CN109724445B - Reinforced heat transfer pipe and cracking furnace - Google Patents
Reinforced heat transfer pipe and cracking furnace Download PDFInfo
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- CN109724445B CN109724445B CN201711027588.XA CN201711027588A CN109724445B CN 109724445 B CN109724445 B CN 109724445B CN 201711027588 A CN201711027588 A CN 201711027588A CN 109724445 B CN109724445 B CN 109724445B
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Abstract
The invention relates to the technical field of fluid heat transfer, and discloses a reinforced heat transfer pipe and a cracking furnace, wherein the reinforced heat transfer pipe (1) comprises a pipe body (10) which is tubular and provided with an inlet (100) for fluid and an outlet (101) for fluid to flow out, the inner wall of the pipe body (10) is provided with a twisting piece, and the outside of the pipe body (10) is provided with a heat insulation piece (14) which at least partially surrounds the periphery of the pipe body (10). The reinforced heat transfer pipe can reduce the thermal stress of the heat transfer pipe, thereby prolonging the service life of the reinforced heat transfer pipe. Because the reinforced heat transfer pipe is arranged in the radiation chamber of the cracking furnace, the heat transfer effect of the cracking furnace can be improved, and the running period and the high temperature resistance of the cracking furnace are improved.
Description
Technical Field
The invention relates to the technical field of fluid heat transfer, in particular to an enhanced heat transfer pipe and a cracking furnace.
Background
The enhanced heat transfer pipe is a heat transfer element capable of achieving enhanced heat transfer of fluid inside and outside the pipe, i.e., transferring as much heat as possible per unit heat transfer area per unit time. The reinforced heat transfer tube is applied to various industries such as thermal power generation, petrochemical industry, food, pharmaceutical industry, light industry, metallurgy, ships and the like. Taking a cracking furnace as an example, the cracking furnace is an important device in petrochemical industry, and the reinforced heat transfer tube is widely applied to the cracking furnace. The mode of enhancing heat transfer is divided into an active mode and a passive mode. The active mode requires external force, and mainly comprises methods of machinery, surface vibration, fluid vibration, electromagnetic field, suction and the like. The mechanism of the active enhanced heat transfer mode is relatively complex, and the required investment is relatively huge, so that the industrial application is not wide. The passive mode does not need external force, and mainly comprises different types of enhanced heat transfer technologies such as an expansion surface, surface treatment, an in-pipe insert and the like, and the specific mode comprises the steps of increasing the heat transfer area, increasing the average temperature difference and increasing the total heat transfer coefficient. The heat transfer area is increased mainly through a finned surface, a special-shaped surface, a multi-hollow substance structure, a small-diameter heat exchange tube and the like; the temperature difference is increased mainly by changing the temperature condition and the flow form of the heat exchange fluid; the method for increasing the total heat transfer coefficient of the fluid is mainly realized by the methods of increasing the fluid speed, enhancing the disturbance of the fluid, cleaning the scaling surface in time and the like.
In the prior art, the heat transfer is generally enhanced by arranging inner ribs on the inner wall of the enhanced heat transfer tube, and the addition of the inner ribs not only increases the surface area of the enhanced heat transfer tube, but also increases the turbulent kinetic energy in the tube. The conventional reinforced heat transfer element with better performance is a twisted sheet, and the twisted sheet is usually arranged in the middle of the reinforced heat transfer tube, so that the boundary layer of the fluid is thinned by utilizing the rotation of the fluid, thereby achieving the purpose of reinforcing the heat transfer. Although the reinforced heat transfer tube with the torsion sheet has a better reinforced heat transfer effect, the torsion sheet and the reinforced heat transfer tube often break due to the fact that the torsion sheet is connected with the tube wall of the reinforced heat transfer tube by welding. Especially in the long-time operation process, in addition, in the ultra-high temperature environment, the phenomenon that the twisting sheets and the tube wall of the reinforced heat transfer tube are cracked is more easily caused, so that the service life of the reinforced heat transfer tube is shortened.
Therefore, the heat transfer effect of the reinforced heat transfer tube is ensured, and the thermal stress of the reinforced heat transfer tube is reduced to prolong the service life of the reinforced heat transfer tube.
Disclosure of Invention
The invention aims to solve the problem of shorter service life of the reinforced heat transfer tube in the prior art, and provides the reinforced heat transfer tube which can reduce the thermal stress of the reinforced heat transfer tube, thereby prolonging the service life of the reinforced heat transfer tube.
In order to achieve the above object, according to an aspect of the present invention, there is provided a reinforced heat transfer tube comprising a tube body having an inlet through which a fluid enters and an outlet through which the fluid exits, wherein an inner wall of the tube body is provided with torsion pieces, and an outer portion of the tube body is provided with a heat insulating member at least partially surrounding an outer periphery of the tube body.
Preferably, the heat insulating piece is in a tubular shape, and the heat insulating piece is sleeved outside the pipe body.
Preferably, a gap is reserved between the heat insulation piece and the outer wall of the pipe body.
Preferably, a connecting piece for connecting the heat insulating piece and the pipe body is arranged between the heat insulating piece and the pipe body.
Preferably, the connector is selected from one or more of the following three structures: the connector comprises a first connecting piece which extends along an axial direction parallel to the pipe body; the connecting piece comprises a second connecting piece which extends spirally along the outer wall of the pipe body; the connecting piece comprises a connecting rod, and two ends of the connecting rod are respectively connected with the outer wall of the pipe body and the inner wall of the heat insulation piece.
Preferably, the connection is made of a hard material or a soft material.
Preferably, the heat insulating member comprises a straight pipe section, and a first tapered pipe section and a second tapered pipe section connected to a first port and a second port of the straight pipe section, respectively, wherein the first tapered pipe section is tapered in a direction from the first port to the second port, and the second tapered pipe section is tapered in a direction from the second port to the second port.
Preferably, an included angle formed between the outer wall surface of the first tapered pipe section and the horizontal plane is 10-80 degrees; and/or the included angle formed between the outer wall surface of the second tapered pipe section and the horizontal plane is 10-80 degrees.
Preferably, the length of extension of the heat insulating member in the axial direction of the pipe body is 1 to 2 times the length of the pipe body.
Preferably, the heat insulating member is located outside the pipe body where the torsion piece is provided.
Preferably, the twisted piece includes a rib protruding from an inner wall of the pipe body toward the inside of the pipe body, the rib spirally extending in an axial direction of the pipe body, wherein a first end surface of the rib toward the inlet is formed as a first arc surface along a spirally extending direction.
Preferably, the first cambered surface is concave; and/or an included angle formed by the first cambered surface and the inner wall of the pipe body at the connecting position is more than 0 degrees and less than or equal to 90 degrees.
Preferably, a second end surface of the rib facing the outlet is formed as a second arc surface in a spiral extending direction.
Preferably, the second cambered surface is concave; and/or an included angle formed by the second cambered surface and the inner wall of the pipe body at the connecting position is more than 0 degrees and less than or equal to 90 degrees.
Preferably, a third end of the rib facing the central axis of the pipe body is formed as a third cambered surface.
Preferably, the third cambered surface is concave.
Preferably, two side wall surfaces of the rib opposite to each other gradually approach in a direction from an inner wall of the pipe body to a center of the pipe body.
Preferably, a smooth transition fillet is formed at the connection of at least one of the two side wall surfaces of the rib opposite to each other and the inner wall of the pipe body.
Preferably, the included angle formed by each side wall surface and the inner wall of the pipe body at the connecting position is 5-90 degrees.
Preferably, the height of the ribs is greater than 0 and less than or equal to 150mm, preferably the height of the ribs is 10-50mm.
Preferably, the ribs are provided with gaps capable of spacing the ribs apart.
Preferably, the plurality of gaps are arranged along the extending direction of the rib.
Preferably, at least one of the two side walls of the gap is formed as a fourth cambered surface.
Preferably, the fourth cambered surface is recessed in a direction facing away from the center of the gap.
Preferably, the plurality of ribs is in a clockwise or anticlockwise vortex shape when seen from the direction of the inlet.
Preferably, a plurality of the ribs are formed at the center of the pipe body so as to enclose a through hole extending in the axial direction of the pipe body, as seen from the direction of the inlet, a ratio D between a diameter D of the through hole and an inner diameter D of the pipe body: d=greater than 0 and less than 1.
Preferably, the rotation angle of the ribs is 90-1080 DEG, and/or the length L of the ribs in the axial direction of the tube body 1 The ratio of the inner diameter D of the pipe body to the inner diameter D of the pipe body is L 1 ：D＝1-10:1。
In the above technical scheme, the heat insulation piece at least partially surrounds the periphery of the pipe body is arranged outside the pipe body, so that the temperature of the pipe wall of the pipe body can be reduced, the thermal stress of the reinforced heat transfer pipe is effectively reduced, the service life of the reinforced heat transfer pipe is prolonged, and the allowable temperature of the reinforced heat transfer pipe is correspondingly increased. When the reinforced heat transfer pipe is applied to the cracking furnace, the long-term stable operation of the cracking furnace can be ensured.
The second aspect of the invention provides a cracking furnace, which comprises a radiation chamber, wherein at least one radiation furnace tube assembly is arranged in the radiation chamber, the radiation furnace tube assembly comprises a plurality of radiation furnace tubes which are sequentially arranged and reinforced heat transfer tubes which are communicated with adjacent radiation furnace tubes, and the reinforced heat transfer tubes are provided by the invention. By arranging the reinforced heat transfer pipe in the radiation chamber of the cracking furnace, the heat transfer effect of fluid in the radiation chamber can be improved, and the thermal stress of the reinforced heat transfer pipe is reduced, so that the operation period and the high temperature resistance of the cracking furnace are improved.
Preferably, the axial length L of the radiation furnace tube 2 The ratio of the water-soluble polymer to the inner diameter D of the pipe body is L 2 : d=15-75, preferably L 2 ：D＝25-50。
Drawings
FIG. 1 is a schematic perspective view of a reinforced heat transfer tube according to a preferred embodiment of the present invention, wherein a cross section of a fin is trapezoidal, an included angle formed by a first arc surface and an inner wall of a tube body at a connection point is 30 degrees, and an included angle formed by a second arc surface and an inner wall of a tube body at a connection point is 30 degrees;
FIG. 2 is a schematic cross-sectional view of the enhanced heat transfer tube shown in FIG. 1;
FIG. 3 is a schematic perspective view of a reinforced heat transfer tube according to another preferred embodiment of the present invention, wherein the cross section of the fin is trapezoidal, an included angle formed by the first cambered surface and the inner wall of the tube body at a connection point is 35 degrees, and an included angle formed by the second cambered surface and the inner wall of the tube body at a connection point is 35 degrees;
FIG. 4 is a schematic perspective view of a reinforced heat transfer tube according to another preferred embodiment of the present invention, wherein the cross section of the fin is trapezoidal, an included angle formed by the first cambered surface and the inner wall of the tube body at a connection point is 40 degrees, and an included angle formed by the second cambered surface and the inner wall of the tube body at a connection point is 40 degrees;
FIG. 5 is a schematic perspective view of a reinforced heat transfer tube according to another preferred embodiment of the present invention, wherein the cross section of the fin is trapezoidal, an included angle formed by the first cambered surface and the inner wall of the tube body at a connection point is 35 °, an included angle formed by the second cambered surface and the inner wall of the tube body at a connection point is 35 °, and the number of gaps provided in the fin is 1;
fig. 6 is a schematic perspective view of a reinforced heat transfer tube according to another preferred embodiment of the present invention, wherein a cross section of a fin is trapezoidal, an included angle formed by the first arc surface and an inner wall of the tube body at a connection point is 35 °, an included angle formed by the second arc surface and the inner wall of the tube body at a connection point is 35 °, and a third end of the fin facing a central axis of the tube body is formed as a third arc surface in a concave shape.
Description of the reference numerals
1-strengthening a heat transfer tube; 10-a tube body; 100-import; 101-outlet; 11-ribs; 110-a first end face; 111-a third end face; 112-sidewall surface; 113-smooth transition fillets; 12-gap; 120-sidewalls; 13-through holes; 14-a thermal insulator; 140-straight pipe sections; 141-a first tapered tube section; 142-a second tapered tube section; 15-void; 160-a first connecting piece; 162-connecting rod.
Detailed Description
In the present invention, unless otherwise indicated, terms of orientation such as "upper, lower, left, right" and the like are used to generally refer to the directions shown in the drawings and the directions in practical use, and "inner and outer" refer to the inner and outer of the outline of the component.
The invention provides a reinforced heat transfer tube, which comprises a tube body 10 in a tube shape, wherein the tube body 10 is provided with an inlet 100 for fluid to enter and an outlet 101 for the fluid to flow out, the inner wall of the tube body 10 is provided with twisting sheets, and the outer part of the tube body 10 is provided with a heat insulating piece 14 at least partially encircling the periphery of the tube body 10. By arranging the heat insulating piece 14 at least partially surrounding the periphery of the pipe body 10 outside the pipe body 10, the temperature of the pipe wall of the pipe body 10 can be reduced, so that the thermal stress of the reinforced heat transfer pipe 1 is effectively reduced, the service life of the reinforced heat transfer pipe 1 is prolonged, and the allowable temperature of the reinforced heat transfer pipe 1 is correspondingly improved. When the reinforced heat transfer pipe 1 is applied to a cracking furnace, the long-term stable operation of the cracking furnace can be ensured. Due to the twisted sheets provided in the tube 10, the fluid entering the tube 10 may become a rotational flow, which may break the boundary layer due to tangential velocity, reducing the coking rate. It should be understood that the heat insulating member 14 may completely encircle the outer circumference of the tube body 10, that is, 360 ° encircle the outer circumference of the tube body 10 in the circumferential direction of the tube body 10, or the heat insulating member 14 may partially encircle the outer circumference of the tube body 10, for example, 90 ° encircle the outer circumference of the tube body 10, or the heat insulating member 14 may have a suitable angle encircling the outer circumference of the tube body 10 according to practical requirements, and it should be noted that, when the reinforced heat transfer tube 1 is applied to a cracking furnace, and when the heat insulating member 14 partially encircling the outer circumference of the tube body 10 is disposed on the outside of the tube body 10, the heat insulating member 14 may be preferably disposed on the heated surface of the tube body 10. In addition, the heat insulating member 14 may be preferably disposed outside the tube body 10 where the torsion piece is disposed, so that the torsion piece is not easily cracked with the tube body 10, and the service life of the reinforced heat transfer tube 1 may be improved.
As shown in fig. 1, 2, 3, 5 and 6, the heat insulating member 14 may be tubular, and the heat insulating member 14 is preferably sleeved outside the tube body 10, so that the temperature of the tube wall of the tube body 10 can be further reduced, thereby further reducing the thermal stress of the reinforced heat transfer tube 1. As for the shape and structure of the heat insulating member 14, there is no particular limitation, and as shown in fig. 1, the heat insulating member 14 may have a cylindrical shape, or as shown in fig. 3, the heat insulating member 14 may have an elliptical shape.
In addition, the arrangement of the heat insulating member 14 is not particularly limited, and as shown in fig. 4, the heat insulating member 14 may be attached to the outer surface of the pipe body 10, or as shown in fig. 5, the heat insulating member 14 may be sleeved outside the pipe body 10, and a gap 15 may be left between the heat insulating member 14 and the outer wall of the pipe body 10, and as a result, the temperature of the pipe wall of the pipe body 10 in use is further reduced, thereby further reducing the thermal stress of the reinforced heat transfer pipe 1.
In order to further enhance the structural stability of the reinforced heat transfer pipe 1, a connection member for connecting the heat insulating member 14 and the pipe body 10 may be provided between the heat insulating member 14 and the pipe body 10. The structural form of the connector is not particularly limited as long as the heat insulating member 14 and the pipe body 10 can be connected. As shown in fig. 5, the connection member may include a first connection tab 160, and the first connection tab 160 may extend in parallel to the axial direction of the pipe body 10; the connection member may include a second connection piece, which may extend spirally along the outer wall of the tube body 10; as shown in fig. 1 and 3, the connection member may include a connection rod 162, and both ends of the connection rod 162 may be connected to the outer wall of the pipe body 10 and the inner wall of the heat insulating member 14, respectively. It will also be appreciated that any two or more of the three structural connectors described above may optionally be provided between the insulating member 14 and the tubular body 10. Preferably, the connection is made of a hard material such as 35Cr45Ni or a soft material such as ceramic fibers.
As shown in fig. 1, 2 and 142, the heat insulating member 14 may include a straight pipe section 140 and first and second tapered pipe sections 141 and 142 connected to the first and second ports of the straight pipe section 140, respectively, wherein the first tapered pipe section 141 tapers in a direction from the first port to the second port, and the second tapered pipe section 142 tapers in a direction from the second port to the second port, and the heat insulating member 14 is configured as described above, so that not only the temperature of the pipe wall of the pipe body 10 is effectively reduced, but also the temperature variation in the axial direction of the pipe body 10 is relatively uniform, while also the thermal stress of the reinforced heat transfer pipe 1 is reduced.
Further, the angle between the outer wall surface of the first tapered pipe section 141 and the horizontal plane is preferably 10-80 °, in particular, the angle between the outer wall surface of the first tapered pipe section 141 and the horizontal plane may be 20 °, 30 °, 40 °, 50 °, 60 ° or 70 °; the angle between the outer wall surface of the second tapered tube section 142 and the horizontal plane is preferably 10-80 °, and likewise, the angle between the outer wall surface of the second tapered tube section 142 and the horizontal plane may be 20 °, 30 °, 40 °, 50 °, 60 °, or 70 °.
In addition, the length of the heat insulator 14 extending in the axial direction of the pipe body 10 is preferably 1 to 2 times the length of the pipe body 10, and setting the axial length of the heat insulator 14 within the above-described range can further reduce the temperature of the pipe wall of the pipe body 10 in use and further reduce the thermal stress of the pipe body 10.
Preferably, the twisted piece may include a rib 11 protruding from an inner wall of the pipe body 10 toward the inside of the pipe body 10, the rib 11 spirally extending in an axial direction of the pipe body 10, wherein a first end surface 110 of the rib 11 toward the inlet 100 is formed as a first arc surface along the spirally extending direction. The rib 11 protruding towards the inside of the pipe body 10 is arranged on the inner wall of the pipe body 10, and the first end face 110 of the rib 11 towards the inlet 100 is formed into the first cambered surface along the spiral extending direction, so that the reinforced heat transfer pipe has good heat transfer effect, meanwhile, the thermal stress of the reinforced heat transfer pipe 1 can be reduced, the maximum thermal stress of the reinforced heat transfer pipe 1 can be reduced by more than 50%, the local overtemperature resistance of the reinforced heat transfer pipe 1 is improved correspondingly, the service life of the reinforced heat transfer pipe is prolonged, in addition, the first end face 110 is formed into the first cambered surface, the turbulent flow effect of fluid in the pipe body 10 is strong, and the coking phenomenon is reduced. The reinforced heat transfer pipe 1 is suitable for a heating furnace and a cracking furnace. The reinforced heat transfer pipe 1 can be installed in a pyrolysis furnace such as an ethylene pyrolysis furnace, so that the fluid in transmission can enter the pipe body 10 of the reinforced heat transfer pipe 1 from the inlet 100, and then the fluid becomes a rotating flow under the effect of the ribs 11, the fluid breaks a boundary layer due to tangential velocity, the coking rate is reduced, the service life of the pyrolysis furnace is prolonged, and meanwhile, the first end face 110 of the ribs 11 facing the inlet 100 is formed into a first arc surface along the spiral extending direction, so that the thermal stress of the reinforced heat transfer pipe 1 is reduced, and the service life of the reinforced heat transfer pipe 1 is prolonged. The first cambered surface is formed along the spiral extending direction, that is, the first end surface 110 is sloping in the direction along the spiral extending direction. In addition, the fluid in the enhanced heat transfer pipe 1 is not particularly limited, and may be selected according to the actual application environment of the enhanced heat transfer pipe 1.
The first cambered surface may be convex or concave, preferably, the first cambered surface is concave, so as to further improve the heat transfer effect of the reinforced heat transfer tube 1 and further reduce the thermal stress of the reinforced heat transfer tube 1. In particular, the first curved surface may be a partial paraboloid cut out from the paraboloid.
In addition, the included angle formed by the first cambered surface and the inner wall of the pipe body 10 at the connecting position can be more than 0 degrees and less than or equal to 90 degrees, so that the thermal stress of the reinforced heat transfer pipe 1 can be further reduced, and the service life of the reinforced heat transfer pipe 1 is greatly prolonged. The angle formed by the first arc surface and the inner wall of the pipe body 10 at the connection point of the first arc surface and the inner wall of the pipe body 10 may be understood as the angle between the tangent plane of the first arc surface at the connection point of the first arc surface and the tangent plane of the inner wall of the pipe body 10 at the connection point of the first arc surface and the inner wall of the pipe body. The included angle formed by the first cambered surface and the inner wall of the pipe body 10 at the connection position of the first cambered surface and the inner wall of the pipe body 10 can be 10 degrees, 15 degrees, 20 degrees, 25 degrees, 30 degrees, 35 degrees, 38 degrees, 40 degrees, 45 degrees, 50 degrees, 55 degrees, 60 degrees, 65 degrees, 70 degrees, 75 degrees, 80 degrees or 85 degrees.
In order to further reduce the thermal stress of the reinforced heat transfer tube 1, the second end surface of the rib 11 facing the outlet 101 may be formed into a second arc surface along the direction of spiral extension, that is, the second end surface may be sloped in the direction of spiral extension, which correspondingly increases the service life of the reinforced heat transfer tube 1. The second cambered surface may be convex, and may also be concave, preferably, the second cambered surface may be concave. In addition, the included angle formed by the second cambered surface and the inner wall of the pipe body 10 at the connecting position is more than 0 degrees and less than or equal to 90 degrees, so that the thermal stress of the reinforced heat transfer pipe 1 can be further reduced, and the service life of the reinforced heat transfer pipe 1 is greatly prolonged. The angle formed by the second arc surface and the inner wall of the pipe body 10 at the connection point of the second arc surface and the inner wall of the pipe body 10 may be understood as the angle between the tangent plane of the second arc surface at the connection point of the second arc surface and the tangent plane of the inner wall of the pipe body 10 at the connection point of the second arc surface and the inner wall of the pipe body. The included angle formed by the second cambered surface and the inner wall of the pipe body 10 at the connection position of the second cambered surface and the inner wall of the pipe body 10 can be 10 degrees, 15 degrees, 20 degrees, 25 degrees, 30 degrees, 35 degrees, 38 degrees, 40 degrees, 45 degrees, 50 degrees, 55 degrees, 60 degrees, 65 degrees, 70 degrees, 75 degrees, 80 degrees or 85 degrees.
As shown in fig. 1 and 3, the third end surface 111 of the rib 11 facing the central axis of the tube body 10 may be formed as a third arc surface, so that the thermal stress of the enhanced heat transfer tube 1 can be reduced without affecting the heat transfer effect of the enhanced heat transfer tube 1. Further preferably, the third cambered surface is concave. Specifically, the third arc is parabolic in shape.
Preferably, the two side wall surfaces 112 of the rib 11 opposite to each other are gradually approaching in a direction from the inner wall of the tube body 10 to the center of the tube body 10, that is, each side wall surface 112 may be disposed obliquely, so that the rib 11 can strengthen disturbance of the fluid entering the tube body 10, improve heat transfer effect, and further reduce thermal stress of the reinforced heat transfer tube 1. It will also be appreciated that the cross-section of the rib 11, i.e. taken along a plane parallel to the radial direction of the tube body 10, may be substantially trapezoidal or trapezoid-like. Of course, the rib 11 may be generally rectangular in cross-section.
In order to reduce the thermal stress of the reinforced heat transfer tube 1, a junction of at least one of two side wall surfaces 112 of the rib 11 opposite to each other and the inner wall of the tube body 10 may be formed with a smooth transition rounded corner 113. Further, the radius of the smooth transition fillet 113 is greater than 0 and less than or equal to 10mm, and the radius of the smooth transition fillet 113 is set within the above range, so that the thermal stress of the reinforced heat transfer tube 1 can be further reduced, and the service life of the reinforced heat transfer tube 1 can be prolonged. Specifically, the radius of the smooth transition fillet 113 may be 5mm, 6mm, or 10mm.
In addition, the included angle formed by each side wall surface 112 and the inner wall of the pipe body 10 at the connection point between them may be 5 ° to 90 °, that is, the included angle between each side wall surface 112 and the tangent plane of the inner wall of the pipe body 10 at the connection point between them may be 5 ° to 90 °, and setting the included angle within the above-mentioned range can further reduce the thermal stress of the reinforced heat transfer pipe 1 and improve the service life of the reinforced heat transfer pipe 1. The angle formed by each side wall surface 112 and the inner wall of the tube body 10 at the point where they are connected to each other may be 20 °, 30 °, 40 °, 45 °, 50 °, 60 °, 70 °, or 80 °.
In order to reduce the thermal stress of the reinforced heat transfer pipe 1, the height of the rib 11, that is, the distance between the third end face 111 of the rib 11 facing the central axis of the pipe body 10 and the inner wall of the pipe body 10 is preferably greater than 0 and 150mm or less, for example, the height of the rib 11 may be 10mm, 20mm, 30mm, 40mm, 50mm, 60mm, 70mm, 80mm, 90mm, 100mm, 110mm, 120mm, 130mm or 140mm.
As shown in fig. 5, the fins 11 may be provided with gaps 12 to enable the fins 11 to be spaced apart, which not only enables the enhanced heat transfer tube 1 to have a good heat transfer effect, but also enables the thermal stress of the enhanced heat transfer tube 1 to be reduced while also enabling the ability to resist local overtemperature to be improved. When the enhanced heat transfer pipe 1 provided with the gap 12 is applied to a heating furnace or a cracking furnace, the operation cycle of the heating furnace or the cracking furnace can also be improved. The number of the gaps 12 is not particularly limited, and may be selected according to actual requirements. For example, 1 gap 12 may be provided, or 2, 3, 4 or 5 gaps may be provided, and when a plurality of gaps 12 are provided, the plurality of gaps 12 are preferably arranged along the extending direction of the rib 11.
Preferably, at least one of the two side walls 120 of the gap 12 is formed as a fourth cambered surface. For example, as shown in fig. 5, both side walls 120 of the gap 12 may be formed in an arc shape, and the distance between the two side walls 120 gradually increases in a direction from near the inner wall of the pipe body 10 to far from the inner wall of the pipe body 10. Wherein the distance between the two side walls 120, i.e. the width of the gap 12, may be greater than 0 and less than or equal to 10000mm, for example, the distance between the two side walls 120 may be 1000mm, 2000mm, 3000mm, 4000mm, 5000mm, 6000mm, 7000mm, 8000mm or 9000mm. In addition, the fourth cambered surface may be recessed in a direction away from the center of the gap 12.
Furthermore, a plurality of ribs 11, for example, 2, 3, or 4, may be provided on the inner wall of the tube body 10, and the plurality of ribs 11 may be swirl-shaped clockwise or counterclockwise as viewed from the direction of the inlet 100. The plurality of ribs 11 are configured into the structure, so that the heat transfer effect of the reinforced heat transfer tube 1 is improved, the thermal stress of the reinforced heat transfer tube 1 is reduced, the high temperature resistance of the reinforced heat transfer tube 1 is improved, and the service life of the reinforced heat transfer tube 1 is greatly prolonged.
Preferably, a plurality of ribs 11 may enclose a through hole 13 formed at the center of the tube body 10 extending in the axial direction of the tube body 10 as viewed from the direction of the inlet 100 to facilitate the flow of fluid into the tube body 10, reducing pressure drop. In order to minimize the pressure drop, the ratio between the diameter D of the through hole 13 and the inner diameter D of the tube body 10 may preferably be D: d is greater than 0 and less than 1, e.g., D: d is 0.1, 0.2, 0.3, 0.4, 0.5, 0.6, 0.7, 0.8 or 0.9.
In order to enhance the disturbance of the fluid by the rib 11, the rotation angle of the rib 11 may be preferably 90 to 1080 °, for example, the rotation angle of the rib 11 may be 120 °, 180 °, 360 °, 720 °, or 1080 °.
In general, the ratio of the axial length of the ribs 11 rotated 180 ° to the inner diameter D of the tube body 10 is a twist ratio, which determines the length of each rib 11, and the rotation angle of the ribs 11 determines the degree of twist of the ribs 11, thereby affecting the heat transfer efficiency. The twist ratio of the rib 11 may be 2.3-2.6, for example, the twist ratio of the rib 11 may be 2.35, 2.4, 2.5, 2.49 or 2.5.
In addition, the length L of the rib 11 in the axial direction of the pipe body 10 1 The ratio of the inner diameter D of the pipe body 10 is L 1 : d=1-10:1, preferably L 1 ：D＝1-6:1。
The invention also provides a cracking furnace, which comprises a radiation chamber, wherein at least one radiation furnace tube assembly is arranged in the radiation chamber, the radiation furnace tube assembly comprises a plurality of radiation furnace tubes which are sequentially arranged, and reinforced heat transfer tubes which are communicated with adjacent radiation furnace tubes, namely reinforced heat transfer tubes 1, can be axially arranged in the radiation furnace tubes in a spacing mode, and the reinforced heat transfer tubes are the reinforced heat transfer tubes 1 provided by the invention. By arranging the reinforced heat transfer pipe 1 provided by the invention in the radiation chamber of the cracking furnace, the heat transfer effect of fluid in the radiation chamber can be improved, and the thermal stress of the reinforced heat transfer pipe 1 is reduced, so that the operation period and the high temperature resistance of the cracking furnace are improved. Specifically, 2, 3, 4, 5, 6, 7, 8, 9, or 10 enhanced heat transfer tubes 1 may be provided in the radiant tube assembly.
Preferably, the axial length L of the radiation furnace tube 2 The ratio of the inner diameter D of the pipe body 10 is L 2 : d=15-75, thus enabling further improvements in heat transfer efficiency and in the operating cycle of the cracking furnace. Further preferably L 2 ：D＝25-50。
The effects of the present invention are further illustrated by examples and comparative examples below.
Examples
Example 1
A plurality of radiation furnace tube assemblies are arranged in a radiation chamber of the cracking furnace, reinforced heat transfer tubes 1 are arranged in 3 radiation furnace tube assemblies, 2 reinforced heat transfer tubes 1 are arranged in each radiation furnace tube assembly at intervals along the axial direction of the radiation furnace tube, the inner diameter of each reinforced heat transfer tube 1 is 65mm, and the axial length of a radiation furnace tube between every two adjacent 2 reinforced heat transfer tubes 1 in each radiation furnace tube assembly is 50 times of the inner diameter of the reinforced heat transfer tube 1. The structure of each of the reinforced heat transfer pipes 1 is: a cylindrical heat insulating piece 14 is arranged outside the pipe body 10, the heat insulating piece 14 completely surrounds the periphery of the pipe body 10, a gap 15 is reserved between the heat insulating piece 14 and the outer wall of the pipe body 10, and the heat insulating piece 14 is connected with the pipe body 10 through a connecting rod 162; on the inner wall of the pipe body 10, 2 ribs 11 are provided, and at both ends of the ribs 11, a first arc surface and a second arc surface are formed in a concave shape along the spiral extending direction as shown in fig. 1, respectively, the first arc surface forms an angle of 30 ° with the pipe wall of the pipe body 10 at the connection point with each other, the second arc surface forms an angle of 30 ° with the pipe wall of the pipe body 10 at the connection point with each other, the cross section of each rib 11 is approximately trapezoidal, that is, the cross section taken along the plane parallel to the radial direction of the pipe body 10, the angle formed by each side wall surface 112 with the inner wall of the pipe body 10 at the connection point with each other is 45 °, the connection point of each side wall surface 112 with the inner wall of the pipe body 10 forms a smooth transition fillet, the two ribs 11 are in a clockwise vortex shape as viewed from the direction of the inlet 100, the two ribs 11 enclose a through hole 13 extending along the axial direction of the pipe body 10 at the center of the pipe body 10, the ratio of the diameter of the through hole 13 to the inner diameter of the pipe body 10 is 0.6, the rotation angle of each rib 11 is 180 °, and the ratio of each rib 11 is 2.5. Wherein the COT temperature of the cracking furnace is 820-830 degrees.
Example 2
The same as in example 1, except that the heat insulating member 14 is elliptical, the angle formed by the first arc surface and the pipe wall of the pipe body 10 at the connection point is 35 °, the angle formed by the second arc surface and the pipe wall of the pipe body 10 at the connection point is 35 °, and the other conditions are unchanged.
Example 3
The same as in example 1, except that the heat insulating member 14 is attached to the outer wall of the pipe body 10, the angle formed by the first arc surface and the pipe wall of the pipe body 10 at the connection point is 40 °, the angle formed by the second arc surface and the pipe wall of the pipe body 10 at the connection point is 40 °, and the other conditions are unchanged.
Comparative example
Comparative example 1
The same as in example 1, except that the structure of the enhanced heat transfer tube was changed, i.e., the enhanced heat transfer tube of the prior art was provided, in which the outside of the tube body was not provided with a heat insulating member, only one twisted piece was provided in the tube body, which was spirally extended in the axial direction of the tube body, and which divided the inside of the tube body into two chambers which were not communicated with each other, and the remaining conditions were unchanged.
Test examples
The results of the respective tests of the cracking furnaces of the examples and the comparative examples after operation under the same conditions are shown in the following table 1.
TABLE 1
Therefore, the reinforced heat transfer pipe provided by the invention is arranged in the cracking furnace, so that the maximum thermal stress of the reinforced heat transfer pipe is reduced, and the service life of the reinforced heat transfer pipe is greatly prolonged.
The preferred embodiments of the present invention have been described in detail above with reference to the accompanying drawings, but the present invention is not limited thereto. Within the scope of the technical idea of the invention, a number of simple variants of the technical solution of the invention are possible, including combinations of individual specific technical features in any suitable way. The various possible combinations of the invention are not described in detail in order to avoid unnecessary repetition. Such simple variations and combinations are likewise to be regarded as being within the scope of the present disclosure.
Claims (31)
1. The reinforced heat transfer tube (1) is characterized in that the reinforced heat transfer tube (1) is arranged between two adjacent sections of radiation furnace tubes of a cracking furnace, the reinforced heat transfer tube (1) comprises a tube body (10) which is tubular and is provided with an inlet (100) for fluid to enter and an outlet (101) for the fluid to flow out, the inner wall of the tube body (10) is provided with twisting sheets, and the outside of the tube body (10) is provided with a heat insulation piece (14) which at least partially surrounds the periphery of the tube body (10).
2. The reinforced heat transfer tube of claim 1, wherein the heat insulating member (14) is tubular, and the heat insulating member (14) is sleeved outside the tube body (10).
3. A reinforced heat transfer tube according to claim 2, wherein a void (15) is left between the heat shield (14) and the outer wall of the tube body (10).
4. A reinforced heat transfer tube according to claim 3, wherein a connection connecting the heat insulating member (14) and the tube body (10) is provided between the heat insulating member (14) and the tube body (10).
5. The enhanced heat transfer tube of claim 4 wherein said connector is selected from one or more of the following three structures: the connection comprises a first connection tab (160), the first connection tab (160) extending in an axial direction parallel to the tube body (10); the connecting piece comprises a second connecting piece which extends spirally along the outer wall of the pipe body (10); the connecting piece comprises a connecting rod (162), and two ends of the connecting rod (162) are respectively connected with the outer wall of the pipe body (10) and the inner wall of the heat insulation piece (14).
6. The reinforced heat transfer tube of claim 4 wherein the connector is made of a hard material or a soft material.
7. The enhanced heat transfer tube of claim 2 wherein the thermal shield (14) comprises a straight tube section (140) and first and second tapered tube sections (141, 142) connected to first and second ports of the straight tube section (140), respectively, wherein the first tapered tube section (141) tapers in a direction from proximate the first port to distal the first port and the second tapered tube section (142) tapers in a direction from proximate the second port to distal the second port.
8. The reinforced heat transfer tube of claim 7, wherein the angle between the outer wall surface of the first tapered tube section (141) and the horizontal plane is 10-80 °; and/or the included angle formed between the outer wall surface of the second tapered pipe section (142) and the horizontal plane is 10-80 degrees.
9. A reinforced heat transfer tube according to claim 1, wherein the length of extension of the heat insulating member (14) in the axial direction of the tube body (10) is 1-2 times the length of the tube body (10).
10. A reinforced heat transfer tube according to claim 1, wherein the insulation (14) is located outside the tube body (10) where the torsion tabs are provided.
11. The reinforced heat transfer tube according to any one of claims 1-10, wherein the twisted sheet comprises ribs (11) protruding from an inner wall of the tube body (10) toward the inside of the tube body (10), the ribs (11) extending helically in an axial direction of the tube body (10), wherein a first end face (110) of the ribs (11) facing the inlet (100) is formed as a first arc surface in a helically extending direction.
12. The enhanced heat transfer tube of claim 11 wherein said first arcuate surface is concave; and/or the included angle formed by the first cambered surface and the inner wall of the pipe body (10) at the connecting part is more than 0 degrees and less than or equal to 90 degrees.
13. A reinforced heat transfer tube according to claim 11, wherein the second end surface of the rib (11) facing the outlet (101) is formed as a second cambered surface in the direction of spiral extension.
14. The enhanced heat transfer tube of claim 13 wherein said second arcuate surface is concave; and/or the included angle formed by the second cambered surface and the inner wall of the pipe body (10) at the connecting part is more than 0 degrees and less than or equal to 90 degrees.
15. A reinforced heat transfer tube according to claim 11, wherein a third end surface (111) of the rib (11) facing the central axis of the tube body (10) is formed as a third cambered surface.
16. The enhanced heat transfer tube of claim 15 wherein said third arcuate surface is concave.
17. The reinforced heat transfer tube of claim 11, wherein two side wall surfaces (112) of the fin (11) opposite to each other are gradually closer in a direction from an inner wall of the tube body (10) to a center of the tube body (10).
18. The reinforced heat transfer tube of claim 17, wherein a smooth transition fillet (113) is formed at a junction of at least one of the two side wall surfaces (112) of the fin (11) opposite to each other and the inner wall of the tube body (10).
19. A reinforced heat transfer tube according to claim 17, wherein each of said side wall surfaces (112) forms an angle of 5 ° to 90 ° with the inner wall of said tube body (10) at the point of connection to each other.
20. A reinforced heat transfer tube according to claim 11, wherein the height of the ribs (11) is greater than 0 and less than or equal to 150mm.
21. A reinforced heat transfer tube according to claim 11, wherein the height of the fins (11) is 10-50mm.
22. A reinforced heat transfer tube according to claim 11, wherein the fins (11) are provided with gaps (12) capable of spacing the fins (11).
23. The reinforced heat transfer tube of claim 22, wherein the plurality of gaps (12) are provided, and wherein the plurality of gaps (12) are aligned along the extending direction of the fin (11).
24. The enhanced heat transfer tube of claim 22 wherein at least one of the two sidewalls (120) of the gap (12) is formed as a fourth arcuate surface.
25. The enhanced heat transfer tube of claim 24 wherein the fourth arcuate surface is concave in a direction away from the center of the gap (12).
26. The reinforced heat transfer tube of claim 11, wherein the plurality of ribs (11) are provided, the plurality of ribs (11) being swirl-like clockwise or counter-clockwise as seen in the direction of the inlet (100).
27. A reinforced heat transfer tube according to claim 26, wherein a plurality of the ribs (11) are formed around a through hole (13) extending in the axial direction of the tube body (10) at the center of the tube body (10) as seen in the direction of the inlet (100), the ratio D between the diameter D of the through hole and the inner diameter D of the tube body (10): d is more than 0 and less than 1.
28. The reinforced heat transfer tube according to claim 11, wherein the rotation angle of the ribs (11) is 90-1080 °, and/or the length L of the ribs (11) in the axial direction of the tube body (10) 1 The ratio of the inner diameter D of the pipe body (10) to the inner diameter D is L 1 ：D＝1-10:1。
29. A cracking furnace, characterized in that the cracking furnace comprises a radiation chamber, at least one radiation furnace tube assembly is arranged in the radiation chamber, the radiation furnace tube assembly comprises a plurality of radiation furnace tubes which are sequentially arranged and reinforced heat transfer tubes which are communicated with adjacent radiation furnace tubes, and the reinforced heat transfer tubes are the reinforced heat transfer tubes (1) of any one of claims 1-28.
30. The pyrolysis furnace of claim 29 wherein the radiant furnace tube has an axial length L 2 The ratio of the inner diameter D of the pipe body (10) to the inner diameter D is L 2 ：D＝15-75。
31. The pyrolysis furnace of claim 30, wherein L 2 ：D＝25-50。
Priority Applications (21)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711027588.XA CN109724445B (en) | 2017-10-27 | 2017-10-27 | Reinforced heat transfer pipe and cracking furnace |
| PCT/CN2018/111797 WO2019080886A1 (en) | 2017-10-27 | 2018-10-25 | Enhanced heat transfer pipe, and pyrolysis furnace and atmospheric and vacuum heating furnace comprising same |
| CA3079638A CA3079638A1 (en) | 2017-10-27 | 2018-10-25 | Heat transfer enhancement pipe as well as cracking furnace and atmospheric and vacuum heating furnace including the same |
| CA3079047A CA3079047A1 (en) | 2017-10-27 | 2018-10-25 | Heat transfer enhancement pipe as well as cracking furnace and atmospheric and vacuum heating furnace including the same |
| CA3079647A CA3079647A1 (en) | 2017-10-27 | 2018-10-25 | Heat transfer enhancement pipe as well as cracking furnace and atmospheric and vacuum heating furnace including the same |
| RU2020117336A RU2757041C1 (en) | 2017-10-27 | 2018-10-25 | Heat transfer intensifying pipe, cracking furnace and atmospheric-vacuum heating furnace comprising said pipe |
| SG11202003400PA SG11202003400PA (en) | 2017-10-27 | 2018-10-25 | Heat transfer enhancement pipe as well as cracking furnace and atmospheric and vacuum heating furnace including the same |
| RU2020115573A RU2753091C1 (en) | 2017-10-27 | 2018-10-25 | Heat transfer intensifying pipe, cracking furnace and atmospheric-vacuum heating furnace comprising said pipe |
| KR1020207015221A KR102442585B1 (en) | 2017-10-27 | 2018-10-25 | Heat transfer enhancement pipe and pyrolysis furnace comprising same, atmospheric and vacuum furnace |
| EP18870774.9A EP3702714A4 (en) | 2017-10-27 | 2018-10-25 | Enhanced heat transfer pipe, and pyrolysis furnace and atmospheric and vacuum heating furnace comprising same |
| US16/758,155 US11976891B2 (en) | 2017-10-27 | 2018-10-25 | Heat transfer enhancement pipe as well as cracking furnace and atmospheric and vacuum heating furnace including the same |
| SG11202003475RA SG11202003475RA (en) | 2017-10-27 | 2018-10-25 | Heat transfer enhancement pipe as well as cracking furnace and atmospheric and vacuum heating furnace including the same |
| KR1020207015185A KR102442584B1 (en) | 2017-10-27 | 2018-10-25 | Heat transfer enhancement pipe, pyrolysis furnace comprising same, and atmospheric and vacuum heating furnace |
| US16/757,836 US20210190442A1 (en) | 2017-10-27 | 2018-10-25 | Heat transfer enhancement pipe as well as cracking furnace and atmospheric and vacuum heating furnace including the same |
| KR1020207015184A KR102482259B1 (en) | 2017-10-27 | 2018-10-25 | Improved heat transfer pipe, and pyrolysis furnace including the same |
| PCT/CN2018/111795 WO2019080885A1 (en) | 2017-10-27 | 2018-10-25 | Enhanced heat transfer pipe, and pyrolysis furnace and atmospheric and vacuum heating furnace comprising same |
| US16/758,850 US20210180879A1 (en) | 2017-10-27 | 2018-10-25 | Heat transfer enhancement pipe as well as cracking furnace and atmospheric and vacuum heating furnace including the same |
| EP18871432.3A EP3702715A4 (en) | 2017-10-27 | 2018-10-25 | Enhanced heat transfer pipe, and pyrolysis furnace and atmospheric and vacuum heating furnace comprising same |
| PCT/CN2018/111798 WO2019080887A1 (en) | 2017-10-27 | 2018-10-25 | Enhanced heat transfer pipe, and pyrolysis furnace and atmospheric and vacuum heating furnace comprising same |
| RU2020115117A RU2753098C1 (en) | 2017-10-27 | 2018-10-25 | Heat transfer intensifying pipe, cracking furnace and atmospheric-vacuum heating furnace comprising this pipe |
| EP18870014.0A EP3702713A4 (en) | 2017-10-27 | 2018-10-25 | Enhanced heat transfer pipe, and pyrolysis furnace and atmospheric and vacuum heating furnace comprising same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711027588.XA CN109724445B (en) | 2017-10-27 | 2017-10-27 | Reinforced heat transfer pipe and cracking furnace |
Publications (2)
| Publication Number | Publication Date |
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| CN109724445A CN109724445A (en) | 2019-05-07 |
| CN109724445B true CN109724445B (en) | 2023-07-21 |
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| CN201711027588.XA Active CN109724445B (en) | 2017-10-27 | 2017-10-27 | Reinforced heat transfer pipe and cracking furnace |
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Family Cites Families (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1133862C (en) * | 1998-09-16 | 2004-01-07 | 中国石油化工集团公司 | Heat exchange pipe and its manufacture method and application |
| CN2836913Y (en) * | 2005-08-05 | 2006-11-15 | 上海惠生化工工程有限公司 | Two-segment radiation furnace pipe with novel structure and arrangement for cracking furnace |
| CN100365370C (en) * | 2005-12-20 | 2008-01-30 | 金龙精密铜管集团股份有限公司 | Internal thread heat transfer pipe |
| CN201770662U (en) * | 2010-05-07 | 2011-03-23 | 华东理工大学 | Cracking furnace tube based on field synergy effect |
| CN102759294B (en) * | 2011-04-29 | 2014-07-16 | 中国石油化工股份有限公司 | Reinforced heat transfer pipe with spinning disks |
| CN103788982B (en) * | 2012-10-30 | 2018-06-15 | 中国石油化工股份有限公司 | The ethane cracking furnace of two-range radiant section boiler tube and its application in chemical field |
| CN104560111B (en) * | 2013-10-25 | 2017-08-25 | 中国石油化工股份有限公司 | Heat-transfer pipe and use its pyrolysis furnace |
| CN103697740A (en) * | 2013-12-18 | 2014-04-02 | 杭州汉惠通用设备有限公司 | Inner petal-shaped irregular-shaped heat exchange tube |
| CN105222634A (en) * | 2014-06-06 | 2016-01-06 | 关中股份有限公司 | Heat-exchange tube |
| JP6357706B2 (en) * | 2015-05-22 | 2018-07-18 | 三菱重工環境・化学エンジニアリング株式会社 | Heat exchanger |
| CN105444602A (en) * | 2015-12-04 | 2016-03-30 | 安阳方快锅炉有限公司 | Novel inner finned pipe for boiler |
| CN105806127B (en) * | 2016-05-03 | 2018-06-26 | 西安交通大学 | A kind of boiler water wall riffled tube with streamline section internal-rib |
| CN205980896U (en) * | 2016-08-03 | 2017-02-22 | 湖南太子新材料科技有限公司 | High temperature cooling tube |
| CN206269658U (en) * | 2016-12-05 | 2017-06-20 | 郑州市意达高能换热设备有限公司 | A kind of thermoexcell |
-
2017
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