CN201059887Y - Rectangular tube bundle heat exchanger supported by swirl fins - Google Patents

Abstract

The utility model discloses a rectangular tube bundle heat exchanger supported by swirl sheets, which comprises a cylinder body, a plurality of rectangular tube bundles with different widths and parallel to each other arranged in the cylinder body and along the axial direction of the cylinder body, and placed in the rectangular tube bundle. The tube sheets at both ends, the upper and lower heads connected to the tube sheets at both ends, and the inlet and outlet interfaces between the tube side and the shell side of the heat exchanger. It is characterized in that: in the tube of the rectangular tube bundle, the swirl fins are roughly evenly spaced along the axial and transverse directions, the centerline of the swirl fins is in the same direction as the centerline of the rectangular tube bundle, and the direction of rotation of the adjacent swirl fins is opposite. The tubes of the tube bundle are also roughly evenly spaced with swirl fins along the axial and transverse directions. The swirl fins can not only effectively support and fix the rectangular tube bundle between plates, but also strengthen the heat transfer of the rectangular tube bundle. The heat exchanger of the utility model can be popularized and applied in industrial gas heat exchange.

Description

Rectangular tube bundle heat exchanger supported by swirl fins

technical field

The utility model relates to a heat exchanger, in particular to a rectangular tube bundle heat exchanger supported by swirl sheets.

Background technique

There are various types of shell-and-tube heat exchangers widely used in industry, such as the traditional shell-and-tube heat exchanger with bow-shaped baffles supporting ordinary smooth tube bundles, and the one with hollow ring screens and swirl screens to support scaling tube bundles. Enhanced heat transfer shell-and-tube heat exchangers (Chinese patents: ZL200420015378.0 and ZL200420088741.1), etc. There are also a variety of plate heat exchangers, such as flat plate heat exchangers and corrugated plate heat exchangers.

The advantages of shell and tube heat exchangers are good mechanical sealing and high pressure bearing capacity. The seal between the cold and hot flow channels on the tube side and the shell side is only the welding or expansion joint seal between the tubes at both ends of the tube bundle and the tube sheet. , so it can be applied to many high-temperature and high-pressure heat exchange occasions, and the heat transfer tube flow area of the tube side and the shell side is large, not easy to be blocked by dirt, easy to clean, the flow resistance of the fluid is low, and the operation of the heat exchanger The energy consumption is less, but the disadvantage is that the wall thickness of the heat transfer tube is relatively large (1 ~ 4mm), and the metal material consumption of the heat exchanger is relatively large under the condition of a certain heat exchange area. The advantage of the plate heat exchanger is that the unit exchange The heat exchange area in the heat exchanger is relatively large, and the heat exchanger is compact. Thin-walled metal plates (0.2-0.8mm) can be used as heat exchange elements. Under the same heat exchange area, the consumption of metal materials is much lower than that of the shell-and-tube type. Heat exchanger, but the disadvantage is that the mechanical seal of the heat exchanger is very difficult. The sealing length between the hot and cold flow channels includes the periphery of each heat exchange plate on the cold and hot sides, a total of 8 boundary seals, The boundary that needs to be sealed is too long, and it is easy to cause fluid leakage, so it is not suitable for high temperature and high pressure heat exchange occasions, and the plate heat exchanger needs to be supported by the ribs of the plate, the distance between the plates is small, and the fluid flow resistance is large , It is easy to cause dirt blockage, the operation of the heat exchanger consumes a lot of energy, and the flow channel of the heat exchanger is not easy to clean, so ordinary plate heat exchangers cannot be used between flue gas and flue gas with high temperature, low density, and huge volume flow. heat exchange between.

Utility model content

The purpose of this utility model is to overcome the shortcomings of the existing heat exchanger technology that the metal material consumption of the shell-and-tube heat exchanger is relatively large, and the plate heat exchanger is easy to leak, and the operating energy consumption is high, and to provide a heat exchanger suitable for high temperature , Low density, huge volume flow flue gas heat exchange between the flue gas and the use of swirl fins to support the rectangular tube bundle heat exchanger.

As shown in Figure 1 and Figure 2, the utility model is realized through the following technical solutions:

A rectangular tube bundle heat exchanger supported by swirl fins, including a cylinder body 5, several rectangular tube bundles 4 with different widths and parallel to each other placed in the cylinder body 5 and along the axial direction of the cylinder body, and rectangular tube bundles 4 placed at both ends of the rectangular tube bundle 4 The tube sheet 2, the upper and lower heads 1, 9 connected to the tube sheets 2 at both ends, the inlet and outlet interfaces 10, 12, 3, 11 of the heat exchanger tube side and the shell side, the inlet and outlet interfaces 10, 12 of the tube side and the upper and lower heads 1 and 9 are connected, the inlet and outlet ports 3 and 11 of the shell side are connected with the cylinder body 5, and the swirl fins 8 are roughly evenly spaced along the axial and transverse directions in the tube of the rectangular tube bundle 4, and the center line of the swirl fin 8 is in line with the rectangular tube bundle The direction of the center line of 4 is the same, the direction of rotation of the adjacent swirl fins 8 is opposite, and the swirl fins 8 are roughly evenly spaced along the axial and transverse directions between the tubes of the rectangular tube bundle 4 .

The preferred solution: the swirl sheet 8 is a sheet-like short twisted belt, the torsion angle is preferably 180 to 360 degrees, and the twist rate (twist rate: the ratio of the length of the swirl sheet to the width of the sheet when the swirl sheet rotates 180 degrees) is 1.5 ~10.

The swirl sheets 8 inside the tubes are in contact with the two inner walls of the rectangular tube bundles 4 , and the swirl sheets 8 between the tubes are in contact with the outer walls of the adjacent rectangular tube bundles 4 .

The swirl fins 8 are connected horizontally by thin flat steels 7 to form groups of transverse swirl fins, and the transverse swirl fins on the same axial direction are fixed by several positioning rods 6 .

The rectangular tube bundle 4 is composed of two parallel plate surfaces closed on both sides, with a certain plate spacing between the two plates; the parallel plate surface is a smooth plate surface or a plate surface with periodic concave-convex rough ribs, and the concave-convex rough The rib surface is a zoom-shaped broken line rib surface or a wavy curved rib surface, and the rough height of the rib surface is 1% to 20% of the distance between the rectangular tube sheets, as shown in Figure 5 and Figure 6.

The spacing of the rectangular tube bundles 4 is preferably 10 mm to 100 mm, the spacing of the swirl fins 8 in the transverse direction is 1.2 to 12 times the spacing of the rectangular tube bundles 4 , and the axial spacing is 3 to 60 times the spacing of the rectangular tube bundles 4 .

The inlet and outlet ports 10 and 12 of the tube side of the heat exchanger can be connected to the upper and lower heads 1 and 9 in a horizontal direction of 0 to 360 degrees, and the inlet and outlet ports 3 and 11 of the shell side are connected to the cylinder body in a horizontal direction.

The method for enhancing heat transfer by applying the rectangular tube bundle heat exchanger supported by the swirl fins described in the present invention: when the fluid passes through a set of horizontal swirl fins in and between the tubes of the rectangular tube bundle 4, several parallel and The spiral flow is independent of each other. After that, the spiral flow relies on the inertia of the fluid itself to maintain the spin flow in the distance between two sets of horizontal swirl sheets and gradually decays. When the fluid passes through the next set of horizontal swirl sheets, the spiral flow is formed again , the fluid repeats the process of spiral flow and spin flow along the flow direction. The fluid spiral flow and spin flow increase the flow velocity of the fluid in the heat transfer boundary layer, which can effectively strengthen the convective heat transfer of the fluid, because the fluid in the spin The flow resistance in the flow area is very small, so it only needs to pay the price of less resistance to obtain a greater improvement in heat transfer performance.

Compared with the prior art, the utility model has the following advantages and effects: thin-walled metal plates (thickness 0.2-0.8mm) can be used to make rectangular tube bundles 4, which can overcome the wall thickness of the heat transfer tubes of shell-and-tube heat exchangers, the metal The disadvantage of high material consumption is that since the rectangular tube bundle 4 has only one axial weld, and the two ends of the rectangular tube bundle 4 are connected to the tube sheet 2, it is equivalent to only three perimeters of each heat transfer plate on the hot and cold sides that need to be sealed. Far less than the plate heat exchanger, each heat transfer plate has 8 perimeters on the cold and hot sides that need to be sealed, which can greatly reduce the length of the sealed perimeter and improve the reliability of the seal. In addition, the distance between the plates of the rectangular tube bundle 4 can be relatively large, and the swirl sheets 8 are used as supports between the plates. The swirl sheets 8 can play a supporting role in the tubes of the rectangular tube bundle 4 and between the tubes on the one hand, so as to prevent the rectangular tube bundle 4 from being inside and outside. When the pressure of the fluid on both sides is not equal, it is deformed under pressure. On the other hand, the fluid can generate spiral flow and spin flow, which can strengthen the convective heat transfer of the fluid in the rectangular tube bundle and between the tubes, and because the flow resistance of the fluid in the spin flow area is very small Small, so only need to pay the price of less resistance, you can get a greater improvement in heat transfer performance, overcome the disadvantages of large fluid resistance and high energy consumption in the operation of the plate heat exchanger, and at the same time, the plate spacing of the rectangular tube bundle 4 is relatively large, and the channel The structure is simple, it is not easy to be blocked by dirt, and it is easy to clean, which is better than the plate heat exchanger. Because of the above advantages, the rectangular tube bundle heat exchanger supported by swirl fins is more suitable for flue gas heat exchange occasions with high temperature, low density and huge volume flow than the existing shell and tube heat exchangers and plate heat exchangers.

Description of drawings

Fig. 1 is a top view schematic diagram of the utility model;

Fig. 2 is a schematic cross-sectional view along line AA of Fig. 1;

Fig. 3 is a front view of a set of transverse swirl fins;

Fig. 4 is a top view of a set of transverse swirl fins;

Fig. 5 is a schematic side view of a rectangular tube bundle formed by a zoom-shaped rough flat plate;

Fig. 6 is a schematic side view of a rectangular tube bundle formed by a wavy rough flat plate;

Figure 7 is a schematic diagram of the tube sheet.

The figure shows: 1: lower head; 2: tube sheet; 3: shell side inlet interface; 4: rectangular tube bundle; 5: cylinder; 6: positioning rod; 7: thin flat steel; 8: swirl plate; 9: Upper head; 10: Tube side inlet port; 11: Shell side outlet port; 12: Tube side outlet port.

Detailed ways

Example 1

Figures 1 and 2 show a structural form of a rectangular tube bundle heat exchanger supported by swirl fins in the present invention. As shown in Figures 1 and 2, the rectangular tube bundle heat exchanger supported by swirl fins includes a cylinder 5, several rectangular tube bundles 4 with different widths and parallel to each other placed in the cylinder 5 and along the axis of the cylinder , the tube sheet 2 placed at both ends of the rectangular tube bundle 4, the upper and lower heads 1, 9 connected to the tube sheet 2 at both ends, and the inlet and outlet interfaces 10, 12, 3, 11 between the tube side and the shell side of the heat exchanger, and the inlet and outlet of the tube side The interfaces 10, 12 are connected with the upper and lower heads 1, 9, the inlet and outlet interfaces 3, 11 of the shell side are connected with the cylinder body 5, and the swirl plates 8 are arranged at approximately uniform intervals in the axial and lateral directions in the tube of the rectangular tube bundle 4, and the swirl flow The center line of the sheet 8 is in the same direction as the center line of the rectangular tube bundle 4, and the direction of rotation of the adjacent swirl sheets 8 is opposite, and the swirl flow is also roughly evenly spaced between the tubes of the rectangular tube bundle 4 along the axial and lateral directions. slice 8. The swirl sheet 8 is a sheet-shaped short twisted strip with a twist angle of 180 degrees. The swirl sheets 8 inside the tubes are in contact with the two inner walls of the rectangular tube bundles 4 , and the swirl sheets 8 between the tubes are in contact with the outer walls of the adjacent rectangular tube bundles 4 . The swirl fins 8 are connected horizontally by thin flat steels 7 to form groups of transverse swirl fins, and the transverse swirl fins on the same axial direction are fixed by several positioning rods 6 .

The rectangular tube bundle 4 is composed of two parallel board surfaces closed on both sides, with a certain distance between the two boards; the parallel board surfaces are smooth board surfaces.

The inlet and outlet ports 10 and 12 of the tube side of the heat exchanger can be connected to the upper and lower heads 1 and 9 in a horizontal direction of 0 to 360 degrees, and the inlet and outlet ports 3 and 11 of the shell side are connected to the cylinder body in a horizontal direction.

The inlet and outlet interfaces 10, 12 of the tube side, the upper and lower heads 1, 9 and the inner tube flow channels of the rectangular tube bundle 4 together constitute the tube side channel of the heat exchanger, the inlet and outlet interfaces 3, 11 of the shell side and the connection between the cylinder body 5 and the rectangular tube bundle 4 The flow channel between the tubes and the tube sheet 2 jointly constitute the shell-side channel of the heat exchanger.

In this example, the cylinder body 5, the diameter of the lower head 1 and the upper head 9 are 1700mm, the wall thickness is 8mm, the length of the cylinder 5 is 4000mm, and the height of the lower head 1 and the upper head 9 is 1100mm , the diameter of the tube sheet 2 is 1000 mm, the thickness is 30 mm, the thickness of the plate of the rectangular tube bundle 4 is 0.5 mm, the distance between the plates is 50 mm, the center distance of the tubes of the rectangular tube bundle 4 is 50 mm, and 17 widths are evenly distributed in the horizontal direction in the cylinder 5 Different rectangular tube bundles 4, the length of the rectangular tube bundle 4 is 4070mm, and the swirl sheets 8 are evenly distributed in the horizontal direction of the rectangular tube bundle 4 and between the tubes at a distance of 150mm. The thickness of the swirl sheet 8 is 2mm and the width is 49.5mm , the torsion rate is 3, the strip length is 150mm, and the thin flat steel 7 with a thickness of 2mm and a height of 15mm is used to connect the horizontally uniform swirl sheets 8 into a group of horizontal swirl sheets, along the axis of the heat exchanger 7 groups of horizontal swirl fins are arranged at an equidistant distance of 600mm, and the diameter of the interface between the tube side and the shell side of the heat exchanger is 800mm. The metal material consumption of the heat exchanger in this example can be 40% to 50% less than that of the shell-and-tube heat exchanger, the reliability of the seal can be increased by 50% compared with the plate heat exchanger, and the fluid resistance or operating energy consumption can be compared with the plate heat exchanger. Reduced by 30% to 40%, suitable for low-density, high-volume flow high-temperature gas-to-gas heat exchange occasions.

Claims (8)

1. adopt the rectangular tube bundle heat exchanger of spinning disk support, comprise cylindrical shell (5), place in the cylindrical shell (5) and along drum shaft to several width rectangular tube bundle (4) of differing and being parallel to each other, place the tube sheet (2) at rectangular tube bundle (4) two ends, the last low head (1 that links to each other with two ends tube sheet (2), 9) and the inlet and outlet connectors (10 of heat exchanger tube side and shell side, 12,3,11), the turnover of tube side connects (10,12) with last low head (1,9) connect, the inlet and outlet connectors (3 of shell side, 11) be connected with cylindrical shell (5), it is characterized in that: in the pipe of rectangular tube bundle (4) vertically with laterally roughly evenly at interval split spinning disk (8), the center line of spinning disk (8) is consistent with the centerline direction of rectangular tube bundle (4), the rotation direction of adjacent spinning disk (8) is opposite, between the tube and tube of rectangular tube bundle (4) also vertically with laterally roughly evenly at interval split spinning disk (8).

2. heat exchanger according to claim 1 is characterized in that: described spinning disk (8) is at the short twisted strip of sheet.

3. heat exchanger according to claim 2 is characterized in that: the torsional angle of described spinning disk (8) is 180～360 degree, and the rate of turning round of spinning disk (8) is 1.5～10.

4. according to each described heat exchanger of claim 1 to 3, it is characterized in that: the spinning disk (8) in the pipe contacts with two inwalls of rectangular tube bundle (4), and the spinning disk between the tube and tube (8) contacts with the outer wall of adjacent rectangular tube bundle (4).

5. heat exchanger according to claim 1 is characterized in that: described spinning disk (8) connects and composes one group of group horizontal cyclone sheet group with thin band steel (7) between laterally, fixes with some positioning tie bars (6) in same horizontal cyclone sheet group on axial.

6. heat exchanger according to claim 1 is characterized in that: described rectangular tube bundle (4) constitutes certain distance between plates of being separated by between two plates by the parallel-plate face of two both sides sealings; The parallel-plate face is the plate face of smooth plate face or the concavo-convex rough rib face of band periodicity, broken line finned surface that described concavo-convex rough rib face is a convergent-divergent shape or corrugated curve finned surface, and the roughness height of finned surface is 1%～20% of a rectangular tube distance between plates.

7. heat exchanger according to claim 1 is characterized in that: the spacing of described rectangular tube bundle (4) is 10mm～100mm.

8. heat exchanger according to claim 7 is characterized in that, described spinning disk (8) is the spacing of 1.2～12 times of rectangular tube bundles (4) in horizontal spacing, is the spacing of 3～60 times of rectangular tube bundles (4) in axial spacing.

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