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    • 专利摘要:
    summary expansion joint an expansion joint is used to accommodate changes in the length of the pipe lines above the ground due to thermal expansion. a tube is surrounded by a ring attached to a sleeve. one end of the pipe is attached to a pipe line, one end of the sleeve is attached to another pipe in the pipe line. the tube and the ring and sleeve are movable axially relative to each other when the pipe expands or contracts in a linear fashion. a seal between the ring and the tube ensures fluid tightness of the joint.
    公开号:BR112014004110B1
    申请号:R112014004110-5
    申请日:2012-08-17
    公开日:2020-03-17
    发明作者:Randy L. Chase；Douglas R. Dole；Lawrence W. Thau；Wayne M. Biery；Scott D. Madara；Ryan D. Kuehner
    申请人:Victaulic Company；
    IPC主号:
    专利说明:

    EXPANSION BOARD
    CROSS REFERENCE FOR RELATED ORDERS
    [001] This application claims priority for: US Provisional Patent Application No. 61 / 525,987, filed on August 22, 2011; US Provisional Patent Application No. 61 / 540,676, filed on September 29, 2011 and US Provisional Patent Application No. 61 / 588,429, filed on January 19, 2012, all of these Provisional Patent Applications being incorporated by reference in its entirety.
    FIELD OF THE INVENTION
    [002] This invention relates to expansion joints used in long pipe lines subjected to thermally induced expansion and contraction.
    FUNDAMENTALS
    [003] Pipe lines used in industries, such as oil extraction, can be long and exposed to alternating heating and cooling cycles. This is of particular concern for above-ground pipe lines, which are subject to greater temperature variation than below-ground lines. Heating and cooling can be the result of large variations in ambient temperature, both daily and seasonal, to which the pipe line is exposed, as well as due to the heat contained in the fluid being pumped through the pipe line. The fluid itself can be hot, or it can be heated by the pumping action. Friction between the fluid and pipe line can also contribute to heating and expansion.
    [004] As is well known, many metals, especially materials such as steel, from which pipe lines are often built, expand and contract in response to heating and cooling. The linear expansion coefficient of the material is the characteristic that quantitatively describes how an elongated item, such as a pipe element, will behave in response to heating and cooling. The units of the linear expansion coefficient, specified in English units of measurement, are inches of expansion per inch of pipe per temperature change in degrees Fahrenheit. Therefore, it is evident that the expansion or contraction of a pipe line will be directly proportional to both the temperature change as well as the length of the pipe line.
    [005] In the case of long pipe lines subject to even small variations in ambient or interior temperature, it is advantageous to provide expansion joints at intervals along the length of the pipe line to accommodate thermally induced changes in length and avoid damage to the pipe line. pipe that could otherwise occur. For example, the pipe line may curve when subjected to compression due to expansion in response to an increase in temperature, or, a joint may fail when subjected to stress loads due to contraction of the pipe line in response to a decrease in temperature. .
    SUMMARY
    [006] The invention relates to an expansion joint for connecting pipe elements. In one embodiment, the expansion joint comprises a tube having an outer surface and opposing first and second ends. A sleeve has a first and a second ends arranged opposite each other, the sleeve being positioned surrounding at least a portion of the tube. The portion includes the second end of the tube. A ring, separated from the sleeve and removably attachable to the first end thereof, surrounds the tube and has an inner surface facing the outer surface of the tube. A coupling is positioned between the ring and the first end of the sleeve. The coupling removably attaches the ring to the sleeve. A seal is mounted on the inner surface of the ring and tightly engages the outer surface of the tube. The ring and sleeve are axially movable, sliding relative to the tube.
    [007] In a particular example embodiment, the first end of the tube has an outward-facing surface with a circumferential groove in it. The coupling can have a plurality of arcuate segments joined end to end around the tube. In this example, each of the segments has a first and second keys projecting radially inwards positioned in a spaced relation and the ring has an outward facing surface with a circumferential groove in it. The sleeve has an outwardly facing surface positioned at the first end thereof with a circumferential groove in it. The first key engages the circumferential groove in the ring, the second key engages the circular groove in the sleeve.
    [008] In an additional example embodiment, the sleeve has an outward facing surface positioned at the second end of it with a circumferential groove in it.
    [009] In a particular embodiment, the seal comprises at least one circumferential groove facing inwardly positioned on the inner surface of the ring with a sealing element positioned within at least one groove. For example, the sealing member may comprise an O-ring. In addition, an anti-extrusion ring positioned inside at least one groove. In another example, the seal comprises a plurality of inwardly circumferential grooves positioned on the inner surface of the ring and a plurality of sealing elements, each positioned within a respective one of the grooves. In this example, sealing elements may comprise O-rings. In addition, a plurality of anti-extrusion rings can be positioned within each of the respective grooves.
    [010] In another example embodiment, the expansion joint may comprise at least one circumferential groove facing inwardly positioned on the inner surface of the ring and at least one supporting element positioned within at least one groove. In addition, the expansion joint may also include at least one inwardly circumferential groove positioned on the inner surface of the ring and at least one cleaning element positioned within at least one groove.
    [011] In another example, the seal comprises a shoulder projecting radially inwards from the inner surface of the ring. Packaging material surrounds the tube and is positioned adjacent the shoulder between the inner surface of the ring and the outer surface of the tube. A ring is attached to the ring and surrounds the tube. The rim is positioned adjacent to the packaging material and the packaging material is captured between the rim and the boss. In this example, the rim is movable axially with respect to the ring to compress the packaging material against the shoulder. For the purpose of movement of the rim the expansion joint comprises a plurality of adjustable fasteners. Each fastener extends between the rim and the ring where tightening the fasteners moves the arc towards the ring to compress the packaging material.
    [012] An example embodiment of the expansion joint may further comprise a plurality of springs. Each of the springs is mounted on one of the fasteners and engages the ring to press the ring towards the ring, thereby compressing the packaging material.
    [013] In another example, the expansion joint also comprises an inlet segment positioned at the first end of the tube. The entry segment has a tapered inner surface. The conical interior surface can be selected from the group consisting of a straight cone and an S-shaped cone having an inflection point marking the transition between a concave interior surface and a convex interior surface. In this example embodiment, the inlet segment can be separated from the first end of the tube and removably attached to it. The inlet segment has a first and a second opposite ends. A second coupling can be positioned between the first end of the tube and the first end of the inlet segment, the second coupling removably attaching the inlet segment to the tube. As an example, the second coupling has a plurality of arcuate segments joined end to end around the tube. Each of the segments has first and second keys projecting radially inwards positioned in a spaced relation. The first end of the tube has an outward-facing surface with a circumferential groove in it. The first end of the entry segment has an outwardly facing surface with a circumferential groove in it. The first key engages the circumferential groove of the tube, the second key engages the circumferential groove in the inlet segment.
    [014] In another example embodiment, the expansion joint comprises a first protrusion projecting outwardly from the outer surface of the tube and a second protrusion projecting outwardly from an outer surface of the ring. A rod is attached to one of the projections and extends through an opening in the other of the projections. The guide rod e is an indicator of relative movement between the tube and the ring. In a particular example, the rod is attached to the first ledge. The rod may include a projection extending radially outwards from it. The projection can be engaged with the second projection to limit the relative movement between the tube and the ring. An actuator can be positioned between the first and second projections. The actuator applies force to the projections to move the ring and tube relative to each other. For example, the actuator can comprise a hydraulic actuator.
    [015] In another example embodiment of an expansion joint for connecting pipe elements, the expansion joint comprises a tube having an outer surface and first and second ends arranged opposite each other. A sleeve is positioned around at least a portion of the tube. The sleeve has an inner surface facing the outer surface of the tube. The sleeve and the tube are slidably movable longitudinally relative to each other. A seal is positioned between the outer surface of the tube and the inner surface of the sleeve. The first surface projects transversely from the outer surface of the tube, the first surface being positioned between the first end of the tube and the seal. The second surface projects transversely from the inner surface of the sleeve to the tube and is interlockable with the first surface to limit the relative sliding movement between the tube and the sleeve when the first and second surfaces contact each other. In a particular example embodiment, the sleeve is less than the length of the tube. In addition, the second end of the tube can project axially outwardly from the sleeve.
    BRIEF DESCRIPTION OF THE DRAWINGS
    [016] Figure 1 is an isometric view in partial section of an example expansion joint;
    [017] Figure 2 is an exploded isometric view of an example mechanical coupling;
    [018] Figure 3 is a sectional view of a portion of the expansion joint in Figure 1;
    [019] Figure 4 is a sectional view of a portion of an example embodiment of an expansion joint;
    [020] Figure 5 is an isometric view of an example of an expansion joint;
    [021] Figure 6 is a partial sectional view of an example of an expansion joint in a pipe line;
    [022] Figure 7 is a partial sectional view of an example of an expansion joint;
    [023] Figure 8 is an isometric view in partial section of an example of expansion joint modality;
    [024] Figures 9, 9A, 9B and 9C are an example partial sectional view of inlet segments usable with an expansion joint;
    [025] Figure 10 is an isometric view in partial section of an example of an expansion joint;
    [026] Figure 11 is a sectional view of a portion of the expansion joint of Figure 10;
    [027] Figure 12 is an isometric view in partial section of the expansion joint of Figure 10 being assembled;
    [028] Figure 13 is a partial sectional view of an example expansion joint in a pipe line; and [029] Figure 14 is an isometric view of an example of an expansion joint modality.
    DETAILED DESCRIPTION
    [030] Figure 1 illustrates an example expansion joint 10 according to the invention. Expansion joint 10 comprises a tube 12 having an outer surface 14 and first and second ends 16 and 18 arranged opposite each other. It may be advantageous to position an abrasion resistant coating 15 within the tube 12. Coating 15 may comprise, for example, hardened steel, or have a chromium carbide coating, or comprise a ceramic that is resistant to abrasion. As the liner 15 provides a sacrificial surface (which prevents wear of the tube 12) it is even more advantageous that the liner 15 is easily removable from the tube to allow for the prompt replacement of worn linings. To facilitate ease of removal, the liner 15 may have a flange 17 which is screwed to the end 16 of the tube 12.
    [031] A sleeve 20 surrounds at least a portion of the tube 12 that includes the second end 18. The sleeve 20 has respective first and second ends 22 and 24, arranged opposite each other. A ring 26 is attached to the sleeve 20. Ring 26 is separated from the sleeve 20 and is removably attached to the first end 22 of the sleeve. In this example, attachment of the ring and sleeve is performed using a segmented mechanical coupling 28. Figure 2 shows an exploded view of coupling 28, which includes arched segments 30 with key pairs 32 in spaced relation. A gasket seal 34 is positioned between the keys 32 when the segments 30 are screwed end to end by circling and joining the ring 26 to the sleeve 20. As shown in Figure 1, the keys 32 engage a circumferential groove 36 on the outer surface of the ring 26 and a groove 38 on the outer surface of the first end 22 of the sleeve 20. Coupling between the keys 32 and grooves 36 and 38 provide positive mechanical engagement between the ring 26 and the sleeve 20, and the seal 34 ensures a fluid tight seal on the Joins. Other types of mechanical couplings, for example, screwed interaction flanges positioned on ring 26 and sleeve 20, are also possible.
    [032] Ring 26 surrounds tube 12 and is positioned between the first and second ends of tube 16 and 18. Ring 26 has an inner surface 40 facing the outer surface 14 of tube 12. A seal 42 is mounted on the inner surface 40 of the ring 26. Seal 42 hermetically engages the outer surface 14 of the tube 12. The ring 26 and sleeve 20 are slidably movable axially relative to the tube 12, the axial direction being shown by the double arrow 44. The outer surface 14 of the tube 12 is smooth and facilitates the formation of a fluid tight seal between seal 42 and tube 12. The smooth surface also allows tube 12 and ring 26 (along with sleeve 20) to slide axially relative to each other while maintaining the seal.
    [033] In this example, as shown in Figure 3, seal 42 comprises a plurality of circumferential grooves 46 positioned on the inner surface 40 of ring 26. One or more of the grooves 46 receive a sealing member 48, such as an O-ring. Other types of sealing elements, such as quadrilateral rings and modified flap seals are also possible. In addition to the sealing elements, anti-extrusion rings 50 can also be positioned inside the grooves 46 adjacent to each sealing element 48. The anti-extrusion rings 50 are installed inside grooves 46 on the low pressure side of the sealing elements 48 and help avoid extrusion of the sealing elements in the space between ring 26 and tube 12. Sealing elements and anti-extrusion rings can be made of compatible materials, such as EPDM, nitrile rubber and other natural and synthetic rubber compounds, as well as others polymers, such as PTFE, nylon, polyurethane and PEEK. It is advantageous to use anti-extrusion rings from elastomers so that they can accommodate significant changes in the diameter of the tube 12 due to thermal effects.
    [034] It is more advantageous to position other functional elements in grooves 46. For example, one or more cleaning elements 52, comprising, for example, quadrilateral rings formed from plastic, such as PTFE, can be positioned in one or more of the grooves 46 Cleaning elements are used to clean the outer surface 14 of the tube 12 from foreign matter that could damage the sealing elements 48. This is especially useful when the expansion joint carries abrasive suspensions, which can work their way into the space between the tube 12 and the sleeve 20 to which the ring 26 is attached, and thereby contaminate the outer surface of tube 14. In addition, support elements 54, for example rings formed of plastic, such as PTFE or composites reinforced by fibers formed by graphite, can also be positioned inside the grooves 46 to support and guide the ring 26 and the tube 12, during the relative movement between the two components onents.
    [035] In the example embodiment shown in Figure 3, a shoulder 58 is positioned adjacent to the seal 42 and projects inwards from the inner surface 40 of the ring 26 towards the outer surface 14 of the tube 12. It is practical to make the shoulder 58 integral with the inner surface 40 of the ring 26 and that it is part of a raised grooved surface 60 that receives the sealing elements 48, 52 wipers, brackets 54 and other interface components between the ring 26 and tube 12. Boss 58 allows another seal 62 to be part of ring 26. Seal 62 can be used alone as the primary seal between ring 26 and tube 12, or, it can be considered as a reserve seal to seal 42. Seal 62 is formed of a material packaging material 64 positioned around the tube 12, the packaging material being positioned adjacent the shoulder 58 and between a portion of the inner surface 40 of the ring 26 and the outer surface 14 of the tube 12. Materia Packing l 64 can be formed, for example, braided graphite, with or without PTFE filling. The package 64 is initially compressed to effect a fluid tight seal. To ensure a fluid-tight seal with packaging wear and pressure variation, the packaging can be further compressed. A compression ring 66 is provided for this function. Compression ring 66 is attached to ring 26 adjacent to packaging material 64 and surrounds tube 12. Ring 66 has an angular cross section, with an angle leg 68 being positioned between the outer surface 14 of the tube 12 and the inner surface 40 of the ring 26 so as to contact the packaging material 64. The other leg 70 of the compression ring 66 extends radially outwardly from the leg 68. Ring 66 is axially movable towards and away from the packaging material 64 so adjusting the bulging caused by packaging compression and thus making a seal. The movement of the compression ring 66 is made by a plurality of adjustable fasteners such as threaded rivets and nuts 72, which pass through the leg 70 and are threadedly engaged with the end of the ring 26. The rivets and nuts 72 are distributed circumferentially around the rim 66, preferably at equal intervals, relatively little spaced. This allows uniform compression to be applied to the package by tightening the nuts 72, Note that additional cleaning elements 52 and / or support elements 54 can be mounted on the leg 68 of the rim 66 to support the ring 26 at its movement interface with surface 14 of pipe 12. The advantage of having a compressible reserve seal such as seal 62 is evident, for example, when seal 42 begins to leak. Unlike seal 62, seal 42 is not adjustable and must be repaired. However, if seal 62 starts to leak it can be further compressed as described above, preventing any leakage and saving time for replacing seal 42.
    [036] As shown in Figure 4, it is advantageous to press the rim 66 to engage the packaging material 64 through spring elements 74. The spring elements are positioned on the adjustable fasteners, in this example, comprising threaded shafts 76 that connect rim 66 to ring 26. Spring elements 74 are positioned between compression nuts 78 and rim leg 70. In this configuration, the tightening of nuts 78 compresses spring elements 74 against rim 66, thereby compressing the rim in relation to the packaging material 64, and also maintaining the compression at a substantially constant compressive force when the packaging material 64 deteriorates and the rim 66 moves to the ring 26. Using pressure spring elements 74 decreases the potential tightening need periodic adjustment of nuts 78. Figure 5 shows an isometric view of the spring-pressed rim 6 6 engaged with ring 26.
    [037] Figure 6 shows the example of expansion joint 10 mounted on a pipe line. A first pipe element 80 of a portion of the pipe line is attached to the first end 16 of the tube 12, and a second pipe element 82 is attached to the second end 24 of the sleeve 20. The second end 18 of the tube 12 is received from coaxial mode inside ring 26 and inside sleeve 20. Tube 12 is in sliding seal engagement with seals 42 and 62 of ring 26 and telescopic engagement with sleeve 20. In this example, attachment of ring 26 to sleeve 20 is effected by a mechanical pipe coupling 28 (shown in detail in Figure 2 and described above). Attachment of the pipe elements 80 and 82 is carried out in a similar way, but it could also be performed by bolted flange joints. As shown in Figure 6, the first end 16 of the tube 12 has an outwardly facing surface 84 with a circumferential groove 86 therein. Likewise, the second end 24 of the sleeve 20 has an outwardly facing surface 88 with a circumferential groove 90 inside it. Another coupling 28, having segments 30 with keys 32, engages a groove 86 at the first end 16 of the tube 12 and a groove 92 at the end of the first pipe element 80. Second pipe element 82 is similarly attached to the second end 24 of the sleeve 20. In this way, the couplings 28 mechanically block the sleeve 20 for the ring 26, the first pipe element 80 for the tube 12 and the second pipe element 82 for the sleeve 20, with the interface between keys and grooves providing positive mechanical engagement. As shown in Figure 6, ring seals 34 extend circumferentially around each interface between the ring 26 and the sleeve 20, the tube 12 and the pipe element 80, and the sleeve 20 and the pipe element 82. The seals rings 34 are compressed by segments 30 against outwardly sealing surfaces in ring 26, sleeve 20 and pipe elements 80 and 82 to provide a fluid tight connection on each coupling 28. The use of mechanical couplings to join the pipe 12 for the pipe element 80, the ring 26 for the sleeve 20, and the sleeve 20 for the pipe element 82 provide the additional advantage of allowing the expansion joint 10 to be rotated about its longitudinal axis without disassembling the assembly . It is only necessary to loosen the fasteners by holding the segments 30 in an end-to-end relationship, thus relieving the fastening force of the couplings 28. The expansion joint 10 can then be rotated relative to the pipe elements 80 and 82, and the fasteners retightened to fix the expansion joint to the pipe elements. The ability to rotate the expansion joint is useful for extending the life of the joint on the face of abrasive wear encountered when abrasive suspensions are pumped through the joint. Abrasive wear is not evenly distributed over the inner surfaces of the expansion joint, but tends to be concentrated on the lower surfaces. This is because the abrasive material tends to settle within the flow stream, and is concentrated near the lower surfaces of the expansion joint. If the expansion joint 10 is periodically rotated about its longitudinal axis it distributes the wear more evenly along the inner surface of the expansion joint which results from the uneven distribution of abrasive particles in the flow. Joint rotation is also effective to increase the life of the joint when a coating (as shown in Figure 1) is present inside the tube 12.
    [038] Relative axial movement between the tube 12, and the ring 26 and sleeve 20 is caused by the thermally induced expansion and contraction of the pipe elements that make up the pipe line. For most materials, heating the pipe line will lengthen it in proportion to its length and temperature rise. This will make the ring 26 together with the attached sleeve 20 move to the first end 16 of the tube 12, and the second end 18 of the tube 12 move more deeply into the sleeve 20. On the other hand, a decrease in temperature will make the ring 26 and the attached sleeve 20 move away from the first end 16 of the tube 12, and the second end 8 of the tube 112 move outwardly from the deeper engagement with the sleeve 20.
    [039] Alternatively, the connection between the pipe elements 80 and 82 and the expansion joint 1 can be made through interacting flanges extending radially outwards to the ends of the pipe elements and expansion joint, the flanges being screwed together using threaded fasteners. Welding is also an option for connection, but mechanical coupling methods (ie segmented couplings and flanged couplings) have the advantage of ease of installation and removal, which can be useful when building the pipe line and, later, for replacement of expansion joints when they wear out.
    [040] There is a preferred flow direction through the expansion joint 10, which is from the pipe end 16 to the pipe end 18. This preferred flow direction prevents disturbances to the flow that would occur for flow passage in the opposite direction at the end 18 of tube 12, which shows a sharp change in the cross-sectional area for the flow and can cause turbulence and its associated increased wear rate. Use of a preferred flow direction reduces abrasive wear on tube 12, when suspensions with a high content of particles, such as tar sands carrying oil or mining wastes are being transported through the pipeline network.
    [041] Expansion joint operation 10 can be easily visualized using Figure 6. For example, an increase in ambient temperature causes the pipe elements such as 80 and 82 along the pipe line to increase in length. As a result, the expansion joint 10 undergoes a compressive force, as the lengths of the pipes connected to the tube 12 and the sleeve 20 respectively grow more. The compressive force is applied to the expansion joint 10 at the end 16 of the tube 12 and at the end 24 of the sleeve 20. This causes the tube 12 and the ring 26 and the sleeve 20 to move in axially opposite directions with respect to each other, as a significant restriction in this movement is the friction between the seals 42 and 62 (attached to the ring 26) and the outer surface 14 of the tube 12, which cannot resist the applied axial force. Likewise, as the ambient temperature decreases, the pipe line cools and the pipe elements contract, placing a tensile force on the expansion joint 10. The pipe line shrinking axially pulls the tube 12 and sleeve 20 in directions opposite, and again, a significant restriction against axial movement is the friction at the interface between seals 42 and 62 and the outer surface 14 of the tube 12, which gives shape to allow relative movement. In practical applications, for a steel pipe line, the linear steel expansion coefficient results in a change in length of ¾ of an inch for every 100 feet of pipe line for every 100 ° F change in temperature. Depending on the room temperature range and the lengths of pipe line between expansion joints, expansion joint 10 may have to accommodate up to about 40 inches of travel.
    [042] Although it is possible to design expansion joints 10 for a wide range of axial displacement, it is sometimes found economical to manufacture expansion joints with the same range of axial displacement and to organize them in series into a composite expansion joint when calculations predict what more displacement will be needed for a specific installation that can be accommodated by a single expansion joint. It can be appreciated that the arrangement of two expansion joints arranged in series doubles the length of the potential axial displacement compared to the use of a single expansion joint of the same type. The number of expansion joints that can be used end to end to suit the expansion capacity for a given application is not limited to two, and it is anticipated that practical limitations will allow for great versatility in the design.
    [043] It is advantageous to use an externally visible indicator / stop on the expansion joint 10 to indicate the degree of engagement between the tube 12 and sleeve 20. In the example shown in Figure 7, an indicator / stop 96 comprises a first projection 98 projecting towards the exterior from the outer surface 14 of the tube 12, and a second protrusion 100 projecting outwardly from the exterior facing surface of the ring 26. The rod 102 can be attached to any of the protrusions 98 and 100 and passed through a hole in the other ledge. The rod can be calibrated, with a length scale, for example, and it serves to measure the relative movement and the position between the tube 12 and the ring 26 and the sleeve 20. Indicator / stop 96 can be used to initially position the tube 12 with respect to sleeve 20 when expansion joint 10 is being installed in a pipe line so that there is sufficient length of travel in both expansion and contraction to accommodate the expected pipe line length excursions. To fulfill the stop function of the indicator / stop 96, the stem 102 may have a projection extending radially outwards to engage the projection through which it passes and limits the relative movement between sleeve 20, ring 26 and tube 12, In the example shown, the projection comprises a nut 104 threaded at the end of the rod 102, however, it is also contemplated that other forms of projection can be used, and be positioned in an adjustable way at any point along the rod to define a point of stop for movement between tube 12 and ring 26. Multiple indicators / stops 96 can, of course, be used as stops to distribute the expansion or contraction load, and multiple projections can be used, for example, one on each side of the projections to allow limits on both expansion and contraction of the joint to be effected. The use of indicator / stop 96 is advantageous when several expansion joints 10 are used in series to force all expansion joints to operate to accommodate pipe line movement. It is conceivable that an expansion joint could have lower frictional forces between its tube and ring than the other expansion joints in the series. If not for the indicator / stop 96, this expansion joint could therefore have all the movement, which, for contraction of the pipe line, can result in a disconnection between the pipe 12 and sleeve 20.
    [044] It is expected that the frictional forces between the seals 42 and 62 and the outer surface 14 of the tube 12 that resist axial movement between the tube 12 and the ring and the sleeve 26 and 20, will be greater due to the high pre- radial load between the seals and the surface 14 necessary to ensure fluid tightness against the internal pressure inside the expansion joint 10. Therefore, it is advantageous to use motorized actuators, for example, hydraulic actuators 105, temporarily positioned between the projections 98 and 100, to apply axially directed forces to the tube and the ring to assemble and disassemble the expansion joint 10 and establish the desired degree of coupling between the tube 12 and the sleeve 20.
    [045] As mentioned above, it is advantageous to periodically rotate the expansion joint around its longitudinal axis to more evenly distribute the abrasive wear caused by the irregular distribution of the suspended abrasive particles passing through the joint. Abrasive particles tend to settle and concentrate near the lower surfaces of the expansion joint, and thus cause an accelerated rate of wear along these lower portions of the joint than along the upper surfaces. However, it is also observed that the entrance to the expansion joint suffers a higher rate of localized abrasive wear than the other parts of the joint. To further extend the life of the expansion joint, and to facilitate the repair of worn parts, it is advantageous to form the inlet portion of the expansion joint from a separate, removable component. An example of an embodiment of such an expansion joint 104 is shown in Figure 8. Expansion joint 104 comprises an inlet segment 106, coupled to tube 12 by a mechanical coupling 28. Coupling 28 comprises segments 30 screwed together end to end around an end of the inlet segment 106 and the tube 12. In this example of expansion joint, both the inlet segment 106 and the tube 12 have circumferential grooves 84 and 108 at their respective ends that receive keys 32 in the coupling segments 30, as shown in Figure 8. Engagement between keys 32 and grooves 84 and 108 provides positive mechanical engagement between coupling 28 and the component parts it joins. The seal 34 captured between the coupling segments 30, the inlet segment 106 and the end of the tube 12 ensures a fluid tight seal between the inlet segment and the tube. Other types of mechanical couplings, for example, screwed interaction flanges positioned on the inlet segment 106 and tube 12, are also possible to make a connection between the inlet segment and the tube that allows easy removal of the inlet segment from the tube.
    [046] Figures 9, 9A, 9B and 9C provide detailed cross-sectional views of examples of inlet segments 106. To reduce turbulence in the flow transition between a pipe element (not shown) and tube 12 (see also the 8), the inner surface 110 of the inlet segment 106, positioned between the pipe element and the tube, can be tapered. The cone may be a straight, tapered cone 111, as shown in Figure 9. Alternatively, as shown in Figure 9A, inner surface 110 may have an "S" shape with an inflection point 112 between the ends of the inlet segment. which marks the transition between a concave surface portion 114 and a convex surface portion 161. Furthermore, the inner surface 110 near each end of the inlet segment 106 can be oriented angularly with respect to a reference line 118 parallel to the longitudinal axis of the input segment. Orientation angles 120 of about 3 ° are advantageous, with angles as high as 10 ° or as low as 2 ° being practical.
    [047] By making the expansion joint inlet portion 104 into a separate component 106, maintenance and repair of the expansion joint is simplified. For example, to extend joint life, inlet segment 106 can only be rotated about its longitudinal axis to even out abrasive wear. The rotation period is based on time and service and service conditions such as flow rate and concentration of abrasive substances. This is simpler than rotating the entire expansion joint 104. In addition, when rotation of the inlet segment 106 will no longer be sufficient to provide a segment of acceptable thickness, it is only necessary to replace the inlet segment 106, instead of the entire expansion joint 104. Replacement is also facilitated by the use of mechanical couplings 28 (see Figures 2 and 8), which allow simple screwing and unscrewing the coupling segments to allow replacement of the input segment 106.
    [048] Maintenance and repair can be improved economically by using an abrasion resistant coating 115 positioned within the inlet segment 106, as shown in Figure 9B. Coating 115 may comprise, for example, hardened steel, or have a chromium carbide coating, or comprise a ceramic that is resistant to abrasion. As the liner 115 provides a sacrificial surface (preventing wear of the inlet segment 106) it is further advantageous that the liner 115 is easily removable from the inlet segment to allow easy replacement of worn linings. To facilitate peelability, liner 115 may have a flange 117 that is screwed to one end of the inlet segment. As with the inner surface of the inlet segment 110, the inner surface 19 of the liner 15 can be formed to reduce turbulence. The inner liner surface 119 can have a straight tapered cone 121, as shown in Figure 9B, or, as shown in Figure 9C, inner liner 19 of the liner 115 can have an "S" shape with an inflection point 112 between the ends of the entry segment which marks the transition between a concave surface portion 114 and a convex surface portion 116.
    [049] Figure 10 is an isometric view in partial section of another example of expansion joint 122 for connecting pipe elements in a pipe line to each other while accommodating thermally induced expansion and axial contraction of the pipe line. Expansion joint 122 comprises a tube 124. Tube 124 has an outer surface 126 on which a seal 128 is mounted. In this example, seal 128 comprises a plurality of circumferential grooves 130 positioned on the outer surface 126 of tube 124.
    [050] As shown in Figure 11, one or more of the grooves 130 receives a sealing element 132, such as an O-ring. Other types of sealing elements, such as quadrilateral rings and modified flap seals are also viable. In addition to the sealing elements, the anti-extrusion rings 134 can also be positioned inside the grooves 130 adjacent to each of the sealing elements 132. Anti-extrusion rings 134 are installed inside the grooves 130 on the low pressure side of the elements sealing 132 and help to prevent extrusion of the sealing elements in the space between the tube 124 and the sleeve 136 to which the tube 124 is attached (described below). Sealing elements and anti-extrusion rings can be made of compatible materials, such as EPDM, nitrile rubber and other natural and synthetic rubber compounds, as well as other polymers such as PTFE, nylon, polyurethane and PEEK.
    [051] As shown in Figure 10, the aforementioned sleeve 136 surrounds a portion of tube 124. Sleeve 136 has an outer surface 138 and an inner surface facing inward 140. The inner surface facing inward 140 is smooth and dimensioned to couple the seal 128. In this example, sealing elements 132 are captured within the respective grooves 130 and compressed between the outer surface 126 of the tube 124 and the inner surface 140 of the sleeve 136 to effect a fluid tight seal between the sleeve and the pipe. The smooth inner surface 140 of the sleeve 136 facilitates fluid tight sealing and allows the sleeve 136 and the tube 124 to slide axially relative to each other. It is also advantageous to position other functional elements in grooves 130. For example, as shown in Figure 11, one or more cleaning elements 142, comprising, for example, plastic-formed quadrilateral rings, such as PTFE, can be placed in one or more of the grooves 130. Cleaning elements are used to clean the outer surface 126 of the pipe 124 from foreign bodies that could damage the sealing elements 132. This is especially useful when the expansion joint is carrying abrasive suspensions, which can work their way in the space between the tube 124 and the sleeve 136, and thus contaminate the outer surface of tube 126. In addition, support elements 144, for example rings formed of plastic, such as PTFE, or of fiber-reinforced composites formed by graphite, they can also be positioned inside the grooves 130 to support and guide the tube 124 and sleeve 136 during the relative movement between the two components.
    [052] With reference again to Figure 10, a surface 146 is positioned at one end 148 of the sleeve 136. Surface 146 projects transversely from the inner surface 140 of the sleeve 136 towards the tube 124. Another surface 150 projects transversely to the outside from the outer surface 126 of the tube 124, the surface 150 being positioned between the seal 128 and the end 152 of the tube 124. Surface 146 in the sleeve 136 is interlockable with surface 150 in the tube 124 and, when in contact, the surfaces act as a stop to limit relative axial sliding movement between the tube and the sleeve. It is practical to make surface 150 integral with the outer surface 126 of tube 124 and to have it as part of a raised grooved surface 154 comprising seal 128. Furthermore, it is practical for surface 146 of sleeve 136 to be formed from of a plurality of curved segments 156 which are screwed to the sleeve 136 using fasteners 158 to form a flange 157 attached to the end 148 of the sleeve 136. These sleeve structures facilitate assembly of the expansion joint 122 as shown in Figure 12. Tube 124 it is prepared by first positioning sealing elements 132, anti-extrusion rings 134, cleaning elements 142 and support elements 144 in grooves 130 on the outer surface 126 of tube 124. The sealing elements, wipers and supports can be lubricated, and the end 151 the tube 124 is inserted coaxially into the sleeve 136 from its end 148. Insertion of the tube into the sleeve becomes possible by a chamfer 160 inside the sleeve 136 at the end 148. Chamfer 160 acts as a guide to guide the tube 124 and initiates the compression of the sealing elements 132, cleaning elements 142 and 144 support elements. The inner surface 140 of the sleeve 136 can also be lubricated to facilitate sliding movement between the tube and the sleeve. Note that the surface 146 on the sleeve 136 (see Figure 10) is not yet installed to allow the sleeve to pass along the raised groove surface 154 that defines the surface 150 of the tube 12.4. Since considerable force is required to insert the tube 124 into the sleeve 136 so that the sealing elements engage the inner smooth surface 140 of the sleeve, it is advantageous to attach protrusions 162 to the respective outer surfaces 126 and 138 of the tube and sleeve , and run threaded rods 164 between the projections. By tightening nuts 166 on the rods 164, it is possible to force the tube 124 into the sleeve 136 uniformly, so that this does not stiffen and damage the sealing elements, which are under considerable compression between the tube and the sleeve. Once the end 148 of the sleeve 136 is passed over the surface 150 in the tube 124 the segments 156 can be screwed to the end 148 of the sleeve 136 in order to form the flange 157 providing the surface 146 (see Figure 10). Threaded rods 164 can be removed and expansion joint assembly 122 is complete as shown in Figure 10.
    [053] Figure 13 shows the example of expansion joint 122 mounted on a pipe line. A first pipe element 168 of a portion of the pipe line is connected to end 152 of tube 124, and a second pipe element 170 is connected to end 153 of sleeve 136. In this example, connection of expansion joint 122 with the pipe elements 168 and 170 are effected by mechanical pipe couplings 28 (see also Figure 2) comprising individual segments 30 which are screwed together around the ends of the pipe elements and the expansion joints. Tube end 152 and sleeve end 153, as well as the ends of pipe elements 168 and 170 have circumferential grooves 172 that receive the keys projecting radially inward 32 that extend from the segments 30. Keys 32 of the respective segments 30 engage the grooves 172 in both pipe elements 168 and 170 and the expansion joint components (tube 124 and sleeve 136) and mechanically lock in an end-to-end relationship, with the key and groove interface providing positive mechanical engagement. Seals 34 extend circumferentially around each interface between the pipe elements and the expansion joint and are compressed by the segments against sealing surfaces on the pipe elements and the expansion joint to provide a fluid tight connection. Alternatively, the connection between the pipe elements 68 and 170 and the expansion joint 122 can be made by interacting flanges extending radially outwardly at the ends of the pipe elements and expansion joints, the flanges being screwed together. Welding is also an option for connection, but mechanical coupling methods (ie, segmented and flanged couplings) have the advantage of ease of installation and removal, which can be useful when building the pipe line and, later, for replacing expansion joints when they wear out.
    [054] The advantage of having sleeve 136 shorter than tube 124 is illustrated in Figure 13, as it allows the end 151 of tube 124 to extend to the downstream pipe element 170. Note that there is a preferred direction of flow through expansion joint 122, which is from tube end 152 to tube end 151. Tube 124 is designed with a hole 174 having a gradual inner cone from end 52 to end 151 to allow insertion into sleeve 136 and pipe element 170 at the same time avoiding interruptions in the flow, which can cause turbulence. This design reduces abrasive wear of tube 124 when suspensions are being transported with a high content of particles, such as tar sands, therefore oil or mining waste through the pipe network. Insertion of the pipe end 151 into the downstream pipe element 170 prevents suspension from flowing from contact with the smooth inner surface 140 of the sleeve 136, thereby protecting this surface from abrasion due to flow through the gasket. expansion.
    [055] Expansion joint operation 122 can be easily visualized using Figure 13. For example, an increase in ambient temperature causes the pipe elements along the pipe line to increase in length. As a result, the expansion joint 122 experiences a compressive force when the lengths of pipe connected at each end of the joint grow further. The compressive force is applied to the expansion joint 122 at the end 152 of the tube 124 and the end 153 of the sleeve 136. This causes the sleeve and the tube to move in axially opposite directions to each other, as a significant restriction in this movement is the friction between the sealing elements 132 (and other components fixed to the tube 124) and the inner surface 140 of the sleeve 136, which cannot resist the applied axial force. Likewise, as the ambient temperature decreases, the pipe line cools and contracts, placing a tensile force on the expansion joint 122. The pipe line shrinking axially pulls the tube and sleeve in opposite directions, and again a significant restriction against axial movement is merely friction at the interface between the sealing elements 132 (and other components attached to the tube 124) and the inner surface 140 of the sleeve 136, which is overcome to allow relative movement. In practical applications, for a steel pipe line, the linear expansion coefficient of steel results in a no inch length change for every 100 feet of pipe line for each 100 ° F change in temperature. Depending on the range of ambient temperature fluctuation and the lengths of pipe line between expansion joints, expansion joint 122 may have to accommodate up to about 40 inches of travel.
    [056] While it is possible to design expansion joints 122 for a wide range of axial displacement, it is sometimes found economical to manufacture expansion joints with the same range of axial displacement and to organize them in series when calculations predict that more displacement will be required for a particular installation that can be accommodated by a single expansion joint.
    [057] As shown in Figure 14, it is advantageous to employ an externally visible indicator / stop 194 in the expansion joint 122 to indicate the degree of coupling between the tube 124 and the sleeve 136. In this example indicator / stop 194 comprises a first protrusion 196 attached to the outer surface 126 of the tube 124, and a second protrusion 198 attached to the outer surface 138 of the sleeve 136. A rod 200 can be attached to any of the projections, in this example, protrusion 196 in the tube 124, and passed through a hole 202 on the other ledge 198 on the sleeve 136. The rod 200 can be calibrated, with a length scale, for example, and serves to measure the relative movement and position between the tube 124 and sleeve 136. Indicator / stop 194 can be used to initially position the sleeve in relation to the tube when expansion joint 122 is being installed in a pipe line so that there is sufficient travel length in both expansion and contraction They are not intended to accommodate the expected pipe line length excursions. To fulfill the stop function of the indicator / stop 194, stem 200 may have a projection 204 extending radially outwardly to engage the protrusion 198 and limit the relative movement between sleeve and tube. In this example, the projection is a washer screwed to the end of the rod 200, however, it is also contemplated that other forms of projection can be used, and be positioned in an adjustable way at any point along the rod 200 to define a stop point for movement between sleeve and tube. Multiple indicators / stops 194 can, of course, be used as stops to distribute the expansion or contraction load, and multiple projections can be used, for example, one on each side of the protrusion 198 to allow limits on both expansion and contraction of the joint to be made. Use of indicator / stop 194 is advantageous when several expansion joints 122 are used in series to force all expansion joints to operate to accommodate pipe line movement. It is conceivable that an expansion joint could have lower frictional forces between its tube and sleeve than other expansion joints in series. If it were not for the indicator / stop 194, this expansion joint could therefore have all the movement, which, for contraction of the pipe line, can result in disconnection between the pipe and the sleeve.
    权利要求:
    Claims (29)
    [1]
    1. Expansion joint (10) for connecting pipe elements, said expansion joint (10) characterized by the fact that it comprises: a tube (12) having an inner surface (40) defining an inner diameter, an outer surface ( 14) surrounding said interior surface (40) and first and second ends (16; 18) opposite each other; an inlet segment (106) having a smooth inner surface (40), an outlet end connected to said first end (16) of said tube (12), and an inlet end disposed opposed thereto, said end outlet having an inner diameter that is less than an inner diameter of said inlet end, said inner diameter of said outlet extermination being equal to said inner diameter of said tube (12), said inlet segment (106) being connected to said tube (12) by an externally mounted mechanical coupling; a sleeve (20) having opposing first and second ends (22; 24), said sleeve (20) being positioned surrounding at least a portion of said tube (12), said portion including said second end (18) of said tube (12), said sleeve (20) having a constant inner diameter over its longitudinal length, said inner diameter being greater than an outer diameter of said tube (12); a ring (26), separated from said sleeve (20) and removably attachable to said first end (22), said ring (26) surrounding said tube (12) and having an inner surface (40) facing said outer surface (14) of said tube (12), said ring (26) supporting said sleeve (20) in said tube (12) only at said first end (22) of said sleeve (20); at least one inward circumferential groove (36) positioned on the inner surface (40) of said ring (26); at least one support element (54) positioned within said at least one groove; an externally mounted coupling positioned circumferentially around a portion of both said ring (26) and said first end (22) of said sleeve (20), said coupling removably coupling said ring (26) to said sleeve (20 ); a seal mounted on said inner surface (40) of said ring (26) and hermetically attaching said outer surface (14) of said tube (12), said ring (26) and said sleeve (20) being slidably movable axially relative to said tube (12); a ring coupled to said ring (26) and surrounding said tube (12) and positioned radially and longitudinally between said ring (26) and said tube (12), said ring being positioned adjacent to a packaging material, the said packaging material being captured between said ring and a shoulder of said ring (26).
    [2]
    Expansion joint (10) according to claim 1, characterized in that said first end (16) of said tube (12) has an outwardly facing surface with a circumferential groove (36) in it .
    [3]
    Expansion joint (10), according to claim 1, characterized in that: said coupling has a plurality of arcuate segments (30) joined end to end surrounding said tube (12), each of said segments (30) having first and second keys (32) projecting radially inwards positioned in spaced relation; said ring (26) has an outwardly facing surface with a circumferential groove (36) in it; said sleeve (20) has an outwardly facing surface positioned at said first end (22) thereof with a circumferential groove (36) thereon, said first key (32) engaging said circumferential groove (36) in said ring (26), said second key (32) engaging said circumferential groove (36) in said sleeve (20).
    [4]
    Expansion joint (10) according to claim 1, characterized in that said sleeve (20) has an outwardly facing surface positioned on said second end (24) of the same with a circumferential groove (36 ) in the same.
    [5]
    Expansion joint (10) according to claim 1, characterized in that said seal comprises a sealing element positioned inside said at least one groove.
    [6]
    Expansion joint (10) according to claim 5, characterized in that said sealing element comprises an O-ring.
    [7]
    Expansion joint (10) according to claim 1, characterized by the fact that it also comprises an anti-extrusion ring (50) positioned inside said at least one groove.
    [8]
    Expansion joint (10) according to claim 7, characterized in that said anti-extrusion ring (50) is formed by an elastomer.
    [9]
    Expansion joint (10) according to claim 1, characterized in that said seal comprises: a plurality of inwardly circumferential grooves positioned on the inner surface (40) of said ring (26); a plurality of sealing elements, each positioned within a respective of said grooves.
    [10]
    10. Expansion joint (10) according to claim 9, characterized in that said sealing elements comprise O-rings.
    [11]
    11. Expansion joint (10) according to claim 9, characterized by the fact that it further comprises a plurality of anti-extrusion rings (50), each positioned within a respective of said grooves.
    [12]
    12. Expansion joint (10) according to claim 11, characterized in that said anti-extrusion rings (50) are formed by an elastomer.
    [13]
    13. Expansion joint (10), according to claim 1, characterized by the fact that it also comprises: at least one circumferential groove (36) facing inwardly positioned on the inner surface (40) of said ring (26); at least one cleaning element (52) positioned within said at least one groove.
    [14]
    14. Expansion joint (10), according to claim 1, characterized by the fact that: said shoulder (58) projects radially inwards from said inner surface (40) of said ring (26); said packaging material surrounds said tube (12) and is positioned adjacent to said shoulder (58) between said inner surface (40) of said ring (26) and said outer surface (14) of said tube (12) ;
    [15]
    15. Expansion joint (10) according to claim 14, characterized in that said ring is axially movable with respect to said ring (26) to compress said packaging material against said shoulder (58).
    [16]
    16. Expansion joint (10) according to claim 15, characterized in that it further comprises: a plurality of adjustable fasteners, each said fastener extending between said ring and said ring (26); and wherein the tightening of said fasteners moves said ring towards said ring (26) to compress said packaging material.
    [17]
    17. Expansion joint (10) according to claim 16, characterized by the fact that it also comprises a plurality of springs, each of said springs mounted on one of said fasteners and engaging said rim to press said rim in the direction of the said ring (26).
    [18]
    18. Expansion joint (10) according to claim 1, characterized by the fact that said entrance segment (106) has an interior surface (40) having a shape selected from the group consisting of a straight conical cone (111 ) and an s shape having an inflection point (112) marking the transition between a concave inner surface portion (114) and a convex inner surface portion (116).
    [19]
    19. Expansion joint (10) according to claim 1, characterized by the fact that it also comprises a lining (15) positioned inside said entry segment (106).
    [20]
    20. Expansion joint (10) according to claim 19, characterized in that said coating (15) comprises a flange (17) extending outwardly from one end thereof, said flange (17) being screwed to one end of said inlet segment (106) to removably couple said liner (15) to it.
    [21]
    21. Expansion joint (10) according to claim 19, characterized by the fact that said coating (15) has an interior surface (40) having a shape selected from the group consisting of a straight conical cone (111) and a shape of s having an inflection point (112) marking the transition between a concave inner surface portion (114) and a convex inner surface portion (116).
    [22]
    22. Expansion joint (10) according to claim 1, characterized in that said inlet segment (106) is separated from said first end of said tube and removably coupled to it, said inlet segment (106) having a first and a second ends arranged opposite each other.
    [23]
    23. Expansion joint (10) according to claim 22, characterized in that it further comprises a second coupling positioned between said first end (16) of said tube (12) and one of said ends of said inlet segment ( 106), said second coupling removably coupling said inlet segment (106) to said tube (12).
    [24]
    24. Expansion joint (10) according to claim 23, characterized in that: said second coupling has a plurality of arcuate segments (30) joined end to end surrounding said tube (12), each of said segments (30) having first and second keys (32) projecting radially inwards positioned in spaced relation; said first end (16) of said tube (12) has an outwardly facing surface with a circumferential groove (36) in it; said first end of said inlet segment (106) has an outwardly facing surface with a circumferential groove (36) in it, said first key (32) engaging said circumferential groove (36) in said tube (12) said second key (32) engaging said circumferential groove (36) in said entry segment (106).
    [25]
    25. Expansion joint (10), according to claim 1, characterized by the fact that it further comprises: a first projection (98) projecting outwards from said outer surface (14) of said tube (12); a second protrusion (100) projecting outwardly from an outer surface (14) of said ring (26); a rod (102) coupled to one of said projections (98; 100) and extending through an opening in another of said projections, said rod (102) guiding and being an indicator of relative movement between said tube (12) and said ring (26).
    [26]
    26. Expansion joint, according to claim 25, characterized by the fact that said rod (102) is coupled to said first projection (98).
    [27]
    27. Expansion joint (10), according to claim 25, characterized by the fact that said rod (102) comprises a projection extending radially to the outside of the same, said projection being coupled with said second projection to limit the movement relative between said tube (12) and said ring (26).
    [28]
    28. Expansion joint, according to claim 25, characterized by the fact that it also comprises an actuator positioned between said first and second projections (98; 100), said actuator for applying force to said projections (98; 100) and moving said ring (26) and said tube (12) relative to each other.
    [29]
    29. Expansion joint (10), according to claim 28, characterized by the fact that said actuator comprises a hydraulic actuator (105).
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    同族专利:
    公开号 | 公开日
    JP6208297B2|2017-10-04|
    EP2748507B1|2016-02-03|
    CA2787799A1|2013-02-22|
    CN106870863A|2017-06-20|
    US9631759B2|2017-04-25|
    CN103988009A|2014-08-13|
    TWI573949B|2017-03-11|
    CN103988009B|2019-11-26|
    CA2949588A1|2013-02-22|
    KR101938750B1|2019-04-10|
    AU2012299165A1|2014-01-16|
    WO2013028493A2|2013-02-28|
    KR20140048892A|2014-04-24|
    ES2567293T3|2016-04-21|
    MX2014002118A|2014-09-22|
    JP2016180512A|2016-10-13|
    TW201319441A|2013-05-16|
    JP2014527144A|2014-10-09|
    CN106870863B|2021-09-21|
    CA2787799C|2017-01-03|
    MX339540B|2016-05-30|
    BR112014004110A2|2017-02-21|
    JP5991787B2|2016-09-14|
    WO2013028493A3|2014-05-22|
    US20130049354A1|2013-02-28|
    EP2748507A2|2014-07-02|
    AU2012299165B2|2016-11-17|
    EP2748507A4|2014-12-31|
    CA2949588C|2019-01-22|
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    法律状态:
    2018-12-11| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2019-07-02| B06T| Formal requirements before examination [chapter 6.20 patent gazette]|
    2019-11-05| B06A| Notification to applicant to reply to the report for non-patentability or inadequacy of the application [chapter 6.1 patent gazette]|
    2020-03-03| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2020-03-17| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 17/08/2012, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    US201161525987P| true| 2011-08-22|2011-08-22|
    US61/525,987|2011-08-22|
    US201161540676P| true| 2011-09-29|2011-09-29|
    US61/540,676|2011-09-29|
    US201261588429P| true| 2012-01-19|2012-01-19|
    US61/588,429|2012-01-19|
    PCT/US2012/051294|WO2013028493A2|2011-08-22|2012-08-17|Expansion joint|
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