High-efficient spiral pipe heat exchanger
阅读说明:本技术 一种高效螺旋管换热器 (High-efficient spiral pipe heat exchanger ) 是由 余龙 俞树荣 张剑 于 2019-11-18 设计创作,主要内容包括:一种高效螺旋管换热器,抛物面分布螺旋换热管(5)叠加安放在内壳体(3)内部,与位于中心位置的主外管(A3)连接,抛物面分布螺旋换热管(5)被抛物面导流支撑架(4)支撑,内壳体(3)底部有内壳体支撑架(6)支撑在外壳体(1)的底部,换热管道分流装置(10)固定在内壳体支撑架(6)上,主外管(A3)的上顶端装有反流堵头(8),反流堵头(8)上方安装有稳流分布罩(7);抛物面导流支撑架(4),由圆环筋板(B1)和抛物面纵向筋板(B2)构成主体部分,最上圈圆环筋板(B1)上面周向均布有固定卡钩(B3),抛物面纵向筋板(B2)之间分布有抗重力导流叶片(B4),抛物面纵向筋板(B2)内侧分布有螺旋管换热管卡扣(B5)。(A high-efficiency spiral tube heat exchanger is characterized in that parabolic distribution spiral heat exchange tubes (5) are stacked inside an inner shell (3) and connected with a main outer tube (A3) located in the center position, the parabolic distribution spiral heat exchange tubes (5) are supported by a parabolic flow guide support frame (4), an inner shell support frame (6) is arranged at the bottom of the inner shell (3) and supported at the bottom of an outer shell (1), a heat exchange tube flow dividing device (10) is fixed on the inner shell support frame (6), a backflow plug (8) is arranged at the upper top end of the main outer tube (A3), and a flow stabilizing distribution cover (7) is arranged above the backflow plug (8); the paraboloid diversion support frame (4) comprises a main body part consisting of annular rib plates (B1) and paraboloid longitudinal rib plates (B2), wherein fixed hooks (B3) are uniformly distributed on the upper most annular rib plate (B1) in the circumferential direction, anti-gravity diversion blades (B4) are distributed between the paraboloid longitudinal rib plates (B2), and spiral pipe heat exchange pipe buckles (B5) are distributed on the inner side of the paraboloid longitudinal rib plate (B2).)
1. High-efficiency screwA coil heat exchanger comprises an outer shell (1) and an inner shell (3), a spiral surrounding inflow pipe (2) is arranged in an interlayer between the two shells, it is characterized in that the paraboloid distribution spiral heat exchange tubes (5) are arranged inside the inner shell (3) in an overlapping way and are connected with a main outer tube (A3) positioned at the central position, the parabolic distribution spiral heat exchange tubes (5) are supported by a parabolic flow guide support frame (4), an inner shell support frame (6) is arranged at the bottom of the inner shell (3) and supported at the bottom of the outer shell (1) and keeps a preset distance from the end enclosure of the outer shell (1), a heat exchange tube flow dividing device (10) is fixed on the inner shell support frame (6), a backflow plug (8) is arranged at the upper top end of the main outer tube (A3), a flow distribution stabilizing cover (7) is arranged above the backflow plug (8) and opposite to the shell pass inlet (F1), and the supports (9) are circumferentially and uniformly distributed on the outer side or the bottom of the outer shell (1); the flow stabilizing distribution cover (7) is provided with radial V-shaped guide grooves uniformly distributed on the flow-facing surface, the groove depth range of the guide grooves is 10-100 mm, the maximum outer diameter range of the flow stabilizing distribution cover (7) is (0.137-0.255) x EXP (V1/V ') of the inner diameter of the shell side inlet (F1), wherein V1 is the flow velocity at the shell side inlet (F1), and V' is the average flow velocity of the shell side in the inner shell (3); the value range of the curvature radius of the outer contour generatrix of the flow stabilizing distribution cover (7) is larger than mm, where e is the natural constant and Re is the Reynolds number at the shell side inlet (F1); the paraboloid diversion support frame (4) comprises a main body part consisting of annular rib plates (B1) and paraboloid longitudinal rib plates (B2), wherein fixed hooks (B3) are uniformly distributed on the upper surface of the uppermost annular rib plate (B1) in the circumferential direction, anti-gravity diversion blades (B4) are distributed among the paraboloid longitudinal rib plates (B2), and spiral pipe heat exchange pipe buckles (B5) are distributed on the inner side of the paraboloid longitudinal rib plate (B2); a fixing hook (B3) on the paraboloid diversion support frame (4) is fixed on the inner wall of the inner shell (3), and a spiral tube heat exchange tube buckle (B5) on the paraboloid diversion support frame (4) is used for fixing the paraboloid distribution spiral heat exchange tube (5); the generatrix of the paraboloid flow guide support frame (4) should satisfy the parabolic equation
2. The high-efficiency spiral tube heat exchanger as claimed in claim 1, wherein the shell-side fluid enters from a connecting tube shell-side inlet (F1) at the top end of the inner shell (3), flows through all the paraboloid distribution spiral heat exchange tubes (5), flows out through an inner shell support frame (6) at the bottom of the inner shell (3), then flows upwards from the interlayer between the inner shell (3) and the outer shell (1), and flows through the spiral surrounding type inflow tube (2) for heat exchange, and finally flows out from a connecting tube shell-side outlet (F2) at the upper side of the outer shell (1); tube side fluid flows in from a connecting tube side inlet (F3) on the upper side of the outer shell (1) and flows into the spiral surrounding type inflow tube (2), the tube wall of the spiral surrounding type inflow tube (2) is provided with an opening connecting tube, the opening connecting tube is connected with a paraboloid distribution spiral heat exchange tube (5) in the inner shell (3) to convey the tube side fluid, and the tail end of the spiral surrounding type inflow tube (2) is sealed; the other end of the paraboloid distribution spiral heat exchange tube (5) is connected with a main outer tube (A3) on a heat exchange tube shunting device (10), fluid in a tube bundle of a lower spiral surrounding type inflow tube (2) enters an inner tube (A5) from the main outer tube (A3) through the heat exchange tube shunting device (10), the upper top end of the inner tube (2A 5) is connected with a backflow plug (8), a flow hole is formed in the tube side of the upper top end of the inner tube (2A 5) to enable the fluid in the tube to flow out, the fluid flowing out from the upper top end of the inner tube (2A 5) is blocked by the backflow plug (8) and then flows back into an interlayer tube wall between the main outer tube (A3) and the inner tube (2A 5), after mixing and exchanging heat with the fluid in the tube bundle of the upper spiral surrounding type inflow tube (2), the fluid flows into the inner tube 1 (A1) through the heat exchange tube shunting device (10), and flows out from a connecting pipe pass outlet (F4) on the bottom end socket of the outer shell (1).
3. The heat exchange pipeline flow dividing device (10) according to claim 1, comprising a main outer pipe (A3), and symmetrical flow dividing plates (a 4) are uniformly distributed in the circumferential direction, wherein the inner pipe 1 (a 1) and the inner pipe 2 (a 5) are respectively sleeved inside the main outer pipe (A3) and are coaxial with the main outer pipe (A3), and the inner pipe 1 (a 1) and the inner pipe 2 (a 5) convey different types or states of fluid media; the number of the inner pipes of the jacket in the main outer pipe (A3) can be increased according to the type of the fluid, and is less than or equal to 10; the fan-shaped front plug (A2) of the inner tube 1 is arranged at the position where the inner tube 1 (A1) extends into the outer edge of the main outer tube (A3) and is connected with the inner tube 1 (A1) and the main outer tube (A3), and the fan-shaped rear plug (A7) of the inner tube 1 is arranged at the tail end of the inner tube 1 (A1); the fan-shaped front plug (A9) of the inner tube 2 is arranged at the position where the inner tube 2 (A5) extends into the outer edge of the main outer tube (A3) and is connected with the inner tube 2 (A5) and the main outer tube (A3), and the fan-shaped rear plug (A6) of the inner tube 2 is arranged at the tail end of the inner tube 2 (A5); the circumferentially uniformly distributed symmetrical flow distribution plates (A4) are circumferentially uniformly distributed by taking the axis of the pipeline as a symmetrical center, penetrate through the inner pipe 1 (A1), the inner pipe 2 (A5), the inner pipe 2 fan-shaped rear plug (A6) and the inner pipe 1 fan-shaped rear plug (A7), and are converged and connected to the axis of the pipeline.
4. The heat exchange tube splitting device of claim 3, wherein: the main outer pipe (A3), the flow distribution plate (A4), the inner pipe 1 (A1) and the inner pipe 2 (A5) are all sleeved inside the main outer pipe (A3) and are coaxial with the main outer pipe (A3); the inner tube 1 (a 1) and the inner tube 2 (a 5) convey different kinds of fluid media therein; the fan-shaped front plug (A2) of the inner tube 1 is arranged at the position where the inner tube 1 (A1) extends into the outer edge of the main outer tube (A3) and is connected with the inner tube 1 (A1) and the main outer tube (A3), and the fan-shaped rear plug (A7) of the inner tube 1 is arranged at the tail end of the inner tube 1 (A1); the fan-shaped front plug (A9) of the inner tube 2 is arranged at the position where the inner tube 2 (A5) extends into the outer edge of the main outer tube (A3) and is connected with the inner tube 2 (A5) and the main outer tube (A3), and the fan-shaped rear plug (A6) of the inner tube 2 is arranged at the tail end of the inner tube 2 (A5); the symmetrical flow distribution plates (A4) are circumferentially and uniformly distributed with the axis of the pipeline as a symmetrical center, penetrate through the inner pipe 1 (A1), the inner pipe 2 (A5), the inner pipe 2 fan-shaped rear plug (A6) and the inner pipe 1 fan-shaped rear plug (A7), and are converged and connected to the axis of the pipeline.
5. The heat exchange tube splitting device of claim 3, wherein: the inner pipe 1 (A1) is coaxially sleeved in the main outer pipe (A3), symmetrical flow distribution plates (A4) are uniformly distributed on the circumference of the pipeline in the circumferential direction and are composed of partition plates connected to the central axis of the flow channel, the number of the plates of the symmetrical flow distribution plates (A4) uniformly distributed in the circumferential direction is related to the type of the transmitted fluid, and if the type of the transmitted fluid is n, the number of the plates of the symmetrical flow distribution plates (A4) uniformly distributed in the circumferential direction is 2 n; the included angle between the width of the medium flow groove formed in the wall surface at the tail end of the inner pipe 1 (A1) and the central axis of the flow channel does not exceed the included angle (An) between two adjacent plates of the symmetrical flow distribution plate (A4) which are uniformly distributed in the circumferential direction.
6. The heat exchange tube splitting device of claim 3, wherein: the inner pipe 1 (A1) and the inner pipe 2 (A5) are coaxially sleeved in the main outer pipe (A3), symmetrical flow distribution plates (A4) are uniformly distributed on the circumference of the pipeline in the circumferential direction, the inner pipe 2 (A5) and the inner pipe 1 (A1) are coaxial, and the top ends of the inner pipe and the inner pipe are oppositely arranged; the length (L1) of a medium flowing groove formed in the wall surface at the tail end of the inner pipe 1 (A1) does not exceed the length of a pipe, wherein the pipe is formed by the inner pipe 1 (A1) penetrating into the main outer pipe (A3) through a fan-shaped front plug (A2) of the inner pipe 1; the pipe port of the inner pipe 1 (A1) is blocked by the inner pipe 1 fan-shaped rear plug (A7), the pipe port of the inner pipe 2 (A5) is blocked by the inner pipe 2 fan-shaped rear plug (A6), and two pipes can also share one plug for blocking.
7. The heat exchange tube splitting device of claim 3, wherein: the length (L2) of a medium circulation groove formed in the wall surface of the tail end of the inner pipe 2 (A5) does not exceed the length of a pipe, wherein the pipe is formed by the inner pipe 2 (A5) penetrating into the main outer pipe (A3) through a fan-shaped rear plug (A6) of the inner pipe 2; the included angle between the width of the medium flow groove formed in the wall surface at the tail end of the inner pipe 2 (A5) and the central axis of the flow channel does not exceed the included angle (An) between two adjacent plates of the symmetrical flow distribution plate (A4) which are uniformly distributed in the circumferential direction.
8. The heat exchange tube splitting device of claim 3, wherein: the medium circulation grooves are formed in the inner pipe 1 (A1) and the inner pipe 2 (A5) through the wall surfaces of the tail ends, flow channels which are symmetrically distributed on the axis of the pipeline and are separated by the symmetrical flow distribution plates (A4) are uniformly distributed in the circumferential direction, fluid is exchanged in the outer pipe (A3), so that the fluid flows from the pipe wall gap to the center of the pipeline, in the flow channels formed by the symmetrical flow distribution plates (A4) which are uniformly distributed in the circumferential direction, the homologous fluid flows in the flow channels which are symmetrically distributed on the axis of the pipeline, and the non-homologous fluid flows on two sides of the partition plates of the symmetrical flow distribution plates (A4) which are uniformly distributed in the circumferential.
9. The heat exchange tube splitting device of claim 3, wherein: the following relationships exist between the tube diameter D1 of the main outer tube (A3) and the tube diameters D2 and D3 of the inner tubes 1 (a 1) and 2 (a 5): when D2= D3, the value range of D1 is (1.3-5.7) D2; when D2 is not equal to D3, the value range of D1 is (1.5-10) D2.
10. The heat exchange tube splitting device of claim 3, wherein: the maximum difference range of the flow area of the medium flow channel formed on the tail end wall surface of the inner pipe 1 (A1), the flow area of the gap between the inner pipe 2 (A5) and the main outer pipe (A3) and the flow area in the inner pipe 1 (A1) is not more than 75%; the maximum difference range of the flow area of the medium flow channel formed by the tail end wall surface of the inner pipe 2 (A5), the flow area of the gap between the inner pipe 1 (A1) and the main outer pipe (A3) and the flow area in the inner pipe 2 (A5) is not more than 75%.
Technical Field
The invention relates to a spiral tube heat exchanger technology.
Background
Disclosure of Invention
The invention aims to provide a high-efficiency spiral tube heat exchanger.
The invention relates to a high-efficiency spiral tube heat exchanger, which comprises an outer shell 1 and an
The invention has the advantages that: in the aspect of improving the heat exchange efficiency of the heat exchanger, the heat exchanger is of an inner-outer double-layer structure, a spiral surrounding inflow pipe of a pipe pass is spirally wound between double layers, a heat exchange spiral pipe of a middle pipe bundle in an inner shell of the heat exchanger adopts a parabolic coil pipe structure, and a steady flow distribution cover is arranged at the bottom of the heat exchange spiral pipe just opposite to a shell pass inlet, so that the flow velocity of the shell pass inlet is uniformly distributed. A paraboloid flow guide support frame is arranged below the heat exchange spiral pipe, and anti-gravity flow guide vanes are arranged between the paraboloid flow guide support frames, so that fluid with relatively low height and relatively high flow velocity at the center of the inner shell of the heat exchanger is guided to a position outside the center of the spiral heat exchange pipe, and the heat exchange efficiency at the position with relatively weak flow is enhanced. In addition, the heat exchanger center is provided with a space-saving pipeline convection device, the device installs a plurality of concentric pipeline jackets in a main pipeline, fluid is shunted to different pipe walls and flows in the pipe through a shunt device, the pipeline arranged and distributed is designed into the spatial layout of a single main pipe, so that cold and hot fluid passes through the position inside and outside the exchange pipe, the fluid completes the conversion between the flow between the pipe walls and the flow in the pipe in the flowing process, the heat exchange efficiency of the rear half casing pipe can be improved, and the space can be obviously saved and installed. The flow dividing device transmits various fluids in the channels uniformly distributed in the circumferential direction, and the symmetrical structure can balance the flow-induced vibration of the pipeline, thereby reducing or even eliminating the flow-induced vibration of the pipeline and ensuring the safety and reliability of the pipeline.
Drawings
Fig. 1 is a half-sectional view of the present invention, fig. 2 is a three-dimensional side view of the present invention, fig. 3 is a structural view of a
Detailed Description
The invention relates to a high-efficiency spiral tube heat exchanger, as shown in figures 1-10, which comprises an outer shell 1 and an
As shown in fig. 1 and 3, the parabolic
As shown in fig. 3 and 4, the anti-gravity guide vane B4 has a small end vane width t1 and a large end vane width t2 that need to satisfy the relationship of t1/t2= 1.5-7.32, an upward inclination angle α of the anti-gravity guide vane B4 is 0.72 × v 1/v', and a rotation angle β of the anti-gravity guide vane B4 is 65-87 degrees.
As shown in fig. 1, fig. 2 and fig. 5, the high-efficiency spiral tube heat exchanger comprises an outer shell 1 and an
As shown in fig. 1, 2 and 5, the shell-side fluid enters from a connecting tube shell-side inlet F1 at the top end of the
As shown in fig. 1 and 5, the heat exchange pipeline shunting device includes a main outer pipe A3, a shunting plate a4, an inner pipe 1a1 and an inner pipe 2 a5, which are all sleeved inside the main outer pipe A3 and are coaxial with the main outer pipe A3. The inner tube 1A1 and the
As shown in fig. 1 and 6, the inner pipe 1a1 is coaxially sleeved in the main outer pipe A3, the circumferentially uniformly distributed symmetrical flow distribution plates a4 are uniformly distributed on the circumference of the pipe and are composed of partition plates connected to the central axis of the flow channel, the number of the plates circumferentially uniformly distributed symmetrical flow distribution plates a4 is related to the type of the fluid to be transmitted, and if the type of the fluid to be transmitted is n, the number of the plates circumferentially uniformly distributed symmetrical flow distribution plates a4 is 2 n. The included angle between the width of the medium flow groove formed in the wall surface at the tail end of the inner pipe 1A1 and the central axis of the flow channel does not exceed the included angle An between two adjacent plates of the symmetrical flow distribution plate A4 which are uniformly distributed in the circumferential direction.
As shown in fig. 7, fig. 7 is a partial sectional view in the direction a-a of fig. 6, the inner tube 1a1 and the inner tube 2 a5 are coaxially sleeved in the main outer tube A3, the symmetrical flow distribution plates a4 are uniformly distributed on the circumference of the pipeline, and the inner tube 2 a5 and the inner tube 1a1 are coaxial and have opposite top ends. The length L1 of the medium flowing groove formed on the end wall surface of the inner pipe 1A1 is not more than the length of the pipe that the inner pipe 1A1 passes through the fan-shaped front plug A2 of the inner pipe 1 and goes deep into the main outer pipe A3. The pipe port of the inner pipe 1A1 is blocked by a fan-shaped rear plug A7 of the inner pipe 1, the pipe port of the inner pipe 2A 5 is blocked by a fan-shaped rear plug A6 of the inner pipe 2, and two pipes can share one plug for blocking.
As shown in fig. 8, fig. 8 is a partial sectional view taken along the direction b-b of fig. 6, the length L2 of the medium flowing groove formed in the end wall surface of the inner tube 2 a5 is not more than the length of the inner tube 2 a5 passing through the fan-ring-shaped rear plug a6 of the inner tube 2 and extending into the main outer tube A3. The included angle between the width of the medium flow groove formed in the wall surface at the tail end of the
As shown in fig. 9, fig. 9 is a partial sectional view in the c-c direction of fig. 7, when fluid flows through the wall gap, a fluid a flows through the wall gap between the inner tube 1a1 and the main outer tube A3, is blocked by the fan-shaped front plug a2 of the inner tube 1, flows into the inner tube 1a1 through the inlets Ra1 and Ra2 which are symmetrically distributed and separated by the circumferentially uniformly distributed symmetrical splitter plate a4, flows through the wall gap between the inner tube 2 a5 and the main outer tube A3, is blocked by the fan-shaped front plug a2 of the inner tube 1, flows into the inner tube 1a1 through the medium flow channel formed in the end wall surface of the inner tube 1a1, flows out through the outlets Ca1 and Ca2 which are symmetrically distributed and separated by the circumferentially uniformly distributed symmetrical splitter plate a4, and can also flow in the.
As shown in fig. 10, fig. 10 is a partial sectional view in the direction d-d in fig. 7, when fluid flows through the tube wall gap, a fluid a is blocked by the fan-shaped front plug a9 of the inner tube 2, flows into the inner tube 2 a5 through the medium flow channel opened by the end wall surface of the inner tube 2 a5, flows out through the Cb1 and Cb2 outflow ports symmetrically distributed and separated by the symmetric flow dividing plates (a 4) uniformly distributed in the circumferential direction, a fluid b flows through the tube wall gap between the inner tube 2 a5 and the main outer tube A3, is blocked by the fan-shaped front plug a9 of the inner tube 2, flows into the inner tube 2 a5 through the Rb1 and Rb2 inflow ports symmetrically distributed and separated by the symmetric flow dividing plates a4 uniformly distributed in the circumferential direction, and the fluid.
The medium circulation grooves are formed in the inner pipe 1 (A1) and the inner pipe 2 (A5) through the wall surfaces of the tail ends, flow channels which are symmetrically distributed on the axis of the pipeline and are separated by the symmetrical flow distribution plates (A4) are uniformly distributed in the circumferential direction, fluid is exchanged in the outer pipe (A3), so that the fluid flows from the pipe wall gap to the center of the pipeline, in the flow channels formed by the symmetrical flow distribution plates (A4) which are uniformly distributed in the circumferential direction, the homologous fluid flows in the flow channels which are symmetrically distributed on the axis of the pipeline, and the non-homologous fluid flows on two sides of the partition plates of the symmetrical flow distribution plates (A4) which are uniformly distributed in the circumferential.
As shown in fig. 1 and 8, the main outer tube A3 has a tube diameter D1, and the inner tubes 1a1, 2 a5 have a tube diameter D2 and D3, which have the following relationships: when D2= D3, the value range of D1 is (1.3-5.7) D2; when D2 is not equal to D3, the value range of D1 is (1.5-10) D2.
As shown in fig. 1, 5 and 7, the maximum difference range of the flow areas of the medium flow channels formed on the tail end wall surfaces of the inner tubes 1a1, the flow areas of the gaps between the inner tubes 2 a5 and the main outer tubes A3 and the in-tube flow areas of the inner tubes 1a1 is not more than 75%; the maximum difference range of the flow area of the medium flow channel formed by the tail end wall surface of the
As shown in fig. 1 to 10, the heat exchange medium respectively passes through the tube side and the shell side, the shell side fluid enters from the connecting tube shell side inlet F1 at the top end of the
As shown in FIG. 1, in the heat exchange tube flow dividing device (10), different fluids relatively flow along the central axis OO' of the flow passage, and the jacket layer in the middle of the concentric sleeves is a flow passage of the different fluids. The fluid passes through symmetrical flow dividing plates A4 which are evenly distributed in the circumferential direction and medium circulation grooves which are formed on the side wall surfaces of the ends of the inner pipe 1A1 and the
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