WO2005047745A2 - Joint d'encastrement sollicite pour raccords mecaniques de tuyaux - Google Patents

Joint d'encastrement sollicite pour raccords mecaniques de tuyaux Download PDF

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Publication number
WO2005047745A2
WO2005047745A2 PCT/US2003/032648 US0332648W WO2005047745A2 WO 2005047745 A2 WO2005047745 A2 WO 2005047745A2 US 0332648 W US0332648 W US 0332648W WO 2005047745 A2 WO2005047745 A2 WO 2005047745A2
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WO
WIPO (PCT)
Prior art keywords
gasket
bell
spigot
segment
gutter
Prior art date
Application number
PCT/US2003/032648
Other languages
English (en)
Other versions
WO2005047745A3 (fr
Inventor
Daniel Albert Copeland
Original Assignee
United States Pipe And Foundry Company, 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.)
Filing date
Publication date
Application filed by United States Pipe And Foundry Company, Llc filed Critical United States Pipe And Foundry Company, Llc
Priority to RU2006110374/06A priority Critical patent/RU2336454C2/ru
Priority to MXPA06003795A priority patent/MXPA06003795A/es
Priority to AU2003282837A priority patent/AU2003282837B2/en
Priority to CNB2003801105049A priority patent/CN100504133C/zh
Priority to CA2536500A priority patent/CA2536500C/fr
Priority to JP2005510604A priority patent/JP4411489B2/ja
Priority to EP03774835A priority patent/EP1673568A4/fr
Priority to PCT/US2003/032648 priority patent/WO2005047745A2/fr
Priority to CA2709737A priority patent/CA2709737C/fr
Publication of WO2005047745A2 publication Critical patent/WO2005047745A2/fr
Publication of WO2005047745A3 publication Critical patent/WO2005047745A3/fr

Links

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
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L21/00—Joints with sleeve or socket
    • F16L21/08—Joints with sleeve or socket with additional locking means

Definitions

  • This invention relates generally to connections between lengths of pipe, or between pipes and fittings. More particularly, the invention is directed toward a device and method of connecting two lengths of pipe that maximizes the advantages of both restrained push-on joints as well as mechanical joints, as are known commonly in the art. The invention has application to long-run pipe lengths as well as fittings, appurtenances, and connections. DESCRIPTION OF RELATED ART
  • a spigot end of a pipe slides into a bell end of another pipe past a tightly fitted gasket.
  • No follower ring, stuffing box, or other external compression means typically is present in a push-on joint.
  • the typical push-on joint does not include a restraining means, though such means as tie bars, concrete thrust blocks, screws, and additional ring attachments have been employed in some cases to effect restraining to the joints.
  • Advancements in the art have led to innovations and modifications of push-on joints to include restraining means. Examples of such restrained push-on joints include U.S. Patent Nos. 5,295,697; 5,464,228; and 5,067,751.
  • connection in such advancements may be effected by locking segments or wedges within the gasket that engage the spigot.
  • the locking segments are oriented in such a manner as to allow entry of the spigot into the bell, but upon counterforces tending to effect removal of the spigot, the segments pivot toward a biting engagement with the spigot, stopping further removal.
  • the effect is much like a child's "finger lock" toy, the stronger the attempt to remove the pipe, the greater the locking effect exerted by the inserts.
  • These push-on type joints enjoy superior flexibility and resistance to both axial and para-axial separative forces. Meaningful difficulty has been experienced in the industry, however, in applying these connections to fittings, where it may be impracticable to secure the fitting sufficiently to exert the high installation pressures necessary initially to push the spigot into the bell in such configurations.
  • a "mechanical joint” is a well-known standardized connection device widely employed in the pipe industry. Such a joint fluid-seals two lengths of pipe together by compressing a gasket around a spigot and within a bell at the intersection.
  • Mechanical joints are characterized by an outwardly flanged bell of a receiving pipe, into which a spigot of a second pipe is inserted. The bell is adapted to seat a gasket that fits snugly about the circumference of the spigot of the second pipe, and further to receive a supporting compression ring or gland. In assembly, the spigot is fully advanced into the bell and the gasket is firmly seated within the bell and around the spigot.
  • the gland is then forced against the gasket by fastening it securely to the bell flange through such means as fastening bolts tightened under relatively high torque.
  • This configuration typically includes a lip about the inner diameter of the gland that upon securement extends axially within the bell.
  • the configuration of the gland is such that as the lip is forced against the gasket, the gasket becomes compressed under pressures sufficient to deform the gasket. As the gasket is compressed between the bell and the gland, the gasket therefore is squeezed inwards toward and into sealing contact with both the exterior of the inserted pipe section and the interior of the bell. This deformation enhances the sealing effectiveness of the gasket beyond that which can be readily obtained in the absence of compression or high insertion forces
  • Additional solutions employ a bolting assembly attached to (or incorporated into) the bell, which assembly is oriented such that upon tightening of certain specially configured bolts, the bolts or a device actuated thereby are driven into the outer surface of the spigot.
  • These bolting schemes are exemplified by devices sold by EBAA Iron, commonly known in the art under the trademark MEGALUG (Registration No. 1383971)
  • Further examples of this type of solution include U.S. Patent No. 4,647,083, to Hashimoto, which modifies the standard gland to include bolts that act upon locking wedges when tightened.
  • each of these solutions may be considered a "static" connection.
  • pipelines are traditionally considered to be rigid and immobile structures, a durable connection must allow for a certain amount of flexibility and "play" at joints. Such accommodation to movement is necessary because the environments in which pipelines lay are not truly static. Thrust forces may create non-longitudinal, or para-axial, loads that tend to drive a pipe length toward an angle from the longitudinal axis of the lengths to either side of such axis. As the pressures of the material being transported within the pipe vary, the forces will similarly vary. Additionally, locations in which pipes are run rarely are as stable as commonly believed. In fact, pipes may be run above ground, in which cases such pipes do not enjoy the benefit of any stability enhancing factors of bedding or trenched installation. Finally, even typical earth-bedded pipes must endure shifting due to sedimentation, erosion, compaction, mechanical forces (such as nearby construction), and earth movement (such as earthquakes).
  • U.S. Patent No. 2,201,372 to Miller, which employs a compression snap-ring fitted within a special lip of the bell, in order to exert pressure onto the locking segments and thus drive them into the spigot.
  • Alternatives in Miller similarly drive locking segments into the spigot upon installation.
  • U.S. Patent No. 3,445,120, to Barr likewise employs a gasket with stiffening segments completely encased therein that are generally disposed in a frustroconical arrangement. Such segments are stated to give the gasket a resistance to compression along the plane that includes both ends of the segment. When a spigot is subjected to withdrawing forces, the gasket rolls with the movement of the pipe.
  • the gasket rolls, it is intended to eventually encounter a position in which the stiffened plane needs to compress for further rolling. In optimal conditions, due to the stiffening, the gasket cannot compress and therefore cannot roll further. As the rolling stops, the gasket becomes a static friction- based lock between the spigot and the bell. Notably, among other distinctions, the arrangement taught by Barr remains a rubber-to-pipe factional connection.
  • an an exemplary and non-exclusive alternative object of this invention is to provide a gasket interchangeable with gaskets of standard mechanical joints which allows for the transformation of the joint into a restrained joint without the need for any reconfiguration or adaptation of the bell, spigot, or gland of the mechanical joint involved.
  • a further exemplary and non-exclusive alternative object is to provide a dynamic connection for pipes that does not require high insertion pressures.
  • a further exemplary and non-exclusive alternative object of the invention is to provide for a cost effective manner and device of restraining a typically configured pipe joint.
  • the present invention may be described basically as a gasket for converting a standard mechanical joint into a restrained mechanical joint without the need for altered configuration of the bell, spigot, or gland of the joint, and without the need for additional fittings or devices.
  • a standard mechanical joint's bell and gland configuration can be employed to connect a spigot end of one pipe length to the bell end of another pipe length in a restrained relationship (restraint being defined as resistance to axial separation of a mated bell and spigot), with the restraint based on forces superior to rubber-to-pipe friction.
  • the invention includes forming the gasket to fit within the bell in such a manner that a void exists during rest, into which void the gasket deforms, which in turn influences the rotational motion of the segment.
  • the configuration of the gasket influences the timing and extent of rotation during the process of securing the gland to the bell. Overpenetration may be avoided, while at the same time ensuring sufficient penetration at the proper moment in time. Controlling the timing and extent of locking segment rotation influences gasket performance and is addressed by the described embodiments of this invention. The extent of segment rotation affects the application of restraint.
  • Figure 1 shows an diagram of the typical mechanical joint, having a gasket in place.
  • Figure 2 depicts a cross-sectional view of an un-stressed gasket of the present invention in the initial phase, at a location in which the position and cross-section of the locking segment can be viewed.
  • Figure 3 demonstrates the cross-sectional view of an embodiment of the gasket.
  • Figure 4 is a depiction of the gasket and segment in the joint during the act of assembly, in the transition phase.
  • Figure 5 shows an embodiment of a locking segment configuration useful in the present invention.
  • Figure 6 shows the joint of the present invention following compression and in a locked state, restraining the joint.
  • Figure 7 is an alternative embodiment of the locking segment useful in a gasket of the current invention.
  • Figure 8 is a cross-sectional view of a gasket for use in the current invention, showing an alternate embodiment of the locking segment in place.
  • Figure 1 presents a diagram of a typical mechanical joint. Assembly of the joint according to the current invention is practiced as known in the art. Particularly, but without limitation of the known variants which shall be as equally applicable to the present invention as they are to the known art, the joint contains the following elements in the following relationship.
  • Compression ring or gland 11 is placed on spigot 10, following which gasket 2 is placed around the exterior of spigot 10.
  • Spigot 10 is then advanced within bell 12 until the end 41 of spigot 10 is stopped by an annular shoulder 42 within bell 12.
  • Gasket 2 is advanced into bell 12 until it seats in the annular recess seat 43, as shown.
  • Gland 11 is then abutted against gasket 2 and is secured to bell 12 by securing devices 44, which are presented for illustration here as bolts 45 passing through perforations 46 and engaged by nuts 47.
  • securing devices 44 which are presented for illustration here as bolts 45 passing through perforations 46 and engaged by nuts 47.
  • the locking segment 1 of the present invention may be constructed to fit within a gasket 2 that is configured to fit within any standard mechanical joint without necessitating changes to the configuration of the bell, gland, or spigot.
  • Gasket 2 is an elastomeric or other resilient or deformable material, such as those in the art will understand may be used in the practice of a mechanical joint.
  • a useful configuration of the gasket 2, as shown in Figure 3, is an annular ring with a radially inner surface 4 that is adapted to be in contact with spigot 10, a gland face 7 that is adapted to be compressed by a gland or compression ring 11, a front face 61 that leads in axial insertion, and a radially outer surface, shown in the drawings as having a configuration that does not mate smoothly with the recess seat 43 in a resting state.
  • the radially outer surface of the gasket 2 has a compression seat surface 9 at the leading portion of the gasket 2 near the front face 61 that is designed to mate with and seal against an area of the recess seat 43.
  • gasket 2 conforms to all of the requirements of ANSI/ A WWA C111/A21.11-95. In particular, for any given spigot 10, gasket 2 tends to have a slightly smaller inner diameter than the outer diameter of the spigot 10. Accordingly, placement of gasket 2 over the exterior of spigot 10 typically will require exertion of force to expand gasket 2 to fit around spigot 10.
  • the gutter 63 being an annular depression (radially speaking) is characterized by the fact that if gasket 2 is advanced into the bell 12 as fully as is possible in the resting state (e.g., prior to deformation), and rotated to contact the bell 12 in the area of the recess-seat 43 as much as possible without deformation, a void remains between the gasket 2 and the recess seat 43; such depression or void is the gutter 63.
  • a portion of the gutter 63 remains vacant of gasket material, even during some advanced stages of compression and assembly.
  • the gutter 63 in other embodiments could be covered by a film of rubber or otherwise be a void below the radially outward surface of gasket 2, and still be and operate as a gutter 63 in the spirit and scope of the invention.
  • Gasket 2 incorporates at least one locking segment 1, which may be configured as shown in Figure 5, also shown as embedded in the gasket 2 in Figure 8.
  • a number of locking segments 1 will be circumferentially dispersed about and within gasket 2, and though preferable, the placement need not be precisely or even nearly symmetrical.
  • the number of such segments 1 may be selected with reference to the expected separative forces to be encountered by the joint, with a higher force tending to recommend a larger number of segments 1.
  • the inventor prefers to use no fewer than three such segments 1, but the invention is not so limited.
  • a preferred configuration of segments 1 for use with a pipe of eight inch diameter intended to carry fluids at pressures of 350 p.s.i. includes eight to ten segments 1 uniformly spaced around the spigot-facing circumference of gasket 2 (e.g., the radially inner surface 4).
  • An alternative would allow a single segment 1 of a circumference appreciable to (at least one-half the size of) the circumference of gasket 2.
  • Separative forces tend to extract spigot 10 from bell 12. As indicated by directional arrow 50, some separative forces follow in-line with the common axis of assembled pipe lengths. Other separative forces are para-axial, as shown by vectors 50a and 50b, which may be due to bedding shifting or non-uniform securement around the periphery of spigot 10.
  • Segment 1 is intended to grip spigot 10 and to translate separative forces into forces at least partially opposing bell 12. To this end, segment 1 possesses teeth 6 that are adapted to protrude from inner surface 4 of gasket 2, at least upon compression of gasket 2 by gland 11.
  • Teeth 6 are adapted to contact spigot 10, and are most preferably fashioned of a substance that is harder than the material comprising the exterior of spigot 10.
  • teeth 6 are, in the uncompressed state of gasket 2, already exposed from the inner surface 4 as shown by Figure 8. This exposure may be by protrusion from the inner surface 4, or by slight recessing beneath inner surface 4 in combination with the absence of gasket material covering the teeth, which is the embodiment shown in Figure 3 and subsequent images.
  • the gasket 2 may be configured with a recess about teeth 6 to prevent interference with penetration of such teeth 6 into spigot 10.
  • An alternative preferred embodiment presents teeth 6 slightly recessed within gasket 2, and covered by a membrane or thin layer of compressible or puncturable material.
  • the inventors suggest that at least some of the area between teeth 6 or immediately adjacent to teeth 6 be free of rubber to allow penetration of the spigot 10.
  • An advantage of initial concealment is that it allows for greater advancement of gland 11, and thus greater compression of gasket 2, prior to substantial engagement of teeth 6 into spigot 10. A greater sealing effectiveness therefore may be achieved.
  • segment 1 possesses a plurality of teeth 6.
  • the tips of teeth 6 are arranged in an arcuate relationship.
  • the arcuate relationship enhances the ability of teeth 6 to bite into spigot 10 despite any variations in circumference of spigot 10 or the inner dimensions of bell 12. This is because a larger gap (frequently due to manufacturing tolerances) between spigot 10 and the inner dimensions of bell 12 (particularly annular gasket recess seat 43) will cause segment 1 in assembly to be rotated upon compression of gasket 2 toward a steeper angle relative to spigot 10 than exists in the unstressed configuration as displayed in Figure 2. Given the arcuate relationship of teeth 6, upon such rotation of segment 1 the most axially inner teeth rotate into contact with spigot 10.
  • the arcuate configuration further urges at least two teeth 6 to be in contact with spigot 10, regardless of the rotation of segment 1. This is because in the arcuate configuration, a straight line can be drawn between any two adjacent teeth 6.
  • the presence of additional teeth 6 to either side of any biting tooth 6 tends to assist in preventing overpenetration of the spigot 10 by segment 1, due to the fact that these adjacent teeth will be pointed at an angle to spigot 10 such that they are not optimally positioned for biting; rather, adjacent teeth 6 will tend to contact spigot 10 at an angle substantially more parallel to spigot 10 than those teeth 6 that are biting into spigot 10. Accordingly, because of the more-parallel angle, adjacent teeth 6 act as stops to further penetration.
  • segment 1 in cross section has a toothed edge 16, with teeth 6 extending therefrom in the arcuate pattern as above discussed; and a back face 13, extending radially and axially along a slope towards protrusion 17.
  • Back face 13 as shown is adapted to be in a close proximity to, or even in direct contact with, gland 11 when the mechanical joint is assembled.
  • Connecting protrusion 17 in the axially inner direction with toothed edge 16, is a surface, or a series of surfaces, denoted compression faces 15.
  • back face 13 is in close proximity to gland 11 when the joint is assembled, and upper protrusion 17, being the most radially outer area of the segment, is in close proximity to gasket land 49 of the bell.
  • a greater volume of elastomeric material of gasket 2 exists between compression seat surface 9 (particularly shoulder 8) and segment 1 than is present between back face 13 and gland 11.
  • toothed edge 16 of segment 1 may be forced radially outwardly by the presence of spigot 10, and may cause pivoting of segment 1.
  • the volume of compressible material present between the segment's compression faces 15 and recess seat 43 allows for such outward movement or pivoting without compromising the integrity of gasket 2.
  • gasket 2 Following such insertion of spigot 10 into bell 12, gasket 2 will be in a position basically as represented in Figure 2, and the gasket 2 may be already in contact with recess-seat 43 at some point. In any event, substantial compression of gasket 2, as in compression sufficient to effect the sealing and securement of the joint is not at this point effected. Further assembly is carried out by advancing of gland lip 71 against the gasket 2 gland face 7, and into the bell 12. As will be evident to those skilled in the art, this advance of gland 11 will by contact with gasket 2 force gasket 2 inwardly into contact or more forceful contact with recess seat 43. As shown from Figure 4, gasket 2, and in the shown embodiment specifically compression seat surface 9, begins deformation against recess-seat
  • This phase of the assembly operation is the transitional phase and is characterized by a relatively decreasing amount of translational motion of segment 1 and a relatively increasing amount of rotational motion of segment 1.
  • upper protrusion 17 advances into the bell at a faster rate than teeth 6 for a given input by gland 11. This occurs because the center of pressure of the compression energy stored in the gasket moves closer to the teeth 6 of segment 1 and away from upper protrusion 17 as the gasket is compressed. Rotation of segment 1 at this point is influenced by the gutter 63 and is related to the movement of the center of pressure of the gasket toward teeth
  • gutter 63 presents the area of least resistance to compression, and hence to deformation (it being known in the art that rubber tends to deform, but not to compress), the upper (as seen in the Figures) portion of the segment 1 rotates toward the gutter 63, reducing the size of the gutter 63 as the gasket material deforms into the area.
  • the resistive contact in the shown embodiment is specifically between a tooth 6 and protrusion 17 of segment 1 and the corresponding joint surfaces of spigot 10 and bell 12. Until the final phase of assembly is entered, if a tooth 6 is in resistive contact with spigot 10, or protrusion 17 is in resistive contact with bell 12 it will be understood that this contact is of a sliding nature. Upon the substantial collapse of gutter 63 and the start of the final phase of assembly, further gasket deformation is extremely limited which effectively prevents further translation of segment 1 further in the axial direction. Any additional clamping force applied to the securing mechanism between gland 11 and bell 12 (e.g.
  • any attempt of the spigot 10 to move outwardly of bell 12 urges at least this one tooth 6 to move axially outwardly of bell 12 along with spigot 10, but axial movement is not possible due to the resistive contact between back face 13 and lip 71 of the gland and a rotation of the locking segment in a direction that exerts axial resistance as well as radial pressure among the segment 1, the bell 12, and the spigot 10.
  • This axial resistance, or restraint is caused by the segment rotating into a direction in which its length is greater than the distance between the spigot 10 and the bell 12.
  • the balance between the axial load and the radial load imparted to the bell and spigot affects the performance of the invention and may be influenced by the configuration of segment 1.
  • teeth 6 are unable to prematurely engage spigot 10 in a manner that may adversely affect the ability to obtain optimal compression of gasket 2.
  • This delayed engagement can be manipulated by the means discussed above; namely, the configuration of the gasket, notably the gutter 63, compression seat surface 9, distortion control surface 62, elastomeric characteristics of the gasket 2, shape of segment 1, position of segment 1 in gasket 2 or various combinations of these features.
  • Due to contact with bell 12 in addition to gland 11, separative forces are transferred by segment 1, not just against gland 11 but also against bell 12. This is significant in that it reduces a potentially substantial force that is resisted by bolts 45 and gland 11. Under high loads, bolts 44 and gland 11 may distort, reducing sealing effectiveness of gasket 2; the current invention's ability to transfer a significant portion of the magnitude of the separative vector directly to bell 12 via segment 1 therefore enhances the effectiveness of sealing.
  • the condition that exists in a large gap situation (e.g. when the manufacturing tolerances and assembly conditions exist such that bell 12 dimensions are at a maximum diameter condition and spigot 10 dimensions are at a minimum diameter condition) is such that upon initial assembly, neither gasket 2 or segment 1 may be in contact with either one or both spigot 10 or bell 12.
  • gasket deformation will occur, as previously described, due to compressive forces acting on gasket 2 by spigot 10, gland 11 and bell 12 forcing gasket 2 into contact with both spigot 10 and bell 12. At this point however, segment 1 may still not be in contact with either spigot 10 or bell 12.
  • segment 1 Approaching the end of the transitional phase of assembly, as gutter 63 of gasket 2 closes up due to elastic deformation of gasket 2 caused by compression of gasket 2, a dramatic rotation of segment 1 will occur due to the previously described shift in the center of pressure of the compressed gasket and its relationship to segment 1. This dramatic rotation allows segment 1 to bridge large gaps for which restraint would otherwise be impossible to provide.
  • the final phase of assembly then proceeds as previously described with teeth 6 embedding in spigot 10 and protrusion 17 embedding in bell 12.
  • upper protrusion 17 may be formed in an angular configuration. Such an angular configuration will cause such points to bite into bell 12 when sufficient pressure is exerted between segment 1 and bell 12.
  • the propensity to bite can be controlled by adjusting the acuteness of the angle.
  • the inventor notes that the more acute the angle at either given point, the earlier along a pressure curve the point will likely bite into bell 12. Accordingly, it is possible to adjust the tendency toward desired points of final rotation of segment 1 by adjusting the acuteness of angle of the upper protrusion 17, which will in turn adjust the maximum probable radially outward movement of upper protrusion 17. It should be noted that at pressures sufficient to drive upper protrusion 17 into bell 12, rotation of segment 1 will be substantially prevented and will occur under conditions of plastic deformation of either segment 1, spigot 10 or bell 12. This mechanism can be employed to balance the rotation of segment 1-and control the point of engagement.
  • segment 1 may be adjusted to allow axial movement of segment 1 until upper protrusion 17 obtains non-compressible abutment with bell 12, at which point the axial and radial forces acting on segment 1 at upper protrusion 17 cause the pivot point to occur in its near vicinity. Variations of this allow further control of segment engagement and the balance of axial and radial loading distributed to all load carrying components of the invention.
  • An alternative embodiment, as shown in Figure 7, may be to incorporate an elbow 3 into the back face of segment 1. Elbow 3 will contact gland 11 during securement of the restraining devices 44 in the initial stages of the transitional assembly phase.
  • the location and configuration of elbow 3 may be tailored to further alter the behavior of segment 1 during rotation, engagement and lockup.
  • the location and configuration of elbow may be to incorporate an elbow 3 into the back face of segment 1. Elbow 3 will contact gland 11 during securement of the restraining devices 44 in the initial stages of the transitional assembly phase.
  • the location and configuration of elbow 3 may be tailored to further alter the behavior of segment 1 during rotation, engagement and lockup.
  • elbow 3 may be further explained by addressing several characteristics of elbow 3 which may be modified to alter segment behavior. If elbow 3 is given a sharp radius, elbow 3 may be made to penetrate gland 11 at the contact point. This penetration will impart additional resistance to further rotation of segment 1 when the final assembly phase is complete thus relieving some of the reliance on the angle of the line of action segment 1 makes relative to spigot 10 and bell 12 when balancing the segments axial and radial load carrying distribution. Additionally, elbow 3 may be positioned radially outward or inward on segment 1. Placing elbow 3 radially outward on the segment will increase the rotational tendency of the segment during the transitional phase of assembly promoting earlier engaement and lockup of segment 1. Placing elbow 3 radially inward on segment 1 will have a correspondingly opposite effect.
  • elbow 3 is made such that it penetrates gland 11 while at the same time upper protrusion 17 penetrates into bell 12, a situation may be created whereas both axial and radial loads transferred into bell 12 may be balanced along multiple load paths.
  • the transition between such points may be less pronounced than in Figure 2.
  • the transition may be so smooth as to create a general curve that acts as both elbow 3 and upper protrusion 17.
  • a curve could be adapted to effect biting engagement, whether by altering the radius of curvature, or by including nubs or other points to operate as engagement points (which, for purposes of this invention could be considered to be elbow 3 or upper protrusion 17).
  • gutter 63 or the area around gutter 63 include the strategic positioning of a secondary or tertiary elastomeric material having different deformation characteristics than the remainder of gasket 2. Such strategic positioning may optimally include placement between frontal slope 15 of segment 1 in the vicinity of upper protrusion

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gasket Seals (AREA)
  • Joints Allowing Movement (AREA)
  • Joints With Sleeves (AREA)

Abstract

De manière générale, l'objet de la présente invention peut être décrit comme un joint servant à transformer un raccord mécanique standard en un raccord mécanique encastré, qui ne nécessite pas de modifier la configuration de l'emboîtement, du cordon ou du presse-étoupe du raccordement ni d'utiliser des raccords ou dispositifs supplémentaires. Dans sa réalisation pratique, une configuration standard à emboîtement et cordon peut s'utiliser pour raccorder l'extrémité cordon d'une longueur de tuyau à l'extrémité emboîtement de l'autre longueur de tuyau, l'encastrement étant assuré par des forces supérieures au frottement entre le caoutchouc et le tuyau. Selon une description plus détaillée des modes de réalisation visés, le procédé de l'invention consiste à former un joint devant s'adapter à l'intérieur de l'emboîtement de manière à ce qu'un creux ou un logement se forme au repos, le joint étant comprimé à l'intérieur de ce creux, ce qui a pour effet d'influencer le mouvement rotatif du segment. De cette manière, la configuration du joint influence la durée et le degré de rotation pendant la fixation de l'emboîtement au cordon.
PCT/US2003/032648 2003-10-15 2003-10-15 Joint d'encastrement sollicite pour raccords mecaniques de tuyaux WO2005047745A2 (fr)

Priority Applications (9)

Application Number Priority Date Filing Date Title
RU2006110374/06A RU2336454C2 (ru) 2003-10-15 2003-10-15 Удерживающая уплотнительная прокладка для механических соединений труб
MXPA06003795A MXPA06003795A (es) 2003-10-15 2003-10-15 Junta de retencion energizada para uniones mecanicas de tuberias.
AU2003282837A AU2003282837B2 (en) 2003-10-15 2003-10-15 Energized restraining gasket for mechanical joints of pipes
CNB2003801105049A CN100504133C (zh) 2003-10-15 2003-10-15 用于填料箱装配的限制衬垫及装配受限机械接头的方法
CA2536500A CA2536500C (fr) 2003-10-15 2003-10-15 Joint d'encastrement sollicite pour raccords mecaniques de tuyaux
JP2005510604A JP4411489B2 (ja) 2003-10-15 2003-10-15 管のメカニカル継手用の付勢拘束ガスケット
EP03774835A EP1673568A4 (fr) 2003-10-15 2003-10-15 Joint d'encastrement sollicite pour raccords mecaniques de tuyaux
PCT/US2003/032648 WO2005047745A2 (fr) 2003-10-15 2003-10-15 Joint d'encastrement sollicite pour raccords mecaniques de tuyaux
CA2709737A CA2709737C (fr) 2003-10-15 2003-10-15 Joint d'encastrement sollicite pour raccords mecaniques de tuyaux

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Application Number Priority Date Filing Date Title
PCT/US2003/032648 WO2005047745A2 (fr) 2003-10-15 2003-10-15 Joint d'encastrement sollicite pour raccords mecaniques de tuyaux

Publications (2)

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WO2005047745A2 true WO2005047745A2 (fr) 2005-05-26
WO2005047745A3 WO2005047745A3 (fr) 2005-08-18

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PCT/US2003/032648 WO2005047745A2 (fr) 2003-10-15 2003-10-15 Joint d'encastrement sollicite pour raccords mecaniques de tuyaux

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EP (1) EP1673568A4 (fr)
JP (1) JP4411489B2 (fr)
CN (1) CN100504133C (fr)
AU (1) AU2003282837B2 (fr)
CA (2) CA2709737C (fr)
MX (1) MXPA06003795A (fr)
RU (1) RU2336454C2 (fr)
WO (1) WO2005047745A2 (fr)

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US7093863B2 (en) 2000-06-08 2006-08-22 United States Pipe And Foundry Company, Llc Restraining gasket for mechanical joints of pipes
US7104573B2 (en) 2000-06-08 2006-09-12 United States Pipe And Foundy Company, Llc Energized restraining gasket for mechanical joints of pipes
US7137653B2 (en) 2003-09-25 2006-11-21 United States Pipe And Foundry Company, Llc Centroidally twistable compression ring for pipe joints
CN101730812B (zh) * 2006-10-31 2013-01-09 圣-戈班Pam集团公司 管接头
CN114662345A (zh) * 2022-05-23 2022-06-24 中国二十二冶集团有限公司 大直径虾壳弯管制作方法
US11774012B2 (en) 2018-09-18 2023-10-03 Asml Netherlands B.V. Apparatus for high pressure connection

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KR101514689B1 (ko) * 2009-01-27 2015-04-23 가부시끼 가이샤 구보다 파이프 조인트
US20110291409A1 (en) * 2010-06-01 2011-12-01 Kennedy Jr Harold Pipe Gripping Elements with Buttress Pockets and Pipe Joint Restraints Incorporating Same
CN102683571A (zh) * 2012-05-31 2012-09-19 华南理工大学 一种大功率led散热结构
CN104913133B (zh) * 2014-03-10 2018-09-18 科斯摩工机股份有限公司 流体管的脱离防止装置和管接头
WO2017169531A1 (fr) * 2016-03-28 2017-10-05 株式会社クボタ Raccord de tuyaux, élément de prévention de séparation, et procédé de raccordement de tuyaux
CN109084105B (zh) * 2018-10-26 2023-08-29 江苏格睿特管网工程有限公司 钢筋混凝土推进管环槽型接头连接结构
WO2021102318A1 (fr) 2019-11-22 2021-05-27 Trinity Bay Equipment Holdings, LLC Systèmes et procédés de raccord de tuyau réutilisable
CN113738983B (zh) * 2020-12-11 2023-03-24 上海威逊机械连接件有限公司 快装式管件组件及其应用

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7093863B2 (en) 2000-06-08 2006-08-22 United States Pipe And Foundry Company, Llc Restraining gasket for mechanical joints of pipes
US7104573B2 (en) 2000-06-08 2006-09-12 United States Pipe And Foundy Company, Llc Energized restraining gasket for mechanical joints of pipes
US7108289B1 (en) 2000-06-08 2006-09-19 United States Pipe And Foundry Company, Llc Restraining gasket for mechanical joints of pipes
US7137653B2 (en) 2003-09-25 2006-11-21 United States Pipe And Foundry Company, Llc Centroidally twistable compression ring for pipe joints
CN101730812B (zh) * 2006-10-31 2013-01-09 圣-戈班Pam集团公司 管接头
US11774012B2 (en) 2018-09-18 2023-10-03 Asml Netherlands B.V. Apparatus for high pressure connection
CN114662345A (zh) * 2022-05-23 2022-06-24 中国二十二冶集团有限公司 大直径虾壳弯管制作方法
CN114662345B (zh) * 2022-05-23 2022-08-05 中国二十二冶集团有限公司 大直径虾壳弯管制作方法

Also Published As

Publication number Publication date
EP1673568A2 (fr) 2006-06-28
WO2005047745A3 (fr) 2005-08-18
RU2006110374A (ru) 2007-11-20
CN1860321A (zh) 2006-11-08
JP4411489B2 (ja) 2010-02-10
CA2536500C (fr) 2010-11-02
AU2003282837A1 (en) 2004-06-06
CA2709737A1 (fr) 2005-05-26
CA2709737C (fr) 2012-09-25
AU2003282837B2 (en) 2010-03-04
RU2336454C2 (ru) 2008-10-20
EP1673568A4 (fr) 2010-07-07
MXPA06003795A (es) 2006-06-14
AU2003282837A8 (en) 2005-06-06
CN100504133C (zh) 2009-06-24
CA2536500A1 (fr) 2005-05-26
JP2007521443A (ja) 2007-08-02

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