CA2130102A1 - Coupling for flanged pipes, process for connecting the flanges and use of the coupling - Google Patents
Coupling for flanged pipes, process for connecting the flanges and use of the couplingInfo
- Publication number
- CA2130102A1 CA2130102A1 CA002130102A CA2130102A CA2130102A1 CA 2130102 A1 CA2130102 A1 CA 2130102A1 CA 002130102 A CA002130102 A CA 002130102A CA 2130102 A CA2130102 A CA 2130102A CA 2130102 A1 CA2130102 A1 CA 2130102A1
- Authority
- CA
- Canada
- Prior art keywords
- flange
- coupling
- bolts
- flanges
- pipe
- Prior art date
- 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.)
- Abandoned
Links
Classifications
-
- E—FIXED CONSTRUCTIONS
- E04—BUILDING
- E04B—GENERAL BUILDING CONSTRUCTIONS; WALLS, e.g. PARTITIONS; ROOFS; FLOORS; CEILINGS; INSULATION OR OTHER PROTECTION OF BUILDINGS
- E04B1/00—Constructions in general; Structures which are not restricted either to walls, e.g. partitions, or floors or ceilings or roofs
- E04B1/62—Insulation or other protection; Elements or use of specified material therefor
- E04B1/74—Heat, sound or noise insulation, absorption, or reflection; Other building methods affording favourable thermal or acoustical conditions, e.g. accumulating of heat within walls
-
- 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
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L23/00—Flanged joints
- F16L23/02—Flanged joints the flanges being connected by members tensioned axially
- F16L23/032—Flanged joints the flanges being connected by members tensioned axially characterised by the shape or composition of the flanges
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Architecture (AREA)
- Mechanical Engineering (AREA)
- Acoustics & Sound (AREA)
- Electromagnetism (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Flanged Joints, Insulating Joints, And Other Joints (AREA)
- Gasket Seals (AREA)
Abstract
Flange for pipe joints with pipes leading fluids under high pressure, where the flange comprises a contact surface (6, 7; 6a, 7a) which, when the securing bolts (3) for the pipe joints are not tightened, form an outwards directed angle to each other, and being forced towards each other when the securing bolts (3) are tightened. The flanges may also comprise outer and inner depending sections (8, 9; 10, 11) for further tightening effect, and may additionally possibly comprise washer/gasket grooves (12) and washers/gaskets (20).
Description
W093/172~ 213 ~1 0 2 PCT/NO93/00029 ~w~ling ror rlanged pipes~ p~ocess for connecting the r~y~s and use Or the coupling.
The present invention concerns compact flanges for pipe connections for pipes carrying fluids under high pressure and/or being subject to large mechanical forces. Such flanges for pipe connections are used within offshore/sub-sea, process and/or landbased indurty and nuclear~power plants, and especially for riser pipes and tension stays in the oil industry. A flange is in this connection each half of a pipe connection or a coupling. The words "connection half" or "flange" are often used alternately, but a coupling of such halves, said halves most often being similar but may be different, makes a pipe connection, and close-fitting pipe connections is the object of the present invention.
Within this area there are several types of known technique for connective methods and devices for such connections of pipelines. The commonly known flanges/connections/clamps are sold under the names API-flanges, API clamps/hub, and they may also comprise threaded connections or couplings.
Common for these connections and methods is that they are ba~ed on e.g. flat or "raised face" flange surfaces with surface gaskets, compact ring-groove washers or inwardly conica:l tightening eIements.
An ex~mple of~such~a known flange type is disclosed in GB
patent 1.559.388 wheré there is shown a flat flange surface with a connection of the fl~ange parts with conventional nuts.
- ~ ~
,i When connecting the flange parts there will also arise tensions-in;the fl~nge material in the parts connecting the :
horizontal and~the vertioal flange parts. To distribute and relieve~such mat~erial tensions it is known to give the , transitional area~between each flange part an eIliptical shape. It is thus known from US patent 4.183.562 to give the surface the shape of a quarter of an ellipse in such an WO93/l7268 213 0 1 0 2 PCT/N093/0~9 area, the larger axis of the ellipse being parallell with the pipe and this larger axis being about two times the length of its smaller axis. However, the tensions in the material in such a flange depends on the load points of the flange surface and on the tension forces in the pipe connection, 80 that this form of an elliptiçal transition is only advantageous for conventionally forme~ flange types of the kind mentioned above.
A disadvantage in the existing flange connections is that there will often arise leaks after a time as a consequence of varying loads and high tensions combined with thermal strains and vibrations. In connection with this it is often necessary to perform mechanical maintainance such as e.g. to post-tighten blots and change washers.
Another disadvantage with these types of pipe connections is that they are characterized by large dimensions and high weight.
A third disadvantage is that the existing couplings have non-resilient tightening elements and simultaneously that the elements of the coupling move relative to each other during load variation, which contributes to leaks and other ti _ -accumulatinq damage~on the connection.
A fourth disadvantage is that the known types of flanges may not without special mea~urments be tested for leaks in a 8imple way during/after their installation.
, 30 ~ I `
A fifth disadvantage from a corrosive point of view is that existing coupIings have "wetn bolts, i.e. bolts being sub~ected to e.g. sea water will develop rust damages after having;been mounted in the flange parts.
~ A~ an example none of the mentioned flange types disclosed ¦ in GB patent 1.559.388 or US patent 4.183.562 will avoid such damage or be exempted from these disadvantages.
The present invention concerns compact flanges for pipe connections for pipes carrying fluids under high pressure and/or being subject to large mechanical forces. Such flanges for pipe connections are used within offshore/sub-sea, process and/or landbased indurty and nuclear~power plants, and especially for riser pipes and tension stays in the oil industry. A flange is in this connection each half of a pipe connection or a coupling. The words "connection half" or "flange" are often used alternately, but a coupling of such halves, said halves most often being similar but may be different, makes a pipe connection, and close-fitting pipe connections is the object of the present invention.
Within this area there are several types of known technique for connective methods and devices for such connections of pipelines. The commonly known flanges/connections/clamps are sold under the names API-flanges, API clamps/hub, and they may also comprise threaded connections or couplings.
Common for these connections and methods is that they are ba~ed on e.g. flat or "raised face" flange surfaces with surface gaskets, compact ring-groove washers or inwardly conica:l tightening eIements.
An ex~mple of~such~a known flange type is disclosed in GB
patent 1.559.388 wheré there is shown a flat flange surface with a connection of the fl~ange parts with conventional nuts.
- ~ ~
,i When connecting the flange parts there will also arise tensions-in;the fl~nge material in the parts connecting the :
horizontal and~the vertioal flange parts. To distribute and relieve~such mat~erial tensions it is known to give the , transitional area~between each flange part an eIliptical shape. It is thus known from US patent 4.183.562 to give the surface the shape of a quarter of an ellipse in such an WO93/l7268 213 0 1 0 2 PCT/N093/0~9 area, the larger axis of the ellipse being parallell with the pipe and this larger axis being about two times the length of its smaller axis. However, the tensions in the material in such a flange depends on the load points of the flange surface and on the tension forces in the pipe connection, 80 that this form of an elliptiçal transition is only advantageous for conventionally forme~ flange types of the kind mentioned above.
A disadvantage in the existing flange connections is that there will often arise leaks after a time as a consequence of varying loads and high tensions combined with thermal strains and vibrations. In connection with this it is often necessary to perform mechanical maintainance such as e.g. to post-tighten blots and change washers.
Another disadvantage with these types of pipe connections is that they are characterized by large dimensions and high weight.
A third disadvantage is that the existing couplings have non-resilient tightening elements and simultaneously that the elements of the coupling move relative to each other during load variation, which contributes to leaks and other ti _ -accumulatinq damage~on the connection.
A fourth disadvantage is that the known types of flanges may not without special mea~urments be tested for leaks in a 8imple way during/after their installation.
, 30 ~ I `
A fifth disadvantage from a corrosive point of view is that existing coupIings have "wetn bolts, i.e. bolts being sub~ected to e.g. sea water will develop rust damages after having;been mounted in the flange parts.
~ A~ an example none of the mentioned flange types disclosed ¦ in GB patent 1.559.388 or US patent 4.183.562 will avoid such damage or be exempted from these disadvantages.
2 1 3 0 1 0 2 PCI /N093/00029 As there are discovered oil finds within the offshore industry on successively larger depths, the use of riser couplings and sub-sea couplings will bç of increasingsly greater importance. In this connection the use of compact couplings with low weight, small physical dimensions and minimal maintainance will also get an incréased signifi-cance, and this represents the basis of the present invention.
A purpose of the present invention is thus to provide a, flange or a pipe connection avoiding the above indicated disadvantages with varying loads, high tensions, high pressure etc, simultanously making testing for pressure tightness very simple and exact during mounting "in situ"
and during performance under full pressure in the pipeline.
j In the following the pre~ent invention will be disclosed with reference to the iattached drawings wherein:
Fig. 1 shows two pipes connected with a coupling of flanges of the relevant type.
, Fig. 2 shows a flange according to Fig. 1 as seen from A.
Fig. 3 ~hows a section through B-B according to Fig. 2 before tightening of the bolts.
Fig. 4 shows a section through a flange in a basic design.
Fig. 5 shows a section through a flange with three conical ;~ ~ ~ur~aces and an outer depressed section on the outer diiameter.
'/ ~ :
Fig. 6 shows a section through a flange with one conical surface, tightening groove and a bore for a test port.
Fig. 7 shows a section through a flange with two conical W093/172~ PCT/NO93/00029 213012 ,.~
surfaces, tightening groove and a threaded hole for pin screws.
Fig. 8 shows a section through a pipe connection with one plane flange, one flange with a conical surface, tightening washer and bore for test port~before tighte~ing of the bolts. ~ ~
Fig. 9 shows a section through a compact flange coupling according to the present invention in a free condition before tightening of the bolts, and where each of the flanges are equipped with two conical surfaces, tightening grooves with a tightening washer, bore for test port in one of the flanges, depressed outer section on the outer diameter and tightening pin screws with base washers and nuts.
Fig. 10 shows a section through a flange coupling according to the present invention where there is present an alternate opening direction between the flanges.
Fig. 11(~-d3 shows a particular flange design according to the i m ention.
With re~erence to Fig.-l the flange assembley, in order that the flanges according to the invention may function prope n y, should to be built into a pipeline or pipe ~tructure l, la with two flange halves 2 and 2a, connection bolt~ 3 with ba e washers 4~,4a and nuts 5,5a. The flanges 2,2a need not necessarily be identical, but may have any individual ~tructure according to Figs. 4, 5, 6, 7 and 8.
The ~tucture of each flange is, however, not limited to ~he e embodiments, but are designed as indicated in the - attached claims.
Accor~ing to the invention the coupIing, to act according to its intension, exhibits the following separate features:
.
WO93~17268 PCT/NO93/00029 - At least one of the two opposite flange surfaces 6,7;6a,7a is designed such that it or they is/are conically shaped (Figs. 3 and 4).
- Each of the two opposite flanges is designed such that the opposite surfaces 6,7;6a,7a (Figs. 3 and 4) are conical.
- Each of the two opposite flanges are designed such that the surfaces 6,7;6a,7a (Figs. 3, 4, 8 and 9) in a radial section form an angle with each other in such a way that the distance between the two opposite surfaces increases with increasing radius in an assembled connection before the bolts 3 are tightened. A preferred angle of inclination of the surfaces 6, 7 relative to a flat imaginary plane constitutes 0,2-3,0 , preferably 0,2-0,5 , but greater and smaller angles may also be used, inter alia depending on material and tolerances in the pipe joint and the flange halves. Two opposite coupling halves are according to the invention designed such that the two adjacent surfaces have an ouwardly directed increasing distance to each other. The greatest angle depends on whether the bolts 3 may be tightened so that the flange planes meet each other (see disclosure below).
i ' :
- When joining the flanges 2, 2a with the bolts 3, the flange surfaces 6, 7 and/or 6a, 7a will rotate under the ; correcting forces, preferably to abutment with each other, so ~hat the conical slot ~etween the surfaces 6, 7 and 6a, 7a become closed.
j ~
Instead of bolts e.g. clamp connections or other con-t~ ventional connecting devices may be used, and the outer part's rear flange surface is simultaneously given a shape suited for this purpose.
-; 35- The angle between the surfaces 6, 7 and 6a, 7a is further preferably designed such that 50-100% of the prestressing force of the bolts is necessary to close the conical slot WO93/17268 PCT/N093/0~29 213UlOï : ~l which is produced by this angle. It is preferred that the compression force by closing the slot is about 70-80~ of the bolts' prestressing force. Such a force is of course dependent on and relative to e.g. the kind of material used in the flange.
The opening angle ~ between two opposing flanges is material-dependent. It is inter alia dependent on the yield point of the flange material, a~, and elasticity modulus, E, in such a way that ~ ~ K(~ ), where K is a constant which is characteristic for the total geometry of the coupling and which may vary from one design of the coupling to the other. Determination of K is within the competence of the person skilled in the art. The diameter and the wall thickness of the pipe and the number, diameter, solidity class of the bolts are among the parameters contributing to the variation of K.
- The prestressed length of the bolts 3 is preferably at least 3 times their diameter, and preferably 6 to 8 times the diameter of the bolts.
A further feature of the design of the flange according to the invention is to equip the outer and/or inner edges 6, 7;
2 6a, 7a with a wedge-shaped projection 6, 8,9: 7, 10, 11 (Fig. 5?. By providing the flange with conical areas 6, 8, 9; 7, 10, 11, the conical surface 10, 11: 8, 9 has a conicity which i8 different from the conicity of the flange surface 6, 7. By such a design there is achieved a further tightening in the flange ~hen tightneing the tension bolts
A purpose of the present invention is thus to provide a, flange or a pipe connection avoiding the above indicated disadvantages with varying loads, high tensions, high pressure etc, simultanously making testing for pressure tightness very simple and exact during mounting "in situ"
and during performance under full pressure in the pipeline.
j In the following the pre~ent invention will be disclosed with reference to the iattached drawings wherein:
Fig. 1 shows two pipes connected with a coupling of flanges of the relevant type.
, Fig. 2 shows a flange according to Fig. 1 as seen from A.
Fig. 3 ~hows a section through B-B according to Fig. 2 before tightening of the bolts.
Fig. 4 shows a section through a flange in a basic design.
Fig. 5 shows a section through a flange with three conical ;~ ~ ~ur~aces and an outer depressed section on the outer diiameter.
'/ ~ :
Fig. 6 shows a section through a flange with one conical surface, tightening groove and a bore for a test port.
Fig. 7 shows a section through a flange with two conical W093/172~ PCT/NO93/00029 213012 ,.~
surfaces, tightening groove and a threaded hole for pin screws.
Fig. 8 shows a section through a pipe connection with one plane flange, one flange with a conical surface, tightening washer and bore for test port~before tighte~ing of the bolts. ~ ~
Fig. 9 shows a section through a compact flange coupling according to the present invention in a free condition before tightening of the bolts, and where each of the flanges are equipped with two conical surfaces, tightening grooves with a tightening washer, bore for test port in one of the flanges, depressed outer section on the outer diameter and tightening pin screws with base washers and nuts.
Fig. 10 shows a section through a flange coupling according to the present invention where there is present an alternate opening direction between the flanges.
Fig. 11(~-d3 shows a particular flange design according to the i m ention.
With re~erence to Fig.-l the flange assembley, in order that the flanges according to the invention may function prope n y, should to be built into a pipeline or pipe ~tructure l, la with two flange halves 2 and 2a, connection bolt~ 3 with ba e washers 4~,4a and nuts 5,5a. The flanges 2,2a need not necessarily be identical, but may have any individual ~tructure according to Figs. 4, 5, 6, 7 and 8.
The ~tucture of each flange is, however, not limited to ~he e embodiments, but are designed as indicated in the - attached claims.
Accor~ing to the invention the coupIing, to act according to its intension, exhibits the following separate features:
.
WO93~17268 PCT/NO93/00029 - At least one of the two opposite flange surfaces 6,7;6a,7a is designed such that it or they is/are conically shaped (Figs. 3 and 4).
- Each of the two opposite flanges is designed such that the opposite surfaces 6,7;6a,7a (Figs. 3 and 4) are conical.
- Each of the two opposite flanges are designed such that the surfaces 6,7;6a,7a (Figs. 3, 4, 8 and 9) in a radial section form an angle with each other in such a way that the distance between the two opposite surfaces increases with increasing radius in an assembled connection before the bolts 3 are tightened. A preferred angle of inclination of the surfaces 6, 7 relative to a flat imaginary plane constitutes 0,2-3,0 , preferably 0,2-0,5 , but greater and smaller angles may also be used, inter alia depending on material and tolerances in the pipe joint and the flange halves. Two opposite coupling halves are according to the invention designed such that the two adjacent surfaces have an ouwardly directed increasing distance to each other. The greatest angle depends on whether the bolts 3 may be tightened so that the flange planes meet each other (see disclosure below).
i ' :
- When joining the flanges 2, 2a with the bolts 3, the flange surfaces 6, 7 and/or 6a, 7a will rotate under the ; correcting forces, preferably to abutment with each other, so ~hat the conical slot ~etween the surfaces 6, 7 and 6a, 7a become closed.
j ~
Instead of bolts e.g. clamp connections or other con-t~ ventional connecting devices may be used, and the outer part's rear flange surface is simultaneously given a shape suited for this purpose.
-; 35- The angle between the surfaces 6, 7 and 6a, 7a is further preferably designed such that 50-100% of the prestressing force of the bolts is necessary to close the conical slot WO93/17268 PCT/N093/0~29 213UlOï : ~l which is produced by this angle. It is preferred that the compression force by closing the slot is about 70-80~ of the bolts' prestressing force. Such a force is of course dependent on and relative to e.g. the kind of material used in the flange.
The opening angle ~ between two opposing flanges is material-dependent. It is inter alia dependent on the yield point of the flange material, a~, and elasticity modulus, E, in such a way that ~ ~ K(~ ), where K is a constant which is characteristic for the total geometry of the coupling and which may vary from one design of the coupling to the other. Determination of K is within the competence of the person skilled in the art. The diameter and the wall thickness of the pipe and the number, diameter, solidity class of the bolts are among the parameters contributing to the variation of K.
- The prestressed length of the bolts 3 is preferably at least 3 times their diameter, and preferably 6 to 8 times the diameter of the bolts.
A further feature of the design of the flange according to the invention is to equip the outer and/or inner edges 6, 7;
2 6a, 7a with a wedge-shaped projection 6, 8,9: 7, 10, 11 (Fig. 5?. By providing the flange with conical areas 6, 8, 9; 7, 10, 11, the conical surface 10, 11: 8, 9 has a conicity which i8 different from the conicity of the flange surface 6, 7. By such a design there is achieved a further tightening in the flange ~hen tightneing the tension bolts
3. The projecting areas 8, 9: 10, 11 may extend for an indefinite distance from the outer edge 7 and the inner edge 6 of the flange respectively, over the inclined area 6, 7, but extend preferably no farther in from the outer/inner edgea than that the ratio between the inclined flange section and the projection(s) is 2:1 or larger. The length of the projecting areas 8, 9; 10, 11 is independent of each other, but will each normally be less than 1/4 of the WO93/172~ 213 a 1 o 2 PCT/NO93/00029 distance between the two main surfaces 6, 7 6a, 7a in the outer edge of the joint To produce a further tightening in the flange-joint it is 5 preferred that the flange is equipped with a groove 12 for a washer/gasket Such a washer/gasket may be of a con-ventional type, but it is preferred that i~ is of a flexible type of the design specified in Norwegian patent application No 90 2332, and which is included herein per reference The washer/gasket is, however, not limited to such a geometrical design, but represents only a preferred embodiment Concerning the washer groove 12, this has preferably side surfaces 13, 14 (Fig 6) forming an angle of ~ 10-20 with a central line extending parallell with the longitudinal axis of the flange A condition is, however, that the outer surfaces 20, 21 (Fig 8) of, the washer/gasket are at least partially aligned with the side surfaces 13, 14 of the groove 12 Tolerances for such adjustments will be known by the person skilIed in the art An alternative embodiment of the design of the flange according to the i m ention will be to equip the flange with a bore 15 (Fig 6)~joining~the threaded connection on the outer ~urface to thé~bottom of th- washer groove 12 By ;~ ~uch~an~alternative~design~it will be possible to pressure te~t~each~joint~for~tightneS~ and pres~sure re8istance ~^~ without adding~an inner pressure~to~the pipe ~See also Nqrwegian pjatent application no 90 2332 ) A~ preYiously~ ntioned, it i8: preferred that the inter-m~édiate~area~ 6, 18~b tw en~the~part of the flange extending mainly~pa~rallell 16,~23 to the length axis A-of the pipe 1, 35~ la, and the~part of th- flange~extending mainly perpen-dicular 18, 22 to the length axsis A of~the pipe (Fig 4) has~an elliptical shapéi to achieve the lowest possible tension concentration factor in connection with this cross-,~
' WO 93/17268 3 o I 0 2 PCI'/N093~0U029 secitonal trar.sitional area. Such an elliptical transi-tional area 16, 18 begins at the outer surface 16 of the flange and is tangential to the rear flange plane 18, 22 (Fig. 4) of the flange. When designing the tightening plane of the flange, as disclosed a~ove, the elliptical form will, however, optimalize the tension distribution in the flange material at a ratio between the large and s'mall axes of the ellipse within the ratio interval 3:1 to 5:1, preferably
' WO 93/17268 3 o I 0 2 PCI'/N093~0U029 secitonal trar.sitional area. Such an elliptical transi-tional area 16, 18 begins at the outer surface 16 of the flange and is tangential to the rear flange plane 18, 22 (Fig. 4) of the flange. When designing the tightening plane of the flange, as disclosed a~ove, the elliptical form will, however, optimalize the tension distribution in the flange material at a ratio between the large and s'mall axes of the ellipse within the ratio interval 3:1 to 5:1, preferably
4:1, 80 that the ability of the connection to resist mechanical loads is optimalized.
The flange is also alternatively designed with a depressed section 19 (Fig. 5) on the outer axis-symmetrical flange surface. The purpose of such a depressed section 19 is primarily to provide a possibility for the material between the depressed ~ection 19 and the plane 10, 11 to act as a resilient section to improve the tightening action at the projecting pàrt 10, 11 when bringing the ioint parts together, and secondarily to be able to reduce the amount 20 of raterial u~ed for the coupling halves, which results in a reduced weight. The dépth of the groove 19 i8 related to j~ the flange material, and it should preferably be deeper than ¦ the d-pth of the projecting section 10, ll,~as an example 2 to 3 times the depth of the projecting section 10, 11. 2S
¦ Each flange of the pipe joint ac¢ording to the invention may individually compri~e at least one of the above indicated fe~tur ~, each of~the features providing an improved tightening ~afety and/or ability~to withstand mechanical ~t,re~s compared to~the type of flangec known. However, it is advantageous~to combine two or more of the above indicat d~S~eatures to provide optimal properties in the ' ~ ~flange joint~according to the invention. The features ~ which~are~preferably to be combined are:
- That the flanges have ¢onical o~pposing surfaces 6, 7 prior to pretensioning the bolts 3;
- That the distan¢e between the opposing surfaces increase , with increasing radius towards the outer surface of the flange;
- That the flange planes 6, 7 rotate to tightening against each other when joining the flanges;
- That the angle beween the opposing surfaces 6, 7 is designed so that 50-100% of the pretension1force of the bolts 3 is necessary to close the slot bet'ween the conical surfaces 6, 7; 6a, 7a;
- That the bolt(s) is/are equipped with suita~le caps preventing an external medium to penetrate into the joint along the bolts.
Further, in addition it is preferred that the flange(s) according to the invention is/are provided with the following alternative features:
- That the pretension length of the bolts 3 is at least 3 times the diameter of the bolts;
- That there on one or both of the outer edges of the flanges are located wedge-like protruding sections 8, 9; 10, 11;
- That the flange is equipped with a washer groove 12, preferably at an angle of between ~ 10 and 200 to a centre Iine parallell to the longitudinal axis of the flange, but other types of grooves may also be of in~erest, e.g. grooves for an O-ring: ~
- That the flange(s) have an elliptical intermediate section 16-18 80 that the ratio between the large and the small axsis of the ellipse lies in the interval 3:1 to 5:1, preferably 4~
As a further preferred design of the flange according to the invention there may be included:
- That the conical plane of the protruding section(s) 8, 9;
10, 11 have a conicity which differs from the one of the flange surface 6, 7;
- That the flange(s) is/are provided with a bore 15 WO 93/17268 ~, i3 0 i 0 2 PCI'/NO93/0~029 joining a threaded connection on the outer surface and the bottom of the tightening groove;
- That the flange(s) is/are equipped with a depressed section 19 on the outer axis-symmetrical flange surface.
The advantages achieved by designing the flange(s) according to the features mentioned above, will consi~st in that there is provided a high contact pressure at the flange surfaces 6, 7: 6, 10: 8, 7: 8, 10 and corresponding surfaces in the opposing flange 2a for a completely tight joint, resulting in that the shafts of the bolts 3, and also the tighteing washer, by using a tightening device, normally will not be exposed neither to external medium nor to internal medium in the pipeline 1, la. Additionally, a thightening washer in the washer groove 12 and in the corresponding washer groove in flange 2a (Fig. 9) will likewise provide complete tightness in the flange joint, even if tightening at a high contact pressure 6, 6a (Fig. 9) should be broken. When the bolts 3 are correctly prestressed and the conical slot between the flanges 2,2a is closed, the bolt tension will be nearly ~tatic, with very small additional tension stresses resulting from varying mechanical and/or thermal loads in the joint, and as a consequence the danger of fatigue in the bolts/joint elements 3 will be as good as eliminated.
By providing the flange(s) with conical surface(s) forming an angle which each other and with a connection such that the 6urfaces are pre~sed towards each other, it will be an advantage to provide the outer surfaces of the flange(s) with an elliptical intermediate section between the parts which extend parallell 16, 23 and perpendicular 18, 22, respectively, to the longitudinal axis A of the pipe 1, la.
Thereby, the flange may be given a small flange diameter in relation to the pipe diameter as compared to conventional pipe connections, and thus small flange dimensions and low weight are ach~eved. Additionally, this results in low and advantageous tension forces in the hollow wedge 16-18 (Fig.
4) so that fatigue is avoided. By combining an elliptical WO 93/17268 213 01 0 2 PCI`/N093/00029 design with a depressed outer groove 19, the flange assembly may additionally be given a further reduced weight As a consequence of the above indicated features and advantages, a pipe joint with flanges according to the invention will also be very environmentally safe since tightness and a large degree of safety aga~nst fatigue in bolts or other mechanical destruction of the mechanically maintainance-free connection during operation will be ensured at any time As a consequence of the feature that at least one of the flanges of the pipe joint may be provided with a bore 15 for access to the groove 12, surveillance/drainage of a possible leakage past the inner flange edge 6, 6a, 9 may be per-formed, which may be of interest when exeptionally strict ; demands to safety are present Additionally, an embodiment of the pipe joint as shown in Figs, 8 and 9, where a re~ilient washer ring is present, may provide for the connection to tolerate overload/~eparation without leakage occurring~
I
!
The ~lange assembly according to the present invention is i~ ~~echa~nically main ainance-free since setting/destruction of ¦ 25 non- -tallic wa~her~/gask:ets or other elements is eliminated ¦~ ~by there being~no~relative movement bet~een~the elements of tho-~lange~as~embly~by~the influence of pressure and loads on th~-~oint The~mechani¢al~str-ngth of the flange as~-~bly may to a~;larg~degree~of reliability be evaluated f,rom tensional estimations`and~material data, since the in-ternally ~tatic~behaviour of~the~joint during operation
The flange is also alternatively designed with a depressed section 19 (Fig. 5) on the outer axis-symmetrical flange surface. The purpose of such a depressed section 19 is primarily to provide a possibility for the material between the depressed ~ection 19 and the plane 10, 11 to act as a resilient section to improve the tightening action at the projecting pàrt 10, 11 when bringing the ioint parts together, and secondarily to be able to reduce the amount 20 of raterial u~ed for the coupling halves, which results in a reduced weight. The dépth of the groove 19 i8 related to j~ the flange material, and it should preferably be deeper than ¦ the d-pth of the projecting section 10, ll,~as an example 2 to 3 times the depth of the projecting section 10, 11. 2S
¦ Each flange of the pipe joint ac¢ording to the invention may individually compri~e at least one of the above indicated fe~tur ~, each of~the features providing an improved tightening ~afety and/or ability~to withstand mechanical ~t,re~s compared to~the type of flangec known. However, it is advantageous~to combine two or more of the above indicat d~S~eatures to provide optimal properties in the ' ~ ~flange joint~according to the invention. The features ~ which~are~preferably to be combined are:
- That the flanges have ¢onical o~pposing surfaces 6, 7 prior to pretensioning the bolts 3;
- That the distan¢e between the opposing surfaces increase , with increasing radius towards the outer surface of the flange;
- That the flange planes 6, 7 rotate to tightening against each other when joining the flanges;
- That the angle beween the opposing surfaces 6, 7 is designed so that 50-100% of the pretension1force of the bolts 3 is necessary to close the slot bet'ween the conical surfaces 6, 7; 6a, 7a;
- That the bolt(s) is/are equipped with suita~le caps preventing an external medium to penetrate into the joint along the bolts.
Further, in addition it is preferred that the flange(s) according to the invention is/are provided with the following alternative features:
- That the pretension length of the bolts 3 is at least 3 times the diameter of the bolts;
- That there on one or both of the outer edges of the flanges are located wedge-like protruding sections 8, 9; 10, 11;
- That the flange is equipped with a washer groove 12, preferably at an angle of between ~ 10 and 200 to a centre Iine parallell to the longitudinal axis of the flange, but other types of grooves may also be of in~erest, e.g. grooves for an O-ring: ~
- That the flange(s) have an elliptical intermediate section 16-18 80 that the ratio between the large and the small axsis of the ellipse lies in the interval 3:1 to 5:1, preferably 4~
As a further preferred design of the flange according to the invention there may be included:
- That the conical plane of the protruding section(s) 8, 9;
10, 11 have a conicity which differs from the one of the flange surface 6, 7;
- That the flange(s) is/are provided with a bore 15 WO 93/17268 ~, i3 0 i 0 2 PCI'/NO93/0~029 joining a threaded connection on the outer surface and the bottom of the tightening groove;
- That the flange(s) is/are equipped with a depressed section 19 on the outer axis-symmetrical flange surface.
The advantages achieved by designing the flange(s) according to the features mentioned above, will consi~st in that there is provided a high contact pressure at the flange surfaces 6, 7: 6, 10: 8, 7: 8, 10 and corresponding surfaces in the opposing flange 2a for a completely tight joint, resulting in that the shafts of the bolts 3, and also the tighteing washer, by using a tightening device, normally will not be exposed neither to external medium nor to internal medium in the pipeline 1, la. Additionally, a thightening washer in the washer groove 12 and in the corresponding washer groove in flange 2a (Fig. 9) will likewise provide complete tightness in the flange joint, even if tightening at a high contact pressure 6, 6a (Fig. 9) should be broken. When the bolts 3 are correctly prestressed and the conical slot between the flanges 2,2a is closed, the bolt tension will be nearly ~tatic, with very small additional tension stresses resulting from varying mechanical and/or thermal loads in the joint, and as a consequence the danger of fatigue in the bolts/joint elements 3 will be as good as eliminated.
By providing the flange(s) with conical surface(s) forming an angle which each other and with a connection such that the 6urfaces are pre~sed towards each other, it will be an advantage to provide the outer surfaces of the flange(s) with an elliptical intermediate section between the parts which extend parallell 16, 23 and perpendicular 18, 22, respectively, to the longitudinal axis A of the pipe 1, la.
Thereby, the flange may be given a small flange diameter in relation to the pipe diameter as compared to conventional pipe connections, and thus small flange dimensions and low weight are ach~eved. Additionally, this results in low and advantageous tension forces in the hollow wedge 16-18 (Fig.
4) so that fatigue is avoided. By combining an elliptical WO 93/17268 213 01 0 2 PCI`/N093/00029 design with a depressed outer groove 19, the flange assembly may additionally be given a further reduced weight As a consequence of the above indicated features and advantages, a pipe joint with flanges according to the invention will also be very environmentally safe since tightness and a large degree of safety aga~nst fatigue in bolts or other mechanical destruction of the mechanically maintainance-free connection during operation will be ensured at any time As a consequence of the feature that at least one of the flanges of the pipe joint may be provided with a bore 15 for access to the groove 12, surveillance/drainage of a possible leakage past the inner flange edge 6, 6a, 9 may be per-formed, which may be of interest when exeptionally strict ; demands to safety are present Additionally, an embodiment of the pipe joint as shown in Figs, 8 and 9, where a re~ilient washer ring is present, may provide for the connection to tolerate overload/~eparation without leakage occurring~
I
!
The ~lange assembly according to the present invention is i~ ~~echa~nically main ainance-free since setting/destruction of ¦ 25 non- -tallic wa~her~/gask:ets or other elements is eliminated ¦~ ~by there being~no~relative movement bet~een~the elements of tho-~lange~as~embly~by~the influence of pressure and loads on th~-~oint The~mechani¢al~str-ngth of the flange as~-~bly may to a~;larg~degree~of reliability be evaluated f,rom tensional estimations`and~material data, since the in-ternally ~tatic~behaviour of~the~joint during operation
5'`~ ~ en~ures~thxt the load~response remains unchanged during the ~ enti # ~operational time~ As a consequence of the above -~ neioned properties, re~ults~from static tests with e g - 35 recordings o~ tension loads~may be transformed to lifetime conditions With # spect to fatigue : , Pipe connections with flanges d-signed according to the .
.:
W093/t72~ PCT/N093/~29 2130102 ;.~
present invention may advantageously be used as flange assemblies in riser pipes extending from a well head to production platforms, in riser pipes i under-water modules, for flange assemblies of stretch stays for stretch stay S platforms, within both off$hore, onshore, and land based process industry, ac wel-l as in nuclear power plants f ~
A preferred embodiment of a flange joint made of steel comprising flange halves according to the invention, will be where the conical area 6, 7 has an angle of 0,3 , where the flange joint is provided both with inner and outer pro-truding sections 8, 9; 10, 11 where the protruding length of both sections are egual, and which length corresponds to 20% of the diference in height between the lower and the upper conical sections 6, 7 The protruding parts advance into the conical section over a distance which is half the distance from the outer edge 10 of the connection to the hole for the bolt Further, such a preferred embodiment comprises a groove 12 for a washer, preferably of the type ~0 disclo ed in Norwegian patent application No 92 2332, as well as an elliptical~transitional section between that part o~ the ~lange which extends mainly parallell 16, 23 to the longitudinal~ axsis A~of the pipe 1, la and that part which extends;mainly perpendicular 18, 22 to the lonqitudinal axis A of~the pipe~ la, the relation between the large and ~; the ~mall axi~ of the~d lipse being 4 1 The groove 12 for j '; , the wash-r is~pr-ferAbly located so that tbe distance from tS the inner surfac~ o~th-~fIange to the clos-st edge of the groove is~l/4 of~,~the~-thickn-ss of the pipe wa}l l, la The wash-r groové is,-;bowever,~not plac-d so close to the inner ~urface,that it~inflUe,nces~on'the inner depending edge 8, 9 Besides,~the,~di~ nsioninq~of~this washer groove is of a ~ork~an-like~,charaoter ~ The circumferential depressed ~' groove 19 providing'~resilienc- to the outer depending '~ 35 ~s-ction 10,~ 11 of~the~,flange half~is located witb its center ~- co that tb point where tb plan- defin-d by the inclined ~lange surf8ce 6, 7 intersects the outer surface 7 of the ~lange liec at a ~maller or an equal distance from the ;~
.
, ,, . ,.. , .. ,.. ~ . .. . . .- -W093/17268 213 ~10 2 PCT/NO93/00029 groove 19 than the distance beween the outer section 18, 22 of the flange extending perpendicular to the axis A of the pipe and the other section of the groove. The width of the groove 19 extends across 2/3 of the outer surface 10, 22; 7, 22 of the flange half, and the depth of the groove 19 is larger than the depth of the outer depending edge 10, 11, preferably twice this depth.
WO93/17268 1Q 2 14 PCT/NO93/0~U29 Leaend~to fiq. ll a-d:
In fig. 11 a-d there is shown a preferred embodiment of a flange according to the invention. The figures refer to a flange with a total outer diameter 01 of 172,6+0,1 mm, diameter 02 between the center line for opposit holes for securing bolts 3 of 144,6 mm, diameter 03 for the bolts' 3 securing holes of l5,0l~Q,1 mm, diameter 04~05 bètween opposit edges of the groove for the washer (inconel 625) located in the groove 20,21 is for outer and inner measure-ments 121,95l0,1 mm and 84,2l0,1 mm, respecitvely. The diameter 06 for the center line of the groove 20,21 for the washer (inconel 625) and the inner and outer edges of the groove is in this embodiment 15+0,05-. The inner measure-ments of the washer groove I is in this embodiment 18,87 +0,05 mm. Fig lla shows an overview of a section of an embodiment of a flange according to the invention, while fig. llb shows the circled detail B in fig. lla. Fig. llc shows a section of the f}ange seen from above with indicated holes for securing bolts 3. In fig. llc an angle ~ between the holes for the securing bolts of 22,5+0,05- is given. In fig. lla the height ~1 of the flange is 103,9~0,2 mm and the height H2 between the horizontally protruding parts and the upper p?rt of the inclined section of the flange plane is 48,3~0,1 mm. The~inclined upper part of the flange has an ' angle c to the porizontal plane of 37,5~2,5-. Detail B from ~ fig. lla, shown ~in fig. lld, has the following measurements:
-~ The di~tance A1 of the pendant~outer edge of the flange from ~' its outer edge to the~joint plane is 3,0~0,1 mm, the .
~distance A2 b~etween the ~uter~edge of the flange to the down~o~t point of the pandant part is 0,5+0,1 mm with an ' i! inclinatidn angle 45-' and the height A3 of the pendant part is 0,023l0,005 mm.~ ~
' 35 The above specifiedlmeàsurements concern a special embodi-,: , ~ , , , - ment of the"flange~according to the invention and other meaSurements and sizes may be used within the scopeof the attatched claims.
1 .
.:
W093/t72~ PCT/N093/~29 2130102 ;.~
present invention may advantageously be used as flange assemblies in riser pipes extending from a well head to production platforms, in riser pipes i under-water modules, for flange assemblies of stretch stays for stretch stay S platforms, within both off$hore, onshore, and land based process industry, ac wel-l as in nuclear power plants f ~
A preferred embodiment of a flange joint made of steel comprising flange halves according to the invention, will be where the conical area 6, 7 has an angle of 0,3 , where the flange joint is provided both with inner and outer pro-truding sections 8, 9; 10, 11 where the protruding length of both sections are egual, and which length corresponds to 20% of the diference in height between the lower and the upper conical sections 6, 7 The protruding parts advance into the conical section over a distance which is half the distance from the outer edge 10 of the connection to the hole for the bolt Further, such a preferred embodiment comprises a groove 12 for a washer, preferably of the type ~0 disclo ed in Norwegian patent application No 92 2332, as well as an elliptical~transitional section between that part o~ the ~lange which extends mainly parallell 16, 23 to the longitudinal~ axsis A~of the pipe 1, la and that part which extends;mainly perpendicular 18, 22 to the lonqitudinal axis A of~the pipe~ la, the relation between the large and ~; the ~mall axi~ of the~d lipse being 4 1 The groove 12 for j '; , the wash-r is~pr-ferAbly located so that tbe distance from tS the inner surfac~ o~th-~fIange to the clos-st edge of the groove is~l/4 of~,~the~-thickn-ss of the pipe wa}l l, la The wash-r groové is,-;bowever,~not plac-d so close to the inner ~urface,that it~inflUe,nces~on'the inner depending edge 8, 9 Besides,~the,~di~ nsioninq~of~this washer groove is of a ~ork~an-like~,charaoter ~ The circumferential depressed ~' groove 19 providing'~resilienc- to the outer depending '~ 35 ~s-ction 10,~ 11 of~the~,flange half~is located witb its center ~- co that tb point where tb plan- defin-d by the inclined ~lange surf8ce 6, 7 intersects the outer surface 7 of the ~lange liec at a ~maller or an equal distance from the ;~
.
, ,, . ,.. , .. ,.. ~ . .. . . .- -W093/17268 213 ~10 2 PCT/NO93/00029 groove 19 than the distance beween the outer section 18, 22 of the flange extending perpendicular to the axis A of the pipe and the other section of the groove. The width of the groove 19 extends across 2/3 of the outer surface 10, 22; 7, 22 of the flange half, and the depth of the groove 19 is larger than the depth of the outer depending edge 10, 11, preferably twice this depth.
WO93/17268 1Q 2 14 PCT/NO93/0~U29 Leaend~to fiq. ll a-d:
In fig. 11 a-d there is shown a preferred embodiment of a flange according to the invention. The figures refer to a flange with a total outer diameter 01 of 172,6+0,1 mm, diameter 02 between the center line for opposit holes for securing bolts 3 of 144,6 mm, diameter 03 for the bolts' 3 securing holes of l5,0l~Q,1 mm, diameter 04~05 bètween opposit edges of the groove for the washer (inconel 625) located in the groove 20,21 is for outer and inner measure-ments 121,95l0,1 mm and 84,2l0,1 mm, respecitvely. The diameter 06 for the center line of the groove 20,21 for the washer (inconel 625) and the inner and outer edges of the groove is in this embodiment 15+0,05-. The inner measure-ments of the washer groove I is in this embodiment 18,87 +0,05 mm. Fig lla shows an overview of a section of an embodiment of a flange according to the invention, while fig. llb shows the circled detail B in fig. lla. Fig. llc shows a section of the f}ange seen from above with indicated holes for securing bolts 3. In fig. llc an angle ~ between the holes for the securing bolts of 22,5+0,05- is given. In fig. lla the height ~1 of the flange is 103,9~0,2 mm and the height H2 between the horizontally protruding parts and the upper p?rt of the inclined section of the flange plane is 48,3~0,1 mm. The~inclined upper part of the flange has an ' angle c to the porizontal plane of 37,5~2,5-. Detail B from ~ fig. lla, shown ~in fig. lld, has the following measurements:
-~ The di~tance A1 of the pendant~outer edge of the flange from ~' its outer edge to the~joint plane is 3,0~0,1 mm, the .
~distance A2 b~etween the ~uter~edge of the flange to the down~o~t point of the pandant part is 0,5+0,1 mm with an ' i! inclinatidn angle 45-' and the height A3 of the pendant part is 0,023l0,005 mm.~ ~
' 35 The above specifiedlmeàsurements concern a special embodi-,: , ~ , , , - ment of the"flange~according to the invention and other meaSurements and sizes may be used within the scopeof the attatched claims.
1 .
Claims (6)
[received by the International Bureau on 16 July 1993 (16.07.93);
original claims 1-16 replaced by amended claims 1-6 (2 pages)]
1. Coupling (2,2a) for high-pressure pipes where the tran-sitional area (16,18) between the part of at least the one coupling half (flange) which extends mainly parallel (16,23) to the longitudinal axis (A) of the pipe and that part of at least the one coupling half which extends mainly perpendicu-lar (18,22) to the longitudinal axis (A) of the pipe, com-prises an elliptical area (16,18), and where each coupling half (flange) has a surface (6,7;8,10;6,10;8,7) forming a contact surface with the opposite coupling half (flange) (2,2a), and where each single coupling half (2,2a) indepen-dent from each other, is designed to contain joining devices such as bolts (3), washers (4,4a) and nuts (5,5a), and where each coupling half (2,2a) optionally may comprise at least one groove for a tightening gasket, and optionally at least a further bore (15) connecting the threads of the outside with the bottom of the gasket groove (12), c h a r a c t e r i z e d i n that at least one coupling half's (flange's) contact surface (6,7;6a,7a;9,11;6,10;6a, 10a)) is designed in such a way that the surfaces (6,7;6a, 7a) between them form a conical slot with an opening angle (.beta.) between the opposite flange's contact surfaces in the interval 0,2 - 3° and with an opening directed out towards the outer surface (7,22;10,22) of the coupling.
2. Coupling according to claim 1, c h a r a c t e r i z e d i n that the prestressed length of the tightening bolts (3) is at least 3 times the diameter of the bolts and preferably 6-7 times the diameter of the bolts (3).
3. Coupling according to claim 1 or 2, c h a r a c t e r i z e d i n that at least one of the contact surfaces (6,7;6a,7a) of at least one of the flanges (2,2a) in the coupling on its outer diameter (7) and/or its inner diameter (6) comprises a projecting section (10,11;8, 9) shaped as a wedge (7,10,11;6,8,9) in front of the contact surface (6,7).
4. Coupling according to claim 3, c h a r a c t e r i z e d i n that at least one of the contact surfaces (6,7) in at least one of the flanges (2,2a) comprises two wedge-formed projecting sections (8,9;10,11) where each of the conical planes for the wedge-formed sections (8,9;10,11) have oppositely directed conicity.
5. Coupling according to any of the proceeding claims, c h a r a c t e r i z e d i n that at least one of the flanges (2,2a) have an elliptical intermediate section (16, 18) extending from the pipe section of the flange and being tangent to the rear flange plane, the ratio between its large axis and its small axis being in the interval 3:1 -5:1, preferably 4:1.
6. Coupling according to any of the proceeding claims, c h a r a c t e r i z e d i n that at least one of the coupling halves (2,2a) further comprises a depressed groove (19) on its outer axis-symmetrical flange surface (7,10,22).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| NO920686A NO177160C (en) | 1992-02-20 | 1992-02-20 | Coupling comprising two opposite coupling halves |
| NO920,686 | 1992-02-20 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2130102A1 true CA2130102A1 (en) | 1993-09-02 |
Family
ID=19894898
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002130102A Abandoned CA2130102A1 (en) | 1992-02-20 | 1993-02-22 | Coupling for flanged pipes, process for connecting the flanges and use of the coupling |
Country Status (13)
| Country | Link |
|---|---|
| EP (1) | EP0630456A1 (en) |
| JP (1) | JPH07504021A (en) |
| KR (1) | KR950700512A (en) |
| AU (1) | AU3576993A (en) |
| BR (1) | BR9305929A (en) |
| CA (1) | CA2130102A1 (en) |
| CZ (1) | CZ9402001A3 (en) |
| FI (1) | FI943841L (en) |
| HU (1) | HUT69904A (en) |
| NO (1) | NO177160C (en) |
| RU (1) | RU2091657C1 (en) |
| SE (1) | SE9402514D0 (en) |
| WO (1) | WO1993017268A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20160186905A1 (en) * | 2012-12-07 | 2016-06-30 | Apl Technology As | Tube connector for detachably connecting two connector parts for gas-tight connecting of riser tubes to vessels |
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|---|---|---|---|---|
| PT907858E (en) * | 1996-07-03 | 2004-02-27 | Codelast Ltd | JOINTS |
| FR2799259B1 (en) * | 1999-10-01 | 2001-12-07 | Georges Dupont | SYSTEM FOR CONNECTING TWO TUBE END CAPS |
| US6758502B2 (en) | 2001-01-17 | 2004-07-06 | Lindab Ab | Coupling ring for ventilation ducts, and method of connecting ventilation ducts |
| SE0100942D0 (en) * | 2001-03-19 | 2001-03-19 | Verax Engineering Ab | Method of manufacturing a flanged element and a flange element |
| DE10141944A1 (en) * | 2001-08-28 | 2003-04-03 | Bayerische Motoren Werke Ag | Mounting flange for pipe connections |
| SE524724C2 (en) * | 2001-12-28 | 2004-09-21 | Verax Engineering Ab | Flanged element provided with a radially concave end surface and joints comprising flanged elements |
| DE102004025375B4 (en) | 2004-05-24 | 2010-01-28 | Airbus Deutschland Gmbh | Window frame for aircraft |
| FR2891606B1 (en) * | 2005-10-05 | 2009-03-06 | Snecma Sa | FLANGED CONNECTION DEVICE. |
| FR2914729B1 (en) | 2007-04-05 | 2009-10-30 | Snecma Sa | PRE-STRESSED FLANGED CONNECTION DEVICE WITH FLANGES |
| US8282136B2 (en) | 2008-06-30 | 2012-10-09 | Mueller International, Llc | Slip on groove coupling with multiple sealing gasket |
| US8015882B2 (en) * | 2009-06-04 | 2011-09-13 | Rosemount Inc. | Industrial process control pressure transmitter and flange coupling |
| US9500307B2 (en) | 2012-01-20 | 2016-11-22 | Mueller International, Llc | Slip-on coupling gasket |
| US9194516B2 (en) | 2012-01-20 | 2015-11-24 | Mueller International, Llc | Slip-on coupling |
| US9534715B2 (en) | 2012-01-20 | 2017-01-03 | Mueller International, Llc | Coupling gasket with multiple sealing surfaces |
| US9039046B2 (en) | 2012-01-20 | 2015-05-26 | Mueller International, Llc | Coupling with tongue and groove |
| US9168585B2 (en) | 2012-11-02 | 2015-10-27 | Mueller International, Llc | Coupling with extending parting line |
| US8857293B2 (en) | 2013-03-11 | 2014-10-14 | American Axle & Manufacturing, Inc. | Power transmitting component with multi-part housing assembly having continuous sealing flange |
| CN103277260A (en) * | 2013-04-23 | 2013-09-04 | 广东明阳风电产业集团有限公司 | A method for preventing cracking of the joint surface of the outer flange of the wind power tower |
| CN103277261A (en) * | 2013-04-23 | 2013-09-04 | 广东明阳风电产业集团有限公司 | An anti-cracking structure for the joint surface of the inner flange of the wind power tower |
| CN107110408B (en) * | 2014-10-28 | 2020-04-24 | 通用电器技术有限公司 | Dissimilar pipe joint in high temperature, high pressure transient and under cyclic loading |
| DE102015104718A1 (en) * | 2015-03-27 | 2016-09-29 | Reinert - Ritz Gmbh | flange |
| NO345662B1 (en) | 2018-11-02 | 2021-06-07 | Tp Products As | A flange element for a flange connection, a flange connection for a tower structure and a tower structure comprising such a flange connection. |
| KR102198803B1 (en) * | 2019-06-17 | 2021-01-05 | 주식회사 성호철관 | Flange integral type corrugated steel pipe |
| JP7529975B2 (en) * | 2020-05-11 | 2024-08-07 | 横浜ゴム株式会社 | Joint Structure |
| JP7461643B2 (en) * | 2020-06-16 | 2024-04-04 | 株式会社水道技術開発機構 | Pipe joint structure and pipe joint connection method |
| RU2763154C1 (en) * | 2021-07-30 | 2021-12-27 | Публичное акционерное общество «Татнефть» имени В.Д. Шашина | Fastening a flange connection at the wellhead |
| US20230204058A1 (en) * | 2021-12-27 | 2023-06-29 | Freudenberg Oil & Gas, Llc | Flange connection |
| US20230250905A1 (en) * | 2022-02-09 | 2023-08-10 | Freudenberg Oil & Gas, Llc | Pipe flange connection system with static seal |
| NO348194B1 (en) * | 2022-03-11 | 2024-09-23 | Tp Products As | Flange element |
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| US2412487A (en) * | 1944-01-03 | 1946-12-10 | Dow Chemical Co | Thermoplastic pipe flange |
| US3214201A (en) * | 1962-05-29 | 1965-10-26 | Ceilcote Company Inc | Pipe flange |
| FR1563983A (en) * | 1968-03-05 | 1969-04-18 | ||
| DE2239314A1 (en) * | 1972-08-10 | 1974-02-21 | Hartmut Soehle | SAFETY FLANGE |
| US4183562A (en) * | 1977-04-01 | 1980-01-15 | Regan Offshore International, Inc. | Marine riser conduit section coupling means |
| DE3103551C2 (en) * | 1981-02-03 | 1986-09-11 | Kempchen & Co Gmbh, 4200 Oberhausen | Sealing arrangement for flange seals |
-
1992
- 1992-02-20 NO NO920686A patent/NO177160C/en not_active IP Right Cessation
-
1993
- 1993-02-22 CZ CZ942001A patent/CZ9402001A3/en unknown
- 1993-02-22 WO PCT/NO1993/000029 patent/WO1993017268A1/en not_active Ceased
- 1993-02-22 FI FI943841A patent/FI943841L/en unknown
- 1993-02-22 AU AU35769/93A patent/AU3576993A/en not_active Abandoned
- 1993-02-22 EP EP93904409A patent/EP0630456A1/en not_active Withdrawn
- 1993-02-22 JP JP5514716A patent/JPH07504021A/en active Pending
- 1993-02-22 HU HU9402359A patent/HUT69904A/en unknown
- 1993-02-22 RU RU9394041734A patent/RU2091657C1/en active
- 1993-02-22 BR BR9305929A patent/BR9305929A/en not_active Application Discontinuation
- 1993-02-22 CA CA002130102A patent/CA2130102A1/en not_active Abandoned
-
1994
- 1994-07-19 SE SE9402514A patent/SE9402514D0/en unknown
- 1994-08-20 KR KR1019940702895A patent/KR950700512A/en not_active Ceased
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20160186905A1 (en) * | 2012-12-07 | 2016-06-30 | Apl Technology As | Tube connector for detachably connecting two connector parts for gas-tight connecting of riser tubes to vessels |
| US10422456B2 (en) * | 2012-12-07 | 2019-09-24 | Apl Technology As | Tube connector for detachably connecting two connector parts for gas-tight connecting of riser tubes to vessels |
Also Published As
| Publication number | Publication date |
|---|---|
| RU2091657C1 (en) | 1997-09-27 |
| AU3576993A (en) | 1993-09-13 |
| BR9305929A (en) | 1997-08-19 |
| NO920686L (en) | 1993-08-23 |
| FI943841A0 (en) | 1994-08-19 |
| HU9402359D0 (en) | 1994-10-28 |
| NO177160B (en) | 1995-04-18 |
| FI943841A7 (en) | 1994-08-19 |
| SE9402514D0 (en) | 1994-07-19 |
| EP0630456A1 (en) | 1994-12-28 |
| CZ9402001A3 (en) | 1995-01-18 |
| FI943841L (en) | 1994-08-19 |
| NO920686D0 (en) | 1992-02-20 |
| NO177160C (en) | 1995-07-26 |
| KR950700512A (en) | 1995-01-16 |
| JPH07504021A (en) | 1995-04-27 |
| RU94041734A (en) | 1996-07-27 |
| HUT69904A (en) | 1995-09-28 |
| WO1993017268A1 (en) | 1993-09-02 |
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