GB1561593A - Creation of Inventions and Patents with Artificial Intelligence

GB1561593A – Valve structure
– Google Patents

GB1561593A – Valve structure
– Google Patents
Valve structure

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Publication number
GB1561593A

GB1561593A
GB40838/76A
GB4083876A
GB1561593A
GB 1561593 A
GB1561593 A
GB 1561593A
GB 40838/76 A
GB40838/76 A
GB 40838/76A
GB 4083876 A
GB4083876 A
GB 4083876A
GB 1561593 A
GB1561593 A
GB 1561593A
Authority
GB
United Kingdom
Prior art keywords
seal
valve
closure member
closure
sealing portion
Prior art date
1975-10-02
Legal status (The legal status 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 status listed.)

Expired

Application number
GB40838/76A
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)

Fisher Controls International LLC

Original Assignee
Fisher Controls International LLC
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.)
1975-10-02
Filing date
1976-10-01
Publication date
1980-02-27

1976-10-01
Application filed by Fisher Controls International LLC
filed
Critical
Fisher Controls International LLC

1980-02-27
Publication of GB1561593A
publication
Critical
patent/GB1561593A/en

Status
Expired
legal-status
Critical
Current

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Classifications

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL

F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING

F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary

F16K5/06—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having spherical surfaces; Packings therefor

F16K5/0663—Packings

F16K5/0668—Single packings

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL

F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING

F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces

F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members

F16K1/18—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps

F16K1/22—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation crossing the valve member, e.g. butterfly valves

F16K1/226—Shaping or arrangements of the sealing

F16K1/228—Movable sealing bodies

F16K1/2285—Movable sealing bodies the movement being caused by the flowing medium

Description

(54) A VALVE STUCTURE
(71) We, FISHER CONTROLS COMPANY
INC., a corporation organised under the laws of the State of Delaware, United States of America, of Marshalltown, State of Iowa,
United States of America, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement:- This invention ralates generally to valve structures and more particularly to valve seal designs which permit sealing effectiveness under the influence of fluid pressure acting upon the valve.
Heretofore, in valves having a pivotable valve closure member which includes a segment of a sphere as a sealing surface, e.g.
butterfly or ball valves, it has been common to employ valve seals of many different configurations and materials. One approach, proposed in U.S. Patent 3,734A57 to Roos, has been to provide a valve seal ring which is of lesser inside diameter of the sealing surface of the valve closure element and which is partially restrained against radial stretching by a resilient metal hoop, whereby an interference fit is achieved between the seal and the disk resulting in compression of the seal and stretching of the hoop upon closing the disk. Still another prior art approach suggested by Helman et al. in
U.S.Patent 3,608,861 and by Swain in
Canadian Patent 695,037 has been to provide a seal member retained in a valve body recess and a rigid annular projection on the downstream side of the body recess which function as a fulcrum to limit flexure under the influence of fluid pressure to improve sealing effectiveness. These seals have included polymeric or elastomeric elements, and thus have been limited to a temperature range below the breakdown temperature of the polymer or elastomer employed.
Prior art metallic seals, suitable for elevated temperatures, are proposed in U.S.
Patent 3,834,663 to Donnelly, U.S. Patents 3,077,332 and 3,153,427 to Burtis, and Swiss
Patent 383,104 to Swain. Such seals are characterized by resilient expansion in a radial direction upon closure d a valve disk, and may rely on the influence of pressure acting on the seal member to enhance sealing effectiveness over some or all of the range of operating pressure.
While these and other related approaches to butterfly and ball valve seal design have proven effective in some applications, nevertheless certain problems have been encountered. In particular, valves employing prior art seal configurations have not always proven effective in bidirectional service, i.e.
in applications in which the higher fluid pressure may be applied to either side of the valve. Further, such seals have been, for the most part, useful only within a limited range of operating pressures.
It is an object of this invention to provide a valve seal for valves having a valve closure member, such as butterfly valves or ball valves, the effectiveness of which is increased by differential fluid pressures acting on the valve in either direction, which will compensate for movement of the valve closure member under the influence of fluid differential pressure.
The seal design in general remains effective at high temperature and compensation is provided for the effects of thermal expansion, or contraction, and wear.
According to the present invention there is provided a valve structure comprising:
a unitary metallic annular seal member having an inner sealing portion of generally
U-shaped cross section, a resilient flexible web portion extending generally outwardly from said sealing potion, and an outer periphery extending outwardly from said web portion, and including a locus of flexure points at the junction of said web and said periphery;
a valve body having a central bore and means within said bore for sealingly engaging said periphery of said seal;;
valve closure means pivotable within said bore between open and closed positions, said closure means having a circumferential sealing surface converging generally toward an axis of said body bore for sealingly engaging said sealing portion of said seal in an interference fit in a region of contact when said closure means is in a closed position;
said locus of flexure points being displaced in the direction of convergence of said sealing surface of said closure means from said region of contact between said seal member and said closure means, whereby upon pivoting of said closure means to said closed position, said inner sealing portion of said seal is radially stretched to accommodate said closure means, and said web portion is resiliently deflected axially and placed in generally outward compression.
In operation, when the valve closure member is pivoted to a closed position the converging surface on the periphery thereof engages the inner sealing portion of the seal member and forces the seal member to expand. In the absence of differential pressure across the valve, sealing portion of the seal member is thus stretched radially, while the web portion functions as a Belleville spring as required to permit axial deflection and radial expansion of the seal member to accommodate the closure member, and the web portion of the seal is placed in radial compression.Under the influence of differential pressure applied from the side of the valve opposite the converging surface of the valve closure member, the closure member is moved in the direction of convergence, wedging its converging surface into the seal member in the downstream direction to increase the sealing force between the seal member and the closure member. When differential pressure is applied from the direction of convergence of the closure member periphery, the closure member is moved away from the direction of convergence, while circumferential hoop stresses in the sealing portion of the seal member induced by initial closure of the closure member cooperate with axial forces provided by the resilient web portion and further aided by the effect of differential pressure acting on the seal to maintain sealing engagement between the seal member and the closure member.
Attention is now directed to the drawings, in which:
FIG. 1 is a partial cross-sectional view of a butterfly valve including a seal embodying the present invention;
FIG. 2 is an enlarged detailed crosssectional view of the seal of FIG. 1, showing the relative dimensions and locations of the seal elements when the valve is opened, and the valve disk when closed, respectively;
FIG. 3 is a detailed cross-sectional view of the seal of FIG. 2, shown with the disk in closed position and in the absence of differential pressure across the valve;
FIG. 4 is a detailed view of the seal of
FIG. 2, shown with pressure applied from the side of convergence of the periphery of the disk;
FIG. 5 is a view of the seal of FIG. 2, shown with fluid pressure applied from the opposite side; and
FIG. 6 is a detailed cross-sectional view of another embodiment of the present invention, showing the relative dimensions and locations of the seal elements when the valve is opened and the valve disk when closed, respectively.
In the embodiment of FIGS. 1-5, there is shown a butterfly valve having a valve body 10 within which a closure member 14 is mounted on a valve stem 12. The valve stem extends externally of the valve body at one end 16, and may be pivoted by connection at the end 16 to any conventional valve actuation means (not here shown).
Suitable stem packing 18 is provided to prevent leakage of a fluid from within the valve. The closure member 14 may be secured to the valve stem 12 by any suitable means, here exemplified by pins 20. This closure member is provided with a converging peripheral sealing surface 15 which is preferably a section of a sphere.
Retained between an annular seal retainer 22 and the valve body 10 is an annular unitary valve seal member, generally designated 24. Fluid-tight sealing between the seal retainer 22, an outer peripheral flange 26 of the seal member 24, and the valve body 10 is provided by clamping the periphery 26 between the retainer and the valve body by a set of screws 28. The seal member 24 is constructed of a flexible resilient metal, for example bronze or a stainless steel, which is chemically and physically resistant to the fluid which is to flow through the valve.
As can be more clearly seen in FIG. 2, which shows the position of the seal 24 when the valve is open, the valve seal member 24 is provided with a radially inner sealing portion 30 and a resilient flexible dished web portion 32 extending outwardly therefrom. The sealing portion 30 is of slightly smaller diameter than the surface 15 at the point of contact with the closure member 14, this latter member being shown by dashed lines to indicate its position when the valve is closed, resulting in an interference fit between these two members when the closure member is pivoted to a closed position. The sealing portion 30 is formed as an annular channel having a generally
U-shaped cross section, one leg of the U being a continuation of the web portion 32 and the other leg terminating in a lip 36 which provides added strength in the sealing portion 30.
The facing surfaces of the valve body 10 and the seal retainer 22 define an annular valve body recess having a first sidewall 38 and a second sidewall 40. Preferably, the sidewalls 38 and 40 should be sufficiently separated that neither the sealing portion 30 nor the web portion 32 of the seal member 24 contacts these sidewalls as the seal is moved axially under the influence of the valve closure member 14 upon closing, or under the influence of differential fluid pressure.
In FIG. 3, the valve is shown with the closure meber 14 pivoted (into a closed position, the sealing surface 15 thereof engaging the inner sealing portion 30 of the seal member 24. In this condition, the inner portion 30 of the seal member expands resiliently to accommodate the surface 15 of the closure member, while the dished web portion 32 is resiliently deflected axially about an annular pivot, or locus of flexure points 34 located generally at the junction of the web portion 32 and the flange portion 26 in the direction of convergence of the closure member surface 15, as can be seen by reference to the dashed lines which indicate the position of the seal 24 in its valve-open condition.Additionally, axial forces imposed upon the closure member 14 by the seal member 24 serves to take up any clearance between the closure member 14 and the valve stem 12, as well as those between the stem 12 and its support bearings.
Under the influence of fluid pressure differential applied across the valve of FIG.
1, the higher pressure being applied from the side of the closure member toward which the periphery 15 converges, the seal 24 and the valve closure member 14 are urged to the position shown in FIG. 4, the positions of the seal member 24 when the valve is open and of the closure member 14 when closed in the absence of differential pressure again being shown by dashed lines for comparison. Fluid pressure urges the closure member 14 away from the direction of convergence of the surface 15, which pressure acting on the seal 24 cooperates with the hoop stresses imposed by the sealing portion 30 and the axial spring forces imposed by the dished web portion -32 of the seal 24 in response to initial closure of the closure member 14, to maintain fluid tight engagement of the seal 24 with the periphery 15 of the closure member.
In FIG. 5 the seal 24 and closure member 14 of this embodiment are sh6wn under the influence of differential pressure acting toward the direction of convergence of the surface 15, and again dashed lines indicate the positions occupied by the seal 24 when the valve is open and the closure member 14 when closed in the absence of fluid pressure. In this condition, the valve closure member 14 is urged toward the direction of the convergence of the surface 15 under the influence of fluid pressure, and the surface 15 is wedged more tightly into sealing engagement with the inner sealing portion 30 of the seal member 24. The axial movement of the sealing portion 30 is limited by axial spring forces imposed by the resilient web portion 32 of the seal.
Preferably, a metal seal according to this invention is formed such that an imaginary line drawn through the pivot 34 of the seal 24 and the center of curvature of the Ushaped inner sealing portion 30, when the seal is in the position shown in FIG. 2, is substantially perpendicular to the sealing surface 15 of the valve closure member 14 at its point of intersection therewith when the closure member 14 is in a closed position. In other words, a line drawn from the point 34 through the center of curvature of the sealing portion 90 of FIG. 2 would desirably intersect the dashed line indicating the closed position of the closure member surface 15 substantially perpendicularly.
By the term “subsantially perpendicularly” is meant within about ten degrees of perpendicularly. Although a seal constructed according to this invention may be constructed so that such an imaginary line intersects the surface 15 in its closed position at an angle departing significantly from the perpendicular, we have found that for most applications an advantageous balance between sealing effectiveness and the torque required to rotate the valve closure member to a closed position is achieved when this angle is within about ten degrees of perpendicular.Such a relationship together with the interference fit indicated in FIG. 2 between the closure member surface 15 and the seal 24, ensures that axial and radial preloading forces will be imposed on the sealing surface 15 of the closure member 14 by the seal members when the closure member is rotated to the closed position of
FIG. 3.
As has been stated before in connection with the discussion of FIG. 3, the web member 32 of this invention is axially flexible about a locus of flexure points 34 located generally at the junction of the web32 and the flange portion 26, and this locus of flexure points 34 is axially displaced, or offset, in the direction of convergence of the valve closure member surface 15 from the region of contact of the closure member surface 15 from the region of contact of the closure member surface 15 and the inner sealing portion 30 of the seal member 24.
This axial displacement of the locus of flexure points 34 is desirable because of substantially perpendicular intersection of the imaginary line drawn through the point 34 and the center of curvature of the seal channel 30 with the surface 15 of the closure member in FIG. 2 referred to above. It will be understood by those skilled in the art that the shortest distance between a point and a surface is the distance measured along a line perpendicular to the surface and passing through the point.Accordingly, when the valve closure member 14 is rotated to the closed position shown in FIG. 3 the sealing portion 30 and the web portion 32 are moved toward the direction of convergence of the closure member surface 15, and the sealing portion 30 of the seal contacts the sealing surface 15 in a region, or band of points, more distant from the flexure point 34 than the shortest distance from point 34 to the surface 15.The web portion 32 of the seal member is simultaneously placed in compression by virtue of the axial displacement, or offset, of the flexure points 34 in the direction of convergence of the surface 15 from the point of contact of the sealing portion 30 with the closure member surface 15 and by the circumferential stretching of the sealing portion 30 of the seal, along with axial deflection thereof, which stretching and deflection urge the region of contact between the seal and the closure member nearer the locus of flexure points 34.As can be seen by reference to FIGS. 4 and 5, the web portion 32 remains in compression as the valve disk and seal move under the influence of fluid pressure differential applied to either side of the closure member 14 inasmuch as the position of the seal member 24 does not move away from the direction of convergence of the surface 15 farther than its dashed-line, or “free”, position.By virtue of this compression of the web 32, the effect of differential pressure applied to the valve seal 24 and closure member 14 from the direction of convergence of the closure member surface 15 tending to force the sealing portion 30 outward on the surface 15 is coqinteracted by forces in the web portion 32 resisting further outward compression of the web 32 as the point of contact of the sealing portion 30 with the closure member surface 15 is moved closer to the flexure point 34, as well as by hoop stresses within the sealing portion 30 of the seal as the sealing portion is forced to expand.Pressure applied to the seal 24 and the closure member 14 from the side of the valve opposite the direction of convergence of the surface 14 will likewise be counteracted by outward compressive forces in the web portion 32 as well as hoop stresses in the sealing portion 30, as the closure member 14 tends to wedge into the seal 24. The Co- action of compressive loading of the web portion 32 and hoop stretching of the sealing portion 30 allows support of the sealing portion 30 by the web 32 to minimize the danger of stretching the sealing portion beyond its elastic limit, while permitting sufficient flexibility in the sealing portion to allow it to conform to the closure member surface to effect tight shut-off when the valve is closed.
The lip 36 on the generally U-shaped sealing portion 30 of the seal 24 operates in a triple capacity. First, it serves as an additional Belleville spring element, cooperating with the web portion 32 to provide additional stiffness of the seal in the axial direction. Secondly, the lip 36 adds radial strength to the sealing portion 30 to counteract the tendency of differential pressure acting from the direction of convergence of the surface 15 to “unfold” the sealing portion and force the seal in a downstream direction, causing leakage of the valve.
Thirdly, provision of the lip 36 insures that the point of contact of the sealing portion 30 with the closure member surface 15 is not at the edge of the seal, minimizing the danger of stress-cracking and erosion of the sealing portion.
Referring to FIG. 6, there is shown a second embodiment of this invention, wherein an annular web portion 132 is provided for linking the inner annular sealing portion 130 and the outer peripheral flange portion 126 of a unitary metallic valve seal 124. As in the embodiment of FIGS. 1-5, this embodiment includes a valve body 10 and an annular seal retaining member 22 for clamping the peripheral flange 126 of the seal member, and a valve closure member 14 having a converging sealing surface 15. The seal 124 is shown in the position which it occupies when the valve is open, while the valve closure member is shown by dashed lines in its valve-closed position for comparison purposes.
The annular web portion 132 of this embodiment differs from that of the embodiment of FIGS. 1-5 in that it is not dished, but is a radial extension of the flange portion 126 of the seal 124. In the vicinity of the junction of the flange 126 with the web 132 there is located a locus of flexure points 134, about which the web portion 132 is deflected axially in the direction of convergence of the sealing surface 15 of the valve closure member 14. Accompanying this axial deflection of the web portion 132 is hoop stretching of the inner sealing portion 130 to accommodate the closure member sealing surface 15, and this hoop stretching of the inner sealing portion increases the diameter of this portion, again placing the web portion 132 in radial compression.
Under the influence of fluid differential pressure applied from the direction of convergence of the closure member surface 15, this radial compression of the web portion 132 cooperates with hoop stresses in the sealing portion 130 to maintain sealing engagement of the seal 124 with the closure member 14 by virtue of the axial displacement of the locus of flexure points 134 in the direction of convergence of the closure member surface 15 from the point of contact between the seal and the closure member, in the same manner as the embodiment of FIGS. 1-5.
Although we have illustrated and described preferred embodiments wherein this seal is employed in a butterfly valve, clearly such a seal may be employed in ball valves equally well.
WHAT WE CLAIM IS:
1. A valve structure comprising:
a unitary metallic annular seal member having an inner sealing portion of generally
U-shaped cross section, a resilient flexible web portion extending generally outwardly from said sealing portion, and an outer periphery extending outwardly from said web portion, and including a locus of flexure points at the junction of said web and said periphery;
a valve body having a central bore and means within said bore for sealingly engaging said periphery of said seal;
valve closure means pivotable within said bore between open and closed positions, said closure means having a circumferential sealing surface converging generally toward an axis of said buddy bore for sealingly engaging said sealing portion of said seal in an interference fit in a region of contact when said closure means is in a closed position;;
said locus of flexure points being displaced in the direction of convergence of said sealing surface of said closure means from said region of contact between said seal member and said closure means,
whereby upon pivoting of said closure means to said closed position, said inner sealing portion of said seal is radially stretched to accommodate said closure means, and said web portion is resiliently deflected axially and placed in generally outward compression.
2. A structure according to Claim 1 in which said generally U-shaped cross section of said seal member sealing portion defines a center of curvature of said cross section, and wherein an imaginary line through said center of curvature and said locus of flexure points when said closure means is in the open position intersects said sealing surface of said closure means substantially perpendicularly when said closure means is in said closed position.
3. A structure according to Claim 2, in which said line intersects said sealing surface perpendicularly.
4. A structure according to any of Claims 1 to 3 in which said sealing surface is a section of a sphere.
5. A structure according to any of Claims 1 to 4 in which said web portion is dished or planar.
6. A structure according to any of Claims 1 to 5 in which said closure member is a disk.
7. A structure according to Claim 1 and subsantially as described with reference to any of the Figures 1 to 6.
**WARNING** end of DESC field may overlap start of CLMS **.

Claims (7)

**WARNING** start of CLMS field may overlap end of DESC **. is hoop stretching of the inner sealing portion 130 to accommodate the closure member sealing surface 15, and this hoop stretching of the inner sealing portion increases the diameter of this portion, again placing the web portion 132 in radial compression. Under the influence of fluid differential pressure applied from the direction of convergence of the closure member surface 15, this radial compression of the web portion 132 cooperates with hoop stresses in the sealing portion 130 to maintain sealing engagement of the seal 124 with the closure member 14 by virtue of the axial displacement of the locus of flexure points 134 in the direction of convergence of the closure member surface 15 from the point of contact between the seal and the closure member, in the same manner as the embodiment of FIGS. 1-5. Although we have illustrated and described preferred embodiments wherein this seal is employed in a butterfly valve, clearly such a seal may be employed in ball valves equally well. WHAT WE CLAIM IS:

1. A valve structure comprising:
a unitary metallic annular seal member having an inner sealing portion of generally
U-shaped cross section, a resilient flexible web portion extending generally outwardly from said sealing portion, and an outer periphery extending outwardly from said web portion, and including a locus of flexure points at the junction of said web and said periphery;
a valve body having a central bore and means within said bore for sealingly engaging said periphery of said seal;
valve closure means pivotable within said bore between open and closed positions, said closure means having a circumferential sealing surface converging generally toward an axis of said buddy bore for sealingly engaging said sealing portion of said seal in an interference fit in a region of contact when said closure means is in a closed position;;
said locus of flexure points being displaced in the direction of convergence of said sealing surface of said closure means from said region of contact between said seal member and said closure means,
whereby upon pivoting of said closure means to said closed position, said inner sealing portion of said seal is radially stretched to accommodate said closure means, and said web portion is resiliently deflected axially and placed in generally outward compression.

2. A structure according to Claim 1 in which said generally U-shaped cross section of said seal member sealing portion defines a center of curvature of said cross section, and wherein an imaginary line through said center of curvature and said locus of flexure points when said closure means is in the open position intersects said sealing surface of said closure means substantially perpendicularly when said closure means is in said closed position.

3. A structure according to Claim 2, in which said line intersects said sealing surface perpendicularly.

4. A structure according to any of Claims 1 to 3 in which said sealing surface is a section of a sphere.

5. A structure according to any of Claims 1 to 4 in which said web portion is dished or planar.

6. A structure according to any of Claims 1 to 5 in which said closure member is a disk.

7. A structure according to Claim 1 and subsantially as described with reference to any of the Figures 1 to 6.

GB40838/76A
1975-10-02
1976-10-01
Valve structure

Expired

GB1561593A
(en)

Applications Claiming Priority (1)

Application Number
Priority Date
Filing Date
Title

US61913375A

1975-10-02
1975-10-02

Publications (1)

Publication Number
Publication Date

GB1561593A
true

GB1561593A
(en)

1980-02-27

Family
ID=24480602
Family Applications (1)

Application Number
Title
Priority Date
Filing Date

GB40838/76A
Expired

GB1561593A
(en)

1975-10-02
1976-10-01
Valve structure

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JP
(1)

JPS608380B2
(en)

AR
(1)

AR210369A1
(en)

AU
(1)

AU509723B2
(en)

BR
(1)

BR7606565A
(en)

CA
(1)

CA1039262A
(en)

DE
(1)

DE2644518A1
(en)

FR
(1)

FR2326637A1
(en)

GB
(1)

GB1561593A
(en)

MX
(1)

MX144243A
(en)

ZA
(1)

ZA765908B
(en)

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1984-06-13
General Signal Corporation
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1979-04-26
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1980-12-12
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SPHERICAL BUTTERFLY VALVE

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1997-05-07
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1976

1976-10-01
AU
AU18317/76A
patent/AU509723B2/en
not_active
Expired

1976-10-01
JP
JP51118925A
patent/JPS608380B2/en
not_active
Expired

1976-10-01
FR
FR7629686A
patent/FR2326637A1/en
active
Granted

1976-10-01
ZA
ZA765908A
patent/ZA765908B/en
unknown

1976-10-01
GB
GB40838/76A
patent/GB1561593A/en
not_active
Expired

1976-10-01
DE
DE19762644518
patent/DE2644518A1/en
active
Granted

1976-10-01
MX
MX166536A
patent/MX144243A/en
unknown

1976-10-01
CA
CA262,472A
patent/CA1039262A/en
not_active
Expired

1976-10-01
BR
BR7606565A
patent/BR7606565A/en
unknown

1976-10-10
AR
AR264937A
patent/AR210369A1/en
active

Cited By (4)

* Cited by examiner, † Cited by third party

Publication number
Priority date
Publication date
Assignee
Title

EP0074782A1
(en)

1981-09-11
1983-03-23
Charles Winn (Valves) Limited
Butterfly valve

EP0110012A2
(en)

1982-08-09
1984-06-13
General Signal Corporation
Valve assembly

EP0110012B1
(en)

1982-08-09
1989-01-18
General Signal Corporation
Valve assembly

WO1998058197A1
(en)

1997-06-13
1998-12-23
Yuping Jiao
Flexible-plastic metallic seal

Also Published As

Publication number
Publication date

DE2644518C2
(en)

1989-08-03

DE2644518A1
(en)

1977-04-14

MX144243A
(en)

1981-09-17

ZA765908B
(en)

1977-12-28

FR2326637A1
(en)

1977-04-29

AU509723B2
(en)

1980-05-22

FR2326637B1
(en)

1983-01-28

JPS608380B2
(en)

1985-03-02

AU1831776A
(en)

1978-04-06

CA1039262A
(en)

1978-09-26

JPS5244423A
(en)

1977-04-07

AR210369A1
(en)

1977-07-29

BR7606565A
(en)

1977-06-07

Contact information