Source: https://patents.google.com/patent/JP4316655B2/en
Timestamp: 2020-07-15 09:40:32
Document Index: 403791159

Matched Legal Cases: ['arts 10', 'art 13', 'art 13', 'art) 14', 'art 13', 'art 12', 'art 13', 'art 3', 'art 8', 'art 10', 'art 14']

JP4316655B2 - Butterfly valve - Google Patents
JP4316655B2
JP4316655B2 JP2008189148A JP2008189148A JP4316655B2 JP 4316655 B2 JP4316655 B2 JP 4316655B2 JP 2008189148 A JP2008189148 A JP 2008189148A JP 2008189148 A JP2008189148 A JP 2008189148A JP 4316655 B2 JP4316655 B2 JP 4316655B2
JP2008189148A
JP2008249150A (en
好治 佐藤
2001-02-26 Priority to JP2001050665 priority Critical
2008-07-22 Application filed by 株式会社キッツ filed Critical 株式会社キッツ
2008-07-22 Priority to JP2008189148A priority patent/JP4316655B2/en
2008-10-16 Publication of JP2008249150A publication Critical patent/JP2008249150A/en
2009-08-19 Publication of JP4316655B2 publication Critical patent/JP4316655B2/en
230000003628 erosive Effects 0.000 description 10
The present invention has a tight shut function and, in addition to preventing the occurrence of erosion, makes it possible to adjust a minute flow rate particularly in a low opening range or a small opening range, and has a remarkable effect on high range ability. It is related with the butterfly valve which has.
The butterfly valve is simple in structure, has features such as light weight and low operating force, and is therefore used as a stop valve or a flow rate adjusting valve depending on the purpose and application. In particular, when used as a flow control valve, cavitation may occur on the downstream side of the valve body at low opening, generating vibration and noise, and so-called erosion that damages and erodes the valve body and piping may occur. There is.
In order to solve these problems, various countermeasures have been proposed so far.
For example, Japanese Patent Application Laid-Open No. 57-157866 discloses a method in which comb-like protrusions are provided on the outer peripheral edge of a valve body, and the cavitation generated on the downstream side of the valve body is suppressed by changing the fluid into a jet flow with the protrusions. It is. Japanese Utility Model Laid-Open No. 62-6568 is a method in which band members are provided on both outer peripheral portions of a valve body, and a large number of small hole groups are formed in these band members to rectify turbulent flow. Japanese Patent Publication No. 5-78713 or Japanese Utility Model Laid-Open No. 5-8139 is a means for preventing cavitation by attaching a current plate to the secondary side of the valve body. Furthermore, Utility Model Registration No. 2589805 is a butterfly valve in which a wing body is provided on one side of an eccentric valve body and a large number of small holes are provided in the wing body to suppress cavitation. Japanese Patent No. 43553 is a butterfly valve that attempts to suppress cavitation by forming small through holes in the circumferential protrusions on both sides of the valve body. Japanese Patent Application Laid-Open No. 7-208615 is a valve that attempts to suppress cavitation by forming small holes in the blades on both sides of the valve body.
JP-A-57-157866 Japanese Utility Model Publication No. 62-6568 Japanese Patent Publication No. 5-78713 Japanese Utility Model Publication No. 5-8139 Utility Model Registration No. 2589805 No. 7-43553 JP-A-7-208615
However, each of the conventional methods described above is mainly intended to rectify the flow of fluid and prevent cavitation, so that the amount of fluid is adjusted in a low opening range or a small opening range. This is practically impossible, and it is insufficient as a control valve for adjusting the flow rate in the low opening range or the fine opening range, so there is no effective product with high rangeability performance. The actual situation was.
For example, this type of butterfly valve used in air-conditioning equipment is used in the fully open state during the summer demand period, while at other times the low opening in the adjustment range of 40% or less is used. Usually, the valve is used in the state of the degree range or the fine opening range, and depending on the purpose of use, this type of valve is often used for fluid control in the low opening range or the fine opening range.
In particular, this butterfly valve is often used with a ring-shaped rubber sheet attached to the valve seat, and if this is used in a low or small opening range, the flow between the valve body and the rubber sheet is low. There is also a possibility that a so-called erosion phenomenon that a rubber sheet or the like is eroded by the flow speed is generated due to the narrowed road.
The present invention has been developed to solve various conventional problems, and its purpose is to have an anti-cavitation function and to prevent the occurrence of erosion. An object of the present invention is to provide a butterfly valve that exhibits a high range ability and is excellent in control function and tight shut function by enabling a minute flow rate adjustment of a fluid in an opening range or a low opening range.
In order to achieve the above object, the invention according to claim 1 is a butterfly valve for opening and closing an elastic seat ring mounted on a cylindrical valve box by the rotation of a disc-shaped valve body. the valve closure is formed on the valve outside perimeter, it closed valve to press the valve closure the elastic seat ring, toward the downstream side of the valve closure of the orifice side and the upstream side of the valve closure portion of the nozzle side A pressure valve portion, which is an outer peripheral spherical wing-shaped piece, is provided to close the nozzle-side flow path by making the pressure valve portion press-contact with the elastic seat ring in the small opening range, and at the orifice side An inflow portion or a flow passage opening that opens along the secondary side of the valve is formed only in the pressure valve portion, and the length of the pressure valve portion, which is the wing-shaped piece, is changed between the nozzle side and the orifice side. When the nozzle leaves the elastic seat ring, Pterygium is a butterfly valve so as to maintain the state of being pressed by the resilient seat ring.
As described above, according to the present invention, a butterfly valve using an elastic seat ring that can be tightly shut, and that achieves a remarkably high rangeability as compared with the past while preventing the erosion phenomenon of the elastic seat ring. A valve can be provided.
Moreover, it can utilize as a control valve which can be used by low opening degree by replacing the valve body in this invention with the butterfly valve using a normal seat ring.
Furthermore, it is possible to provide a butterfly valve that is a control valve that has a wide flow rate adjustment range such as equal percent characteristics, low noise, low torque, and is inexpensive .
In addition, by changing the length of the pressure valve portion between the orifice side and the nozzle side, even if one pressure valve portion is separated from the seat ring, the state where the other pressure valve portion is pressed against the seat ring is maintained. Therefore, the occurrence of the jumping phenomenon of the valve body can be surely prevented.
BEST MODE FOR CARRYING OUT THE INVENTION In order to describe the best mode for carrying out the present invention in detail, this will be described with reference to the accompanying drawings.
5 and 6, the butterfly valve of the present example has a rubber elastic seat ring 2 such as NBR or EPDM attached to the inner periphery of a cylindrical valve box 1 by a baking means. A disc-like valve body 3 is rotatably provided to open and close the valve body 3.
Further, as shown in FIG. 1, mounting portions 6 and 7 for attaching the upper stem 4 and the lower stem 5 are formed at the center facing position of the valve body 3, and the valve formed on the outer peripheral edge of the valve body 3. The closing portions 3a and 3b have a shape that exhibits a valve closing function (tight shut function).
As shown in FIG. 4, the valve body 3 is formed such that the orifice-side valve closing portion 3a is inclined toward the valve primary side at an angle of about 3 ° with respect to the nozzle-side valve closing portion 3b. As a result, the orifice-side valve closing portion 3a contacts the seat ring 2 at a shallow angle, the range pressed against the seat ring 2 is narrowed, and the amount of the orifice-side valve closing portion 3a that bites into the seat ring 2 is reduced. Therefore, when the valve body 3 is rotated from the valve fully closed position, the so-called jumping phenomenon in which the valve body 3 moves suddenly is suppressed, and the orifice side valve closing portion 3a is quickly separated from the seat ring 2 to reduce the Flow rate adjustment can be started from the opening.
The inclination angle shown above should be small in order to start the flow rate adjustment from a low opening, while it is better to increase as the valve nominal diameter becomes smaller (example: 3 ° in the case of 100A, 50A) Case is 7 °). This is because a valve with a small nominal diameter has a small valve body radius, and the width of movement of the valve body at the maximum movable part (position perpendicular to the valve shaft) of the valve shaft (stem) rotation angle This is because is small. Therefore, the inclination angle is preferably 3 ° to 7 °.
3 and 4, press valve portions 10 and 11 are formed on the orifice side 8 and the nozzle side 9 around the stems 4 and 5 of the valve body 3. The pressure valve portions 10 and 11 are in pressure contact with the elastic seat ring 2 when the valve body 3 is at a low opening degree, and in particular, a so-called erosion phenomenon on the orifice side 8 is prevented. The orifice side 8 refers to the opening where the valve body 3 is on the upstream side, and the nozzle side 9 refers to the opening where the valve body 3 is on the downstream side.
The press valve parts 10 and 11 in this example are wing-like pieces (press valve parts) 10a and 11a formed on the outer peripheral edges of the valve body 3 toward the closing direction side of the valve body 3, respectively. 11 a has a function of pressing and contacting the elastic seat ring 2 when the valve body 3 is at a low opening degree, and an outer peripheral surface thereof is formed in a spherical shape so as to make spherical contact with an inner peripheral surface of the seat ring 2. In the wing-like pieces 10a and 11a, the positive pressure and the negative pressure are balanced and the pressure is balanced, so that the valve body 3 can be moved with a light operating force, and the operating torque of the valve can be significantly reduced.
As shown in FIG. 4, on the basis of the nozzle side valve closing portion 3b, the angle α of the wing piece 10a on the orifice side 8 is set to 27 °, and the angle β of the wing piece 11a on the nozzle side 9 is set to 30 °. , Α <β. Even if the wing-like piece 10a on the orifice side 8 is separated from the seat ring 2 and the fluid flows into a crescent-shaped channel (not shown) formed between the orifice side 8 and the seat ring 2, the nozzle This is because a fluid is not allowed to flow from the side 9 so as to obtain a predetermined flow rate characteristic (equal percent characteristic or the like) through the communication part 13, the inlets 14 and 15, and the crescent-shaped channel described above.
In addition, by changing the length of the pressure valve portions 10 and 11 between the orifice side 8 and the nozzle side 9 in this way, even if one pressure valve portion is separated from the seat ring 2, the other pressure valve portion is still the seat ring. 2 is maintained, it is possible to further prevent the jumping phenomenon of the valve body 3.
The lengths of the press valve portions 10 and 11 are set in consideration of flow rate control and cavitation suppression. This setting varies depending on the valve diameter. For example, α <β is preferable for the valve nominal diameter 50A. However, if the degree of considering the suppression of cavitation increases as the diameter increases, such as the nominal diameter 150A, α> β. There is also a case. Therefore, α and β may be in a relationship of α ≠ β from the viewpoint of suppressing the occurrence of the jumping phenomenon of the valve body 3.
In this embodiment, the diameter φB of the press valve portions 10 and 11 and the diameter φA of the valve body 3 are the same size, but as shown in FIGS. 11 and 12, the diameter of the press valve portions 10 and 11 is the same. φB may be formed to be smaller than the diameter φA of the valve body 3 (valve closing portion 3a). In this case, the seat ring by the pressure valve portions 10a and 11a is less than the pressing amount a to the seat ring 2 by the valve body 3. The pressing amount b to 2 is smaller. That is, by making the diameter φB smaller than φA, the pressing amount of the seat ring 2 is set as a> b, and the sliding resistance on the φB side accompanying the rotation of the valve body 3 is reduced. This prevents the jumping phenomenon.
As shown in FIG. 1, a void portion (slit) 12 is formed on the orifice side 8 of the valve body 3 on the outer peripheral edge of the valve body 3 or on the downstream side of the outer peripheral edge. A communication portion (communication hole) 13 that communicates toward the side is formed. This gap portion (slit) 12 attenuates the fluid flowing from the primary valve side to the secondary valve side via the communicating portion 13 in the fine valve opening range (3 ° to 5 ° in this example), and its pressure Is provided so as not to fall below the saturated water vapor pressure of the fluid and prevent cavitation. That is, in FIG. 9, since the inner wall 12a of the gap 12 exhibits the function of a resistance plate, the gap 12 has a function as a pressure chamber. The width of the gap portion (slit) 12 is preferably wide in order to allow a large amount of fluid to flow, but narrow in order to prevent the seat ring 2 from biting into the slit 12. Furthermore, considering the case where the slit 12 is formed at the time of casting, etc., the optimum dimension is set to 3 mm to 10 mm, although it varies depending on the nominal diameter of the valve. The depth of the slit 12 is set to 1/3 to 1/2 of the distance between the maximum movable part of the valve body and the center of the valve body in consideration of flow maximum setting and casting.
This communication portion 13 is provided to control the flow rate flowing from the valve primary side to the valve secondary side in the fine valve opening range, and in this example, four communication portions 13 are provided at the maximum rotation portion on the orifice side. However, these sizes, shapes, and numbers are arbitrary depending on the implementation, and the flow characteristics can be arbitrarily changed by changing the hole diameter and the arrangement interval.
Furthermore, by providing the communication part 13 in the vicinity of the bottom part of the slit 12, the fluid can flow to the valve secondary side in a state where the influence of cavitation is sufficiently removed in the slit 12. The shape and number of the communication portions 13 are arbitrary depending on the target fluid characteristics, but the sum of the opening areas is equal to or larger than the opening area of the slits 12 on the outer periphery of the valve body, so that the flow into the slits 12 It is possible to efficiently guide the fluid to the secondary side without extremely reducing the fluid.
Further, as shown in FIG. 1, the wing-like piece 10a on the orifice side 8 is provided with a plurality of radial inflow portions (inflow holes) 14 that flow in from the outer peripheral surface toward the downstream side, or are provided in a radial manner. As shown in FIG. 13, a plurality of micro inflow portions (inflow holes) 14 and micro inflow portions 15 that flow in from the outer peripheral surface toward the downstream side are provided in a radial pattern. Each is provided so as to have a rectifying action. The minute inflow portion 15 is an inflow hole provided on the slit 12 side rather than the minute inflow portion 14 side, and is provided in order to increase the resolution of the flow rate control for each rotation of the valve shaft (stem). It is preferable to provide a large valve, for example, a valve having a nominal diameter of 200A or more.
These inflow holes 14 and 15 are provided for controlling the flow rate flowing from the valve primary side to the valve secondary side together with the communication portion 13 mainly in the low valve opening range (5 ° to 30 ° in this example). .
In this example, as shown in FIGS. 1 and 2, the circular inlet (inflow part) 14 having the same shape is arranged on the meridian of the spherical outer peripheral surface of the wing-shaped piece 10 a and centered on the maximum movable part of the valve body 3. Five are arranged at an angular interval of 20 degrees. When the valve is opened, fluid begins to flow simultaneously through the five holes 14 as the valve body 3 rotates, and as the valve opening increases, the flow rate passing through the holes 14 varies depending on the difference in position. .
On the other hand, as shown in FIG. 4, since the nozzle side 9 of the valve body 3 is not provided with a hole for communicating the primary side and the secondary side of the valve, fluid in the fine valve opening range and the low valve opening range is provided. All flow through the communicating portion 13 and the inflow hole 14 provided in the valve body 3 on the orifice side 8, so that accurate flow rate control can be performed even in a low valve opening range, and high rangeability is realized. A butterfly valve can be obtained.
In the figure, reference numeral 16 denotes a flange portion fixed to the pipe 17, and the butterfly valve of this example is sandwiched between the flange portions 16 and 16 with bolts and nuts.
In FIG. 5, when the valve body 3 is in the fully closed state (valve opening degree 0%), when a liquid (fluid) such as water flows from the right side indicated by the arrow, the valve closing portions 3a and 3b of the valve body 3 are made of rubber. The seat ring 2 is pressed and in close contact with the fully-closed state.
In the fully closed state, the nozzle side valve closing portion 3b is pressed and intimately inclined slightly with respect to the seat ring 2, and the orifice side valve closing portion 3a is pressed and intimately contacted with the seat ring 2 at an angle more inclined than that. is doing.
Next, as shown in FIG. 9, when the valve body 3 is rotated counterclockwise to the valve opening (5 to 10%), the orifice side valve closing portion 3a causes a jumping phenomenon as described above. The nozzle-side valve closing portion 3b is separated from the seat ring 2 afterward.
In this case, a liquid with a small flow rate is rectified from the vicinity of the orifice side maximum rotation portion of the valve body 3, and the communication portion 13 communicates with the secondary side of the valve while suppressing the generation of vortex and turbulence, and in particular, the slit 12 has a minute amount. When liquid flows in at a flow rate, the liquid collides with the inner wall 12a of the gap 12 so that the momentum is reduced to the extent that it does not fall below the saturated water vapor pressure, the generation of the low pressure portion is prevented, and the occurrence of cavitation is suppressed. However, the minute flow rate can be adjusted while suppressing the generation of noise. Subsequently, as the valve body 3 is sequentially rotated, the opening area of the gap portion 12 increases and the flow rate gradually increases, so that the minute flow rate can be controlled with high accuracy and functions as a control valve.
That is, since the pressing valve portion 10 of the valve body 3, in this example, the wing-like piece 10 a presses and contacts the elastic sheet ring 2, the liquid reliably passes without passing between the pressing valve portion 10 and the elastic sheet ring 2. It passes through the communication part 13. Therefore, the minute flow rate control depending on the shape of the communication portion 13 can be performed without the elastic seat ring 2 being eroded by a so-called erosion phenomenon.
In FIGS. 11 and 12, when the valve opening is 10% from the valve closed state when the valve opening is 0%, the pressing amount of the seat ring 2 by the pressing valve portions 10 and 11 is a> b. The spherical wing-like pieces 10a and 11a of the pressing valve portions 10 and 11 press the inner peripheral surface of the seat ring 2 with a force weaker than the pressing force to the seat ring 2 by the valve closing portion 3a. Since the sliding resistance when rotating the valve shaft is small, the opening degree can be adjusted slightly without the valve body 3 rotating rapidly, so that a so-called jumping phenomenon can be reliably prevented.
Next, as shown in FIG. 10, when the valve opening degree is 15%, the liquid (fluid) flows out from the valve body 3 of the maximum rotation part through the gap part 12 while being rectified from the communication part 13, Since the liquid flows in from the minute inflow portion 15, the liquid is rectified, whilst vortex flow and turbulence are suppressed, and a rapid increase in the flow velocity is suppressed, so that generation of a low pressure portion can be prevented. In addition, the minute flow rate can be adjusted while being rectified.
Even at this valve opening, the pressing valve portion 10 of the valve body 3 presses and contacts the elastic seat ring 2, so that the liquid does not pass between the pressing valve portion 10 and the elastic seat ring 2, and the communication portion 13 is surely provided. And passes through the minute inflow portion 15. Therefore, the minute flow rate control depending on the shapes of the communicating portion 13 and the minute inflow portion 15 can be performed without the elastic seat ring 2 being eroded by a so-called erosion phenomenon.
Further, as shown in FIG. 6, when the valve opening degree is 28%, on the orifice side 8, the liquid communicates from the gap portion 12 through the communicating portion 13 and flows radially from the minute inflow portions 14 and 15. When the body 3 passes through the orifice side 8, vortex flow and turbulence on the orifice side are suppressed and flows while being rectified, the occurrence of cavitation is suppressed, erosion is prevented, and noise and vibration are not generated. Occurrence is suppressed.
In the valve opening shown in FIG. 6, the liquid also passes between the pressing valve portion 10 and the elastic seat ring 2, but the liquid flows in a dispersed manner in the communication portion 13 and the minute inflow portions 14 and 15. The elastic sheet ring 2 is not eroded by the erosion phenomenon.
Thus, as shown in FIGS. 5 and 6, when the valve body 3 rotates, the spherical wing-like pieces 10 a and 11 a of the press valve portions 10 and 11 press the inner peripheral surface of the seat ring 2. Since the opening degree can be adjusted slightly without the valve body 3 rotating rapidly due to the elastic force of the seat ring 2 at a very small opening degree, so-called jumping phenomenon can be reliably prevented, It functions as a control valve that enables flow rate adjustment.
In the case of a butterfly valve using a rubber sheet, as is clear from the comparative example shown in FIG. 7 and FIG. In general, control is performed. On the other hand, according to the present example, as shown in the figure, the flow rate can be adjusted in the range of 0 ° to 30 °, and the Cv value at the valve opening degree where the flow rate can be adjusted is made as small as possible. And high range ability performance can be obtained. FIG. 7 is a graph showing the relationship between the valve opening degree and the Cv value in the present invention and showing the high range ability state, and shows the high range ability characteristic. In this case, the Cv value is lower than that of the comparative product as the valve is fully opened. In particular, when the butterfly valve of the present invention is used in the hot water or cold water supply line to the air conditioner, the opening degree is usually low. Therefore, the actual use is not affected.
In the figure, all data are for a nominal valve diameter of 100A, and the valve body material is SCS13A. The comparative product data is for a butterfly valve using a known center type valve body, and no flow path opening or wing portion is formed on the valve body. Other parts such as the seat ring are the same as those of the present invention.
In the comparative example in the figure, the flow rate can be accurately controlled in the range of about 30% to 80% of the valve opening, and the range ability is 10: 1. On the other hand, it was confirmed that the product of the present invention can perform accurate flow rate control within a valve opening range of about 10% to 100% and obtain a high rangeability characteristic of 200: 1.
FIG. 13 shows another example of the butterfly valve according to the present invention. The same parts as those in the above example are indicated by the same reference numerals, and the description thereof is omitted. In the same figure, a plurality of flow path holes 13a are provided without providing slits, and the flow rate can be adjusted by flowing a fluid through the communication portion (flow path port) 13a in the fine opening range. It has substantially the same effect as the example.
FIGS. 14-16 shows the other example of the valve body in this invention, The slit 19 and the slit 20 are formed in the outer periphery of the valve body 18, Furthermore, the communication hole 21 and the communication hole 22 are formed, In addition to rectifying the fluid, generation of a low-pressure portion on the downstream side of the valve body 18 is prevented, cavitation is suppressed, and flow control in a low opening range is made possible. In this case, the relationship is set such that the diameter of the communication hole 21> the diameter of the communication hole 22, and the flow rate is increased as the valve opening increases.
In addition, the sizes of the slit 19 and the slit 20 are set so that the relationship of slit 19> slit 20 is established, and the fluid pressure is attenuated step by step to prevent the occurrence of cavitation. That is, as shown in FIGS. 15 and 16, the relationship of slit 19> slit 20 is set so as not to be equal to or lower than the saturated water vapor pressure to prevent cavitation.
FIG. 17 shows still another example of the valve body 23 according to the present invention, which is provided with slits 24, 25, 26 and communication holes 27, 28, 29. It goes without saying that the other examples also exhibit substantially the same functions and effects as the above embodiments.
In addition, by arranging a strainer on the upstream side of the butterfly valve of each example in the present invention and using it as a valve system, the liquid after the foreign matter is removed by the strainer can be guided to the butterfly valve of the present invention, and the communication portion The flow rate control with high accuracy can be continued without clogging 13 and the inflow portions 14 and 15.
It is the perspective view which showed an example of the valve body used for the butterfly valve in this invention. It is a front view of FIG. It is the sectional view on the AA line of FIG. FIG. 3 is a plan view of FIG. 2. It is sectional drawing which shows the state of valve opening 0% of the butterfly valve in this invention. It is sectional drawing which shows the valve opening degree 28% in FIG. 5, and a fully open state of 100%. It is the graph which showed the high range ability characteristic of the butterfly valve in this invention. It is the graph which expanded and showed the low opening degree area range in FIG. It is the elements on larger scale which showed the state by the side of the orifice of valve opening degree 10%. It is the elements on larger scale which showed the state of 15% of valve opening in FIG. It is a partial explanatory view of valve opening degree 0% explaining the jumping phenomenon of a valve element. FIG. 12 is a partial explanatory view showing a state in which the valve opening degree is 10% in FIG. 11. FIG. 10 is a partial enlarged cross-sectional view illustrating another example of the example illustrated in FIG. 9. It is sectional explanatory drawing which showed the other example of the butterfly valve in this invention. It is a partially cutaway enlarged view of the valve body in FIG. It is explanatory drawing explaining prevention of cavitation generation | occurrence | production with the valve body structure in FIG. It is the partially cutaway enlarged view of the valve body which showed the further another example of the butterfly valve in this invention.
DESCRIPTION OF SYMBOLS 1 Cylindrical valve box 2 Elastic seat ring 3 Valve body 3a Orifice side valve closing part 3b Nozzle side valve closing part 8 Orifice side 9 Nozzle side 10,11 Pressing valve part 10a, 11a Wing piece 12 Gap part (slit)
13 Communication part 14, 15 Inflow part
A butterfly valve for opening and closing the inside of the resilient seat ring mounted on the cylindrical valve case in the rotation of the disk-shaped valve body, and a valve closure the valve outside periphery of the orifice side and the nozzle side, the valve closure Press the elastic seat ring to close the valve, and press the pressure valve part which is an outer peripheral spherical wing-shaped piece toward the downstream side of the valve closing part on the orifice side and toward the upstream side of the valve closing part on the nozzle side. In the fine opening range, the pressure valve portion is pressed against the elastic seat ring to close the flow path on the nozzle side, and only the pressure valve portion on the orifice side opens along the valve secondary side. The pressure valve portion, which is the wing-shaped piece, is changed between the nozzle side and the orifice side, and the wing-shaped piece on the nozzle side is elastic when the wing-shaped piece on the orifice side leaves the elastic sheet ring. The state pressed by the seat ring Butterfly valve, characterized in that so as to lifting.
JP2008189148A 2001-02-26 2008-07-22 Butterfly valve Active JP4316655B2 (en)
JP2001050665 2001-02-26
JP2008189148A JP4316655B2 (en) 2001-02-26 2008-07-22 Butterfly valve
JP2002567722 Division
JP2008249150A JP2008249150A (en) 2008-10-16
JP4316655B2 true JP4316655B2 (en) 2009-08-19
ID=18911590
JP2002567722A Active JP4209193B2 (en) 2001-02-26 2002-02-26 Butterfly valve
JP2008189148A Active JP4316655B2 (en) 2001-02-26 2008-07-22 Butterfly valve
JP2008189149A Active JP4252618B2 (en) 2001-02-26 2008-07-22 Butterfly valve
JP2009062265A Active JP4808792B2 (en) 2001-02-26 2009-03-16 Butterfly valve
US (1) US6758458B2 (en)
JP (4) JP4209193B2 (en)
CN (1) CN1303347C (en)
WO (1) WO2002068846A1 (en)
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2002-02-26 CN CNB028045807A patent/CN1303347C/en not_active IP Right Cessation
2002-02-26 US US10/250,445 patent/US6758458B2/en not_active Expired - Fee Related
2002-02-26 WO PCT/JP2002/001732 patent/WO2002068846A1/en active Application Filing
2002-02-26 JP JP2002567722A patent/JP4209193B2/en active Active
2008-07-22 JP JP2008189148A patent/JP4316655B2/en active Active
2008-07-22 JP JP2008189149A patent/JP4252618B2/en active Active
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JP4252618B2 (en) 2009-04-08
JP2009174719A (en) 2009-08-06
US20040051071A1 (en) 2004-03-18
JP2008249150A (en) 2008-10-16
US6758458B2 (en) 2004-07-06
JPWO2002068846A1 (en) 2004-06-24
JP4808792B2 (en) 2011-11-02
JP4209193B2 (en) 2009-01-14
CN1498319A (en) 2004-05-19
WO2002068846A1 (en) 2002-09-06
JP2008249151A (en) 2008-10-16
CN1303347C (en) 2007-03-07
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2008-08-02 A871 Explanation of circumstances concerning accelerated examination
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