Curved pipe pressure balance type expansion joint for complex pipeline connection
The three-way assembly and hinge structure design of the welded elbow and special-shaped pipe solves the damage problem of the traditional curved pipe pressure balancing expansion joint under the impact of high-flow medium and multi-plane force, achieves higher stability and anti-torsion ability, and reduces vibration and pressure drop.
Patent Information
- Application Number
- CN202510949617.6
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2025-07-10
- Publication Date
- 2025-09-19
AI Technical Summary
Traditional curved pipe pressure balancing expansion joints are easily damaged under the impact of high-velocity media, have poor torsional resistance, and are prone to torsional deformation and failure of the bellows under the action of multi-plane forces.
The three-way assembly welded with bent and shaped pipes is combined with the hinge structure of the load-bearing assembly, including the first main hinge plate, secondary hinge plate, annular anti-torsion ring, etc. It is designed into a hinge structure to absorb internal pressure thrust, limit torsional force and torque, enhance stability, and absorb vibration through damping shock absorbers.
It improves the stability of the expansion joint, reduces vibration, prevents erosion of the balancing end, extends service life, enhances anti-torsion ability, and reduces pressure drop.
Smart Images
Figure CN120667599A_ABST
Abstract
Description
Technical Field
[0001] The present invention relates to the technical field of pipe fittings, and in particular to a curved pipe pressure-balanced expansion joint used for connecting complex pipelines. Background Art
[0002] Expansion joints, as flexible compensating components capable of free expansion and contraction, are essential accessories commonly used in piping systems. Composed of a bellows as a flexible element and supplemented by structural components, they are used to address high stresses in piping systems caused by thermal expansion of pipes (and equipment), equipment vibration, and other factors, reducing the forces acting on equipment and mounting brackets.
[0003] For the pipelines of gas turbines, steam turbines and other equipment, the service conditions of expansion joints are relatively harsh, with high temperatures, large flow rates, and limited load-bearing capacity. Usually, high product flexibility is required. In such pipelines, curved pipe pressure-balanced expansion joints are generally used, which can compensate for axial and lateral displacements at the same time and withstand internal pressure thrust.
[0004] However, due to space and load constraints, most pipelines usually have many turns and a complex layout. It is also difficult to divide pipe sections and set supports according to traditional pipeline layout principles. The expansion joint is very likely to be affected by multiple plane forces, causing the expansion joint to twist. Since the load-bearing components of traditional curved pipe pressure-balanced expansion joints use a pull rod structure, their stability is poor. Especially in the case of vibration, heavy intermediate pipes, and high flexibility of the expansion joint, unexpected damage is very likely to occur. The tee of the traditional curved pipe pressure-balanced expansion joint is welded with straight pipes and has a working end and a balancing end. When the fluid flows through the expansion joint, the pressure drop is large. Under high flow rate conditions, the high flow rate medium directly impacts the balancing end of the expansion joint, which can easily cause excessive vibration or direct damage to the balancing end. The anti-torsion ability is also poor. Under the action of multi-plane forces, it is very easy to cause the bellows to twist and deform and fail. Summary of the Invention
[0005] In view of the above-mentioned shortcomings and deficiencies of the prior art, the present invention provides a curved pipe pressure-balanced expansion joint for complex pipeline connections, which solves the technical problems that high-flow medium directly impacts the balanced end of the expansion joint, easily causing excessive vibration or direct damage to the balanced end; and the bellows has poor anti-torsion ability, which easily leads to torsional deformation and failure under the action of multi-plane forces.
[0006] In order to achieve the above objectives, the main technical solutions adopted by the present invention include:
[0007] An embodiment of the present invention provides a curved pipe pressure-balanced expansion joint for complex pipeline connections, comprising a working end assembly, a tee assembly, and a balancing end assembly;
[0008] The working end assembly is a horizontal cylindrical structure, and the working end assembly has a first end connected to the pipeline and a second end opposite to the first end;
[0009] The three-way assembly includes an elbow and a special-shaped tube, the elbow having a third end connected to the second end of the working end assembly, and the third end is coaxially arranged with the second end, the elbow further having a fourth end bent upward toward one side of the working end assembly relative to the third end, the axis of the fourth end being perpendicular to the axis of the third end, a through hole being opened on the tension side of the elbow, the special-shaped tube having a fifth end opened by a curved tangent and a sixth end opened by a flat cut, the special-shaped tube being coaxially arranged with the third end of the elbow, and the fifth end of the special-shaped tube being welded to the tension side of the elbow to cover the through hole, the elbow being connected to the special-shaped tube through the through hole;
[0010] The balancing end assembly is a horizontal cylindrical structure, and has a seventh end connected to the sixth end of the special-shaped tube and an eighth end opposite to the seventh end and blocked;
[0011] It also includes a load-bearing component, which includes a first main hinge plate connected to the first end of the working end component, a second main hinge plate connected to the eighth end of the balancing end component, and a secondary hinge plate located between the first main hinge plate and the second main hinge plate and hinged to the two; the load-bearing component also includes a first annular anti-torsion ring mounted on the outer wall of the third end of the bent pipe and a second annular anti-torsion ring mounted on the outer wall of the sixth end of the special-shaped pipe.
[0012] Optionally, the working end assembly includes a first connecting pipe, an intermediate pipe, a first bellows and a second bellows;
[0013] One end of the first pipe is connected to the first damping shock absorber via a clamp, the other end of the first pipe is connected to one end of the first bellows, the other end of the first bellows is connected to one end of the intermediate pipe, the other end of the intermediate pipe is connected to one end of the second bellows, and the other end of the second bellows is connected to the tee assembly;
[0014] A support plate is fixedly mounted on the outer wall of the first pipe, and a side wall of the support plate is connected to one end of the first main hinge plate.
[0015] Optionally, a limiting structural member is provided on the outer wall of the intermediate tube;
[0016] The limiting structure includes two limiting plates distributed along the axial direction of the intermediate tube, and the two limiting plates are symmetrically arranged on both sides of the auxiliary hinge plate; the limiting structure also includes two limiters respectively located on the inner sides of the two limiting plates.
[0017] Optionally, two auxiliary hinge plate support plates are further provided on the outer wall of the intermediate tube, and the two auxiliary hinge plate support plates are located between the two limiting plates and are perpendicular to each other. A first rectangular hole for passing the auxiliary hinge plate is provided on the auxiliary hinge plate support plates, and the first rectangular hole is opened along the radial direction of the intermediate tube so that the auxiliary hinge plate and the two auxiliary hinge plate support plates are clearance-fitted.
[0018] Optionally, the third end of the bent pipe is connected to the second corrugated pipe through a second pipe, and the fourth end of the bent pipe is provided with a third pipe, and the third pipe is connected to the damping shock absorber 2 through a clamp.
[0019] Optionally, a first annular anti-torsion ring is sleeved on the outer wall of the second connecting pipe, and a second annular anti-torsion ring is sleeved on the outer wall of the sixth end of the special-shaped tube, and the first annular anti-torsion ring and the second annular anti-torsion ring are both provided with a second rectangular hole for passing the second main hinge plate, and the second rectangular hole is opened along the radial direction of the second connecting pipe so that the second main hinge plate is loosely fitted with the first annular anti-torsion ring and the second annular anti-torsion ring respectively.
[0020] Optionally, the balancing end assembly includes a balancing bellows, one end of the balancing bellows is connected to the special-shaped tube, the other end of the balancing bellows is connected to a fourth connecting pipe, the end of the fourth connecting pipe serves as the eighth end, and a sealing plate is provided at the end of the fourth connecting pipe.
[0021] Optionally, it further includes a first displacement sensor and a second displacement sensor, wherein the first displacement sensor is located above the outer wall of the first bellows, and both ends of the first displacement sensor are connected to the support plate and the secondary hinge plate support plate respectively through a first mounting bracket;
[0022] The second displacement sensor is located above the outer wall of the balancing bellows, and both ends of the second displacement sensor are connected to the special-shaped tube and the blocking plate respectively through second mounting brackets.
[0023] Optionally, a first flow guide tube is provided on the inner wall of the first corrugated tube, and a second flow guide tube is provided on the inner wall of the second corrugated tube, and both ends of the first flow guide tube respectively extend into the first connecting pipe and the intermediate pipe and are welded with the first connecting pipe and the intermediate pipe with a gap fit, and both ends of the second flow guide tube respectively extend into the intermediate pipe and the second connecting pipe and are welded with the gap fit;
[0024] The first flow guide tube and the second flow guide tube have the same structure, and the first flow guide tube includes a first horizontal section, a first inclined section, a second inclined section and a second horizontal section which are formed in sequence;
[0025] One end of the first inclined section away from the first horizontal section is inclined inwardly and connected to one end of the second inclined section, and the other end of the second inclined section is inclined inwardly and connected to the second horizontal section.
[0026] Optionally, a guide and limiting tube is provided on the inner wall of the balancing end assembly, and both ends of the guide and limiting tube extend to the special-shaped tube and the connecting tube respectively to fit the gap and be welded.
[0027] The beneficial effects of the present invention are as follows: the present invention provides a curved pipe pressure-balanced expansion joint for complex pipeline connections, wherein the tee assembly is welded by an elbow and a special-shaped pipe, and is usually used in situations where the pressure in the pipeline is relatively high, and a plurality of through holes are opened on the intersection surface of the elbow and the special-shaped pipe. The arrangement of the through holes enables the balancing end assembly and the working end assembly of the pressure-balanced expansion joint to be connected to maintain the same pressure. The structure of the through holes, on the one hand, reduces the pressure drop of the overall pipeline system, and on the other hand, prevents the erosion of the balancing end by the high-flow medium. In addition, the load-bearing component adopts the first main hinge plate, the secondary hinge plate, the second main hinge plate, the secondary hinge plate support plate and the first annular anti-torsion ring and the second annular anti-torsion ring for linkage design, that is, the load-bearing component adopts a hinge structure to absorb the internal pressure thrust generated by the expansion joint while improving the stability of the expansion joint and reducing the vibration of the expansion joint; the first annular anti-torsion ring and the second annular anti-torsion ring are added between the pipe 1 and the balancing end component, and the first annular anti-torsion ring and the second annular anti-torsion ring are added between the pipe 1 and the balancing end component together with the first main hinge plate, the second main hinge plate, the secondary hinge plate and the secondary hinge plate support plate The function limits the direction of displacement absorption of the curved pipe pressure balanced expansion joint, can absorb the torsional force and torque acting on the curved pipe pressure balanced expansion joint, and protect the first bellows, the second bellows and the balancing bellows. At the same time, the inner walls of the first annular anti-torsion ring and the second annular anti-torsion ring both adopt a circular ring structure. The first annular anti-torsion ring and the second annular anti-torsion ring are respectively welded and fixed to the pipe No. 2 and the special-shaped pipe of the tee assembly, which increases the rigidity of the tee assembly and prevents the first bellows, the second bellows and the balancing bellows from becoming instable due to deformation of the pipe No. 3 and the special-shaped pipe under high stress. BRIEF DESCRIPTION OF THE DRAWINGS
[0028] Figure 1 This is a schematic structural diagram of a curved pipe pressure-balanced expansion joint for complex pipeline connections according to the present invention;
[0029] Figure 2 for Figure 1 A schematic diagram of the structure of the working end component;
[0030] Figure 3 for Figure 1 Schematic diagram of the structure of the three-way component;
[0031] Figure 4 for Figure 1 Schematic diagram of the structure of the balanced end component;
[0032] Figure 5 for Figure 1 Partial longitudinal cross-sectional view of the middle load-bearing component;
[0033] Figure 6 for Figure 2 A partial transverse cross-sectional view of one side (limiting structure not shown);
[0034] Figure 7 for Figure 4 A partial transverse cross-sectional view of one side of the middle;
[0035] Figure 8 for Figure 1 Schematic diagram of the longitudinal cross-section of the guide tube portion of the inner wall of the first bellows and the second bellows.
[0036] Description of Reference Numerals
[0037] 1. Working end assembly; 101. First end; 102. Second end; 11. Pipe connection 1; 12. Intermediate pipe; 13. First bellows; 14. Second bellows; 2. Tee assembly; 201. Third end; 202. Fourth end; 203. Fifth end; 204. Sixth end; 21. Elbow; 22. Special-shaped pipe; 23. Pipe connection 2; 24. Pipe connection 3; 25. Damping shock absorber 2; 3. Balancing end assembly; 301. Seventh end; 302. Eighth end; 31. Balancing bellows; 32. Pipe connection 4; 33. Blocking plate; 4. Through hole; 5. Load-bearing assembly; 51. First main hinge plate; 52. Second main hinge plate; 53. Secondary Hinge plate; 54, auxiliary hinge plate support plate; 55, first rectangular hole; 56, pin; 57, gasket; 6, damping shock absorber 1; 7, support plate; 8, limiting structure; 81, limiting plate; 82, limiter; 9, first annular anti-torsion ring; 10, second annular anti-torsion ring; 20, second rectangular hole; 30, first displacement sensor; 40, second displacement sensor; 50, first mounting bracket; 60, second mounting bracket; 70, guide pipe; 701, first horizontal section; 702, first inclined section; 703, second inclined section; 704, second horizontal section; 80, guide limiting pipe; 90, drain pipe; 100, temperature sensor. DETAILED DESCRIPTION
[0038] In order to better explain the present invention and facilitate understanding, the present invention is described in detail below through specific implementation methods in conjunction with the accompanying drawings.
[0039] See also Figures 1 to 8As shown, an embodiment of the present invention proposes a curved pipe pressure-balanced expansion joint for complex pipeline connections, comprising a working end assembly 1, a tee assembly 2, and a balancing end assembly 3. The working end assembly 1 is a horizontal cylindrical structural member, and the working end assembly 1 has a first end 101 connected to the pipeline and a second end 102 opposite to the first end 101. The tee assembly 2 includes a bend 21 and a special-shaped pipe 22, the bend 21 has a third end 201 connected to the second end 102 of the working end assembly 1, and the third end 201 is coaxially arranged with the second end 102. The bend 21 also has a fourth end 202 that is bent upward toward one side of the working end assembly 1 relative to the third end 201, and the axis of the fourth end 202 is perpendicular to the axis of the third end 201. Specifically, the centers of the bend 21 and the special-shaped pipe 22 in the horizontal direction are on the same axis and the two pieces are welded and fixed.
[0040] Specifically, the special-shaped tube 22 is an irregular cylindrical tube that rides on the back of the curved tube 21 and fits perfectly with the back of the curved tube 21. The joining line between the two is a closed spatial curve. The actual position of the spatial curve is determined by the size specifications and riding position of the curved tube 21 and the special-shaped tube 22.
[0041] In this embodiment, a through hole 4 is formed on the tension side of the elbow 21. The special-shaped tube 22 has a fifth end 203 with a curved tangential opening and a sixth end 204 with a flat cut opening. The special-shaped tube 22 is coaxially arranged with the third end 201 of the elbow 21. The fifth end 203 of the special-shaped tube 22 is welded to the tension side of the elbow 21 to cover the through hole 4. The elbow 21 is connected to the special-shaped tube 22 via the through hole 4. The balancing end assembly 3 is a horizontal cylindrical structural member and has a seventh end 301 connected to the sixth end 204 of the special-shaped tube 22 and an eighth end 302 opposite to the seventh end 301 and blocked.
[0042] The load-bearing assembly 5 also includes a first main hinge plate 51 connected to the first end 101 of the working end assembly 1, a second main hinge plate 52 connected to the eighth end 302 of the balancing end assembly 3, and a secondary hinge plate 53 located between the first and second main hinge plates 51, 52 and hingedly connected to the two plates via a pin 56. The load-bearing assembly 5 also includes a first annular anti-torsion ring 9 sleeved on the outer wall of the third end 201 of the curved tube 21, and a second annular anti-torsion ring 10 sleeved on the outer wall of the sixth end 204 of the special-shaped tube 22. In this embodiment, the pin 56 cooperates with a wear-resistant washer 57 to absorb displacement and torque. Wear-resistant washers 57 are provided between the first and second main hinge plates 51, 52, and the secondary hinge plate 53, effectively preventing wear and jamming between the first and second main hinge plates 51, 52, and the secondary hinge plate under torsional forces and moments or multi-directional displacement.
[0043] In this embodiment, a curved pipe pressure-balanced expansion joint for complex pipeline connections is provided. Multiple through-holes 4 are provided on the intersecting surface of the curved pipe 21 and the special-shaped pipe 22. The provision of through-holes 4 allows the balanced end assembly and the working end assembly 1 of the pressure-balanced expansion joint to intersect and maintain the same pressure. The structure of through-holes 4 reduces the pressure drop of the overall pipeline system and prevents erosion of the balanced end by high-velocity media. Furthermore, the load-bearing assembly 5 employs a first main hinge plate 51, a secondary hinge plate 53, a second main hinge plate 52, and a secondary hinge plate support plate 54 in conjunction with the first annular anti-torsion ring 9 and the second annular anti-torsion ring 10. This means that the hinge structure of the load-bearing assembly 5 can absorb the internal pressure thrust generated by the expansion joint while improving the stability of the expansion joint and reducing its vibration.
[0044] Furthermore, the working end assembly 1 includes a pipe 11, an intermediate pipe 12, a first bellows 13, and a second bellows 14. One end of the pipe 11 is connected to a damping vibration absorber 6 via a clamp, so that after the pipe 11 is connected to the pipeline, vibration is reduced by the damping vibration absorber 6. The other end of the pipe 11 is connected to one end of the first bellows 13, the other end of the first bellows 13 is connected to one end of the intermediate pipe 12, the other end of the intermediate pipe 12 is connected to one end of the second bellows 14, and the other end of the second bellows 14 is connected to the tee assembly 2. A support plate 7 is fixedly mounted on the outer wall of the pipe 11, and a side wall of the support plate 7 is connected to one end of the first main hinge plate 51. The damping vibration absorber 6 can absorb high-frequency vibrations generated by the impact of high-velocity media, reduce damage to the expansion joint caused by vibration, and extend the service life of the expansion joint.
[0045] Furthermore, a limiting structure 8 is provided on the outer wall of the intermediate tube 12. The limiting structure 8 includes two limiting plates 81 distributed along the axial direction of the intermediate tube 12. The two limiting plates 81 are symmetrically spaced apart and arranged on either side of the secondary hinge plate 53. The limiting structure 8 also includes two limiters 82 located on the inner sides of the two limiting plates 81.
[0046] It should be noted here that a limiting structural member 8 is additionally provided on the intermediate tube 12 and the auxiliary hinge plate support plate 54. The two limiting plates 81 can effectively limit the rotation angle of the first main hinge plate 52 and the second main hinge plate 52. At the same time, a damping limiter 82 is provided on the limiting member. When the displacement exceeds the limit and touches the damping limiter 82, the impact is reduced and an alarm is sounded to prevent damage to the expansion joint due to unexpected excessive displacement.
[0047] Furthermore, two auxiliary hinge plate support plates 54 are provided on the outer wall of the intermediate tube 12. The two auxiliary hinge plate support plates 54 are located between the two limit plates 81 and are perpendicular to the limit plates 81. A first rectangular hole 55 for passing the auxiliary hinge plate 53 is provided on the auxiliary hinge plate support plates 54, and the first rectangular hole 55 is opened along the radial direction of the intermediate tube 12 so that the auxiliary hinge plate 53 and the two auxiliary hinge plate support plates 54 are clearance-fitted.
[0048] Furthermore, the third end 201 of the elbow 21 is connected to the second bellows 14 via a second pipe 23. The fourth end 202 of the elbow 21 is provided with a third pipe 24, which is connected to a second damping vibration absorber 25 via a clamp. It should be noted that, in combination with the aforementioned connection of the first pipe 11 to the first damping vibration absorber 6 via a clamp, the clamp-type damping vibration absorber fixedly connected to the outer walls of the first pipe 11 and the third pipe 24 (i.e., each connected to the corresponding damper via a clamp) can absorb high-frequency vibrations generated by the impact of high-velocity media, reduce vibration damage to the expansion joint, and extend the service life of the expansion joint.
[0049] Furthermore, a first annular anti-torsion ring 9 is sleeved on the outer wall of the second pipe 23, and a second annular anti-torsion ring 10 is sleeved on the outer wall of the sixth end 204 of the special-shaped pipe 22. The first annular anti-torsion ring 9 and the second annular anti-torsion ring 10 are both provided with a second rectangular hole 20 for passing the second main hinge plate 52, and the second rectangular hole 20 is provided along the radial direction of the second pipe 23, so that the second main hinge plate 52 is loosely fitted with the first annular anti-torsion ring 9 and the second annular anti-torsion ring 10. It should be noted that the outer sides of the first annular anti-torsion ring 9 and the second annular anti-torsion ring 10 are provided with lugs and second rectangular holes 20, and the first annular anti-torsion ring 9 and the second annular anti-torsion ring 10 are loosely fitted with the second main hinge plate 52. At the same time, stress relief holes are provided at the four corners of the second rectangular hole 20 to prevent stress concentration.
[0050] In this embodiment, a torsion-resistant assembly formed by a first annular torsion-resistant ring 9 and a second annular torsion-resistant ring 10 is added between the connecting pipe 11 and the balancing end assembly 3. The torsion-resistant assembly, together with the first main hinge plate 51, the second main hinge plate 52, the auxiliary hinge plate 53, and the auxiliary hinge plate support plate 54, limits the direction in which the curved pipe pressure balanced expansion joint absorbs displacement, can absorb the torsional force and torque acting on the curved pipe pressure balanced expansion joint, and protect the first bellows 13, the second bellows 14 and the balancing bellows 31. At the same time, the inner wall of the torsion-resistant assembly adopts a circular ring structure and is welded and fixed to the tee assembly 2, which increases the rigidity of the tee assembly 2 and prevents the balancing bellows 31 from becoming instable due to deformation of the connecting pipe 3 24 and the special-shaped pipe 22 under high stress.
[0051] Furthermore, the balancing end assembly 3 includes a balancing bellows 31, one end of which is connected to the special-shaped tube 22. The other end of the balancing bellows 31 is connected to a fourth pipe 32, the end of which serves as an eighth end 302. A sealing plate 33 is provided at the end of the fourth pipe 32. The drain pipe 90, on the one hand, removes condensate generated on the inner wall of the balancing end assembly 3 during operation of the curved pipe pressure-balancing expansion joint. On the other hand, it can more thoroughly remove water from the balancing cavity after the hydraulic pressure test of the curved pipe pressure-balancing expansion joint and dry the balancing end cavity, which helps to delay rusting in the balancing cavity of pipelines that require high cleanliness.
[0052] It should also be noted that the second main hinge plate 52 is directly welded to the sealing plate 33, which reduces the overall weight of the curved pipe pressure balanced expansion joint while making the curved pipe pressure balanced expansion joint structure more compact. When the curved pipe pressure balanced expansion joint is working, the internal pressure thrust acts on the working end component 1 and the balancing end component 2 at the same time, and the two are in opposite directions. The load-bearing component 5 bears the internal pressure thrust, and the equipment as a whole is like a "rigid body". The internal pressure will no longer generate internal pressure thrust on the equipment pipe mouth or fixed bracket, and because the first bellows 13, the second bellows 14 and the balancing bellows 31 have the same average diameter, no matter how the internal pressure changes, it is always in a balanced state; the fourth end 202 of the connecting pipe 11 and the bend pipe 21 are respectively connected to the two ends of the pipeline, and the deformation of the working end component 1 absorbs the axial and radial displacement of the pipeline caused by thermal expansion and contraction, installation deviation, vibration, etc. The axial displacement from the pipeline or equipment compresses (or stretches) the working end assembly, which is transmitted to the balancing end assembly 3 through the load-bearing assembly 5, causing the balancing end assembly 3 to stretch (or compress). The thermal displacement reaction directions of the two are the same. The force borne by the equipment pipe mouth or fixed bracket is the sum of the stiffness forces of the working end assembly 1 and the balancing end assembly 3. Since the load-bearing assembly 5 does not transmit bending moment, the balancing end assembly 3 is not affected by the force of lateral displacement; the torsional force and torque transmitted through the pipe 11 and the pipe 3 24 are absorbed by the first annular anti-torsion ring 9 and the second annular anti-torsion ring 10 and the first main hinge plate 51, the second main hinge plate 52, the secondary hinge plate 53, and the secondary hinge plate support plate 54.
[0053] Furthermore, the device further includes a first displacement sensor 30 and a second displacement sensor 40. The first displacement sensor 30 is located above the outer wall of the first bellows 13, and its two ends are connected to the support plate 7 and the secondary hinge plate support plate 54 via a first mounting bracket 50. The second displacement sensor 40 is located above the outer wall of the balancing bellows 31, and its two ends are connected to the special-shaped pipe 22 and the blocking plate 33 via a second mounting bracket 60. In this embodiment, the first displacement sensor 30 and the second displacement sensor 40 form a displacement sensor assembly. The first displacement sensor 30 can monitor the axial and lateral displacements of the first bellows in real time, while the second displacement sensor 40 can monitor the axial and lateral displacements of the balancing bellows in real time, thereby determining the axial and lateral displacements absorbed by the entire curved pipe pressure-balanced expansion joint. The monitored data is transmitted to a monitoring center via a data acquisition and transmission module for display and storage. When the displacement of the curved pipe pressure-balanced expansion joint exceeds a predetermined value, an alarm signal is issued, enabling remote monitoring of the curved pipe pressure-balanced expansion joint's operating status and remaining life assessment. The curved-pipe pressure-balanced expansion joint also includes a temperature and pressure sensor assembly, comprising a temperature sensor 100 and a pressure sensor, capable of real-time monitoring of the expansion joint's temperature and pressure. The data monitored by the first displacement sensor 30, the second displacement sensor 40, and the temperature and pressure sensor assembly are combined to integrate the actual service status of the curved-pipe pressure-balanced expansion joint under different operating conditions. Two first displacement sensors 30 are arranged at the 0° and 270° positions of the first bellows 13 and connected to the support plate and the secondary hinge plate support plate 54. There is one second displacement sensor 40, one arranged at the 270° position of the balancing bellows 31 and connected to the sealing plate 33 and the second annular anti-torsion ring 10. Based on the displacement change principle of the curved-pipe pressure-balanced expansion joint (hereinafter referred to as the expansion joint), combined with proprietary displacement synthesis algorithm technology (this technology is prior art and will not be elaborated on here), the axial and lateral displacement absorbed by the expansion joint are monitored in real time. The monitored data is transmitted to a monitoring center via a data acquisition and transmission module for display and storage. An alarm signal is issued if the displacement exceeds a predetermined value, enabling remote monitoring of the expansion joint's service status and remaining life assessment. Specifically, the temperature sensor 100 and the pressure sensor are inserted from the outer wall of the intermediate tube 12 into the inner cavity of the expansion joint to monitor the temperature and pressure of the expansion joint in real time.
[0054] The data monitored by the first displacement sensor 30 , the second displacement sensor 40 , the temperature sensor 100 , and the pressure sensor can be combined to integrate the actual service status of the expansion joint under different working conditions.
[0055] In this embodiment, the second main hinge plate 52 is directly welded to the blocking plate 33, which reduces the weight of the expansion joint and makes the expansion joint structure more compact.
[0056] Furthermore, a first flow guide 70 is provided on the inner wall of the first bellows 13, and a second flow guide 70 is provided on the inner wall of the second bellows 14. The ends of the first flow guide 70 extend into the first pipe 11 and the intermediate pipe 12, respectively, and are welded with a gap fit between the first pipe 11 and the intermediate pipe 12. The ends of the second flow guide 70 extend into the intermediate pipe 12 and the second pipe 23, respectively, and are welded with a gap fit between the intermediate pipe 12 and the second pipe 23. The first and second flow guide 70 and pipes have the same structure, comprising a first horizontal section 701, a first inclined section 702, a second inclined section 703, and a second horizontal section 704, which are formed in sequence. The end of the first inclined section 702, facing away from the first horizontal section 701, is inclined inward and connected to one end of the second inclined section 703. The other end of the second inclined section 703 is also inclined inward and connected to the second horizontal section 704. In this embodiment, the first horizontal section 701 is gap welded to the first pipe 11, and the second horizontal section 704 is gap welded to the intermediate pipe 12.
[0057] In this embodiment, the first flow guide tube 70 adopts a small-angle flaring and a multi-stage buffer streamlined reducing and varying diameter structure to reduce the instantaneous impact force of the high-velocity medium on the flow guide tube while reducing fluid noise and vibration. At the same time, the inner wall is composited with a wear-resistant coating to increase the erosion resistance of the first flow guide tube 70. The first horizontal section 701 of the flared end of the first flow guide tube 70 forms a surface contact with the pipe 1 11 and the intermediate pipe 12 (the pipe 2 23 and the intermediate pipe 12). In addition to increasing the strength of the girth weld of the first flow guide tube 70, it can also provide a certain degree of protection for the girth weld of the bellows under vibration conditions. The first guide tube 70 on the inner wall of the first bellows 13 is clearance-matched with the inner walls of the first bellows 13 and the intermediate tube 12, and the gap does not affect the movement of the expansion joint. The first guide tube 70 on the inner wall of the second bellows 14 is coaxially gap-welded with the inner wall of the intermediate tube 12 and forms surface contact with the intermediate tube 12. The first guide tube 70 on the inner wall of the second bellows 14 is clearance-matched with the second bellows 14 and the tee assembly 2, and the gap does not affect the movement of the curved pipe pressure-balanced expansion joint. The flared end of the first guide tube 70 forms surface contact with the connecting pipe and the intermediate tube 12. In addition to increasing the strength of the girth weld of the first guide tube 70, it can also protect the girth weld of the bellows to a certain extent under vibration conditions, avoid the impact of high-pressure water flow, and improve the service life of the first bellows 13 and the second bellows 14.
[0058] Furthermore, a guide and stop tube 80 is provided on the inner wall of the balancing end assembly 3. The ends of the guide and stop tube 80 extend to the shaped tube 22 and the pipe 4 32, respectively, to provide a clearance fit and are welded thereto. The ends of the guide and stop tube 80 feature a flared structure. One end of the guide and stop tube 80 is welded to the tee assembly 2, while the other end of the guide and stop tube 80 is coated with a wear-resistant composite coating and secured to the inner wall of the pipe 4 32. High-temperature resistant grease is sprayed onto the exterior of the composite wear-resistant coating to reduce friction between the coating and the inner wall of the pipe 4 32. During operation of the curved pipe pressure-balanced expansion joint, the guide and stop tube 80 limits the deflection of the pipe 4 32, thereby improving the stability of the curved pipe pressure-balanced working end.
[0059] The existing layout of complex piping systems is generally divided into simple-shaped independent expansion joint pipe sections (such as straight pipe sections, L-shaped pipe sections, Z-shaped pipe sections, etc.) through fixed brackets, and then compensation design is carried out. Due to the poor ability of bellows to absorb torsion, when setting up fixed pipe racks and arranging expansion joints, it is necessary to avoid more than two planes composed of independent pipe sections to prevent torsional loads from acting on the expansion joints and causing damage to the bellows.
[0060] For equipment and equipment with strict thrust restrictions, curved pipe pressure-balanced expansion joints are often used due to the initial displacement of the equipment and the thermal and vibration displacement of the piping system. They can absorb both axial and lateral displacements while also balancing the thrust generated by internal pressure on the fulcrum. When arranging the expansion joint, one end of the expansion joint is generally placed close to a fixed bracket or guide bracket, and the other end is placed close to the guide bracket to ensure that the expansion joint's displacement is within expectations.
[0061] In comparison, in this embodiment, when the expansion joint is working, the internal pressure thrust acts on the working end component 1 and the balancing end component 3 at the same time in opposite directions. The load-bearing component 5 bears the internal pressure thrust, and the equipment as a whole is like a "rigid body". The internal pressure will no longer generate internal pressure thrust on the equipment pipe mouth or fixed bracket, and since the average diameters of the working bellows and the balancing bellows are the same, they are always in a balanced state regardless of how the internal pressure changes. The first end of the connecting pipe 11 and the fourth end 202 of the elbow 21 are respectively connected to the two ends of the pipeline. The deformation of the working end component 1 absorbs the axial and radial displacements of the pipeline caused by thermal expansion and contraction, installation deviation, vibration, etc., resulting in the axial displacement of the pipeline or equipment, causing the working end component 1 to be compressed (or stretched), and transmitted to the balancing end component 3 through the load-bearing component 5, causing the balancing end component 3 to be stretched (or compressed). The directions of the thermal displacement reaction forces of the two are the same. The force borne by the equipment pipe mouth or fixed bracket is the sum of the stiffness forces of the working end component 1 and the balancing end component 3. Since the load-bearing component 5 does not transmit bending moment, the balancing end component 3 is not subject to the force of lateral displacement; the torsional force and torque transmitted through the connecting pipe 11 and the elbow 21 are absorbed by the first annular anti-torsion ring 9, the second annular anti-torsion ring 10 and the first main hinge plate 51, the second main hinge plate 52, the secondary hinge plate 53, and the secondary hinge plate support plate 54. When the displacement from the pipeline or equipment exceeds the predetermined maximum value, the hinge plate rotates to trigger the limiter 82 on the limiting structure, slowing down the impact until the rotation stops and an alarm is sounded; the dampers on the pipe 11 and pipe 3 24 can effectively absorb the high-frequency and low-amplitude vibrations from the pipeline or equipment, reduce the damage to the expansion joint caused by vibration, and extend the service life of the expansion joint.
[0062] In the description of the present invention, it should be understood that the terms "first" and "second" are used for descriptive purposes only and should not be understood to indicate or imply relative importance or implicitly specify the number of the technical features indicated. Therefore, a feature specified as "first" or "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, "plurality" means two or more, unless otherwise specifically defined.
[0063] In the present invention, unless otherwise expressly specified or limited, the terms "mounted," "connected," "connect," "fixed," etc. should be understood broadly. For example, they may refer to fixed connection, detachable connection, or integration; mechanical connection or electrical connection; direct connection or indirect connection through an intermediate medium; and internal communication between two components or interaction between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on specific circumstances.
[0064] In the description of this specification, the terms "one embodiment", "some embodiments", "embodiments", "examples", "specific examples" or "some examples" refer to the specific features, structures, materials or characteristics described in conjunction with the embodiment or example and included in at least one embodiment or example of the present invention. In this specification, the schematic expressions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art may combine and combine different embodiments or examples described in this specification and features of different embodiments or examples, unless they are mutually inconsistent.
[0065] Although the embodiments of the present invention have been shown and described above, it will be understood that the above embodiments are illustrative and are not to be construed as limitations on the present invention. A person skilled in the art may alter, modify, replace and modify the above embodiments within the scope of the present invention.
Claims
1. A curved pipe pressure-balanced expansion joint for complex pipeline connections, characterized by: It comprises a working end assembly (1), a three-way assembly (2) and a balancing end assembly (3); The working end assembly (1) is a horizontal cylindrical structure, and the working end assembly (1) has a first end (101) connected to the pipeline and a second end (102) opposite to the first end (101); The three-way assembly (2) comprises a bend (21) and a special-shaped tube (22), wherein the bend (21) has a third end (201) connected to the second end (102) of the working end assembly (1), and the third end (201) and the second end (102) are coaxially arranged, and the bend (21) further comprises a fourth end (202) bent upward toward one side of the working end assembly (1) relative to the third end (201), and the axis of the fourth end (202) is aligned with the axis of the third end (201). The axes are perpendicular to each other, a through hole (4) is provided on the tension side of the bent pipe (21), the special-shaped pipe (22) has a fifth end (203) with a curved tangent opening and a sixth end (204) with a flat cut opening, and the special-shaped pipe (22) is coaxially arranged with the third end (201) of the bent pipe (21), and the fifth end (203) of the special-shaped pipe (22) is welded to the tension side of the bent pipe (21) to cover the through hole (4), and the bent pipe (21) is connected to the special-shaped pipe (22) through the through hole (4); The balancing end assembly (3) is a horizontal cylindrical structural member, and the balancing end assembly (3) has a seventh end (301) connected to the sixth end (204) of the special-shaped tube (22) and an eighth end (302) opposite to the seventh end (301) and blocked; The invention also includes a load-bearing assembly (5), wherein the load-bearing assembly (5) includes a first main hinge plate (51) connected to the first end (101) of the working end assembly (1), a second main hinge plate (52) connected to the eighth end (302) of the balancing end assembly (3), and a secondary hinge plate (53) located between the first main hinge plate (51) and the second main hinge plate (52) and hinged to the two. The load-bearing assembly (5) also includes a first annular anti-torsion ring (9) sleeved on the outer wall of the third end (201) of the bent pipe (21) and a second annular anti-torsion ring (10) sleeved on the outer wall of the sixth end (204) of the special-shaped pipe (22).
2. The curved pipe pressure-balanced expansion joint for complex pipeline connections according to claim 1, characterized in that: The working end assembly (1) comprises a first connecting pipe (11), an intermediate pipe (12), a first bellows (13) and a second bellows (14); One end of the pipe (11) is connected to a damping shock absorber (6) via a clamp, the other end of the pipe (11) is connected to one end of the first bellows (13), the other end of the first bellows (13) is connected to one end of the intermediate pipe (12), the other end of the intermediate pipe (12) is connected to one end of the second bellows (14), and the other end of the second bellows (14) is connected to the three-way assembly (2); A support plate (7) is fixedly mounted on the outer wall of the pipe 1 (11), and a side wall of the support plate (7) is connected to one end of the first main hinge plate (51).
3. The curved pipe pressure-balanced expansion joint for complex pipeline connections according to claim 2, characterized in that: A limiting structural member (8) is provided on the outer wall of the intermediate tube (12); The limiting structure (8) includes two limiting plates (81) distributed along the axial direction of the intermediate tube (12), and the two limiting plates (81) are symmetrically arranged on both sides of the auxiliary hinge plate (53) at intervals; the limiting structure (8) also includes two limiters (82) respectively located on the inner sides of the two limiting plates (81).
4. The curved pipe pressure-balanced expansion joint for complex pipeline connections according to claim 3, characterized in that: Two secondary hinge plate support plates (54) are further provided on the outer wall of the intermediate tube (12). The two secondary hinge plate support plates (54) are located between the two limiting plates (81) and are perpendicular to the limiting plates (81). The secondary hinge plate support plates (54) are each provided with a first rectangular hole (55) for passing the secondary hinge plate (53). The first rectangular hole (55) is opened along the radial direction of the intermediate tube (12) so that the secondary hinge plate (53) and the two secondary hinge plate support plates (54) are both clearance-fitted.
5. The curved pipe pressure-balanced expansion joint for complex pipeline connections according to claim 4, characterized in that: The third end (201) of the curved pipe (21) is connected to the second corrugated pipe (14) via a second connecting pipe (23), and the fourth end (202) of the curved pipe (21) is provided with a third connecting pipe (24), and the third connecting pipe (24) is connected to a second damping shock absorber (25) via a clamp.
6. The curved pipe pressure-balanced expansion joint for complex pipeline connections according to claim 5, characterized in that: A first annular anti-torsion ring (9) is sleeved on the outer wall of the second connecting pipe (23), and a second annular anti-torsion ring (10) is sleeved on the outer wall of the sixth end (204) of the special-shaped pipe (22). The first annular anti-torsion ring (9) and the second annular anti-torsion ring (10) are both provided with a second rectangular hole (20) for passing the second main hinge plate (52), and the second rectangular hole (20) is opened along the radial direction of the second connecting pipe (23) so that the second main hinge plate (52) is loosely matched with the first annular anti-torsion ring (9) and the second annular anti-torsion ring (10).
7. The curved pipe pressure-balanced expansion joint for complex pipeline connections according to claim 4, characterized in that: The balancing end assembly (3) includes a balancing bellows (31), one end of which is connected to the special-shaped tube (22), and the other end of which is connected to a fourth connecting pipe (32), the end of which serves as an eighth end (302), and a blocking plate (33) is provided at the end of the fourth connecting pipe (32).
8. The curved pipe pressure-balanced expansion joint for complex pipeline connections according to claim 7, characterized in that: It also includes a first displacement sensor (30) and a second displacement sensor (40), wherein the first displacement sensor (30) is located above the outer wall of the first corrugated tube (13), and two ends of the first displacement sensor (30) are respectively connected to the support plate (7) and the secondary hinge plate support plate (54) through a first mounting frame (50); The second displacement sensor (40) is located above the outer wall of the balancing bellows (31), and both ends of the second displacement sensor (40) are connected to the special-shaped tube (22) and the blocking plate (33) respectively through a second mounting frame (60).
9. The curved pipe pressure-balanced expansion joint for complex pipeline connections according to claim 5, characterized in that: The inner wall of the first bellows (13) is provided with a first flow guide tube (70), and the inner wall of the second bellows (14) is provided with a second flow guide tube, and the two ends of the first flow guide tube (70) respectively extend into the first connecting pipe (11) and the middle pipe (12) and are welded with the first connecting pipe (11) and the middle pipe (12) in a clearance fit, and the two ends of the second flow guide tube respectively extend into the middle pipe (12) and the second connecting pipe (23) and are welded with the middle pipe (12) and the second connecting pipe (23) in a clearance fit; The first flow guide tube (70) and the second flow guide tube have the same structure, and the first flow guide tube (70) comprises a first horizontal section (701), a first inclined section (702), a second inclined section (703) and a second horizontal section (704) formed in sequence; One end of the first inclined section (702) away from the first horizontal section (701) is inclined inwardly and connected to one end of the second inclined section (703), and the other end of the second inclined section (703) is inclined inwardly and connected to the second horizontal section (704).
10. The curved pipe pressure-balanced expansion joint for complex pipeline connections according to claim 7, characterized in that: The inner wall of the balancing end assembly (3) is provided with a guide and limit tube (80), and both ends of the guide and limit tube (80) respectively extend to the special-shaped tube (22) and the fourth connecting tube (32) to be gap-fitted and welded.