CN210321332U

CN210321332U - Double-torsional-flow heat exchanger

Info

Publication number: CN210321332U
Application number: CN201920992899.8U
Authority: CN
Inventors: 古新; 王通通; 陈卫杰; 方运阁; 宋帅
Original assignee: Zhengzhou University
Current assignee: Zhengzhou University
Priority date: 2019-06-28
Filing date: 2019-06-28
Publication date: 2020-04-14
Anticipated expiration: 2029-06-28

Abstract

The utility model provides a two torsional flow heat exchangers, including casing, a plurality of heat exchange tubes and a plurality of baffling boards of organizing, the heat exchange tube wear to establish with on the baffling board, baffling board slope set up and with the contained angle homogeneous phase of heat exchange tube, the baffling board is the cycle and arranges, including four baffling boards of group in every cycle, including the baffling board of two at least parallels in every group, wherein, preceding two sets of baffling board mutually orthogonal, back two sets of baffling boards also mutually orthogonal, and the line of the nodical baffling board of preceding two sets of each baffling boards is perpendicular with the line of the. The double-torsion flow heat exchanger has the advantages of collecting spiral flow and torsion flow, is small in pressure drop and high in heat exchange coefficient, is convenient to assemble, and has wide application prospect.

Description

Double-torsional-flow heat exchanger

Technical Field

The utility model relates to a indirect heating equipment, specific theory has related to a two torsional flow heat exchangers.

Background

The heat exchanger is widely applied to various industrial fields such as chemical industry, petroleum, energy, power, metallurgy, refrigeration, transportation and the like, has the main functions of completing heat exchange and waste heat utilization in the technical process, and has remarkable influences on investment, energy consumption, safe and economic operation, pollutant emission and the like of the industrial process due to the advantages and disadvantages of heat transfer and fluid flow performance. The most shell-and-tube heat exchangers are used in the heat exchanger, the application technology is the most mature, the arch-shaped baffle plate heat exchanger accounts for about 70% of the total amount of the shell-and-tube heat exchanger, but the defects of large flow resistance, high energy consumption and the like are not fundamentally improved.

Researchers in the last 60 th century proposed the concept of a continuous spiral baffle plate heat exchanger, which can eliminate the shell pass flow dead zone of the arch baffle plate heat exchanger to a great extent, so that the flow line of fluid is smoother, the shell pass pressure drop of the shell-and-tube heat exchanger is effectively reduced, the heat exchange coefficient is obviously improved under the same pump power, but the continuous spiral baffle plate heat exchanger has the problems of large difficulty in processing and mounting baffle plates and difficult matching of heat exchange tubes and baffle plates; aiming at the problems, the scientists Lutcha and Nemcansky of the former Czeslex national chemical engineering equipment research institute put forward a quarter-spiral baffle structure for the first time in the 90 s, a fan-shaped plate replaces a continuous spiral baffle plate, spiral flow is generated by means of an inclined overlapping arrangement method of the baffle plate, discontinuity exists at the overlapping position of the fan-shaped plate in the structure, a triangular leakage area is formed, the heat exchange performance of a heat exchanger is reduced, the shell side pressure drop and the heat transfer coefficient of the heat exchanger are lower than those of an arched baffle plate heat exchanger in large flow, and the heat exchange efficiency is low.

In recent years, chinese patent CN201621266057.7 discloses a shell-and-tube heat exchanger with trapezoidal-like inclined baffle plates, wherein the trapezoidal-like inclined baffle plates are orthogonally arranged to change the flow direction of fluid in a shell, improve the turbulent flow effect, and improve the average flow velocity and turbulent flow degree of shell-side fluid. Chinese patent CN201810650108.3 discloses a shell-and-tube heat exchanger with a twisted flow, which uses a dropper to replace a conventional straight tube to effectively improve the heat exchange coefficient of the heat exchanger, but the dropper is a special tube which is relatively complex to process and install and is not beneficial to industrial application.

In order to solve the above problems, people are always seeking an ideal technical solution.

Disclosure of Invention

The utility model aims at the not enough of prior art to a two torsional flow heat exchangers are provided.

In order to realize the purpose, the utility model discloses the technical scheme who adopts is:

the heat exchange tubes are arranged on the baffle plates in a penetrating mode, included angles of the baffle plates and the heat exchange tubes are the same, the baffle plates are arranged in a periodic mode and comprise four groups of baffle plates in each period, each group of baffle plates comprises at least two parallel baffle plates, the front two groups of baffle plates are orthogonal to each other, adjacent sides of the front two groups of baffle plates are in contact, the rear two groups of baffle plates are also orthogonal to each other, adjacent sides of the rear two groups of baffle plates are in contact, and a connecting line of intersection points of the front two groups of baffle plates is perpendicular to a connecting line of intersection points of the rear two groups of baffle plates.

Based on the above, the included angle between the baffle plate and the heat exchange tube is theta, theta is more than or equal to 20 degrees and less than or equal to 70 degrees, and the axial distance between the front two groups of baffle plates and the rear two groups of baffle plates is

Wherein R is the radius of the shell.

Based on the above, after the plurality of groups of rectangular plates are fixed according to the arrangement mode of the baffle plates, the annular cutters with the same radius as the shell are used for cutting to obtain a plurality of groups of baffle plates; wherein the height of the rectangular plate is

The rectangleThe width of the plate is larger than that of the rectangular plate with the radius of the shell being 5-6 mm.

Based on the above, the distance between the baffle plates in each group is

Wherein h is the tube pitch of each heat exchange tube.

The utility model discloses relative prior art has substantive characteristics and progress, specific theory, the utility model provides a two advantage that twist current heat exchanger set spiral flows and twist current separately, and coefficient of heat transfer is high, the pressure reduces, the assembly is simple and convenient, has wide application prospect. Specifically, fluid flows obliquely near the central axis of the shell in the heat exchanger, so that the heat exchanger has the effects of strongly washing the tube bundle by the oblique flow, thinning a thermal boundary layer and improving a heat exchange coefficient; the fluid on the outer side flows spirally, so that the flow field distribution is uniform, the flow resistance is small, the heat exchange coefficient of the heat exchanger can be improved, and the pressure drop of the heat exchanger can be effectively reduced. The numerical simulation research shows that when the shell pass flow is 1.37 Kg/s-4.12 Kg/s, the shell pass pressure drop of the double-torsion flow heat exchanger is reduced by 50-59% compared with that of an arch baffle plate heat exchanger and is reduced by 17.9-22.3% compared with that of a continuous spiral baffle plate heat exchanger; under the same Reynolds number, the shell-side heat exchange coefficient of the double-torsional flow heat exchanger is improved by 31.9-49.3% compared with that of a spiral flow heat exchanger, and the comprehensive performance is improved by 12.2-25.5%.

Drawings

Fig. 1 is a schematic structural diagram of the present invention.

Fig. 2 is a schematic view of the housing of the present invention.

Fig. 3 is a schematic view of the baffle arrangement structure of the present invention.

Fig. 4 is a side view schematic of fig. 3.

Fig. 5 is a pressure drop comparison of the segmental baffle, helical baffle and the dual torsional flow heat exchanger of the present invention.

Fig. 6 is a comparison of the heat transfer coefficients of the helical baffle and the dual torsional flow heat exchanger of the present invention.

Fig. 7 is a comparison of the overall performance of the helical baffle and the dual torsional flow heat exchanger of the present invention.

Fig. 8 is a diagram showing the effect of the shell-side fluid flow of the present invention.

In the figure: 1. a housing; 2. a baffle plate; 3. a heat exchange pipe; 21. a first set of baffles; 22. a second set of baffles; 23. a third set of baffles; 24. and a fourth set of baffles.

Detailed Description

The technical solution of the present invention will be described in further detail through the following embodiments.

As shown in fig. 1 to 4, a double-torsional-flow heat exchanger includes a shell 1, a plurality of heat exchange tubes 3 and a plurality of groups of baffle plates 2, the heat exchange tubes 3 are arranged on the baffle plates 2 in a penetrating manner, the baffle plates 2 are arranged in an inclined manner and have the same included angle with the heat exchange tubes 3, the baffle plates 2 are arranged in a periodic manner, each period includes four groups of baffle plates 2, each group includes four parallel baffle plates 2, wherein the first group of baffle plates 21 and the second group of baffle plates 22 are orthogonal to each other and have adjacent side edges in contact, the third group of baffle plates 23 and the fourth group of baffle plates 24 are orthogonal to each other and have adjacent side edges in contact, and the connecting line of the intersection points of the first two. In other embodiments, two, three, five, six, or more baffles may be provided per set, as desired.

The double-torsion flow heat exchanger integrates the advantages of spiral flow and torsion flow, greatly simplifies the processing technology, is more convenient to assemble, can improve the heat exchange coefficient of the heat exchanger, and can effectively reduce the pressure drop of the heat exchanger.

Furthermore, the included angle between the baffle plate 2 and the heat exchange tube 3 is theta, the included angle theta can be selected from other values of 20 degrees, 70 degrees, 45 degrees or 20 degrees to 70 degrees, and the axial distance between the front two groups of baffle plates and the rear two groups of baffle plates is theta

Wherein R is the radius of the shell.

Furthermore, each group of baffle plates 2 can be prepared by fixing a plurality of groups of rectangular plates according to the arrangement mode of the baffle plates and then connecting the baffle plates with the shell halfCutting by annular cutters with the same diameter to obtain a plurality of groups of baffle plates; wherein the height of the rectangular plate is

The width of the rectangular plate is larger than that of the rectangular plate with the radius of the shell being 5-6 mm. The arc edge of the baffle plate is tangent with the inner wall of the shell, and the baffle plate can also play a self-supporting role.

Further, the distance between the baffle plates in each group is

Wherein h is the tube pitch of each heat exchange tube 3.

The numerical simulation research results show in fig. 5-7, and as can be seen from fig. 5-7, when the shell pass flow is 1.37 Kg/s-4.12 Kg/s, the shell pass pressure drop of the double-twisted-flow heat exchanger is reduced by 50% -59% compared with that of the bow-shaped baffle plate heat exchanger, and is reduced by 17.9% -22.3% compared with that of the continuous spiral baffle plate heat exchanger; under the same Reynolds number, the shell pass heat exchange coefficient of the double-torsional flow heat exchanger is improved by 31.9-49.3 percent compared with that of a spiral flow heat exchanger, and the comprehensive performance (Nu/f)^1/3) The improvement is 12.2 to 25.5 percent.

Referring to fig. 8, it can be seen from fig. 8 that the fluid in the heat exchanger flows obliquely near the central axis of the shell, and has the effects of strongly washing the tube bundle, thinning the thermal boundary layer and improving the heat exchange coefficient by the oblique flow; the fluid on the outer side flows spirally, so that the flow field distribution is uniform, the flow resistance is small, the heat exchange coefficient of the heat exchanger can be improved, and the pressure drop of the heat exchanger can be effectively reduced.

Finally, it should be noted that the above embodiments are only used for illustrating the technical solutions of the present invention and not for limiting the same; although the present invention has been described in detail with reference to preferred embodiments, it should be understood by those skilled in the art that: the invention can be modified or equivalent substituted for some technical features; without departing from the spirit of the present invention, it should be understood that the scope of the claims is intended to cover all such modifications and variations.

Claims

1. The utility model provides a two torsional flow heat exchangers, includes casing, a plurality of heat exchange tube and a plurality of group baffling board, its characterized in that: the heat exchange tubes penetrate through the baffle plates, the baffle plates are obliquely arranged and have the same included angle with the heat exchange tubes, the baffle plates are periodically arranged, each period comprises four groups of baffle plates, each group comprises at least two parallel baffle plates, the front two groups of baffle plates are orthogonal to each other, the adjacent side edges of the front two groups of baffle plates are in contact with each other, the rear two groups of baffle plates are orthogonal to each other, the adjacent side edges of the rear two groups of baffle plates are in contact with each other, and the connecting line of the intersection points of the front two groups of baffle plates is.

2. The dual torsional flow heat exchanger of claim 1, wherein: the included angle between the baffle plate and the heat exchange tube is theta, theta is more than or equal to 20 degrees and less than or equal to 70 degrees, and the axial distance between the front two groups of baffle plates and the rear two groups of baffle plates is

Wherein R is the radius of the shell.

3. The dual-twisted-flow heat exchanger of claim 1 or 2, wherein: after a plurality of groups of rectangular plates are fixed according to the arrangement mode of the baffle plates, cutting the rectangular plates by an annular cutter with the same radius as the shell to obtain a plurality of groups of baffle plates; wherein the rectangular plate has a height of π R-

The width of the rectangular plate is 5-6 mm larger than the radius of the shell; wherein theta is an included angle between the baffle plate and the heat exchange tube, and R is the radius of the shell.

4. The dual torsional flow heat exchanger of claim 3, wherein: the distance between every two baffle plates in each group is

Wherein h is the tube pitch of each heat exchange tube.