CN212620276U - Heat exchange device - Google Patents

Abstract

The utility model relates to a heat exchange device, including casing and a plurality of hollow tube, a plurality of hollow tubes are arranged in the inside of casing is formed with first clearance between the inner wall of casing and its adjacent hollow tube, be formed with the second clearance that communicates with first clearance between a plurality of hollow tubes, be equipped with first entry and first export on the casing to and second entry and second export, first entry and first export with a plurality of hollow tube intercommunication, second entry and second export with first clearance intercommunication, its characterized in that: the positioning plate is perpendicular to the axial direction of the hollow pipe, a plurality of through holes are formed in the positioning plate, the hollow pipe at least penetrates through part of the through holes, and the through holes comprise overflowing holes for allowing shell pass fluid in the second gap to pass through. An object of the utility model is to provide a when increasing heat exchanger's total heat transfer coefficient, can reduce the heat exchange device of fluid flow resistance again.

Description

Heat exchange device

Technical Field

The utility model relates to a heat exchange device, especially a heat exchange device.

Background

Heat transfer refers to the transfer of energy due to temperature differences, also known as heat transfer. Many heat transfer-related problems are involved in industrial sectors, such as energy, space navigation, power, machinery, and other sectors, as well as in agricultural and environmental protection sectors. The chemical industry is particularly concerned with heat transfer because many processes and unit operations in chemical production require heating and cooling. At present, a heat exchange device is indispensable equipment for realizing heat exchange and transfer in the production process in the fields of chemical engineering and the like.

Chinese patent CN201387261Y discloses a bidirectional anticorrosion type teflon column tube heat exchanger, which is composed of a cylinder and a plurality of teflon heat exchange tubes located inside the cylinder, wherein the inner wall of the cylinder has a teflon coating. The heat exchanger can realize heat exchange for two strong corrosive media at the same time, and when the two materials A and B are heat exchange media, the material A is used for heating the material B or the material B is used for cooling the material A, so that the purposes of energy conservation and consumption reduction are achieved.

In the prior art, in order to increase the heat transfer coefficient of the heat exchanger, a baffle is arranged in the cylinder, when fluid flows between the heat exchange tubes, the flow velocity and the flow direction are continuously changed, when the Reynolds index Re of the fluid is more than 100, turbulent flow can be achieved, and the convection heat transfer coefficient is increased. However, due to the action of the baffle, when the liquid flows axially in the cylinder, the liquid can only flow between the baffle and the gap of the inner wall of the shell, and the flow resistance of the liquid is increased at the moment, so that the total heat transfer coefficient of the heat exchanger is influenced.

SUMMERY OF THE UTILITY MODEL

The utility model aims to achieve provides a heat exchange device which can reduce the fluid flow resistance while increasing the total heat transfer coefficient of the heat exchanger.

In order to achieve the above purpose, the utility model adopts the following technical scheme: a heat exchange device comprises a shell and a plurality of hollow pipes, wherein the hollow pipes are arranged in the shell, a first gap is formed between the inner wall of the shell and the adjacent hollow pipes, a second gap is formed between the hollow pipes, the first gap is communicated with the second gap, a first inlet for pipe-side fluid to flow in and a first outlet for pipe-side fluid to flow out are arranged on the shell, a second inlet for shell-side fluid to flow in and a second outlet for shell-side fluid to flow out are arranged on the shell, the first inlet and the first outlet are communicated with the hollow pipes, and the second inlet and the second outlet are communicated with the first gap, and the heat exchange device is characterized in that: the positioning plate is perpendicular to the axial direction of the hollow pipe, a plurality of through holes are formed in the positioning plate, the hollow pipe at least penetrates through part of the through holes, and the through holes contain overflowing holes for shell side fluid in the second gap to pass through.

The heat exchanger of the utility model is a typical dividing wall type shell-and-tube heat exchanger, and the heat exchanger is characterized in that cold fluid and hot fluid are separated by a solid wall surface and are not mixed with each other, and heat exchange is carried out through a dividing wall. After entering the plurality of hollow tubes through the first inlet, the tube-side fluid flows out of the hollow tubes from the first outlet, the shell-side fluid flows between the first gap and the second gap through the second inlet and then flows out of the shell through the second outlet, and the process realizes the heat exchange process of the two fluids. In order to ensure that a plurality of hollow pipes can be fully contacted with shell side fluid to complete heat exchange, gaps with fixed distances are required among the hollow pipes. The utility model discloses in, the inside locating plate that has a plurality of through-holes that is equipped with of casing, hollow tube pass part the through-hole for be formed with the second clearance between the hollow tube.

The fluid has viscosity, and the internal friction existing during flowing is the root cause of the fluid resistance. When the shell-side fluid flows in the shell, because of the existence of the baffle, resistance which hinders the fluid flow is generated between the shell-side fluid and the baffle. The utility model discloses in, set up the discharge orifice that supplies shell side fluid to pass through on the locating plate, partial shell side fluid can flow through in the discharge orifice, can reduce the energy of shell side fluid at the in-process consumption that flows, reduces energy loss.

Further, the overflowing holes comprise first overflowing holes, the hollow pipe penetrates through the first overflowing holes, and a gap for allowing shell-side fluid to axially pass through is formed between the inner wall of each first overflowing hole and the outer wall of the hollow pipe penetrating through the first overflowing hole.

The overflowing hole comprises a first overflowing hole through which the hollow pipe can pass, and a gap is formed between the outer wall of the hollow pipe and the inner wall of the first overflowing hole and is used for allowing shell-side fluid to axially pass through. By the design, the resistance loss of the shell side fluid is reduced, and meanwhile, a stable second gap is formed between the hollow pipes, so that the heat exchange function of the heat exchanger is ensured.

Further, the overflowing hole is a circumscribed polygon of the hollow pipe.

First overflowing hole is the circumscribed polygon of pipe, and first overflowing hole can stabilize the hollow tube so, prevents that the hollow tube is not hard up and bump, and simultaneously, first overflowing hole also has a lot of spaces that do not occupied by the pipe, and when shell side fluid was at the inside axial of casing flow, not only can pass through first clearance, can also pass through the space that does not occupy by the hollow tube in the overflowing hole, consequently, increased the cross-sectional area that shell side fluid flows, reduced flow resistance and energy loss, guaranteed going on of heat exchange.

Furthermore, the through hole comprises a positioning hole, the hollow pipe penetrates through the positioning hole, the positioning hole is distributed at one end of the positioning plate, the first overflowing holes are distributed at the rest positions of the positioning plate, and the two adjacent positioning plates are arranged in the shell in a staggered mode.

The locating hole has on the locating plate, so the design can guarantee the holding that a plurality of hollow tubes can stabilize in the casing, prevent between the hollow tube collision each other and lead to its damage. The positioning holes and the first overflowing holes are distributed on the positioning plate according to a certain arrangement mode, specifically, the overflowing holes are distributed at one end of the positioning plate, the positioning holes are distributed at the rest positions of the positioning plate, and two adjacent positioning plates are arranged in a staggered mode. By the design, shell-side fluid flows in a baffling manner between the shell and the hollow pipe along the positioning plate, so that the convection heat transfer coefficient of the heat exchanger can be increased.

Further, the cross section of the positioning plate is circular, the edge of the positioning plate and the inner wall of the shell form a third annular gap, the height of the third annular gap is recorded as H, the inner diameter of the shell is recorded as D, and the inner diameter of the shell satisfies the following conditions: H/D is more than or equal to 0.05 and less than or equal to 0.1.

The edge of locating plate and the inner wall of casing form annular third clearance, and the height H in third clearance satisfies with the internal diameter D of casing: H/D is more than or equal to 0.05 and less than or equal to 0.1. While H/D < 0.05 or H/D > 0.1 is not good for heat transfer.

Furthermore, the edge of the positioning plate extends to the inner wall of the shell in the first gap, a plurality of openings are formed in the positioning plate, and the openings are located in the first gap.

The edge of locating plate extends to the inner wall of casing, the locating plate is seted up the trompil in the first clearance. So design, guaranteed the stability of locating plate in casing inside, and then avoided the hollow tube to take place to rock because of rocking of locating plate. And the opening of the positioning plate at the position of the first gap can allow the shell pass fluid to flow through, so that the normal flow of the shell pass fluid in the shell is ensured.

Further, the overflow hole comprises a second overflow hole which only allows the shell side fluid to axially pass through.

The flow holes comprise second flow holes which only allow the shell-side fluid to pass through axially, i.e. the hollow tube does not pass through the second flow holes. By the design, the phenomenon that the shell pass fluid is blocked due to the existence of the positioning plate is avoided, and the circulation of the shell pass fluid in the shell is further ensured.

Further, the cross section of the positioning plate is in a segmental shape, the height of a cut arch is marked as A, the inner diameter of the shell is marked as D, and the space between A and D satisfies the following conditions: A/D is more than or equal to 0.1 and less than or equal to 0.4.

The cross-section of locating plate is the circle and lacks the shape, and the bow-shaped height of cutting off is marked as A and is satisfied between D with the internal diameter of casing: A/D is more than or equal to 0.1 and less than or equal to 0.4. Too large or too small a to D ratio is detrimental to heat transfer.

Further, the distance between two adjacent locating plates is marked as h, the inner diameter of the shell is marked as D, and the distance between h and D satisfies: h/D is more than or equal to 0.2 and less than or equal to 1.

The ratio of the distance h between two adjacent positioning plates to the inner diameter D of the shell meets the following requirements: h/D is more than or equal to 0.2 and less than or equal to 1. If h/D is less than 0.2, the manufacturing and the maintenance are not convenient, and simultaneously, the resistance is also larger; if h/D > 1, it is difficult for the fluid to flow vertically through the tube bundle, resulting in a reduced convection coefficient.

Further, the central connecting line of the adjacent through holes is a regular polygon.

When the shell-side fluid flows in the first gap and the second gap, the heat transfer condition is complicated due to the influence between the hollow tubes, wherein the arrangement mode of the hollow tubes influences the convection heat transfer coefficient. Generally, the arrangement mode of the hollow pipes is a regular polygon shape, which can not only strengthen the convection heat transfer coefficient, but also facilitate the calculation of the convection coefficient.

Drawings

The present invention will be further explained with reference to the accompanying drawings:

fig. 1 is a schematic view of a heat exchange device according to a first embodiment of the present invention;

fig. 2 is a partial cross-sectional view of a heat exchange device according to a first embodiment of the present invention;

fig. 3 is a partially enlarged view of a heat exchange device according to a first embodiment of the present invention;

fig. 4 is a schematic cross-sectional view of a positioning plate according to a first embodiment of the present invention;

fig. 5 is a schematic view illustrating an influence of a plate pitch of a positioning plate on a shell-side fluid according to a first embodiment of the present invention;

fig. 6 is a schematic view of a shell-side fluid flowing transversely through a hollow tube bundle according to a first embodiment of the present invention;

fig. 7 is a schematic view of a heat exchange device according to a second embodiment of the present invention;

fig. 8 is a schematic cross-sectional view of a positioning plate according to a second embodiment of the present invention;

fig. 9 is a schematic cross-sectional view of a positioning plate and a heat exchange device according to a third embodiment of the present invention;

fig. 10 is a schematic cross-sectional view of a positioning plate and a heat exchange device according to a fourth embodiment of the present invention.

Detailed Description

In order to make the aforementioned objects, features and advantages of the present invention more clearly understood, the present invention will be described in further detail with reference to the accompanying drawings and detailed description. It should be noted that the embodiments and features of the embodiments of the present application may be combined with each other without conflict.

In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, however, the present invention may be practiced in other ways than those specifically described herein, and therefore the scope of the present invention is not limited by the specific embodiments disclosed below.

The first embodiment is as follows:

as shown in fig. 1, a schematic diagram of a heat exchange device 1 includes a housing 2, and the housing 2 is provided with a first inlet 3 for a tube-side fluid to flow in and a first outlet 4 for the tube-side fluid to flow out, and a second inlet 5 for a shell-side fluid to flow in and a second outlet 6 for the shell-side fluid to flow out. As shown in fig. 2, a partial cross-sectional view of the heat exchanger and a partial enlarged view of the heat exchanger in fig. 3, a plurality of hollow tubes 8 are installed in the heat exchanger 1, and a tube-side fluid enters the heat exchanger through the first inlet 3, is distributed to enter each hollow tube 8, flows through the hollow tubes 8, and flows out through the first outlet 4. Shell side fluid enters through a second inlet 5 and exits through a second outlet 6. The shell side fluid and the tube side fluid are two fluids with different temperatures, and the fluids respectively flow on two sides of the wall surface of the hollow tube to exchange heat. In order to enable each hollow tube 8 to perform a heat exchange process, the hollow tubes 8 are spaced apart from each other to form a second gap 10, and in order to prevent the shell-side fluid from being blocked when entering the interior of the housing 2 from the second inlet 5, a first gap 9 is formed between the hollow tubes 8 and the inner wall surface of the housing 2, so as to ensure the normal flow of the shell-side fluid, and further ensure the heat exchange function of the heat exchange device 1.

Simultaneously, in order to prevent that heat exchange device 1 from getting into the inside of casing 2 from its access & exit when idle, increasing and examining and repairing abluent degree of difficulty, the utility model provides a four access & exits of heat exchange device 1 dispose nut 7 respectively, and nut 7 passes through the thread tightening with the access & exit. Of course, it will be appreciated by those skilled in the art that the inlet and outlet of the heat exchange device 1 may be designed differently according to the requirements.

Further, in order to form the second gap 10, a plurality of positioning plates 11 are installed inside the housing 2, and the positioning plates 11 have through holes, through which the hollow tubes 8 pass, so that the hollow tubes 8 have a certain distance therebetween to form the second gap 10. The existence of the positioning plate 11 enables the flow speed and the flow direction of the shell-side fluid to be changed constantly, and the shell-side fluid can easily achieve turbulent flow when flowing inside the shell 2, so that the convection heat transfer coefficient of the heat exchange device 1 is increased.

As is well known, the fluid has viscosity, and there is internal friction when flowing, which is a source of fluid resistance. The presence of the locating plate 11 increases the flow resistance of the shell-side fluid. The utility model discloses in, set up the discharge orifice that supplies shell side fluid to pass through on the locating plate 11, partial shell side fluid can flow through in the discharge orifice, can reduce the energy of shell side fluid at the in-process consumption that flows, reduces energy loss.

In order to ensure that the second gap 10 has a space for the shell-side fluid to flow sufficiently, and to avoid the shell-side fluid from being blocked when flowing inside the housing 2, which affects the heat exchange function of the heat exchange device 1, as shown in the cross section of the positioning plate in fig. 4, the overflowing hole has a first overflowing hole 13 through which the hollow tube 8 can pass, and at this time, a gap is formed between the outer wall of the hollow tube 8 and the inner wall of the first overflowing hole 13, through which the shell-side fluid can pass axially. By the design, the second gap 10 is formed between the hollow pipes 8, so that the resistance loss of the shell-side fluid is reduced, the flow area of the shell-side fluid is increased, the flow resistance of the fluid is reduced, and the heat exchange function of the heat exchanger is ensured.

And first overflow hole 13 is the circumscribed polygon of hollow tube 8, so first overflow hole 13 can stabilize hollow tube 8, prevent that hollow tube 8 from becoming flexible and colliding, simultaneously, first overflow hole 13 also has a lot of spaces not occupied by hollow tube 8, when shell side fluid is at the inside axial flow of casing 2, can pass through the space not occupied by hollow tube 8 in first overflow hole 13, consequently, increased shell side fluid flow's cross-sectional area, reduce flow resistance and energy loss, guaranteed going on of heat exchange. Of course, those skilled in the art will appreciate that the shape of the first overflow aperture 13 is not just a square as shown in fig. 4, as long as the polygonal shape of the hollow tube 8 is satisfied.

The positioning plate 11 has a positioning hole 15, and the inner diameter of the positioning hole 15 is approximately the same as the outer diameter of the hollow tube 8. And the hollow tube 8 can pass through the positioning hole 15 to form the second gap 10. Further, the positioning holes 15 and the first overflowing holes 13 are respectively distributed at two ends of the positioning plate 11, and meanwhile, two adjacent positioning plates 11 are distributed in a staggered manner at a certain angle inside the housing 2, as shown in fig. 2, two adjacent positioning plates 11 are overlapped after rotating 180 ° inside the housing 2. Of course, it should be understood by those skilled in the art that two adjacent positioning plates 11 may be staggered at any angle. By such design, the shell-side fluid flows between the shell 2 and the hollow pipe 8 in a baffling manner along the positioning plate 11, the flow speed and the flow direction of the shell-side fluid are constantly changed, and the convection heat transfer coefficient of the heat exchange device 1 can be increased.

As shown in the enlarged partial view of the heat exchange device in fig. 3, in order to ensure the heat transfer coefficient of the heat exchange device 1, the edge of the circular positioning plate 11 forms a third annular gap with the inner wall of the shell 2, the height of the third annular gap is denoted as H, the inner diameter of the shell 2 is denoted as D, and the inner diameter between H and D satisfies: H/D is more than or equal to 0.05 and less than or equal to 0.1 so as to ensure the heat transfer of the heat exchange device 1.

Furthermore, the overflow opening comprises a second overflow opening 14, wherein the second overflow opening 14 only allows the shell-side fluid to pass through axially, i.e. the hollow tube 8 does not pass through the second overflow opening 14. So design avoids shell side fluid to take place to block up the detention phenomenon because of the existence of locating plate 11, and further assurance shell side fluid is at the inside circulation of casing 2, and can effectively utilize locating plate 11, furthest's guide shell side.

The distance h between the two adjacent positioning plates 11 is 0.2-1 times of the inner diameter D of the shell 2. As shown in fig. 5, the influence of the plate spacing of the positioning plate on the shell-side fluid is schematically shown, (a) the plate spacing is too large, and at this time, the shell-side fluid is difficult to vertically flow through the hollow tube, so that the convection heat transfer coefficient is reduced; (c) the distance between the plates is too small, so that the manufacturing and the maintenance are inconvenient, and the resistance is also large; (b) at normal plate spacing, where the shell-side fluid is able to pass vertically through the hollow tubes, the heat transfer coefficient of the heat exchange device 1 is maximized.

When the shell-side fluid flows through the tube bundle transversely, the heat transfer condition is complex due to the influence between the tubes, and the convection heat transfer coefficient is influenced by the geometrical conditions of the tube bundle, such as the tube diameter, the tube spacing, the number of rows and the arrangement mode. As shown in fig. 6, in which the shell-side fluid flows transversely through the hollow tube bundle, the hollow tubes 8 are generally arranged in the form of (a) regular triangles, (b) corner regular triangles, (c) squares, and (d) corner squares.

Example two:

compared with the first embodiment, the difference of the first embodiment is that, as shown in the schematic diagram of a heat exchange device in fig. 7, the edge of the positioning plate 11 extends to the inner wall of the housing 2, so that the stability of the positioning plate 11 inside the housing 2 is ensured, and the situation that the hollow tube 8 shakes due to the shaking of the positioning plate 11 is avoided. As shown in the cross-sectional view of the positioning plate of fig. 8, the positioning plate 11 is provided with a positioning hole 15, a first overflowing hole 13 and a second overflowing hole 14, and the positioning plate 11 is provided with an oval opening 17 in the first gap 9 for the shell-side fluid to flow through, so as to ensure the normal flow of the shell-side fluid in the housing 2. Of course, those skilled in the art will appreciate that the shape of the openings 17 is not limited to an elliptical configuration, and that the number of openings 17 may be specifically set according to the flow rate of the shell-side fluid.

Example three:

compared with the first embodiment, the difference of the present embodiment is that, as shown in the schematic cross-sectional view of the positioning plate and the heat exchange device in fig. 9, the positioning plate 11 is a segment, and the height a of the cut-off segment is about 10% -40% of the inner diameter D of the shell 2, and if the height of the cut-off segment is too high or too low, it is not good for the heat transfer of the heat exchange device.

Example four:

compared with the first embodiment, the difference of this embodiment is that, as shown in the schematic cross-sectional view of the positioning plate and the heat exchanging device in fig. 10, the positioning plate 11 may have the shape of (a) a ring-disk-shaped positioning plate and (b) an arc-shaped positioning plate, and the positioning plate 11 of these two structures may cause the shell-side fluid to deflect inside the shell, which affects the heat transfer coefficient of the heat exchanging device 1.

The preferred embodiments of the present invention have been described in detail, but it should be understood that various changes and modifications can be made by those skilled in the art after reading the above teaching of the present invention. Such equivalents are intended to fall within the scope of the claims appended hereto.

Claims (10)

1. A heat exchange device comprises a shell and a plurality of hollow pipes, wherein the hollow pipes are arranged in the shell, a first gap is formed between the inner wall of the shell and the adjacent hollow pipes, a second gap is formed between the hollow pipes, the first gap is communicated with the second gap, a first inlet for pipe-side fluid to flow in and a first outlet for pipe-side fluid to flow out are arranged on the shell, a second inlet for shell-side fluid to flow in and a second outlet for shell-side fluid to flow out are arranged on the shell, the first inlet and the first outlet are communicated with the hollow pipes, and the second inlet and the second outlet are communicated with the first gap, and the heat exchange device is characterized in that: the hollow pipe is characterized by further comprising at least one positioning plate, the positioning plate is perpendicular to the axial direction of the hollow pipe, a plurality of through holes are formed in the positioning plate, the hollow pipe at least penetrates through part of the through holes, and the through holes comprise through holes for allowing shell pass fluid in the second gap to axially pass through.

2. The heat exchange device according to claim 1, wherein the overflowing holes comprise first overflowing holes, the hollow pipes penetrate through the first overflowing holes, and gaps for shell-side fluid to axially pass through are formed between inner walls of the first overflowing holes and outer walls of the hollow pipes penetrating through the first overflowing holes.

3. The heat exchange device of claim 2, wherein the first overflow aperture is a circumscribed polygon of the outer wall of the hollow tube.

4. The heat exchange device according to claim 2, wherein the through-hole includes a positioning hole through which the hollow tube passes, the positioning hole being distributed at one end on the positioning plate, the first overflowing holes being distributed at remaining positions on the positioning plate, adjacent two of the positioning plates being staggered inside the housing.

5. The heat exchange device according to claim 1, wherein the positioning plate is circular in cross section, and the edge of the positioning plate forms a third annular gap with the inner wall of the shell, the height of the third annular gap is denoted by H, the inner diameter of the shell is denoted by D, and the H and D satisfy: H/D is more than or equal to 0.05 and less than or equal to 0.1.

6. The heat exchange device of claim 1, wherein an edge of the positioning plate extends to an inner wall of the housing within the first gap, and the positioning plate defines a plurality of openings therein, the openings being located within the first gap.

7. A unit according to claim 2 or claim 3 in which the flow-through holes comprise second flow-through holes which only and only allow axial passage of shell-side fluid.

8. The heat exchange device according to claim 1, wherein the positioning plate is a segmental positioning plate, the height of a cut-off arch is marked as A, the inner diameter of the shell is marked as D, and the inner diameter between A and D satisfies the following conditions: A/D is more than or equal to 0.1 and less than or equal to 0.4.

9. The heat exchange device according to claim 1, wherein the distance between two adjacent positioning plates is recorded as h, the inner diameter of the shell is recorded as D, and the following relationship is satisfied between h and D: h/D is more than or equal to 0.2 and less than or equal to 1.

10. The heat exchange device of claim 1, wherein the line connecting the centers of the adjacent through holes is a regular polygon.

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