball seat 15 is rotated until the highest portion (completely threaded portion) of the thread 33a of the seat retainer 14 and the screw thread 30a of the ball seat 15 is locked, and the start portions of the screw tips are not Do not align the positions of the complete threaded parts).
- re-screwing of the ball seat 15 after the seat retainer 14 is mounted is prevented, and the ball seat 15 is reliably moved.
- the start portion of the screw tip is arranged avoiding the 3 o'clock position x when the male screw portion 30a is compared with a watch in FIG. This is because when the valve body 10 in the valve closed state is rotated counterclockwise to make the valve open state, the flow path 23 closed by the ball 12 starts to open from the position 3 o'clock, This is because the ball seat 15 tends to pop out when the flow velocity at the beginning of opening of the valve is high. Specifically, it is preferable to arrange the highest portions of the thread 33a of the seat retainer 14 and the thread 30a of the ball seat 15 at the 3 o'clock position.
- the threaded portion 30 is provided on the outer peripheral side of the ball seat 15 and the female threaded portion 33 is provided on the seat retainer 14, but the female threaded portion is provided on the inner peripheral side of the ball seat 15 and the threaded portion is provided on the seat retainer 14. (Both not shown), and the ball seat 15 may be mounted in the mounting groove 32 of the seat retainer 14 in a free state while being screwed in the same manner as described above.
- the locking portion 30 and the engaging portion 33 may be other than screws, and the locking portion 30 and the engaging portion 33 are locked to each other so that the ball seat 15 protrudes from the seat retainer 14. As long as the ball seat 15 can be mounted in the mounting groove 32 in a free state, these can be provided in various shapes.
- the trunnion-type ball valve of the present invention has a structure that prevents high-pressure fluid from being sealed by the ball seat 15 mounted in a free state in FIG.
- the structure can be simplified while minimizing the number of points, and the ball seat 15 can be mounted simply by screwing it into the seat retainer 14.
- the male thread part 30 and the female thread part 33 can be screwed together to insert the ball seat 15 into the bottomed hole 34, thereby preventing wear or damage without applying excessive force.
- it can be mounted accurately and easily to a predetermined position with a small number of assembly steps.
- it is possible to mount the seat retainer 14 and the ball seat 15 while providing a sufficient clearance CL and gap G without requiring a special jig or the like, so that extra stress is generated from the initial state of assembly. Prevents and has good durability during operation.
- it can be assembled in a state that is not easily affected by the environmental temperature.
- the sheet material for example, various materials such as a low temperature material, a high temperature material, a low strength material, and a high strength material.
- a material can be used, and even when the ball sheet 15 is provided with a high-strength material, the mounting becomes easy.
- the ball seat 15 After the ball seat 15 is completely screwed in, the ball seat 15 can be mounted in a state of idling to the bottomed hole 34 side, so that the ball seat 15 can be naturally loosened without a separate member for preventing looseness. Dropping can be prevented.
- the ball seat 15 When the pressure in the cavity 35 increases due to abnormal pressure increase, the ball seat 15 is pushed by this pressure as shown in FIG. 5 and tilts toward the inner diameter side as shown by the arrow in the figure. Due to this deformation, the ball seat 15 and the ball 12 are sealed with a seal diameter ⁇ dR at a seal point R slightly smaller in diameter than the seal point before occurrence of abnormal pressure increase, and the ball seat 15 and the seat retainer 14 are sealed at the seal point P. Sealing is performed with a back seal diameter ⁇ dP.
- the pressure in the cavity 35 (cavity pressure) is applied to both the sealing surface 25 side and the back surface 15a side.
- a difference S is provided in the seal diameter so that each seal point has a relationship of seal diameter ⁇ dR> back seal diameter ⁇ dP.
- the force applied to the back side of the ball sheet 15 by the cavity pressure is set to be larger than the force applied to the ball 12 side, and the ball sheet 15 is pushed out to the ball 12 side. ing.
- the cavity pressure is applied to both the cap 21 side and the mounting groove 32 side of the ball seat 14 in the seat retainer 14.
- the seat retainer 14 is sealed from the inner periphery of the cap 21 by an O-ring 42 on the cap 21 side.
- this seal point is represented by D
- this seal diameter is represented by retainer seal diameter ⁇ D.
- each seal point is ⁇ dD> ⁇ dR.
- FIG. 6 shows a state in which the ball sheet 15 is pushed out to the ball 12 side by the cavity pressure.
- excessive pressure from the cavity 35 flowing into the gap G between the male thread portion 30 of the ball seat 15 in the mounting groove 32 and the female thread portion 33 of the seat retainer 14 pushes the ball seat 15 toward the ball 12.
- excess pressure in the cavity 35 is relieved in the flow path on the primary side of the ball 12 from the communication portion 40 between the inner peripheral surface 27 of the ball seat 15 and the mounting groove 32 through the relief groove 31.
- a gap G can be formed in the gap 35, and excess pressure in the cavity 35 can be relieved from the back surface 15 a of the ball seat 15 to the flow path 23 on the primary side via the communication portion 40.
- the jump-out of the ball seat 15 due to the back pressure effect of the fluid pressure can be controlled by the relationship between the thread shear strength and the ball seat back pressure, that is, the relationship between the material strength and the pressure acting area on the back side. If the ball sheet 15 is formed while adjusting the height, it is possible to reliably prevent the pop-out.
- FIG. 8 shows a second embodiment of the trunnion type ball valve of the present invention.
- the same parts as those in the above embodiments are denoted by the same reference numerals, and the description thereof is omitted.
- the front end side of the thread 33a of the female thread portion 33 is cut away, and a surface 33b parallel to the outer periphery of the ball seat 15 is provided.
- a surface 33b parallel to the outer periphery of the ball seat 15 is provided.
- FIG. 9 shows a third embodiment of the trunnion type ball valve of the present invention.
- the rear surface of the ball sheet 15 is located at a seal point P closest to the inner diameter of the inclined surface 15b.
- the seal between 15a and the mounting groove 32 of the seat retainer 14 is performed.
- the back surface 15a of the ball seat 15 is a surface that is parallel to the bottom surface of the mounting groove 32 of the seat retainer 14 and orthogonal to the flow path center axis O of FIG.
- An annular protrusion 45 may be provided at the point P. In this case, the space between the mounting groove 32 of the seat retainer 14 can be sealed by the annular protrusion 45 on the innermost diameter side of the back surface 15 a of the ball seat 15.
- FIG. 10 shows a seat retainer and a ball seat in the fourth embodiment of the trunnion type ball valve of the present invention.
- an annular edge portion having two to four notches 50 in the circumferential direction instead of the female thread portion provided on the inner periphery of the mounting groove in the seat retainer 14. 51.
- two to four annular protrusions 52 instead of the male thread portion provided on the outer periphery of the ball seat 15, two to four annular protrusions 52 corresponding to the notch portions 50 are provided in the circumferential direction.
- the ball seat 15 When the ball seat 15 is mounted on the seat retainer 14, the ball seat 15 is inserted into the seat retainer 14 with the annular protrusion 52 aligned with the position of the notch 50 as shown in FIG. Then, the ball seat 15 is rotated in the direction of the arrow in FIG. 10B with respect to the seat retainer 14 until the annular protrusion 52 shown in FIG. Like that. As a result, the annular protrusion 52 is engaged with the annular edge 51 in FIG. 10C, and the ball seat 15 is mounted in a free state, that is, in a movable state with respect to the mounting groove 32 by this rotational engagement. , It can be prevented from falling off.
- FIG. 11 shows a fifth embodiment of the trunnion type ball valve of the present invention.
- an A portion is formed in an annular shape on the mounting groove 32 side of the ball seat 15, and this A portion can contact the mounting groove 32 and can be sealed on the back surface, and is provided at a fulcrum position.
- the ball seat 15 is prevented from jumping out of the mounting groove 32 and is elastically deformable in a direction in which the ball 12 is opened around the fulcrum position A, and the flow axis of the valve body 10 in FIG. It is mounted in a free state that can move in the direction of the central axis (O).
- the inner diameter dimension L1 of the A portion is provided closer to the inner diameter than the sealing surface 25 which is a sealing portion of the ball sheet 15, and the A portion is formed so as to project annularly in this manner.
- a bottom hole 34 of the mounting groove 32 is formed with a gap H.
- the ball seat 15 is provided so as to be elastically deformed so as to open at a portion A as a fulcrum at high pressure, and to seal the ball 12 at least in a surface contact state with the sealing surface 25 facing the inner diameter side from the outer diameter.
- the gap H also contributes to the rotating action when the ball seat 15 is elastically deformed so as to open.
- the sealing surface 25 is formed by a spherical portion that is a spherical surface that can come into surface contact with the outer periphery of the ball 12, and a sealing portion C is formed on the primary side of the sealing surface 25 in the flow path 23 direction, and a sealing portion B is formed on the secondary side.
- the sealing portion B is provided so as to be in line contact with the ball 12 at the time of low pressure.
- the positional relationship between the A portion that is the fulcrum position and the sealing portion B and the sealing portion C that are the sealing surfaces 25 is when the inner diameter dimension of the sealing portion B is L2 and the inner diameter dimension of the sealing portion C is L3.
- the inner diameter ⁇ DS from the sealing portion C to the sealing portion B of the sealing surface 25 is equal to the spherical diameter ⁇ DB of the ball 12. Unlike these, they are formed to have different diameter dimensions.
- the inner diameter ⁇ DS is smaller than the ball sphere diameter ⁇ DB, that is, the seal portion inner diameter ⁇ DS ⁇ the ball sphere diameter ⁇ DB.
- the center Q1 of the inner diameter ⁇ DS and the center Q2 of the ball ball diameter ⁇ DB are both arranged on the flow path center axis O of the valve body 10 as shown in FIG.
- a predetermined clearance CL is provided between the inner peripheral surface 32a of the mounting groove 32 and the outer peripheral surface 15b on the seal surface side of the ball seat 15, and the ball seat 15 is opened to the clearance CL side at high pressure. , Too much opening is suppressed.
- a projecting engagement portion 60 is formed on the back side of the mounting groove 32 so as to have a length that is approximately half of the thickness in the mounting direction of the ball sheet 15.
- a projecting locking portion 61 is formed from the opening side to approximately half the length of the mounting groove 32.
- the clearance CL is provided at least between the inner peripheral surface 32a of the locking portion 61 and the outer peripheral surface 15c side of the ball 12 from the engaging portion 60 of the ball seat 15.
- a bottomed hole 34 having a diameter larger than the outer diameter of the engaging portion 60 is provided on the back side of the locking portion 61 of the seat retainer 14, and the depth of the bottomed hole 34 is larger than the length of the engaging portion 60.
- the inner diameter of the bottomed hole 60 is slightly larger than the outer diameter of the engaging portion 60.
- the ball seat 15 is mounted in the mounting groove 26 in a state where the engaging portion 32 is accommodated in the bottomed hole 34. After the mounting of the ball seat 15, the rear end side of the engaging portion 60 and the rear end side of the locking portion 61 are opposed to each other so as to be locked in the loading direction of the engaging portion 60. The ball seat 15 is in a free state while being prevented from jumping out of the groove 32.
- the communication portion that communicates the cavity 35 and the upstream side of the ball 12 between the inner peripheral surface 27 side and the outer peripheral side (engagement portion 60 side) of the ball seat 15. 40 is provided.
- the seat retainer 14 is moved in the direction opposite to the ball 12 by the self-tightening force using the high pressure, and the ball is moved by the excessive pressure flowing into the back surface 15a side of the ball seat 15 in the mounting groove 32.
- the seat 15 is pushed out to the ball 12 side, and at this time, excess pressure due to abnormal pressure increase in the cavity 35 is relieved in the flow path 23 via the communication portion 40.
- the trunnion type ball valve in this embodiment is suitable for a large diameter of 8 inches or more.
- ball seat material PTFE
- ball Ball diameter ⁇ 460 mm
- the inner diameter ⁇ DS of the seal portion is reduced by about 3% to 5% with respect to the ball ball diameter ⁇ DB
- the sealing surface 25 of the ball seat 15 is provided in the vicinity of the seal to the ball 12 and has a shape other than the spherical portion if it can be sealed by line contact or surface contact with the ball 12 according to the height of the fluid pressure.
- it may be formed in a taper shape or a circular arc surface shape.
- the ball sheet 15 is inserted from the opening side toward the mounting groove 32 so as to push the engaging portion 60 into the locking portion 61.
- the engaging portion 60 reaches the bottomed hole 34, the mounting of the ball seat 15 is completed, and the ball seat 15 is prevented from being detached from the seat retainer 14 and mounted in a free state.
- the engaging portion 60 since the depth of the bottomed hole 34 is larger than the length of the engaging portion 60, the engaging portion 60 surely exceeds the region of the locking portion 61, and the engaging portion 60 is It is accommodated in the bottomed hole 34.
- a clearance CL is formed between the ball groove 15 and the mounting groove 32, and the clearance CL can be elastically deformed in a direction in which the ball 12 side of the ball seat 15 opens around the A portion serving as a fulcrum position.
- a space U is provided in the loading direction (the direction of the axis O of the flow path in FIG. 1). Since the inner diameter of the bottomed hole 34 is slightly larger than the outer diameter of the engaging portion 60, a radial gap G is also provided between them. Due to the gap G, the ball seat 15 can advance and retreat in a range of the space U of the seat retainer 14 with a low sliding resistance.
- Dimension settings such as clearance CL, space U, and gap G are set in consideration of the environmental temperature during assembly and the temperature difference due to the difference in assembly location. In the case of this embodiment, it is provided so as to be able to cope with an assembly temperature of a maximum of 40 ° C. in the summer and a minimum of 10 ° C. in the winter.
- valve body 10 when the fluid pressure on the upstream side of the flow path 23 is low, sealing is performed with the portion A of the ball seat 15 in contact with the bottom surface side of the mounting groove 32 as shown in FIG. 11.
- the part B is kept in contact with the ball 12 in a sealed state.
- This line contact seal has a lower sealing force than a surface contact seal, but since the fluid is at a low pressure, it does not reach the yield point of the ball seat material, so wear that impairs the seal performance does not occur. The leakage at the low pressure is surely prevented.
- the positional relationship between the A portion that is the fulcrum position and the sealing portion B and the sealing portion C that are the sealing portions is A ⁇ C ⁇ B with respect to the inner diameter dimension, and is outside the A portion. Since the sealing portion B is positioned on the radial side, the rotation of FIG. 13 causes the sealing portion B side to rotate counterclockwise so as to move in a direction away from the ball 12, and by this rotation, from the ball 12 until then. The side of the sealing portion C that has been separated is surely brought into surface contact with the ball 12.
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Abstract
Description
さらに、このボール弁では、シールリングの内径側にはシール部材が設けられ、このシール部材によって背面側への圧力の浸入が防止され、背圧作用によるシールリングの飛び出しに起因するシールリング背面への圧力浸入が防止されている。
図14のボールバルブにおいても、特許文献1と同様に、ボールシート3に形成される一次側シール部4から二次側シール部5までの範囲のシール面6が、ボール弁体7外周の弁体シール面8と同じ曲率に設けられている。
すなわち、これらのボールバルブでは、図14において、ボールシート3の脱落を防ぐと共に、ボール弁体7の球形とボールシート3のシール面6との形状が同一寸法に設けられていることで、低圧時から高圧時まで、弁体シール面8にシール面6が一次側シール部4から二次側シール部5までの範囲で常に面接触した状態になっていることで、流体圧力が封止されるようになっている。
特許文献5のボールバルブにおいては、シートリングの底面と、シート保持手段のシートリング保持溝の底面との空間が外径になるほどボール側に傾斜しながら広くなるように設けられ、シートリングに押圧力が加わったときの押圧変形が空間に吸収されることにより、シール部の位置が変わることを防いでシール性を保持しようとするものである。
上述の各トラニオン型ボールバルブでは、一般に樹脂材料がボールシートとして使用され、この場合、流体圧力が高温になるとその圧力に応じてボールシートが弾性変形しながら流体をシールする。
さらに、このボール弁では、キャビティ内に異常昇圧が生じた場合のリリーフが考慮されておらず、このようなボールシートがコイルスプリングで弾発される構造の場合、キャビティ内に異常昇圧が生じたときには、ボールシートがシートリテーナと共に一次側に移動してシートと弁体との間から圧力をリリーフするため、シートの弁体との接触面の摩耗が激しくなる。その結果、シールポイントが不安定になってリリーフ圧にばらつきが生じる。リリーフの際には、シートの接触部をこじ開けるように圧力が抜けるため、接触面にダメージが加わりやすいという問題も生じる。
これに加えて、キャビティ内の異常昇圧のリリーフにより、シートパッキンが消耗しやすいという問題もある。
11 ボデー
12 ボール
12a 貫通孔
13 ステム
14 シートリテーナ
15 ボールシート
15a 外周面
16 ボール面
25 シール面(シール部位)
27 内周面
30 おねじ部(係止部)
30a ねじ山
31 リリーフ溝
32 装着溝
32a 内周面
33 めねじ部(係合部)
33a ねじ山
35 キャビティ
40 連通部
A部 支点位置
B、C 封止部
CL クリアランス
L1、L2、L3 内径寸法
O 流路中心軸(流路軸芯)
ボデー11内には、上ステム13a、下ステム13bからなるステム13を介してボール12が回動可能に設けられ、このボール12の双方、すなわち上下流側にシートリテーナ14が配設され、このシートリテーナ14にボールシート15が取付けられる。ボール12はステンレス鋼を材料として形成され、バルブ本体10内の流路23と連通可能な貫通孔12aが設けられる。本実施形態では、ボール12の上下流側にボールシート15、シートリテーナ14が取付けられているが、これらは上下流側の一方又は双方に設けられていればよい。図1に示すように、上下流側にボールシート15、シートリテーナ14が取付けられているボールバルブ本体10の場合、図において右側又は左側の何れの側を一次側としてもよい。
ボールシート15外周のシートリテーナ14装着側にはおねじ部30が係止部として設けられ、このおねじ部30は、ボールシート15の装着方向の厚さに対して略半分程度の長さまで設けられる。
図示しないが、サイズ10B以上の大口径バルブについては、ボールシート15の外周に締付治具により締付け或は取外し可能となる溝や穴が設けられていてもよく、この場合、ボールシート15の組付けが容易になる。
本発明のトラニオン型ボールバルブは、図5において、シートリテーナ14の装着溝32内で飛び出しを防止し、フリーな状態で装着したボールシート15により高圧流体を封止できるようにしているため、部品点数を最小限に抑えつつ構造も単純化でき、かつボールシート15をシートリテーナ14に螺じ込むだけで装着できる。
ボールシート15の背面15aは、図7(a)に示すように、最内径位置のシールポイントPでシートリテーナ14と密着しており、この部位から流路23内の流体がキャビティ35に通過するのを防止している。
[キャビティ圧PR]×[ボールシート6の背面におけるキャビティ圧の受圧面積M]
で表すことができる。
また、受圧面積Mは、
受圧面積M=(φdR-φdP)2×π×4
で表すことができる。
の関係となるよう、シール径に差Tを設けている。この径の差Tを利用して、キャビティ圧によりシートリテーナ14がコイルばね41の弾発力に抗して、ボール12とは反対側に引き戻されるように設定している。
この引き戻し力は、自緊力ともいい、
[キャビティ圧PR]×[ボールシート15の装着溝32におけるキャビティ圧の受圧面積N]
で表すことができる。また、受圧面積Nは、
受圧面積N=(φdP-φdR)2×π×4
で表すことができる。
また、ボールシート15が拡径し、シートリテーナ14の装着溝32に設けられためねじ部33に過度に押圧されると、ボールシート15が損傷するおそれがある。このようなボールシート15の拡径現象は、図7に示すようなバルブ本体10の微開状態において、ボール12とボールシート15との狭小な空間に、流れの速い流体が浸入したときにより顕著となる。
また、平行面33bの内径を、ボールシート15の外径に近い寸法に設定することにより、ボールシート15の拡径を抑制し、ボールシート15とボール12とのシール位置のずれを低減することができる。
この実施形態では、ボールシート15の装着溝32側にはA部が環状に突出形成され、このA部は、装着溝32に当接して背面シール可能であり、支点位置となるように設けられている。ボールシート15は、装着溝32から飛び出し防止され、かつ、支点位置A部を中心にボール12側が開口する方向に弾性変形可能な状態で、図12のバルブ本体10の流路軸芯(流路中心軸)Oの方向に移動可能なフリーな状態で装着されている。
係合部60と係止部61との間の図11に示すように装入方向(図1の流路の軸芯Oの方向)には、空間Uが設けられる。有底穴34の内径が係合部60の外径よりもやや大きく設けられていることで、これらの間には径方向の隙間Gも設けられる。この隙間Gにより、ボールシート15がシートリテーナ14の空間Uの範囲において、摺動抵抗の少ない状態で進退可能となる。
Claims (11)
- ボデー内に設けた貫通孔を有するボールの一方又は双方にボールシートを装着したシートリテーナを配設し、前記ボールをステムを介して回動可能に設け、前記ボールシートは、前記シートリテーナに形成した装着溝内に飛び出しを防止し、かつフリーな状態で装着したボールバルブにおいて、全閉時または全開時のキャビティ内の異常昇圧による余剰の圧力をこの圧力を利用した自緊力で前記シートリテーナをボールとは反対方向に移動させ、かつ、装着溝内のボールシートの裏面側に流入した前記余剰の圧力でボールシートをボール側に押し出してボールシートの内周面と装着溝との間に設けた連通部を介して流路内にリリーフするようにしたことを特徴とするトラニオン型ボールバルブ。
- 前記装着溝の内周の開口側に設けた係合部に前記ボールシートの外周装着側に設けた係止部を装入方向に係止可能に対向させて前記シートリテーナの装着溝からの前記ボールシートの飛び出しを防止し、前記ボールシートを前記装着溝にフリーな状態で装着した請求項1に記載のトラニオン型ボールバルブ。
- 前記装着溝内周に設けためねじ部を係合部とし、このめねじ部に前記ボールシートのおねじ部を係止部として螺合し、前記おねじ部の後端側と前記めねじ部の後端側とを係止可能に設けて前記ボールシートの飛び出しを防止した請求項2に記載のトラニオン型ボールバルブ。
- 前記めねじ部内端のねじ山と前記おねじ部外端のねじ山とを係止させて前記ボールシートの飛び出しを防止した請求項3に記載のトラニオン型ボールバルブ。
- 前記ボールシートの内周面、または、この内周面に対向するシートリテーナの装着溝に、前記連通部を構成する少なくとも一つのリリーフ溝を形成した請求項1乃至3の何れか1項に記載のトラニオン型ボールバルブ。
- 前記ボールシートの背面シールの支点位置であるA部の内径寸法を前記ボールシートのシール部位よりも内径寄りに設け、高圧時におけるボールシートがA部を支点として開くように弾性変形して前記シール部位を外径側より内径側に向けて少なくとも面接触状態にシールするようにした請求項1に記載のトラニオン型ボールバルブ。
- 前記支点位置であるA部と前記シール部位である封止部B及び封止部Cの位置関係を、内径寸法に対してA<C<Bとした請求項6に記載のトラニオン型ボールバルブ。
- 請求項7において、組立初期及び流体圧力が低圧の場合、前記封止部Bが線接触状態を保持し、かつ前記封止部Cがボール面に非接触状態としたトラニオン型ボールバルブ。
- 前記ボールシートのシール部位を球状面に形成し、この球状面は、その中心を前記ボールの中心と同様に前記ボデー内の流路軸芯上に配置すると共に、その内径を前記ボールの球形よりも縮径して形成した請求項6乃至8の何れか1項に記載のトラニオン型ボールバルブ。
- 前記装着溝の内周面と前記ボールシートのシール面側の外周面との間に所定のクリアランスを設け、高圧時にボールシートが開くようにすると共に、開き過ぎを抑制するようにした請求項6に記載のトラニオン型ボールバルブ。
- 前記装着溝に形成した係止部内周面と前記ボールシートの外周面側との間にクリアランスを設けた請求項10に記載のトラニオン型ボールバルブ。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201580059196.4A CN107110385B (zh) | 2014-10-28 | 2015-08-27 | 固定型球阀 |
EP15855254.7A EP3098491B1 (en) | 2014-10-28 | 2015-08-27 | Trunnion-type ball valve |
US15/108,685 US10018276B2 (en) | 2014-10-28 | 2015-08-27 | Trunnion-type ball valve |
KR1020167017726A KR101956090B1 (ko) | 2014-10-28 | 2015-08-27 | 트러니언형 볼 밸브 |
ES15855254T ES2813378T3 (es) | 2014-10-28 | 2015-08-27 | Válvula de bola de tipo Trunnion |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2014-219455 | 2014-10-28 | ||
JP2014219455A JP6426435B2 (ja) | 2014-10-28 | 2014-10-28 | トラニオン型ボールバルブ |
JP2015014295A JP6474262B2 (ja) | 2015-01-28 | 2015-01-28 | トラニオン型ボールバルブ |
JP2015-014295 | 2015-01-28 |
Publications (1)
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WO2016067737A1 true WO2016067737A1 (ja) | 2016-05-06 |
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PCT/JP2015/074234 WO2016067737A1 (ja) | 2014-10-28 | 2015-08-27 | トラニオン型ボールバルブ |
Country Status (6)
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US (1) | US10018276B2 (ja) |
EP (1) | EP3098491B1 (ja) |
KR (1) | KR101956090B1 (ja) |
CN (1) | CN107110385B (ja) |
ES (1) | ES2813378T3 (ja) |
WO (1) | WO2016067737A1 (ja) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
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JPWO2018003977A1 (ja) * | 2016-06-30 | 2018-11-15 | 株式会社キッツ | バルブ用耐圧検査装置とその検査方法並びに水素ガス検出ユニットとバルブ |
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DE102021120801A1 (de) | 2021-08-10 | 2023-02-16 | MSP-Armaturen GmbH | Kugelhahn |
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- 2015-08-27 EP EP15855254.7A patent/EP3098491B1/en active Active
- 2015-08-27 ES ES15855254T patent/ES2813378T3/es active Active
- 2015-08-27 US US15/108,685 patent/US10018276B2/en active Active
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Also Published As
Publication number | Publication date |
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KR20170072832A (ko) | 2017-06-27 |
EP3098491A1 (en) | 2016-11-30 |
EP3098491B1 (en) | 2020-06-03 |
KR101956090B1 (ko) | 2019-03-08 |
EP3098491A4 (en) | 2017-11-22 |
CN107110385A (zh) | 2017-08-29 |
US20160319940A1 (en) | 2016-11-03 |
ES2813378T3 (es) | 2021-03-23 |
CN107110385B (zh) | 2019-09-17 |
US10018276B2 (en) | 2018-07-10 |
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