CN108343943B - Overheating section structure for improving input rate of high-pressure heater - Google Patents
Overheating section structure for improving input rate of high-pressure heater Download PDFInfo
- Publication number
- CN108343943B CN108343943B CN201710045909.2A CN201710045909A CN108343943B CN 108343943 B CN108343943 B CN 108343943B CN 201710045909 A CN201710045909 A CN 201710045909A CN 108343943 B CN108343943 B CN 108343943B
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- steam
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- baffle
- tube
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- 238000013021 overheating Methods 0.000 title description 5
- 238000005253 cladding Methods 0.000 claims description 17
- 238000009833 condensation Methods 0.000 claims description 8
- 230000005494 condensation Effects 0.000 claims description 8
- 238000007789 sealing Methods 0.000 claims description 6
- 239000002184 metal Substances 0.000 claims description 4
- 239000007787 solid Substances 0.000 claims description 3
- 230000000903 blocking effect Effects 0.000 abstract description 2
- 230000000694 effects Effects 0.000 abstract description 2
- 230000002401 inhibitory effect Effects 0.000 abstract description 2
- 238000005452 bending Methods 0.000 description 8
- 230000008093 supporting effect Effects 0.000 description 7
- 238000011010 flushing procedure Methods 0.000 description 6
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 6
- 238000009991 scouring Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000003628 erosive effect Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000011835 investigation Methods 0.000 description 1
- 238000011418 maintenance treatment Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000003595 mist Substances 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000004080 punching Methods 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000008646 thermal stress Effects 0.000 description 1
- 238000005406 washing Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22G—SUPERHEATING OF STEAM
- F22G3/00—Steam superheaters characterised by constructional features; Details of component parts thereof
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Cookers (AREA)
Abstract
The invention relates to the field of high-pressure heaters, and discloses a superheating section structure for improving the input rate of a high-pressure heater, which comprises a shell and a steam inlet, wherein a tube plate is arranged on one side of the shell, a U-shaped tube is arranged in the shell, a port of the U-shaped tube is fixed on the tube plate, a heat shield plate is arranged between the tube plate and the superheating section, the steam inlet is positioned on the shell near the tube plate and below the steam inlet, and a plurality of anti-impact rods are arranged above the U-shaped tube side by side. In the prior art, although the baffle plate arranged at the steam inlet has a certain steam blocking effect, blocked steam still directly washes out the U-shaped pipe at the outermost periphery after being folded, after the baffle rod is arranged, the baffle rod is washed out firstly and then flows to the U-shaped pipe below after the superheated steam enters, so that the condition that the U-shaped pipe is directly washed out is avoided, and the baffle plate has a great effect of inhibiting the thinning of the pipe wall.
Description
Technical Field
The invention relates to the field of high-pressure heaters, in particular to a superheating section structure of a high-pressure heater.
Background
The high-pressure heater is an important device in a water supply and heat recovery system of a thermal power plant and a nuclear power plant, and the performance and reliability of the high-pressure heater directly influence the economy and the safety of the operation of a unit. In recent years, high-parameter and high-capacity units are continuously increased, and the operation conditions of the heater are progressively worse due to frequent starting and abrupt load change of the units. In actual operation of the high-pressure heater, once leakage occurs, the high-pressure heater must be taken out of operation and subjected to maintenance treatment. Through the investigation of the high-pressure heater operated at home and abroad, we find that the parts of the high-pressure heater tube bundle which are easy to damage are: two or three rows of tubes at the outermost periphery of a steam inlet of a superheated steam cooling section (hereinafter referred to as a superheating section), tubes near an outlet of the superheating section, and tubes at the innermost rows of tubes at the center of a tube bundle.
In particular, there are many causes of leakage of the high-pressure heater, and from the design point of view only, there are three more common aspects: (1) scour erosion: when the steam flow channel is small and the steam flow rate is high, especially when the steam contains water mist, the steam and water are washed for a long time, the outer wall of the pipe is gradually thinned, and under the action of thermal stress and steam and water pressure difference, the weak part of the U-shaped pipe can bulge, crack or even burst, and finally leakage is generated; (2) tube vibration: when the length of the free section of the tube bundle (without supporting span) is too long and the steam flow speed is high, the tube bundle vibrates under the action of steam disturbance force, and when the frequency of exciting force is identical to the natural frequency of the tube bundle or multiple thereof, the resonance of the tube bundle is caused, the amplitude is greatly increased, the tube bundle is damaged, and leakage is generated; (3) The minimum bending radius of the U-shaped pipe at the central position of the pipe bundle is small, the deformation of the bent pipe is large in manufacturing, the local pipe wall is thinned, the flushing to the pipe wall is large in operation, and the pipe is easy to damage.
The reason is mainly because the following defects exist in the overheat section structure of the existing high-pressure heater: (1) Although the steam inlet adopts the design of a baffle plate, the most peripheral pipe is still very seriously washed by steam and water (the baffle plate can be seen from a steam baffle plate (5) pointed by Chinese patent publication No. CN 2753964Y); (2) Steam flow rate is high, humidity is high and steam-water scouring occurs at the outlet of the superheating section; (3) The free section of the tube bundle has large length (no supporting span) and is easy to vibrate; (4) The minimum bending radius of the U-shaped pipe at the central position of the pipe bundle is small, the local pipe wall is thinner, and the U-shaped pipe is easy to damage in operation.
Disclosure of Invention
The invention aims to solve the technical problem of providing a high-pressure heater overheating section structure so as to effectively control the leakage rate of a U-shaped pipe of the high-pressure heater, improve the input rate of the high-pressure heater and bring economic benefits to a power plant.
The technical scheme adopted for solving the technical problems is as follows: the utility model provides an improve super hot section structure of high pressure heater input rate, includes casing and steam inlet, one side of casing is equipped with the tube sheet, has arranged the U-shaped pipe in the casing, the port of U-shaped pipe is fixed the tube sheet on, and be provided with the heat shield between tube sheet with super hot section, steam inlet be located on the casing near the tube sheet, be located steam inlet's below, the top of U-shaped pipe is provided with a plurality of anti-punching pins side by side.
The tubes in the three rows of areas at the outermost periphery of the U-shaped tube bundle in the prior structure can be replaced by the anti-impact rod, and the anti-impact rod can be made of metal pieces. In the prior art, the anti-collision baffle arranged at the steam inlet has a certain steam blocking effect, but the blocked steam can still directly wash the U-shaped pipe at the outermost periphery after being folded. After the anti-flushing rod is arranged, when the superheated steam enters, the anti-flushing rod is flushed firstly and then flows to the U-shaped pipe below, so that the situation that the U-shaped pipe is flushed directly is avoided, and the anti-flushing rod has a great effect of inhibiting the thinning of the pipe wall.
Further, the device also comprises a cladding which is of a semicircular arc structure and is arranged at the periphery of the U-shaped pipe at the tail section of the overheat section; the bottom of the shell is sealed through a bottom plate, one side, close to the condensation section, of the shell is sealed through a second baffle, one side, close to the front section of the superheating section, of the shell is sealed through a first baffle, and a gap is reserved between the bottom of the first baffle and the bottom plate for steam to pass through; the top of the cladding is also provided with a notch for steam in the cladding to flow into the condensation section. After entering, steam flows downwards transversely relative to the U-shaped pipe and flows into the front section of the superheating section, then flows into the tail section of the superheating section longitudinally through the gap to enter the cladding, flows upwards transversely in the cladding and finally flows out of the notch at the top to enter the condensing section, so that after the steam flows in the superheating section in a folded manner, the flow speed is reduced when the steam flows out of the superheating section, the scouring of pipe walls is reduced, and the steam after flowing out can be gradually and uniformly distributed into the whole condensing section along the inner wall of the shell.
Further, a sealing plate for preventing steam from passing through is arranged between the steam inlet and the notch at the top of the cladding. The sealing plate can prevent steam from directly flowing to the upper part of the cladding without flowing through the U-shaped pipe below after entering, and then flows into the condensation section, so that the heat exchange purpose can not be achieved, namely, the sealing plate prevents the occurrence of steam short circuit.
Further, the innermost U-shaped tube is arranged above said gap between the bottom of the first baffle and the bottom plate. The gap is a steam flow passage positioned below the innermost U-shaped pipe, and the flow passage is communicated with the front section and the tail section of the superheating section. In the prior art, the minimum bending radius of the innermost U-shaped pipe is smaller, so that after the U-shaped pipe is bent, the pipe wall is thinner and is easy to damage, and the arrangement position of the innermost U-shaped pipe is raised above the gap, so that the minimum bending radius is increased, and the situation that the pipe is easy to damage after being washed due to the fact that the local pipe wall is too thin when the pipe is manufactured due to the fact that the bending radius is too small is avoided.
Further, one end of the anti-impact rod penetrates through the heat shielding plate to be fixed on the tube plate, and the other end of the anti-impact rod is fixed on the first baffle.
Further, one end of the bottom plate is fixed on the second baffle plate, and the other end of the bottom plate is fixed on the heat shield plate.
Further, the anti-impact rod is a solid metal rod piece.
Further, the distance between the first baffle and the second baffle and the distance between the first baffle and the heat shield can be determined according to the actual steam flow rate, and meanwhile, the number and the distance of the U-shaped pipe supporting plates can be set and adjusted according to the actual conditions, so that the unsupported span of the pipe bundle is reduced, and vibration is prevented.
In summary, the beneficial effects of the invention are as follows: (1) By arranging the anti-impact rod, the tube bundle is prevented from being directly eroded by scouring; (2) The flow speed of steam at the outlet of the superheating section is reduced, and the flowing steam can be uniformly distributed to the condensing section, so that the condition that the flow speed of steam at the outlet of the superheating section is too high and the tube bundle is easily eroded is prevented; (3) The minimum bending radius of the innermost U-shaped pipe is increased, so that the wall thickness is increased, and the anti-scouring capability is improved; (4) The occurrence of the vibration of the U-shaped pipe at the overheating section is effectively prevented, and the condition that the pipe bundle is damaged by the vibration is avoided. Therefore, the leakage rate of the U-shaped pipe of the high-pressure heater is effectively controlled, the input rate of the high-pressure heater is improved, and the economic benefit of a power plant is improved.
Drawings
FIG. 1 is a schematic diagram of the structure of the present invention;
FIG. 2 is a sectional view of A-A of FIG. 1;
FIG. 3 is a front view of the enclosure;
FIG. 4 is a cross-sectional view of FIG. 3;
FIG. 5 is a schematic diagram of the steam flow of FIG. 1;
FIG. 6 is a schematic diagram of the steam flow of FIG. 2;
marked in the figure as: 1-tube plate, 2-heat shield plate, 3-anti-impact rod, 4-U-shaped tube, 5-steam inlet, 6-sealing plate, 7-shell, 8-cladding, 9-distance tube, 10-second baffle, 11-bottom plate, 12-support plate, 13-first baffle, 14-gap and 15-gap.
Detailed Description
The present invention will be described in further detail with reference to specific examples, but embodiments of the present invention are not limited thereto.
As shown in fig. 1-4, a superheating section structure for improving the input rate of a high-pressure heater comprises a shell 7, wherein a tube plate 1 is arranged on one side of the shell 7, a port of a U-shaped tube 4,U 4 arranged in the shell 7 is fixed on the tube plate 1, and a heat shielding plate 2 is arranged between the tube plate 1 and the superheating section.
The superheating section is divided into a front section and a rear section, wherein the front section is provided with a steam inlet 5, and the rear section is provided with a cladding 8. The steam inlet 5 is arranged on the shell 7 near the tube plate 1, a plurality of anti-impact rods 3 are arranged above the U-shaped tubes 4 side by side under the steam inlet 5, the anti-impact rods 3 can be arranged at the three rows of U-shaped tubes at the outermost periphery in the existing superheating section structure (namely, the three rows of U-shaped tubes at the outermost periphery in the existing structure are replaced by the anti-impact rods 3 of the invention, which are equivalent to the replacement of false tubes at the place), the anti-impact rods 3 are solid metal rods, one ends of the anti-impact rods 3 penetrate through the heat shielding plate 2 to be in threaded connection with the tube plate 1, and the other ends of the anti-impact rods penetrate through the first baffle 13 and are firmly welded with the first baffle 13. The cladding 8 is of a semicircular arc structure and is arranged at the periphery of the U-shaped pipe 4 at the tail section of the overheating section; the bottom of the shell 8 is sealed through a bottom plate 11, one side close to the condensation section is sealed through a second baffle plate 10, one side close to the front section of the superheating section is sealed through a first baffle plate 13, a gap 14 is reserved between the bottom of the first baffle plate 13 and the bottom plate 11 for steam to pass through, one end of the bottom plate 11 is welded at the bottom of the second baffle plate 10, and the other end is welded on the heat shield plate 2; a notch 15 is also formed in the top of the cladding 8 to allow steam in the cladding 8 to flow into the condensation section.
In order to prevent the entering steam from bypassing the U-shaped pipe at the front section of the superheating section and directly entering the notch 15 above the tail section of the superheating section to cause steam short circuit, a semicircular sealing plate 6 for preventing the steam from passing is welded between the outer wall of the cladding 8 between the steam inlet 5 and the notch 15 and the inner wall of the shell 7.
In addition, no U-tubes are arranged in the region of the gap 14 between the bottom of the first baffle 13 and the bottom plate 11, i.e. the innermost U-tube 4 is located above this gap 14. Therefore, the minimum bending radius of the innermost U-shaped pipe can be increased, and the situation that the pipe is easily damaged after being washed due to the fact that the local pipe wall is too thin when the pipe is manufactured due to the fact that the bending radius is too small is avoided.
With respect to the flow direction of the steam, as shown in fig. 5 and 6, after the steam enters from the steam inlet 5, the steam firstly brushes the anti-flushing rod 3 and then flows down the U-shaped pipe 4, then flows transversely downwards relative to the U-shaped pipe, flows to the position close to the bottom plate, longitudinally passes through the gap 14 relative to the U-shaped pipe, enters the shell of the tail section of the superheating section, then flows transversely upwards relative to the U-shaped pipe, finally flows out from the notch 15 at the top, and after the steam flows out, the steam is gradually and uniformly distributed into the whole condensing section along the inner wall of the high-pressure heater shell 7. Because the steam does not directly wash the U-shaped pipe 4 after entering, but firstly washes the anti-flushing rod 3 and then enters the shell 8, the possibility of leakage caused by direct washing erosion of the pipe is avoided to a great extent; in addition, because the flow rate of steam flowing into the condensation section from the notch 15 at the top of the cladding 8 is reduced compared with the prior art after the steam is folded in the superheating section for a plurality of times, the strength of the pipe wall washed is reduced.
In addition, in the prior art, an arch-shaped baffle plate (the arch-shaped baffle plate can be seen in fig. 2 of Chinese patent publication No. CN 205482419U) is adopted to support the U-shaped pipe, and the unsupported span of the pipe at the notch of the arch-shaped baffle plate is twice the baffle plate spacing, so that the natural frequency of the pipe is reduced, and the pipe is easy to vibrate. In the invention, because the steam transversely flows through the U-shaped pipe in the superheating section, the U-shaped pipe can be supported by adopting the supporting plate 12 and the distance pipe 9, and the supporting plate 12 adopts an integral supporting structure (the problem that the steam passes through the middle of the plate body is not needed to be considered), so that the fixing and supporting effects on the U-shaped pipe are better, the vibration condition of the pipe bundle in operation is effectively prevented, and the leakage condition of the U-shaped pipe caused by the vibration is further avoided.
In conclusion, the leakage rate of the U-shaped pipe of the high-pressure heater is effectively controlled, the input rate of the high-pressure heater is improved, and the economic benefit of a power plant is improved.
Claims (4)
1. The utility model provides an improve super hot section structure of high pressure heater input rate, includes casing (7) and steam inlet (5), one side of casing (7) is equipped with tube sheet (1), has arranged U-shaped pipe (4) in casing (7), the port of U-shaped pipe (4) is fixed tube sheet (1) on, and be provided with heat-proof plate (2) between tube sheet (1) with super hot section, steam inlet (5) be located on casing (7) near tube sheet (1), its characterized in that: a plurality of anti-impact rods (3) are arranged above the U-shaped pipe (4) side by side and below the steam inlet (5);
the hot-air furnace also comprises an envelope (8), wherein the envelope (8) is of a semicircular arc structure and is arranged at the periphery of the U-shaped pipe (4) at the tail section of the hot section; the bottom of the shell (8) is sealed through a bottom plate (11), one side close to the condensation section is sealed through a second baffle (10), one side close to the front section of the superheating section is sealed through a first baffle (13), and a gap (14) is reserved between the bottom of the first baffle (13) and the bottom plate (11) for steam to pass through; a notch (15) is formed in the top of the cladding (8) for steam in the cladding (8) to flow into the condensation section;
the innermost U-shaped tube (4) is arranged above the gap (14) between the bottom of the first baffle (13) and the bottom plate (11);
a sealing plate (6) for preventing steam from passing through is arranged between the steam inlet (5) and a notch (15) at the top of the cladding (8).
2. The superheating section structure for improving the input rate of a high-pressure heater according to claim 1, wherein: one end of the anti-collision rod (3) penetrates through the heat shield plate (2) to be fixed on the tube plate (1), and the other end of the anti-collision rod is fixed on the first baffle plate (13).
3. The superheating section structure for improving the input rate of a high-pressure heater according to claim 1, wherein: one end of the bottom plate (11) is fixed on the second baffle plate (10), and the other end is fixed on the heat shield plate (2).
4. The superheating section structure for improving the input rate of a high-pressure heater according to claim 1, wherein: the anti-collision rod (3) is a solid metal rod piece.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710045909.2A CN108343943B (en) | 2017-01-22 | 2017-01-22 | Overheating section structure for improving input rate of high-pressure heater |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710045909.2A CN108343943B (en) | 2017-01-22 | 2017-01-22 | Overheating section structure for improving input rate of high-pressure heater |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108343943A CN108343943A (en) | 2018-07-31 |
| CN108343943B true CN108343943B (en) | 2023-11-07 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710045909.2A Active CN108343943B (en) | 2017-01-22 | 2017-01-22 | Overheating section structure for improving input rate of high-pressure heater |
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| Country | Link |
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| JPH08145305A (en) * | 1994-11-21 | 1996-06-07 | Hitachi Ltd | Feed water heater and power generating plant |
| CN2753964Y (en) * | 2004-12-16 | 2006-01-25 | 上海动力设备有限公司 | Superheated steam cooling device for surface horizontal heater |
| CN1818464A (en) * | 2000-09-01 | 2006-08-16 | 株式会社东芝 | Feed water heater |
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| CN102798116A (en) * | 2012-08-26 | 2012-11-28 | 哈尔滨锅炉厂有限责任公司 | Horizontal-type three-section thermal power high-pressure feed-water heater and heating method |
| CN202973973U (en) * | 2012-12-11 | 2013-06-05 | 吉林省同达传热技术有限公司 | Overall expansion type heater for heating network |
| CN203464834U (en) * | 2013-07-19 | 2014-03-05 | 青岛博德化机有限公司 | Scour-preventing device used for heat exchange tube bundle of heat exchanger |
| CN105258547A (en) * | 2015-08-20 | 2016-01-20 | 无锡鼎邦换热设备有限公司 | Anti-scouring structure of heat exchanger |
| CN205482419U (en) * | 2016-03-31 | 2016-08-17 | 国网湖北省电力公司咸宁供电公司 | Horizontal high pressure feed water heater |
| CN106288322A (en) * | 2016-10-18 | 2017-01-04 | 东方电气集团东方锅炉股份有限公司 | A kind of nothing reducing low-pressure heater device diameters is indulged and is plunderred heat exchange superheat section structure |
| CN206469247U (en) * | 2017-01-22 | 2017-09-05 | 东方电气集团东方锅炉股份有限公司 | A kind of overheat segment structure for improving high pressure heater available rate |
-
2017
- 2017-01-22 CN CN201710045909.2A patent/CN108343943B/en active Active
Patent Citations (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS53147103A (en) * | 1977-05-27 | 1978-12-21 | Hitachi Ltd | Multitubular system heat exchager |
| JPH08145305A (en) * | 1994-11-21 | 1996-06-07 | Hitachi Ltd | Feed water heater and power generating plant |
| CN1818464A (en) * | 2000-09-01 | 2006-08-16 | 株式会社东芝 | Feed water heater |
| CN2753964Y (en) * | 2004-12-16 | 2006-01-25 | 上海动力设备有限公司 | Superheated steam cooling device for surface horizontal heater |
| CN201016589Y (en) * | 2006-11-29 | 2008-02-06 | 田雅杰 | Shell-and-tube steam-water heat exchanger |
| CN201104137Y (en) * | 2007-09-29 | 2008-08-20 | 华南理工大学 | Helical baffle plate supporting special-shaped pipe condenser |
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| CN106288322A (en) * | 2016-10-18 | 2017-01-04 | 东方电气集团东方锅炉股份有限公司 | A kind of nothing reducing low-pressure heater device diameters is indulged and is plunderred heat exchange superheat section structure |
| CN206469247U (en) * | 2017-01-22 | 2017-09-05 | 东方电气集团东方锅炉股份有限公司 | A kind of overheat segment structure for improving high pressure heater available rate |
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| Publication number | Publication date |
|---|---|
| CN108343943A (en) | 2018-07-31 |
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