CN214537526U - Combined double-shell-pass heat exchanger - Google Patents
Combined double-shell-pass heat exchanger Download PDFInfo
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- CN214537526U CN214537526U CN202120623518.6U CN202120623518U CN214537526U CN 214537526 U CN214537526 U CN 214537526U CN 202120623518 U CN202120623518 U CN 202120623518U CN 214537526 U CN214537526 U CN 214537526U
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Abstract
The utility model relates to a modular double-shell side heat exchanger belongs to heat exchange technical field. The heat exchange tube comprises a shell, wherein a heat exchange tube is arranged in the shell, the shell comprises an outer shell and an inner shell, the outer shell is internally provided with the inner shell, the first end of the inner shell is connected with a fixed tube plate, the second end of the inner shell is provided with an opening, and the inner shell is internally provided with an inner shell baffle plate; a shell pass baffle plate is spirally arranged around the periphery of the inner shell pass shell; the first end of the outer shell pass shell is provided with a shell pass inlet, the first end of the inner shell pass shell is provided with a shell pass outlet, and the shell pass outlet penetrates through the outer shell pass shell. The utility model discloses divide into two solitary shell sides of inner shell side and shell side with the shell side, improved the coefficient of heat transfer and the pressure drop of heat exchanger shell side, improved the anti-scaling ability of shell side, reduced the fluidic resistance of shell side.
Description
Technical Field
The utility model relates to a modular double-shell side heat exchanger belongs to heat exchange technical field.
Background
The shell-and-tube heat exchanger has the advantages of simple structure, wide applicable pressure range, high reliability, mature technology and wide application in petroleum and chemical production. The improvement of the heat exchange efficiency of the heat exchanger has a very positive effect on improving the operation quality of the device and reducing the cost of unit products, so the research of people on the improvement of the heat exchange efficiency of the shell-and-tube heat exchanger is continuously improved for many years. Currently, conventional segmental baffle heat exchangers have several disadvantages in industrial practice: the heat transfer area is not fully utilized, so that the heat transfer coefficient of the shell pass is reduced; due to sudden contraction and expansion of medium flow, fluid impacts the shell wall, and the pressure drop on the shell side is large; and the shell side flow is vertical to the vibration caused by the tube bundle, so that the tube bundle is easy to lose efficacy.
In recent years, a spiral baffle plate heat exchanger capable of effectively improving heat transfer efficiency basically eliminates the flow dead zone and throttling of the traditional bow baffle plate heat exchanger, is particularly suitable for the conditions requiring low pressure drop, low dirt accumulation and precipitation and small induced vibration, and can realize long-period and high-efficiency operation of the heat exchanger. However, such a heat exchanger has the following technical drawbacks:
the medium flow of the main spiral flow channel is divided, and the medium flow rate and the heat exchange performance are reduced;
the structure with a spiral period formed by 4 baffle plates is difficult to mount, the roundness and concentricity of the tube bundle are not easy to guarantee, and the rigidity of the tube bundle is not good.
SUMMERY OF THE UTILITY MODEL
The to-be-solved technical problem of the utility model is: the combined double-shell-pass heat exchanger is provided, the shell pass is divided into an inner shell pass and an outer shell pass, so that the heat transfer coefficient and the pressure drop of the shell pass of the heat exchanger are improved, the anti-scaling capability of the shell pass is improved, and the resistance of shell pass fluid is reduced.
The combined double-shell-pass heat exchanger comprises a shell, wherein a heat exchange tube is arranged in the shell, the shell comprises an outer shell-pass shell and an inner shell-pass shell, the outer shell-pass shell is internally provided with an inner shell-pass shell, a first end of the inner shell-pass shell is connected with a fixed tube plate, a second end of the inner shell-pass shell is provided with an opening, and an inner shell-pass baffle plate is arranged in the inner shell-pass shell; a shell pass baffle plate is spirally arranged around the periphery of the inner shell pass shell; the first end of the outer shell pass shell is provided with a shell pass inlet, the first end of the inner shell pass shell is provided with a shell pass outlet, and the shell pass outlet penetrates through the outer shell pass shell.
Working process or working principle:
the combined double-shell-pass heat exchanger is characterized in that an inner shell pass shell is connected with a fixed tube plate, the shell pass of the heat exchanger is divided into an inner shell pass and an outer shell pass, and shell pass fluid enters the outer shell pass through a shell pass inlet, then flows through the inner shell pass and flows out through a shell pass outlet.
Preferably, the shell pass baffle plate is a spiral ladder type folded surface baffle plate, and the spiral ladder type folded surface baffle plate is formed by bending a flat plate twice and comprises two parallel folded plates and a folded plate which is at the same bending angle with the two parallel folded plates.
Preferably, the adjacent spiral ladder type folded surface baffles are arranged in a staggered and opposite mode and are used for forming spiral vortex flow by the shell-side fluid.
Preferably, the spiral stair type folded surface baffle plate is arranged as a large semicircular hole crossing the center line.
Preferably, the cutting percentage of the spiral stair type folding surface baffle plate parallel to the central line is 30-40%.
Preferably, the bending angle between the folded plate and the folded panel is 30-45 degrees; the bending degree of the folded panel is 0.3-0.5.
Preferably, the flap is arranged perpendicular to the outer housing.
Preferably, the inner shell side baffle is a square hole baffle.
Preferably, the square hole baffle plate is arranged perpendicular to the axis of the inner shell.
Preferably, the heat exchange tube is bent and formed corresponding to the shell side outlet and avoids the shell side outlet.
Compared with the prior art, the beneficial effects of the utility model are that:
1. the utility model discloses a set up shell side and inner shell side, set up shell side baffling board in the shell side, set up inner shell side baffling board in the inner shell side, shell side fluid flows through two shell sides and carries out the heat exchange, under the condition that does not increase heat exchanger length, has prolonged the time of heat exchange, and the heat exchange is more abundant, has improved the coefficient of heat transfer and the pressure drop of heat exchanger shell side, has also improved the anti-scaling ability of shell side moreover, has reduced the fluidic resistance of shell side.
2. Through setting up the spiral ladder formula folded surface baffling board, utilize their self folded surface characteristics during the connection, make two adjacent baffling boards contact closely to eliminated the triangle district that ordinary overlap joint spiral baffling board exists and leaked the flow, increased main spiral medium flow, made shell side fluid be more close continuous spiral flow, simultaneously, made the tangential velocity and the radial velocity of medium all obviously increase. The tangential velocity can generate centrifugal force, and radial secondary flow can be formed under the action of the centrifugal force, so that the fluid disturbance is greatly increased, and the boundary layer is thinned; the radial velocity forces the fluid to flow toward the center of the tube bundle, and the effective heat exchange area is the largest, so that the heat transfer performance of the shell side of the heat exchanger is enhanced. Compared with the common spiral baffle structure, the spiral-ladder type folding-face baffle structure has the advantages that the total heat transfer coefficient is increased by 18.1-22.5 percent and averagely increased by 21.4 percent, and the heat transfer coefficient of the shell side is increased by 22.3-32.6 percent and averagely increased by 27.3 percent. Compared with the common spiral baffle plate structure, the spiral ladder type folding surface baffle plate structure has the advantages that the total pressure drop of the shell side is increased by 19.3-31 percent, the average pressure drop is increased by 26.2 percent, the pressure drop of the tube bundle of the shell side is increased by 68.1-86.9 percent, and the average pressure drop is increased by 80.3 percent. Compared with a common spiral baffle plate structure, the spiral ladder type folded surface baffle plate structure has the advantages that the thermal performance factors of the heat exchanger are all larger than 1.0, the comprehensive performance is increased by 14.8% -24.2%, and the average performance is increased by 19.5%.
3. The rotary ladder type folded surface baffle structure is characterized in that 1 pitch is formed by 2 baffles, and the positioning and the installation are simpler and more convenient.
4. The fluid passes through the square hole and then alternately generates and breaks away from vortexes at two sides of the square hole, namely a cartoon vortex street, and the flow cross section of the fluid is reduced and then enlarged when the fluid passes through the square hole, thereby generating a Venturi effect. Under the action of the cartoon vortex street and the Venturi effect, the fluid can wash the pipe wall more strongly, so that the heat transfer boundary layer is thinned, and the shell side heat transfer is enhanced. (2) Because the shell pass fluid flows in parallel to the heat exchange tubes, the flow resistance is small, the flow direction of the fluid in the whole tube bundle is not changed, and the flow path is smooth, so that the shell pass fluid resistance loss is small. (3) The fluid strongly washes the pipe wall, so that dirt is not easy to deposit on the pipe wall, and the parallel flow ensures that the flow path is smooth without dead zones, so that the dirt is difficult to deposit, and the dirt is easy to wash away by the fluid when the dirt is deposited more, thereby having a certain self-cleaning effect. (4) The shell pass fluid is changed from the traditional transverse scouring tube bundle into the longitudinal scouring tube bundle, so that the induced vibration of the fluid among the heat exchange tube bundles is effectively controlled when the Re is larger, and the shell pass resistance is reduced.
Drawings
FIG. 1 is a schematic view of the overall structure and the flow direction of the shell-side medium of the present invention;
FIG. 2 is a schematic view of the fixed tube sheet layout of the present invention;
FIG. 3 is a schematic view of the spiral stair type folded baffle structure of the present invention;
FIG. 4: the left-hand side view of figure 3,
FIG. 5: the structure schematic diagram of the square hole baffle plate of the utility model;
FIG. 6: a heat exchange tube bent pipe diagram in which the position C in the tube plate layout area is in collision with the shell side outlet;
FIG. 7: and D position in the tube plate distribution area is in contact with the shell side outlet.
In the figure: 1. the device comprises a tube box 2, a fixed tube plate 3, an outer shell pass shell 4, an inner shell pass shell 5, a spiral stair type folded surface baffle plate 6, a square hole baffle plate 7, a heat exchange tube 8, an outer head cover 9, a shell pass inlet 10 and a shell pass outlet;
5.1, a first folding plate 5.2, a folding panel 5.3 and a second folding plate.
In fig. 3, alpha represents the bending angle of the spiral stair type folding surface baffle plate;
in fig. 3, S represents the degree of bending of the spiral stair type folding surface baffle plate;
in FIG. 3, L represents the cutting percentage of the spiral stair type folding surface baffle plate;
in FIG. 4, b represents the side length of the square hole baffle plate;
in fig. 1: arrow a indicates the direction of shell-side flow, spiral flow;
in fig. 1: arrow B indicates the direction of flow of the inner shell pass media, parallel to the longitudinal flow of the tube bundle.
Detailed Description
The technical solution in the embodiment of the present invention will be further clearly and completely described below with reference to the embodiment of the present invention and the accompanying drawings:
example 1
As shown in fig. 1 to 7, the combined double shell side heat exchanger of the present invention includes a tube box 1, a fixed tube plate 2 and an outer head cover 8; the heat exchanger comprises a shell, wherein a heat exchange tube 7 is arranged in the shell, the shell comprises an outer shell-side shell 3 and an inner shell-side shell 4, the inner shell-side shell 4 is arranged in the outer shell-side shell 3, a first end of the inner shell-side shell 4 is connected with a fixed tube plate 2, a second end of the inner shell-side shell 4 is provided with an opening, and an inner shell-side baffle plate is arranged in the inner shell-side shell 4; a shell pass baffle plate 5 is spirally arranged around the periphery of the inner shell pass shell 4; a shell pass inlet 9 is formed in the first end of the shell pass shell 3, and the shell pass inlet 9 is formed in the fixed tube plate end of the shell pass shell 3; the first end of the inner shell pass shell 4 is provided with a shell pass outlet 10, and the shell pass outlet 10 penetrates through the outer shell pass shell 3. The shell-side outlet 10 is provided at the fixed tubesheet end of the inner shell-side shell 4. The inner shell pass shell 4 is welded and connected with the tube pass side of the fixed tube plate to form an inner shell pass.
As shown in fig. 1 and fig. 3 to 4, the shell-side baffle plate is a spiral-ladder-type folded-surface baffle plate 5, and the spiral-ladder-type folded-surface baffle plate 5 is formed by bending a flat plate twice, and comprises two folded plates arranged in parallel and a folded plate 5.2 which has the same bending angle with the two parallel folded plates.
The flaps comprise a first flap 5.1 and a second flap 5.3.
The adjacent spiral ladder type folded surface baffle plates 5 are arranged in a staggered and reverse mode and are used for forming spiral vortex for shell pass fluid.
As shown in fig. 1 and 3 to 4, the spiral stair type baffle 5 is formed as a large semicircular hole passing over the center line. When two adjacent rotary ladder type folded surface baffle plates are connected, the parts are overlapped, and the installation is more stable. The spiral stair type folded surface baffle plate 5 is semicircular in shape on the cross section, a left semicircle and a right semicircle are sequentially installed during installation, the left semicircle and the right semicircle are placed in opposite directions just, and a spiral vortex is formed when shell pass fluid flows in the left semicircle and the right semicircle. The rotary ladder type folded surface baffle plates 5 are cut in parallel to the central line during processing, and the folded plates can be in close contact connection when the adjacent rotary ladder type folded surface baffle plates 5 are installed. Usually, the rotary ladder type folded baffle plates are positioned and installed by distance pipes, the distance pipes are arranged between the rotary ladder type folded baffle plates, and the distance pipes are arranged in parallel to the heat exchange pipes.
The cutting percentage of the rotary ladder type folded surface baffle plate 5 parallel to the central line is 30-40%.
The bending angle between the folded plate and the folded panel is 30-45 degrees; the bending degree of the folded panel is 0.3-0.5.
The folding degree S of the spiral stair type folding surface baffle plate can be 0.3, 0.4 or 0.5, the cutting percentage L can be 30%, 32%, 33%, 35%, 37% or 40%, and the folding angle alpha can be 30 degrees, 35 degrees, 37 degrees, 40 degrees, 43 degrees or 45 degrees.
The flaps are arranged perpendicular to the outer shell 3.
The combined double-shell pass heat exchanger is provided with a rotary ladder type folded surface baffle plate in the shell pass. The rotary ladder type folded surface baffle plate is formed by bending a large flat plate for 2 times to form 3 planes, namely a first folded plate, a folded panel and a second folded plate, wherein the first folded plate and the second folded plate are vertical to the axis of the shell; the included angle between the folding plate and the first folding plate is the same as the included angle between the folding plate and the second folding plate. Two rotary ladder type folded surface baffle plates form a cycle, and positioning and installation are simpler and more convenient during assembly. The spiral ladder type folded surface baffle plate has two folded surfaces, namely a first folded plate and a second folded plate, on two sides of the spiral ladder type folded surface baffle plate, the characteristics of the folded surfaces of the two adjacent spiral ladder type folded surface baffle plates can be utilized during connection, so that the adjacent two spiral ladder type folded surface baffle plates are in close contact, the triangular area leakage current existing in the common overlapped spiral baffle plate is eliminated, the flow of a main spiral medium is increased, the shell side fluid is more close to continuous spiral current, and simultaneously, the tangential speed and the radial speed of the medium are both obviously increased. The tangential velocity can generate centrifugal force, and radial secondary flow can be formed under the action of the centrifugal force, so that the fluid disturbance is greatly increased, and the boundary layer is thinned; the radial velocity forces the fluid to flow toward the center of the tube bundle, and the effective heat exchange area is the largest, so that the heat transfer performance of the shell side of the heat exchanger is enhanced.
As shown in fig. 1 and 5, the inner shell side baffle is a square hole baffle 6. The square hole baffle plate is arranged perpendicular to the axis of the inner shell pass shell 4.
The combined double-shell pass heat exchanger is provided with a square hole baffle plate in the inner shell pass. The square hole baffle plate is provided with a square hole at the position corresponding to the pipe hole, and has the advantages that: the vortex generating device has the advantages that vortex is alternately generated and separated on two sides of a fluid after the fluid passes through a square hole, so that the vortex generating device is called as a cartoon vortex street, and the flow cross section of the fluid is reduced and then is expanded when the fluid flows through the square hole, so that a Venturi effect is generated. Under the action of the cartoon vortex street and the Venturi effect, the fluid can wash the pipe wall more strongly, so that the heat transfer boundary layer is thinned, and the shell side heat transfer is enhanced. And the shell pass fluid flows in parallel to the heat exchange tubes, so that the flow resistance is low, the flow direction of the fluid in the whole tube bundle is not changed, and the flow path is smooth, so that the shell pass fluid resistance loss is low. And the fluid strongly washes the pipe wall, so that dirt is not easy to deposit on the pipe wall, and the parallel flow is adopted, so that the flow path is smooth, no dead zone is formed, on one hand, the dirt is difficult to deposit, and on the other hand, the dirt is easy to wash away by the fluid when the dirt is deposited more, so that the self-cleaning device has a certain self-cleaning effect.
The square hole of the square hole baffle plate can be a square hole, and the side length b of the square hole can be 26mm and corresponds to the heat exchange tube with the specification of phi 25 mm; the size of the side length b of the square hole can be 20mm, and the size of the corresponding heat exchange tube is phi 19 mm.
As shown in fig. 2 and fig. 6 to 7, the heat exchange tube 7 is bent and formed corresponding to the shell-side outlet 10 so as to be away from the shell-side outlet 10. The heat exchange tubes in the tube plate layout area, which are in contact with the shell side outlet 10, namely the positions C and D, are subjected to appropriate bending forming treatment when penetrating through the heat exchange tubes.
Working process or working principle:
as shown in fig. 1, the shell-side fluid enters the outer shell-side from the shell-side inlet, flows into the inner shell-side from the inner shell-side opening, and then flows out of the heat exchanger through the shell-side outlet.
As shown in fig. 1 and fig. 3 to 4, the shell pass fluid continuously and spirally flows in the outer shell pass space formed by the inner shell pass shell and the spiral ladder-type folded surface baffle plates, and when adjacent spiral ladder-type folded surface baffle plates are connected, the characteristics of the bent surfaces of the adjacent spiral ladder-type folded surface baffle plates can be utilized to make the adjacent spiral ladder-type folded surface baffle plates closely contact with each other, so that the flow of the main spiral medium is increased, and the tangential speed and the radial speed of the medium are obviously increased. Because the tangential velocity can generate centrifugal force, radial secondary flow can be formed under the action of the centrifugal force, the fluid disturbance is greatly increased, and the boundary layer is thinned; the increased radial velocity forces the fluid to flow toward the center of the tube bundle where the effective heat exchange area is maximized, thereby enhancing the heat transfer performance of the heat exchanger shell side.
As shown in fig. 1 and 5, the shell-side fluid flows in from the opening of the inner shell-side, i.e. the outer shell-side is close to the floating tube plate end, the cut of the inner shell-side shell is converged into the inner shell-side space, and a square-hole baffle plate is arranged in the inner shell-side. The shell pass fluid flows longitudinally in parallel with the heat exchange tubes, the flow resistance is small, the flow direction of the shell pass fluid in the whole tube bundle is not changed, and the flow path is smooth, so the loss of the resistance of the shell pass fluid is small. Meanwhile, the fluid alternately generates and breaks away from vortices on both sides of the fluid after passing through the square hole, which is called cartoon vortex street, and the flow cross section of the fluid is reduced and then expanded when passing through the square hole, thereby generating a venturi effect. Under the combined action of the cartoon vortex street and the Venturi effect, the fluid strongly scours the tube wall, so that the heat transfer boundary layer is thinned, and the shell-side heat transfer is enhanced.
The utility model discloses in to the direction of structure and the description of relative position relation, it is right not to constitute like the description from top to bottom all around the utility model discloses a restriction only is the description convenient.
Claims (10)
1. A combined double-shell-pass heat exchanger comprises a shell, wherein a heat exchange tube (7) is arranged in the shell, and the combined double-shell-pass heat exchanger is characterized in that the shell comprises an outer shell-pass shell (3) and an inner shell-pass shell (4), the inner shell-pass shell (4) is arranged in the outer shell-pass shell (3), the first end of the inner shell-pass shell (4) is connected with a fixed tube plate (2), the second end of the inner shell-pass shell (4) is provided with an opening, and an inner shell-pass baffle plate is arranged in the inner shell-pass shell (4); a shell pass baffle plate is spirally arranged around the periphery of the inner shell pass shell (4); the first end of the outer shell pass shell (3) is provided with a shell pass inlet (9), the first end of the inner shell pass shell (4) is provided with a shell pass outlet (10), and the shell pass outlet (10) penetrates through the outer shell pass shell (3).
2. The combined double-shell-pass heat exchanger as recited in claim 1, characterized in that the shell-pass baffle plate is a spiral-stair-type folded-face baffle plate (5), and the spiral-stair-type folded-face baffle plate (5) is formed by bending a flat plate twice, and comprises two parallel folded plates and a folded plate (5.2) having the same folded angle with the two parallel folded plates.
3. The combined double-shell-pass heat exchanger according to claim 2, characterized in that adjacent spiral-trapezoidal folded-surface baffles (5) are arranged in a staggered and opposite manner for forming a spiral vortex for the shell-pass fluid.
4. A combined double shell-side heat exchanger according to claim 2, characterized in that the spiral stair-fold baffle (5) is provided as a large semicircular hole across the centre line.
5. A combined double-shell-pass heat exchanger according to claim 4, characterized in that the cutting percentage of the spiral-staircase-type folded-surface baffle plate (5) parallel to the center line is 30-40%.
6. The combined double-shell-side heat exchanger according to claim 4, wherein the bending angle between the folded plate and the folded panel is 30-45 °; the bending degree of the folded panel is 0.3-0.5.
7. A combined, double-shell-side heat exchanger according to any of claims 1 to 6, characterized in that the flaps are arranged perpendicular to the outer shell-side shell (3).
8. The combined double-shell-side heat exchanger according to claim 7, characterized in that the inner shell-side baffle is a square-hole baffle (6).
9. The combined double-shell-side heat exchanger according to claim 8, characterized in that the square-hole baffle plate is arranged perpendicular to the axis of the inner shell-side shell (4).
10. The combined double-shell-side heat exchanger according to claim 8, wherein the heat exchange tubes (7) are bent and formed corresponding to the shell-side outlet (10) and are free from the shell-side outlet (10).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202120623518.6U CN214537526U (en) | 2021-03-26 | 2021-03-26 | Combined double-shell-pass heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202120623518.6U CN214537526U (en) | 2021-03-26 | 2021-03-26 | Combined double-shell-pass heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN214537526U true CN214537526U (en) | 2021-10-29 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202120623518.6U Active CN214537526U (en) | 2021-03-26 | 2021-03-26 | Combined double-shell-pass heat exchanger |
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| Country | Link |
|---|---|
| CN (1) | CN214537526U (en) |
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2021
- 2021-03-26 CN CN202120623518.6U patent/CN214537526U/en active Active
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