CN114234680A - High-temperature high-pressure double-pipe heat exchanger - Google Patents
High-temperature high-pressure double-pipe heat exchanger Download PDFInfo
- Publication number
- CN114234680A CN114234680A CN202111328850.0A CN202111328850A CN114234680A CN 114234680 A CN114234680 A CN 114234680A CN 202111328850 A CN202111328850 A CN 202111328850A CN 114234680 A CN114234680 A CN 114234680A
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- Prior art keywords
- heat exchange
- tube
- medium
- pipe
- exchange tube
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
- F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
- F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
- F28F21/081—Heat exchange elements made from metals or metal alloys
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/0243—Header boxes having a circular cross-section
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
Abstract
The invention provides a high-temperature high-pressure sleeve type heat exchanger which is simple and compact in structure, uniform in internal flow temperature distribution, high in heat exchange efficiency, easy to machine and manufacture, high-temperature and high-pressure resistant, and comprises a plurality of groups of sleeve type heat exchange tubes, a first medium tube box and a second medium tube box, wherein the first medium tube box and the second medium tube box are arranged at two ends of each sleeve type heat exchange tube; the sleeve type heat exchange tube is formed by combining an outer heat exchange tube, an inner heat exchange tube and a flow guide rod in a coaxial sleeve mode, and spiral flow guide convex bodies are arranged on the outer surfaces of the inner heat exchange tube and the flow guide rod, so that two media in the heat exchange tube form spiral annular turbulent flow and small-flow fast flow to form countercurrent heat exchange, the flow of the two media is ensured to be equal, the flow distribution is uniform, the flow is increased, and the heat exchange efficiency is improved. The inner heat exchange tube and the outer heat exchange tube can freely stretch and retract along with the change of the temperature of the fluid, are not mutually fixed, can effectively eliminate the thermal stress, and are particularly suitable for the large temperature difference and the high-temperature and high-pressure working conditions of two media.
Description
Technical Field
The invention belongs to the field of heat exchange, and particularly relates to a high-temperature high-pressure micro-fine shell-and-tube heat exchanger.
Background
In the fourth generation high temperature gas cooled reactor nuclear power plant and the research and development of solar photo-thermal supercritical carbon dioxide brayton cycle power generation, the supercritical carbon dioxide brayton cycle is considered as a novel, efficient and safe energy cycle system. In the supercritical carbon dioxide brayton cycle, a heat collector and a heat regenerator are one of the most important heat exchange components, and the thermal performance of the heat collector and the heat regenerator has important influence on the efficiency of the whole cycle and the size of a system.
At present, the heat exchangers adopted in the second and third generation pressurized water reactor nuclear power stations are generally shell-and-tube heat exchangers. The traditional shell-and-tube heat exchanger has the advantages of simple structure, low cost, wide flow cross section and easy cleaning. However, because the heat exchange tube has a large diameter and a long tube pass, the shell-and-tube heat exchanger has low heat exchange efficiency, large floor area and poor pressure resistance and seismic performance, and the traditional shell-and-tube heat exchanger cannot meet the development requirements of the supercritical carbon dioxide Brayton cycle high-temperature gas cooled reactor.
In addition, the conventional shell-and-tube heat exchanger has the following disadvantages in structure:
the heat exchange temperature difference of the fixed tube-plate heat exchanger can not exceed 100 ℃ usually, the U-shaped tube heat exchanger has fewer tube bundles and the tube bundles are difficult to clean and maintain, the floating head heat exchanger has a complex structure and high manufacturing cost, the temperature and flow inside the spiral wound tube heat exchanger are uneven in distribution, and the tube bundles are difficult to replace and clean. Therefore, a new high-temperature high-pressure heat exchange device with high efficiency and compactness is needed.
The conventional size tube bundle is changed into the micro-tube bundle, the ratio of the heat exchange area to the volume of the shell-and-tube heat exchanger can be greatly improved, and compact heat exchange can be realized. In addition, the pressure resistance of the heat exchanger is improved due to the reduction of the size. Therefore, the micro-fine shell-and-tube heat exchanger can be used for heat exchange of a supercritical carbon dioxide Brayton cycle high-temperature gas cooled reactor. However, in the supercritical carbon dioxide Brayton cycle high-temperature gas cooled reactor, the operation condition of the regenerator is usually 20MPa in the cold side,
300 ℃, hot side 10MPa and 500 ℃. Due to the increase of working temperature and pressure, the great increase of temperature difference of cold and hot fluids and the reduction of the size of the heat exchanger, the design and manufacture difficulty of the micro-fine shell-and-tube heat exchanger is greatly increased compared with that of the traditional shell-and-tube heat exchanger. In particular, the difficulty of sealing connection between the tube plate and the micro-tube bundle is multiplied compared with the conventional size. The metal microtubes are usually brazed in a sealing connection mode, but the traditional brazing process is easy to generate the phenomena of microtube deformation, fusion corrosion, insufficient welding and the like during processing, and cannot meet the processing requirements. The new technologies developed at present, such as vacuum electron beam brazing, pulse laser welding and the like, of the metal micro-tube have the defects of immature process, low processing efficiency, high processing cost and the like.
Chinese patent, patent publication No. CN 103128519a, discloses a method and apparatus for manufacturing a microchannel heat exchanger, in which a heat exchanger tube bundle and a header of the heat exchanger are connected by cold extrusion, and the cold extrusion is connected with advantages of saving raw materials and energy, improving efficiency and reducing cost, but the process is not suitable for high-temperature and high-pressure working conditions.
Chinese patent, patent No. CN 206709658U discloses a micro-tube hairpin heat exchanger, which is used for heat exchange
The shell pass cylinder and the tube bundle of the device are U-shaped, so that the stress generated in heat exchange can be eliminated, the material is saved, and the processing procedures are reduced. But the heat exchanger tube bundle and the tube plate are connected by threads, so that the working conditions of high temperature and high pressure cannot be met.
Chinese patent, patent No. CN 109654909B, discloses a high-temperature high-pressure fine shell-and-tube heat exchanger, which overcomes various disadvantages of the above heat exchanger, but also causes some problems, for example, after the heat exchanger tube bundle is changed into a sine-shaped bent tube or a trapezoid bent tube, although the length of the heat exchange tube is correspondingly increased and the heat exchange area is also increased synchronously, the fluid resistance in the fine tube is also greatly increased, and after the tube is bent, the flow channel inside the bent part is easy to narrow, which not only affects the flow rate, but also is easy to block; on the other hand, the diameter of the microtube is controlled between 1mm and 3mm, and the sealing of both ends of the tube bundle is not easy; although the flow paths of all the heat exchanger tube bundles are equal to ensure uniform flow distribution on the tube side, the flow paths on the shell side are not equal to each tube bundle, and the uniform flow distribution on the shell side is difficult to ensure.
Disclosure of Invention
In order to solve the problems in the background art, the invention provides a high-temperature high-pressure double-pipe heat exchanger which is simple and compact in structure, uniform in internal flow temperature distribution, high in heat exchange efficiency, easy to process and manufacture and resistant to high temperature and high pressure.
In order to achieve the purpose, the invention adopts the following technical scheme to realize the purpose:
the invention provides a high-temperature high-pressure double-pipe heat exchanger, which comprises a heat exchanger body and is characterized in that the heat exchanger body consists of a plurality of groups of double-pipe heat exchange pipes, a first medium pipe box and a second medium pipe box, wherein the two ends of each double-pipe heat exchange pipe are respectively provided with the first medium pipe box and the second medium pipe box, and the first medium pipe box is positioned at the outermost end; the first medium channel box at one end of the heat exchanger body is provided with a first medium outlet, the second medium channel box is provided with a second medium inlet, the first medium channel box at the other end of the heat exchanger is provided with a first medium inlet, the second medium channel box is provided with a second medium outlet, the sleeve type heat exchange tube comprises an outer heat exchange tube and an inner heat exchange tube, the inner heat exchange tube is also provided with a flow guide rod, and the outer heat exchange tube, the inner heat exchange tube and the inner heat exchange tube are combined together through a coaxial sleeve; after the inner heat exchange tube passes through the outer heat exchange tube without being constrained, two ports of the inner heat exchange tube are fixedly connected with a first tube plate respectively, two ports of the outer heat exchange tube are fixedly connected with a second tube plate respectively, the first tube plate and the second tube plate at the same end are fixedly connected through a tube shell to form a second medium tube box, an expansion joint is arranged on the tube shell, and the outer heat exchange tube is communicated with the second medium tube box; the outer end of each first tube plate is fixedly connected with an end socket respectively, the end sockets and the end sockets form the first medium tube box, and the inner heat exchange tube is communicated with the first medium tube box; two media in the sleeve type heat exchange tube form a countercurrent heat exchange mode.
Furthermore, spring-shaped spiral flow guide convex bodies are respectively arranged on the outer surface of the inner heat exchange tube and the outer surface of the flow guide rod. Generally, the spiral flow guide convex body can be wound on the outer surface of the inner heat exchange tube or the flow guide rod by adopting a stainless steel wire, or the spiral flow guide convex body is integrally formed by machining the thickened inner heat exchange tube and the flow guide rod; the guide rods are generally hollow.
Furthermore, the inner heat exchange tube, the first tube plate and the end enclosure are all made of 42CrMo alloy steel or other high-temperature-resistant high-strength alloy materials.
Furthermore, the outer heat exchange tube, the second tube plate, the tube shell, the expansion joint and the flow guide rod are made of high-temperature-resistant alloy steel or high-temperature-resistant stainless steel or high-temperature-resistant nickel-based alloy or high-temperature-resistant titanium alloy.
The invention has the beneficial effects that:
1. the sleeve type heat exchange tube adopted by the invention is formed by combining an outer heat exchange tube, an inner heat exchange tube and a flow guide rod in a coaxial sleeve manner, and the outer surfaces of the inner heat exchange tube and the flow guide rod are provided with the spiral flow guide convex bodies, so that two media in the heat exchange tube form spiral annular turbulence and small-flow rapid flow, and the two media form countercurrent heat exchange, thereby ensuring that the flows of the two media in the inner heat exchange tube and the outer heat exchange tube are equal, the flow distribution is absolutely uniform, the flows are increased, and the heat exchange efficiency is greatly improved.
2. Compared with the existing shell-and-tube heat exchanger, the manufacturing difficulty is not increased, and the heat exchange efficiency is not reduced compared with various micro-channel heat exchangers and plate heat exchangers; meanwhile, compared with the existing shell-and-tube heat exchanger, a baffle plate assembly can be omitted, and the processing difficulty and cost are further reduced.
3. The inner and outer heat exchange tubes of the double-tube heat exchanger can freely stretch and retract along with the change of the temperature of fluid, and are not fixed with each other, so that the heat stress can be effectively eliminated, and the double-tube heat exchanger is particularly suitable for the large temperature difference and high-temperature and high-pressure working conditions of two media.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the description of the embodiments will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without creative efforts. The drawings are only for reference and illustration purposes and are not intended to limit the invention.
Fig. 1 is a schematic structural view of an appearance of a high-temperature high-pressure double pipe heat exchanger according to the present invention;
FIG. 2 is a top view of the invention provided in accordance with FIG. 1;
FIG. 3 is a schematic view of the cross-sectional structure designated E-E in FIG. 1 according to the present invention;
FIG. 4 is a schematic cross-sectional view B-B of FIG. 2 according to the present invention;
FIG. 5 is a schematic view of a portion A marked in FIG. 4 according to the present invention;
FIG. 6 is a schematic structural view of an inner heat exchange tube provided with spiral flow guide protrusions on the surface thereof according to the present invention;
fig. 7 is a schematic structural view of a flow guide rod provided with spiral flow guide protrusions on the surface.
The reference numbers are as follows:
the heat exchanger comprises a heat exchanger body 1, a sleeve type heat exchange tube 2, a first medium tube box 3, a second medium tube box 4, a first medium inlet 5, a first medium outlet 6, a second medium inlet 7, a second medium outlet 8, an outer heat exchange tube 9, an inner heat exchange tube 10, a flow guide rod 11, a first tube plate 12, a second tube plate 13, a tube shell 14, an expansion joint 15, a seal head 16 and a spiral flow guide convex body 17.
Detailed Description
The following are specific embodiments of the present invention and are further described with reference to the drawings, but the present invention is not limited to these embodiments.
Example (b):
as shown in fig. 1, 2, 3, 4, 5, 6 and 7, a high-temperature and high-pressure double-pipe heat exchanger includes a heat exchanger body 1, the heat exchanger body 1 is composed of a plurality of sets of double-pipe heat exchange pipes 2, a first medium pipe box 3 and a second medium pipe box 4, the two ends of the double-pipe heat exchange pipes 2 are respectively provided with the first medium pipe box 3 and the second medium pipe box 4, and the first medium pipe box 3 is located at the outermost end; the first medium channel 3 at one end of the heat exchanger body 1 is provided with a first medium outlet 6, the second medium channel 4 is provided with a second medium inlet 7, the first medium channel 3 at the other end of the heat exchanger is provided with a first medium inlet 5, the second medium channel 4 is provided with a second medium outlet 8, the double-pipe heat exchange pipe 2 comprises an outer heat exchange pipe 9 and an inner heat exchange pipe 10, a flow guide rod 11 is further arranged in the inner heat exchange pipe 10, and the three are formed by combining a coaxial double-pipe; after the inner heat exchange tube 10 passes through the outer heat exchange tube 9 without being constrained, two ports of the inner heat exchange tube are fixedly connected with a first tube plate 12 respectively, two ports of the outer heat exchange tube 9 are fixedly connected with a second tube plate 13 respectively, the first tube plate 12 and the second tube plate 13 at the same end are fixedly connected through a tube shell 14 to form a second medium tube box 4, an expansion joint 15 is arranged on the tube shell 14, and the outer heat exchange tube 9 is communicated with the second medium tube box 4; the outer end of each first tube plate 12 is fixedly connected with a seal head 16 respectively, the seal heads and the first tube plate form a first medium tube box 3, and the inner heat exchange tube 10 is communicated with the first medium tube box 3; two media in the sleeve type heat exchange tube form a countercurrent heat exchange mode.
Other preferred designs in this implementation are as follows:
1. the inner heat exchange tube 10, the first tube plate 12 and the end enclosure 16 are all made of 42CrMo alloy steel materials, and the connection mode is welding.
2. The outer heat exchange tube 9, the second tube plate 13, the tube shell 14, the expansion joint 15 and the flow guide rod 11 are made of high-temperature-resistant 316L stainless steel; the connection form of the outer heat exchange tube 9, the second tube plate 13, the tube shell 14 and the expansion joint 15 is welding.
3. Spring-shaped spiral flow guide convex bodies 17 are respectively arranged on the outer surface of the inner heat exchange tube 10 and the outer surface of the flow guide rod 11. Generally, the spiral flow guide convex body 17 can be formed by winding a stainless steel wire on the outer surface of the inner heat exchange tube 10 or the flow guide rod 11, or by integrally machining and molding a thickened inner heat exchange tube and a thickened flow guide rod; the guide rods are generally hollow.
As shown in fig. 1 or fig. 4, the low-pressure high-temperature thermal fluid in this embodiment flows into the second medium tube box 4 through the second medium inlet 7, flows into the second medium tube box 4 at the other end through the spiral annular flow channel formed between the outer heat exchange tube 9 and the inner heat exchange tube 10, and then flows out through the second medium outlet 8, thereby completing heat exchange; the high-pressure low-temperature fluid flows into the first medium channel 3 at the other end from the first medium inlet 5 through the first medium channel 3 and the spiral annular flow channel formed by the inner heat exchange tube 10 and the flow guide rod 11, and then flows out from the first medium outlet 6 to finish heat exchange, and the two media form a counter-flow heat exchange mode.
The specific embodiments described herein are merely illustrative of the spirit of the invention. Various modifications or additions may be made to the described embodiments or alternatives may be employed by those skilled in the art without departing from the spirit or ambit of the invention as defined in the appended claims.
Although terms such as a heat exchanger body, a double pipe heat exchange pipe, a first medium pipe box, a second medium pipe box, a first medium inlet, a first medium outlet, a second medium inlet, a second medium outlet, an outer heat exchange pipe, an inner heat exchange pipe, a flow guide rod, a first pipe plate, a second pipe plate, a pipe shell, an expansion joint, a head, a spiral flow guide convex body and the like are used more herein, the possibility of using other terms is not excluded, and these terms are used only for the convenience of describing and explaining the essence of the present invention; they are to be construed as being without limitation to any additional limitations that may be imposed by the spirit of the present invention.
Claims (4)
1. A high-temperature high-pressure double-pipe heat exchanger comprises a heat exchanger body and is characterized in that the heat exchanger body consists of a plurality of groups of double-pipe heat exchange pipes, a first medium pipe box and a second medium pipe box, wherein the two ends of each double-pipe heat exchange pipe are respectively provided with the first medium pipe box and the second medium pipe box, and the first medium pipe box is positioned at the outermost end; the first medium channel box at one end of the heat exchanger body is provided with a first medium outlet, the second medium channel box is provided with a second medium inlet, the first medium channel box at the other end of the heat exchanger is provided with a first medium inlet, the second medium channel box is provided with a second medium outlet, the sleeve type heat exchange tube comprises an outer heat exchange tube, an inner heat exchange tube and a flow guide rod in the inner heat exchange tube, and the outer heat exchange tube, the inner heat exchange tube and the flow guide rod are coaxially and telescopically combined; after the inner heat exchange tube passes through the outer heat exchange tube without being constrained, two ports of the inner heat exchange tube are fixedly connected with a first tube plate respectively, two ports of the outer heat exchange tube are fixedly connected with a second tube plate respectively, the first tube plate and the second tube plate at the same end are fixedly connected through a tube shell to form a second medium tube box, an expansion joint is arranged on the tube shell, and the outer heat exchange tube is communicated with the second medium tube box; the outer end of each first tube plate is fixedly connected with an end socket respectively, the end sockets and the end sockets form the first medium tube box, and the inner heat exchange tube is communicated with the first medium tube box; two media in the sleeve type heat exchange tube form a countercurrent heat exchange mode.
2. A high-temperature high-pressure double pipe heat exchanger according to claim 1, wherein spiral flow guide protrusions are provided on an outer surface of the inner heat exchange pipe and an outer surface of the flow guide rod, respectively.
3. A high-temperature high-pressure double-pipe heat exchanger as claimed in claim 1, wherein the inner heat exchange pipe, the first tube plate and the end enclosure are all made of 42CrMo alloy steel or other high-temperature-resistant high-strength alloy materials.
4. A high temperature and high pressure double pipe heat exchanger according to claim 1, wherein the outer heat exchange pipe, the second pipe plate, the pipe shell, the expansion joint, and the flow guide rod are made of high temperature resistant alloy steel or high temperature resistant stainless steel or high temperature resistant nickel-based alloy or high temperature resistant titanium alloy.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111328850.0A CN114234680A (en) | 2021-11-10 | 2021-11-10 | High-temperature high-pressure double-pipe heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111328850.0A CN114234680A (en) | 2021-11-10 | 2021-11-10 | High-temperature high-pressure double-pipe heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN114234680A true CN114234680A (en) | 2022-03-25 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111328850.0A Withdrawn CN114234680A (en) | 2021-11-10 | 2021-11-10 | High-temperature high-pressure double-pipe heat exchanger |
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| CN (1) | CN114234680A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116592512A (en) * | 2023-04-26 | 2023-08-15 | 无锡市前卫化工装备有限公司 | Gas heating device |
-
2021
- 2021-11-10 CN CN202111328850.0A patent/CN114234680A/en not_active Withdrawn
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116592512A (en) * | 2023-04-26 | 2023-08-15 | 无锡市前卫化工装备有限公司 | Gas heating device |
| CN116592512B (en) * | 2023-04-26 | 2024-02-06 | 无锡市前卫化工装备有限公司 | Gas heating device |
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Application publication date: 20220325 |