CN201059887Y - Rectangular figure bundled tubes heat exchanger supported by rotational flow piece - Google Patents
Rectangular figure bundled tubes heat exchanger supported by rotational flow piece Download PDFInfo
- Publication number
- CN201059887Y CN201059887Y CNU2007200539737U CN200720053973U CN201059887Y CN 201059887 Y CN201059887 Y CN 201059887Y CN U2007200539737 U CNU2007200539737 U CN U2007200539737U CN 200720053973 U CN200720053973 U CN 200720053973U CN 201059887 Y CN201059887 Y CN 201059887Y
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- heat exchanger
- rectangular tube
- spinning disk
- tube bundle
- plates
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Abstract
The utility model discloses a rectangular pipe bundle heat exchanger which adopts a plurality of swirling flow plates to support. The heat exchanger comprises a barrel body, a plurality of mutually in parallel rectangular pipe bundles with different width which are arranged in the barrel body along the axial direction of the barrel body, pipe plates which are arranged at two ends of the rectangular pipe bundle, an upper end plate cover and a lower end plate cover which are connected with the pipe plates at the two ends, and the inlet connector and the outlet connector of the tube pass and the shell pass of the heat exchanger. The inlet connector and the outlet connector of the tube pass are connected with the upper end plate cove and the lower end plate cover, and the inlet connector and the outlet connector of the shell pass are connected with the barrel body. The utility model is characterized in that swirling flow plates are uniformly arranged at intervals in the rough along the axial direction and the cross direction in the rectangular pipe bundles, the direction of the center line of the swirling flow plate is identical with the direction of the center line of the rectangular pipe bundle, the swirling direction of the adjacent swirling flow plates is opposite, the swirling flow plates are uniformly arranged at intervals in the rough along the axial direction and the cross direction between pipes of the rectangular pipe bundles, and the swirling flow plates not only has the effective supporting and fixing functions between the plates to the rectangular pipe bundles, but also intensifies the heat transfer of the rectangular pipe bundles. The heat exchanger of the utility model can be popularly popularized and applied to the industrial gas heat exchange.
Description
Technical field
The utility model relates to heat exchanger, particularly a kind of rectangular tube bundle heat exchanger that adopts spinning disk to support.
Background technology
Have now at industry-wide all kinds of shell-and-tube heat exchangers, support the shell-and-tube heat exchanger of normal optical slip pipe bundle as traditional segmental baffle, adopt the augmentation of heat transfer shell-and-tube heat exchanger (Chinese patent: ZL200420015378.0 and ZL200420088741.1) of cavity ring web plate and eddy flow web plate support convergent-divergent tube bank etc., multiple plate type heat exchanger is also arranged, as dull and stereotyped plate type heat exchanger and corrugated plating plate type heat exchanger etc.
The advantage of shell-and-tube heat exchanger is that mechanical seal is good, the bearing capacity height, sealing between cold and hot two side runners of tube side and shell side has only welding or the expanded joint sealing between the tube-to-tube sheet connection of tube bank two ends, therefore can be applied to the heat exchange occasion of many high temperature and high pressure, and the heat-transfer pipe flow area of tube side and shell side is bigger, be difficult for being stopped up by dirt, be convenient to cleaning, the flow resistance of fluid is lower, the operation energy consumption of heat exchanger is less, but shortcoming is the pipe thickness big (1～4mm) of heat-transfer pipe, the consumption of the metal material of heat exchanger is more under the condition of certain heat exchange area, the advantage of plate type heat exchanger is that heat exchange area is bigger in the unit heat exchanger volume, the heat exchanger compactness, (0.2～0.8mm) as heat exchange element can to adopt the thin-wall metal plate, the consumption of metal material is far below shell-and-tube heat exchanger under the condition of identical heat exchange area, but shortcoming is that the mechanical seal difficulty of heat exchanger is big, seal length between cold and hot two side runners comprises the surrounding of every heat exchanger plates face in cold and hot both sides, amount to the sealing on 8 borders, need the border of sealing oversize, admittedly being easy to generate fluid leaks, the heat exchange occasion that should not be used for high temperature and high pressure, and need to rely on the fin of plate to support between the plate of plate type heat exchanger, distance between plates is less, fluid flow resistance is bigger, causes dirt to stop up easily, and the operation energy consumption of heat exchanger is bigger, the heat exchanger runner is not easy cleaning, therefore common plate type heat exchanger can not be applicable to high temperature, low-density, the flue gas of enormousness flow and the heat exchange between the flue gas.
The utility model content
It is bigger for the consumption of shell-and-tube heat exchanger metal material that the purpose of this utility model is to overcome existing heat exchanger technology, and plate type heat exchanger leaks easily, and the shortcoming that operation energy consumption is higher, a kind of high temperature that is applicable to is provided, low-density, the rectangular tube bundle heat exchanger that the employing spinning disk of heat exchange between enormousness flow flue gas and the flue gas supports.
As shown in Figure 1 and Figure 2, the utility model is achieved through the following technical solutions:
The rectangular tube bundle heat exchanger that adopts spinning disk to 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 inlet and outlet connectors 10 of tube side, 12 with last low head 1,9 connect, the inlet and outlet connectors 3 of shell side, 11 are connected with cylindrical shell 5, 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.
Preferred version: described spinning disk 8 is at the short twisted strip of sheet, preferred 180～360 degree of torsional angle, and the rate of turning round (is turned round rate: be 1.5～10 the ratio of slip length and slip width when the spinning disk Rotate 180 is spent).
Spinning disk 8 in the pipe contacts with two inwalls of rectangular tube bundle 4, and the spinning disk 8 between the tube and tube contacts with the outer wall of adjacent rectangular tube bundle 4.
Described spinning disk 8 connects and composes one group of group horizontal cyclone sheet group with thin band steel 7 between laterally, fix with some positioning tie bars 6 in same horizontal cyclone sheet group on axial.
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, as Fig. 5, shown in Figure 6.
Preferred 10mm～the 100mm of the spacing of described rectangular tube bundle 4, 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.
The direction of the inlet and outlet connectors 10,12 of described heat exchanger tube side can be connected with last low head 1,9 in 0～360 degree horizontal direction, and the inlet and outlet connectors 3,11 of shell side is connected with cylindrical shell in the horizontal direction.
Use rectangular tube bundle heat exchanger that employing spinning disk described in the utility model supports and realize the method for augmentation of heat transfer: fluid is every during through one group of horizontal cyclone sheet group in the pipe of rectangular tube bundle 4 and between pipe, form some parallel and separate spiral flows, afterwards, spiral flow relies on the motional inertia of fluid self to keep spin current and decay gradually in the spacing of two groups of horizontal cyclone sheets, when fluid is organized horizontal cyclone sheet through next, form spiral flow again again, the fluid streamwise repeats the process of described spiral flow and spin current, fluid spiral flow and spin current make fluid improve in the flowing velocity of heat transfer boundary layer, convection heat transfer' heat-transfer by convection that can the efficient hardening fluid, because fluid is very little in the flow resistance in spin current zone, so only need pay the cost of less resistance, just can obtain the raising of big heat transfer property.
The relative prior art of the utility model has following advantage and effect: metallic plate (thickness 0.2～0.8mm) the making rectangular tube bundle 4 that can adopt thin-walled, can overcome shell-and-tube heat exchanger heat-transfer pipe thickness of pipe wall like this, the many shortcomings of metal material consumption, because rectangular tube bundle 4 has only an axial weld seam, the two ends of rectangular tube bundle 4 are connected with tube sheet 2, therefore being equivalent to every heat transfer plate face has only 3 peripheries to need sealing in cold and hot both sides, being less than every heat transfer plate face of plate type heat exchanger far away has 8 peripheries to need sealing in cold and hot both sides, thereby can significantly reduce the length of seal perimeter, improve the reliability of sealing.In addition, the distance between plates of rectangular tube bundle 4 can be at a distance of bigger, adopt spinning disk 8 as supporting between plate, spinning disk 8 can be played a supporting role in the pipe of rectangular tube bundle 4 and between pipe on the one hand, avoid rectangular tube bundle 4 compressive deformation when inside and outside both sides fluid pressure does not wait, can make fluid produce spiral flow and spin current on the other hand, strengthen in the rectangular tube beam tube and the heat transfer of the fluid convection between pipe, and because fluid is very little in the flow resistance in spin current zone, so only need pay the cost of less resistance, just can obtain the raising of big heat transfer property, it is big to overcome the plate type heat exchanger fluid resistance, the shortcoming that operation energy consumption is high, the distance between plates of rectangular tube bundle 4 is bigger simultaneously, and channel design is simple, is not easy to be stopped up by dirt, be convenient to cleaning, this all is better than plate type heat exchanger.Because possess above advantage, the rectangular tube bundle heat exchanger that adopts spinning disk to support is more suitable in high temperature the flue gas heat exchange occasion of low-density and enormousness flow than existing shell-and-tube heat exchanger and plate type heat exchanger.
Description of drawings
Fig. 1 is a schematic top plan view of the present utility model;
Fig. 2 is the cross-sectional schematic of Fig. 1 along the AA line;
Fig. 3 is the front view of one group of horizontal cyclone sheet group;
Fig. 4 is the vertical view of one group of horizontal cyclone sheet group;
Fig. 5 is the schematic side view that convergent-divergent shape Rough Flat Plate constitutes rectangular tube bundle;
Fig. 6 is the schematic side view that the waveform Rough Flat Plate constitutes rectangular tube bundle;
Fig. 7 is the tube sheet schematic diagram.
Shown in the figure: 1: low head; 2: tube sheet; 3: the shell side ingress interface; 4: rectangular tube bundle; 5: cylindrical shell; 6: positioning tie bar; 7: thin band steel; 8: spinning disk; 9: upper cover; 10: the tube side ingress interface; 11: the shell side discharge coupling; 12: the tube side discharge coupling.
The specific embodiment
Embodiment 1
Fig. 1,2 show a kind of version of rectangular tube bundle heat exchanger that the utility model adopts spinning disk to support.As Fig. 1, shown in 2, the rectangular tube bundle heat exchanger that adopts spinning disk to 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 inlet and outlet connectors 10 of tube side, 12 with last low head 1,9 connect, the inlet and outlet connectors 3 of shell side, 11 are connected with cylindrical shell 5, 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.Described spinning disk 8 is at the short twisted strip of sheet, and torsional angle is 180 degree.Spinning disk 8 in the pipe contacts with two inwalls of rectangular tube bundle 4, and the spinning disk 8 between the tube and tube contacts with the outer wall of adjacent rectangular tube bundle 4.Described spinning disk 8 connects and composes one group of group horizontal cyclone sheet group with thin band steel 7 between laterally, fix with some positioning tie bars 6 in same horizontal cyclone sheet group on axial.
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 smooth plate face.
The direction of the inlet and outlet connectors 10,12 of described heat exchanger tube side can be connected with last low head 1,9 in 0～360 degree horizontal direction, and the inlet and outlet connectors 3,11 of shell side is connected with cylindrical shell in the horizontal direction.
The inlet and outlet connectors 10,12 of tube side and the pipe inner flow passage of last low head 1,9 and rectangular tube bundle 4 constitute the tube side passage of heat exchanger jointly, runner and the tube sheet 2 common shell side passages that constitute heat exchanger between the inlet and outlet connectors 3,11 of shell side and the pipe of cylindrical shell 5 and rectangular tube bundle 4.
In this example, cylindrical shell 5, low head 1 is 1700mm with the diameter of upper cover 9, wall thickness is 8mm, cylindrical shell 5 long 4000mm, low head 1 is 1100mm with the height of upper cover 9, the diameter of tube sheet 2 is 1000mm, thickness is 30mm, and the slab-thickness of rectangular tube bundle 4 is 0.5mm, and dull and stereotyped spacing is 50mm, the tube pitch of rectangular tube bundle 4 is 50mm, the rectangular tube bundle 4 that in cylindrical shell 5, differs along horizontal uniform 17 width, the length of rectangular tube bundle 4 is 4070mm, the laterally equidistant uniform spinning disk 8 of 150mm in edge in rectangular tube bundle 4 pipes and between pipe, the slip thickness of spinning disk 8 is 2mm, width is 49.5mm, and the rate of turning round is 3, and slip length is 150mm, employing thickness is 2mm, highly for the thin band steel 7 of 15mm laterally uniform spinning disk 8 be connected to one group of horizontal cyclone sheet group, settle 7 groups of horizontal cyclone sheet groups along the axially equidistant 600mm of heat exchanger, the interface diameter of heat exchanger tube side and shell side is 800mm.The consumption of the metal material of this routine heat exchanger can less 40%～50% than shell-and-tube heat exchanger, the reliability of sealing can improve 50% than plate type heat exchanger, the comparable plate type heat exchanger of fluid resistance or operation energy consumption reduces by 30%～40%, be suitable for low-density, the heat exchange occasion of the high-temperature gas of large volume flow and gas is used.
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.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007200539737U CN201059887Y (en) | 2007-07-11 | 2007-07-11 | Rectangular figure bundled tubes heat exchanger supported by rotational flow piece |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007200539737U CN201059887Y (en) | 2007-07-11 | 2007-07-11 | Rectangular figure bundled tubes heat exchanger supported by rotational flow piece |
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| Publication Number | Publication Date |
|---|---|
| CN201059887Y true CN201059887Y (en) | 2008-05-14 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2007200539737U Expired - Lifetime CN201059887Y (en) | 2007-07-11 | 2007-07-11 | Rectangular figure bundled tubes heat exchanger supported by rotational flow piece |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201059887Y (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100498180C (en) * | 2007-07-11 | 2009-06-10 | 华南理工大学 | Rectangular tube bundle heat exchanger adopting swirl plate support and its intensified heat-conduction method |
| CN109443073A (en) * | 2018-10-30 | 2019-03-08 | 佛山科学技术学院 | A kind of tube bundle support structure of shell-and-tube heat exchanger |
| CN111578383A (en) * | 2020-04-16 | 2020-08-25 | 宁波奥克斯电气股份有限公司 | Heat exchanger and air conditioner |
-
2007
- 2007-07-11 CN CNU2007200539737U patent/CN201059887Y/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100498180C (en) * | 2007-07-11 | 2009-06-10 | 华南理工大学 | Rectangular tube bundle heat exchanger adopting swirl plate support and its intensified heat-conduction method |
| CN109443073A (en) * | 2018-10-30 | 2019-03-08 | 佛山科学技术学院 | A kind of tube bundle support structure of shell-and-tube heat exchanger |
| CN111578383A (en) * | 2020-04-16 | 2020-08-25 | 宁波奥克斯电气股份有限公司 | Heat exchanger and air conditioner |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Effective date of abandoning: 20070711 |
|
| C25 | Abandonment of patent right or utility model to avoid double patenting |