CN109900143B - Heat exchanger for flue gas heat exchange and heat exchange method - Google Patents
Heat exchanger for flue gas heat exchange and heat exchange method Download PDFInfo
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- CN109900143B CN109900143B CN201910249076.0A CN201910249076A CN109900143B CN 109900143 B CN109900143 B CN 109900143B CN 201910249076 A CN201910249076 A CN 201910249076A CN 109900143 B CN109900143 B CN 109900143B
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Abstract
The invention provides a heat exchanger for flue gas heat exchange and a heat exchange method, wherein the heat exchanger comprises a cylindrical heat exchanger main body (6), a flue gas inlet (1) and a flue gas outlet (4) are respectively arranged on two sides of the heat exchanger main body (6) along the axial direction, a flue gas runner (5) penetrates through the interior of the heat exchanger main body (6), a heat exchange pipe (3) is arranged in the flue gas runner (5) along the axial direction, and a pouring gas runner (2) is formed in the space inside the heat exchanger main body (6) and outside a flue gas pipeline (5); the flue gas is introduced through the flue gas inlet (1), flows through the flue gas runner (5) through the flue gas runner inlet (51), is cooled by a heat exchange medium introduced into the heat exchange tube (3) and/or the pouring gas runner (2), and is discharged from the flue gas outlet (4) through the flue gas runner outlet (52). According to the invention, the heat exchanger can ensure that the working fluid is uniformly distributed in the heat exchanger in a stroke way, the speed is uniform, the heat exchange efficiency is high, the resistance is lower, and the heat exchanger is an effective improvement on the existing heat exchanger.
Description
Technical Field
The invention relates to the fields of refrigeration, industrial refrigeration, air conditioning, heating and the like, in particular to a heat exchanger for flue gas heat exchange and a heat exchange method.
Background
The existing heat exchanger is generally of a traditional tube bundle structure, as shown in fig. 1, a large number of convection tube bundles are arranged, and when flue gas passes through gaps between the transverse direction and the longitudinal direction of tubes, the flue gas can generate 'turbulent flow' such as rotation, flow distribution, confluence and the like, so that the flue gas resistance is high; due to the reasons of height, size, structural limitation and the like of the flue gas inlet and outlet, the total average heat exchange coefficient is low because the heat exchange coefficient is uneven caused by the dead space which can not be flushed by local flue gas; sometimes, the convection bank vibrates due to reasons such as long length of the convection bank, high flue gas speed, unreasonable arrangement of the bank spacing and the like, so that the operation safety is damaged; in the convection tube bundle, as the flue gas is gradually cooled, the flow velocity is gradually reduced, which leads to the reduction of the heat exchange coefficient of the end heat exchange tube.
Disclosure of Invention
The invention aims to solve at least one of the problems that the smoke resistance is high, the heat exchanger has dead space to cause uneven heat exchange coefficient, the tail smoke flow speed is reduced to cause lower heat exchange coefficient, and the vibration of the heat exchange tube harms the operation safety.
In order to solve the problems in the prior art, the inventor of the present invention has conducted a keen study to provide a heat exchanger for flue gas heat exchange, wherein a plurality of flue gas flow channels are uniformly distributed in the heat exchanger, flue gas is cooled by heat exchange tubes arranged in the flue gas flow channels and/or heat exchange media in pouring gas flow channels outside the flue gas flow channels and then discharged, and limit and rigidity enhancement measures are provided for the heat exchange tubes to avoid vibration of the heat exchange tubes. The heat exchanger has a novel structure, can ensure that the working fluid has uniform distribution of stroke, uniform speed, high heat exchange efficiency and lower resistance in the heat exchanger, and has safe operation, thereby completing the invention.
The invention aims to provide the following technical scheme:
(1) a heat exchanger for flue gas heat exchange comprises a cylindrical heat exchanger body 6, wherein a flue gas inlet 1 and a flue gas outlet 4 are respectively arranged on two sides of the heat exchanger body 6 along the axial direction, a flue gas channel inlet 51 is formed on the side wall of the heat exchanger body 6 on the flue gas inlet side, a flue gas channel 5 penetrates through the interior of the heat exchanger body, a flue gas channel outlet 52 is formed on the side wall of the heat exchanger body 6 on the flue gas outlet side, a heat exchange tube 3 is arranged in the flue gas channel 5 along the axial direction, and a pouring gas channel 2 is formed in the space inside the heat exchanger body 6 and outside the flue gas channel 5;
the flue gas is introduced through the flue gas inlet 1, flows through the flue gas runner 5 through the flue gas runner inlet 51, is cooled by the heat exchange medium introduced into the heat exchange tube 3 and/or the pouring gas runner 2, and is discharged from the flue gas outlet 4 through the flue gas runner outlet 52.
(2) A heat exchange method comprises the steps that flue gas passes through a flue gas flow channel which is uniformly distributed in a heat exchanger, and is discharged out of the heat exchanger after being cooled;
preferably, the heat exchanger is the heat exchanger used for flue gas heat exchange in the above (1).
According to the heat exchanger and the heat exchange method for flue gas heat exchange provided by the invention, the following beneficial effects are achieved:
(1) according to the invention, the plurality of flue gas flow channels are uniformly distributed in the heat exchanger main body of the heat exchanger, flue gas passes through the uniformly distributed flue gas flow channels, the airflow organization is uniform, the stroke is smooth and intuitive, the stroke length of each flue gas flow channel is basically equivalent, and compared with the traditional convection tube bundle structure, the heat exchanger has the advantages of lower flue gas resistance and higher heat exchange coefficient.
(2) In the pouring gas flow channel, the diameter of the section of the ring on the periphery of the heat exchange tube is gradually reduced along with the flowing direction of the flue gas, and/or the width of the pouring gas flow channel is reduced along the way, so that the tail end flue gas flow can still keep a certain speed to keep the heat exchange effect.
(3) According to the invention, the plurality of convex structures are arranged in the pouring gas flow channel and/or the plurality of convex structures are arranged on the outer wall of the heat exchange tube to support the heat exchange tube to enhance the rigidity of the heat exchange tube, so that the vibration problem of the convection tube bundle caused by the length of the tube bundle, the arrangement of the tube bundle, the smoke speed and the like is avoided.
Drawings
FIG. 1 is a schematic diagram of a heat exchanger in the prior art;
fig. 2 shows a longitudinal sectional view and a transverse sectional view of a heat exchanger according to a preferred embodiment of the present invention;
FIG. 3 is a transverse sectional view showing a heat exchanger according to a preferred embodiment of the present invention, in which the diameter of the circular cross section of the circumference of the heat exchange tube is gradually reduced with the flow direction of the flue gas;
FIG. 4 shows a transverse cross-sectional view of a heat exchanger according to a preferred embodiment of the present invention, wherein several raised structures are arranged within the cast gas flow channel;
fig. 5 shows a transverse cross-section of a heat exchanger according to a preferred embodiment of the invention, wherein a number of raised structures are arranged on the outer wall of the heat exchanger tubes.
The reference numbers illustrate:
1-a flue gas inlet;
2-pouring a gas flow channel;
3, heat exchange tubes;
4-a flue gas outlet;
5-flue gas flow channel;
51-flue gas channel inlet;
52-flue gas runner outlet;
6-heat exchanger body.
7-bulge structure I;
8-bulge structure II.
Detailed Description
The invention is explained in more detail below with reference to the figures and examples. The features and advantages of the present invention will become more apparent from the description.
The word "exemplary" is used exclusively herein to mean "serving as an example, embodiment, or illustration. Any embodiment described herein as "exemplary" is not necessarily to be construed as preferred or advantageous over other embodiments.
As shown in fig. 2, the invention provides a heat exchanger for flue gas heat exchange, which comprises a cylindrical heat exchanger body 6, wherein a flue gas inlet 1 and a flue gas outlet 4 are respectively arranged on two sides of the heat exchanger body 6 along the axial direction, a flue gas channel inlet 51 is formed on the side wall of the heat exchanger body 6 on the flue gas inlet side, a flue gas channel 5 passes through the inside of the heat exchanger body, a flue gas channel outlet 52 is formed on the side wall of the heat exchanger body 6 on the flue gas outlet side, a heat exchange tube 3 is arranged in the flue gas channel 5 along the axial direction, and a pouring gas channel 2 is formed in the space inside the heat exchanger body 6 and outside the flue gas; the flue gas is introduced through the flue gas inlet 1, flows through the flue gas runner 5 through the flue gas runner inlet 51, is cooled by the heat exchange medium introduced into the heat exchange tube 3 and/or the pouring gas runner 2, and is discharged from the flue gas outlet 4 through the flue gas runner outlet 52.
In the present invention, the heat exchanger body 6 constitutes a main body and an external structure of the heat exchanger, and the heat exchanger body 6 is a cylindrical structure, preferably an axially symmetric structure, such as a cylinder, a regular prism cylinder (e.g., a regular triangular cylinder, a regular rectangular prism cylinder), a cylinder having an elliptical cross section, a cylinder having a fan-shaped cross section, and the like, and more preferably a cylinder.
In the invention, the pouring gas channel 2 can be a solid structure, that is, the structure body of the pouring gas channel 2 is a solid structure, and at the moment, the pouring gas channel 2 mainly plays a role in supporting other structures, such as limiting and protecting the flue gas channel 5 and the heat exchange tube 3.
The pouring gas channel 2 can also be a shell structure, that is, the pouring gas channel 2 structure body is a hollow structure, at this time, the flue gas channel 5 is an independently formed structure (such as a channel surrounded by plates), a heat exchange medium can be introduced into the pouring gas channel 2, and the heat exchange medium flows in the axial direction and exchanges heat with the flue gas flowing in the flue gas channel 5.
The heat exchange medium in the pouring gas flow channel 2 can be a liquid heat exchange medium or a gas heat exchange medium, the liquid heat exchange medium is cold water, and the gas heat exchange medium is low-temperature flue gas.
In a preferred embodiment of the invention, the flue gas channel inlet 51 of the flue gas channel 5 falls into the flue gas inlet 1 and the flue gas channel outlet 52 falls into the flue gas outlet 4. Preferably, all of the flue gas channel inlets 51 fall into the flue gas inlet 1 and all of the flue gas channel outlets 52 fall into the flue gas outlet 4.
The flue gas channels 5 are evenly distributed in the heat exchanger body 6 to reduce the risk of "dead space" due to uneven heat transfer coefficients.
Preferably, the channel stroke of each flue gas channel 5 is similar; the number of the heat exchange tubes in each flue gas flow channel 5 is similar, and preferably, the number of the heat exchange tubes in each flue gas flow channel 5 is the same.
More preferably, the flue gas channels 5 are not communicated with each other and are independent gas channels.
The flue gas runner 5 is evenly arranged, the stroke length of each flue gas runner 5 is basically equivalent, so that the flue gas passes through the flue gas runner 5, the airflow organization is even, the stroke is smooth and intuitive, compared with the traditional convection bank structure, the flue gas circulates on the set path, the problem that the flue gas resistance is higher due to 'turbulent flow' such as rotation, flow distribution and convergence when the stroke of the flue gas passes through the transverse and longitudinal gaps of the heat exchange tube in the heat exchanger is solved, and meanwhile, the flue gas heat exchange coefficient is higher.
In the present invention, the heat exchange tubes 3 are preferably disposed generally axially within the flue gas flow channel 5. In addition, the heat exchange tubes 3 can be arranged in the vertical axial direction, the diameter of each heat exchange tube can be a straight line or a curve, and heat exchange is carried out between a heat exchange medium in each heat exchange tube and flue gas in the flue gas flow channel 5 through heat conduction or heat radiation.
For example, the heat exchange tube 3 may be sleeved inside or outside the flue gas channel 5, and a heat exchange medium circulates in a channel formed between the heat exchange tube 3 and the flue gas channel 5 to exchange heat with the flue gas in the flue gas channel 5.
In the invention, the heat exchange tubes 3 are uniformly distributed in the heat exchanger main body 6, so that the uniformity of heat exchange is improved, and preferably, when the heat exchanger main body 6 is of an axially symmetrical structure, the heat exchange tubes 3 are symmetrically distributed in the heat exchanger main body 6 along the symmetrical axis of the heat exchanger main body.
In a preferred embodiment of the invention, the casting gas flow channel 2 is a cylinder, the heat exchange tubes 3 comprise 1 central heat exchange tube axially arranged in the center of the heat exchanger main body 6, 6I-stage heat exchange tubes surrounding the central heat exchange tube, and 13 II-stage heat exchange tubes surrounding the I-stage heat exchange tubes, the distances between the I-stage heat exchange tubes are similar, the distances between the II-stage heat exchange tubes are similar, and the I-stage heat exchange tubes and the II-stage heat exchange tubes are distributed in an axial symmetry manner. Four independent flue gas runners 5 are formed in the pouring gas runner 2, each flue gas runner 5 comprises 5 heat exchange tubes 3, and the principle that the flue gas runners 5 are communicated with the heat exchange tubes 3 is a nearby principle and the principle that the flow of each flue gas runner 5 is similar.
In the present invention, the heat exchange tube 3 may be designed as a light tube, a threaded tube, a flat tube, a finned tube, or other special tubes.
In a preferred embodiment of the invention, in the flue gas flowing direction, the width of the flue gas flow channel 5 close to two sides of the heat exchange tube 3 is not more than the maximum radial width of the heat exchange tube 3, the flue gas flow channel 5 part passing through the heat exchange tube 3 is expanded to form an annular flow channel surrounding the heat exchange tube 3, and the flue gas is divided when passing through the heat exchange tube 3 and is in integral contact with the heat exchange tube 3, so that the heat exchange is carried out efficiently. The cross-sectional area of the annular flow passage can be circular, elliptical, square, polygonal and the like, and is not limited herein, but is preferably circular, so that the smoke flow resistance is reduced.
For example, when the heat exchange tube 3 is a round tube, a portion of the flue gas flow channel 5 passing through the heat exchange tube 3 is expanded to form a circular flow channel surrounding the heat exchange tube 3, and the flue gas can be in integral contact with the heat exchange tube 3 when passing through the heat exchange tube 3.
In the invention, the heat exchange medium in the heat exchange tube 3 can be a liquid heat exchange medium such as cold water or a gas heat exchange medium such as low-temperature flue gas. The heat exchange medium can be freely selected according to the use environment of the heat exchange tube.
The inventor discovers that in a convection tube bundle, as flue gas is gradually cooled, the flow speed is gradually reduced, the heat exchange coefficient of the tail end is greatly reduced, the overall heat exchange coefficient is low, and the heat exchange of the heat exchanger is uneven through research on the heat exchanger in the prior art. To solve this problem, the present inventors provide the following embodiments.
As shown in fig. 3, in a preferred embodiment of the present invention, the flue gas flow channel 5 has a constant width, and the cross section of the flue gas flow channel part (preferably, the flow channel part is an annular flow channel) at the periphery of the heat exchange tube 3 is gradually reduced along with the flow direction of the flue gas, so that the flow rate of the flue gas is substantially stable, and the tail end flue gas flow is kept at a certain speed to keep the heat exchange effect.
In another preferred embodiment of the present invention, the flue gas flow channel portion (preferably, the flow channel portion is an annular flow channel) at the periphery of the heat exchange tube 3 has the same cross section, the width of the flue gas flow channel 5 gradually decreases along the flow direction of the flue gas, and the cross section of the flow channel gradually decreases along the travel of the flue gas, so that the tail end flue gas flow still maintains a certain speed.
In another preferred embodiment of the present invention, the cross section of the flue gas channel portion (preferably, the channel portion is an annular channel) at the periphery of the heat exchange tube 3 and the width of the flue gas channel 5 gradually decrease along the flow direction of the flue gas, so as to maintain sufficient scouring speed and heat exchange effect.
The inventor researches and discovers that in the prior art, under the conditions of long length of a heat exchange tube, high flue gas speed, unreasonable interval arrangement of the heat exchange tube and the like, the vibration of the convection tube is easily caused, and the operation safety is damaged. The invention can effectively inhibit the vibration of the heat exchange tube by controlling the flue gas in the flue gas flow channel and uniformly arranging the heat exchange tube. Meanwhile, the inventor carries out further research, and strengthens the limit or enhances the rigidity of the heat exchange pipe so as to reduce the vibration degree of the convection pipe under sudden conditions (such as sudden change of flue gas flow velocity) and further improve the safety of the heat exchange pipe.
In a preferred embodiment of the invention, as shown in fig. 4, a plurality of convex structures I7 facing the heat exchange tubes 3 are arranged on the flue gas flow passage portion (preferably, the flow passage portion is an annular flow passage) of the periphery of the heat exchange tubes 3 to support the heat exchange tubes 3.
In another preferred embodiment of the present invention, as shown in fig. 5, a plurality of convex structures II 8 facing the flue gas channel 5 are arranged on the outer wall of the heat exchange tube 3, and the convex structures II 8 shorten (or even cancel) the distance between the heat exchange tube 3 and the flue gas channel 5, so as to limit the heat exchange tube 3.
When the convex structure II 8 is a strip-shaped protrusion, the convex structure II 8 can further serve as a reinforcing strip to enhance the strength of the heat exchange tube 3.
The convex structure I7 or the convex structure II 8 can be discontinuously connected with the heat exchange tube 3 and the flue gas runner 5, so that the absolute limiting effect is achieved; or the convex structure I7 or the convex structure II 8 is not connected with the heat exchange tube 3 and the flue gas flow channel 5, so that the relative limiting effect is achieved. It should be understood that when the raised structures I7 or II 8 are intermittently connected with the heat exchange tubes 3 and the flue gas flow channel 5, the raised structures I7 or II 8 are not arranged to cause absolute obstruction to the flow of flue gas on either side.
Preferably, the convex structure I7 or the convex structure II 8 is not connected with the heat exchange tube 3 and the flue gas flow channel 5, so that the difficulty of the manufacturing process is reduced.
In a further preferred embodiment, the protruding structures I7 or II 8 may be dot-shaped protruding structures, axial stripe-shaped protruding structures, radial stripe-shaped protruding structures, random/non-specific direction stripe-shaped protruding structures, or the like.
It is worth noting that the arrangement of the protruding structure can generate disturbance to the flue gas in the flue gas channel 5, reduce the thermal resistance of the boundary layer in the flue gas channel 5, enhance the heat transfer, improve the heat exchange efficiency, and meanwhile, the normal circulation of the flue gas is not affected by too high flue gas resistance (especially when the protruding structure plays a relative limiting role), and the strength of the disturbed flow can be adjusted by changing the size of the protruding structure.
In the invention, the materials of the heat exchanger body 6, the pouring gas flow passage 2 and the flue gas flow passage 5 can be designed into plastic (with the temperature range of 20-80 ℃), glass (with the temperature range of 30-150 ℃), cast iron (with the temperature range of 100-400 ℃), cast aluminum (with the temperature range of 30-400 ℃), cast steel (with the temperature range of 50-450 ℃) and alloy steel (with the temperature range of 450-1250 ℃) and the like according to the temperature of the introduced flue gas.
As mentioned above, the casting gas channel 2 may also be a shell structure, that is, the casting gas channel 2 itself is a hollow structure, and the flue gas channel 5 is a separately formed structure (such as a channel surrounded by plates), and the casting gas channel 2 does not fix/support the flue gas channel 5. At this time, the flue gas flow path 5 is positioned and fixed by the outer frame.
In the present invention, the heat exchange pipe 3 is fixed in the flue gas flow passage 5 through an outer frame.
In the present invention, the heat exchange tube 3 is used in an air preheater, a flue gas/water heat exchanger, and the like.
In the invention, the heat exchanger can be used for heat exchange of flue gas and can also be used for heat exchange of other gas fluids or liquid fluids. The flue gas channel can be filled with high-temperature gas, and low-temperature gas, high-temperature liquid and low-temperature liquid are also applicable.
Another aspect of the present invention is to provide a method for enhancing heat exchange of flue gas, which comprises passing flue gas through a plurality of flue gas channels uniformly distributed in a heat exchanger, cooling the flue gas and discharging the cooled flue gas out of the heat exchanger.
Preferably, the heat exchanger is the heat exchanger for flue gas heat exchange.
In the invention, the heat exchanger is suitable for the flue gas with the flow speed of 1-30 m/s and the temperature of 20-1250 ℃.
Examples
Examples 1 to 1
As shown in fig. 2, a heat exchanger with a gas flow passage and a heat exchange method using the heat exchanger are provided, the heat exchanger is used as a flue gas/water heat exchanger in a boiler waste heat recovery system, and the flue gas introduced into the heat exchanger can heat water in the heat exchange pipe.
The heat exchanger comprises a cylindrical heat exchanger body 6, wherein a flue gas inlet 1 and a flue gas outlet 4 are respectively arranged on two sides of the heat exchanger body 6 along the axial direction, a flue gas channel inlet 51 is formed on the side wall of the heat exchanger body 6 on the flue gas inlet side, four flue gas channels 5 which are not communicated with each other penetrate through the interior of the heat exchanger body 6, a flue gas channel outlet 52 is formed on the side wall of the heat exchanger body 6 on the flue gas outlet side, a heat exchange tube 3 is arranged in the flue gas channel 5 along the axial direction, all the flue gas channel inlets 51 of a pouring gas channel 2 formed in the space inside the heat exchanger body 6 and outside the flue gas channel 5 fall into the flue gas inlet 1, and all the flue; the heat exchanger main body 6 is made of glass, and the heat exchange tube 3 is made of carbon steel.
The pouring gas flow channel 2 is of a solid structure and is formed by pouring glass; the heat exchange tubes 3 comprise a central heat exchange tube axially arranged in the center of the heat exchanger body 6, six I-grade heat exchange tubes surrounding the central heat exchange tube, and thirteen II-grade heat exchange tubes surrounding the I-grade heat exchange tubes, the distances between the I-grade heat exchange tubes are close, the distances between the II-grade heat exchange tubes are close, and the I-grade heat exchange tubes and the II-grade heat exchange tubes are axially and symmetrically distributed. Each flue gas flow channel 5 in the pouring gas flow channel 2 comprises five heat exchange tubes 3, and the heat exchange tubes 3 are light tubes. The flue gas flow passage 5 passing through the heat exchange tube 3 is partially expanded to form a circular flow passage surrounding the heat exchange tube 3.
When the device works, smoke passes through the four groups of smoke runners 5 which are uniformly arranged, is cooled by heat exchange media of the heat exchange tubes 3 arranged in the smoke runners, and is discharged through the smoke outlet 4. When the flue gas passes through the flue gas flow channel 5, the gas flow organization is uniform, the flue gas passage has no section mutation, the local resistance is small, the stroke is smooth and clear, a dead and stagnant area is avoided, the stroke length of each gas flow channel is basically equivalent, the integral flue gas resistance is low, and the average heat exchange coefficient is high.
The section radius of a cylinder surrounded by the cylindrical heat exchanger main body 6 is 0.30m, and the length is 0.5 m;
the inner diameter of the heat exchange tube 3 is 0.050m, the outer diameter is 0.056m, and the length is 0.5 m;
the width of the inlet of the flue gas runner is 0.02m, the width of the flue gas runner 5 along the flue gas runner is unchanged, and the radial width of the circular runner surrounding the heat exchange tube 3 is 0.01 m.
High-temperature flue gas with the temperature of 120 ℃ is introduced into the inlet of the flue gas channel, the flow velocity of the flue gas is 10m/s, the temperature of the flue gas at the outlet of the flue gas channel is 70 ℃, and the average flow velocity of the flue gas is 8.7 m/s; the heat exchange tube is filled with cold water with the temperature of 40 ℃, and the flow rate of the cold water is 1.5 m/s.
Examples 1 to 2
The structure of the heat exchanger was identical to that of example 1-1 except that the heat exchange tube was a threaded tube having a minimum inner diameter of 0.050m, a length of 0.5m, a pitch of 0.08m, and a thread groove depth of 3 mm. The technical parameters of the other parts of the heat exchanger were in accordance with example 1-1.
Examples 1 to 3
The structure of the heat exchanger was identical to that of example 1-1, except that the on-way width of the flue gas channel 5 was gradually reduced, the width of the inlet of the flue gas channel was 0.03m, and the width of the outlet of the flue gas channel was 0.015 m. The radial width of the circular flow channel surrounding the heat exchange tube 3 is the same, and the radial width of the circular flow channel is 0.01 m. The technical parameters of the other parts of the heat exchanger were in accordance with example 1-1.
Examples 1 to 4
As shown in fig. 3, the structure of the heat exchanger is identical to that of embodiment 1-1, except that the flue gas flow channel 5 has the same width along the way, and the width is 0.02 m; the radial width of the annular runner surrounding the heat exchange tube 3 is gradually reduced, and the radial width of the annular runner is 0.01m, 0.008m, 0.006m and 0.005m in sequence. The technical parameters of the other parts of the heat exchanger were in accordance with example 1-1.
Examples 1 to 5
The structure of the heat exchanger is consistent with that of the embodiment 1-1, and the difference is only that the width of the flue gas channel 5 along the way is gradually reduced, the width of the inlet of the flue gas channel is 0.03m, and the width of the outlet of the flue gas channel is 0.015 m; the radial width of the annular runner surrounding the heat exchange tube 3 is gradually reduced, and the radial width of the annular runner is 0.01m, 0.008m, 0.006m and 0.005m in sequence. The technical parameters of the other parts of the heat exchanger were in accordance with example 1-1.
Examples 1 to 6
As shown in fig. 4, the heat exchanger has a structure identical to that of example 1-1 except that a plurality of convex structures I7 facing the heat exchange tube 3 are arranged on the annular flow channel around the heat exchange tube 3. The raised structure I7 is used to position and secure the heat exchange tube therein. The height of the protrusion is 3-5 mm.
Example 2-1
The structure of the heat exchanger is identical to that of example 1-1, except that the casting gas channel 2 is a hollow structure.
Examples 2 to 2
The structure of the heat exchanger is identical to that of example 1-2, except that the casting gas channel 2 is a hollow structure.
Examples 2 to 3
The construction of the heat exchanger is identical to that of examples 1 to 3, with the only difference that the casting gas channel 2 is of hollow construction.
Examples 2 to 4
The construction of the heat exchanger is identical to that of examples 1 to 4, with the only difference that the casting gas channel 2 is of hollow construction.
Examples 2 to 5
The construction of the heat exchanger is identical to that of examples 1 to 5, with the only difference that the casting gas channel 2 is of hollow construction.
Examples 2 to 6
The construction of the heat exchanger is identical to that of examples 1 to 6, with the only difference that the casting gas channel 2 is of hollow construction.
Comparative example
Comparative example 1
As shown in the shell and tube heat exchanger of fig. 1, the flue gas passes and is deflected multiple times in the heat exchanger tube bundle. When the flue gas passes through the tube bundle, the flow area is continuously and violently changed, the flow velocity mutation of the flue gas is obvious, and a low-velocity vortex area of the flue gas at the middle and rear parts of the heat exchange tube is formed, and the heat exchange coefficient cannot be correspondingly and greatly increased due to the change of the flow velocity of the flue gas and the low-velocity vortex area, so that the power of the flue gas is wastefully consumed, and the resistance is increased. In addition, because the flue gas flows to have inertia, and the outside and the inboard of some flue gas corners have flue gas stagnation district, and these stagnation district heat transfer worsen, have reduced total heat exchange efficiency.
Comparative example 2
The structure of the heat exchanger is the same as that of the embodiment 1-1, and the difference is only that the width of the flue gas flow channel is widened along the way, the width of the annular flow channel is increased, for example, the width of the annular flow channel reaches 15mm, the heat exchange coefficient is reduced, and the heat exchange effect is poor.
The present invention has been described above in connection with preferred embodiments, but these embodiments are merely exemplary and merely illustrative. On the basis of the above, the invention can be subjected to various substitutions and modifications, and the substitutions and the modifications are all within the protection scope of the invention.
Claims (9)
1. A heat exchanger for flue gas heat exchange is characterized by comprising a cylindrical heat exchanger body (6), wherein a flue gas inlet (1) and a flue gas outlet (4) are respectively arranged on two sides of the heat exchanger body (6) along the vertical axial direction, a flue gas channel inlet (51) is formed in the side wall of the heat exchanger body (6) on the flue gas inlet side, a flue gas channel (5) penetrates through the inside of the heat exchanger body (6), a flue gas channel outlet (52) is formed in the side wall of the heat exchanger body (6) on the flue gas outlet side, a heat exchange tube (3) is arranged in the flue gas channel (5) along the axial direction, and a pouring gas channel (2) is formed in the space inside the heat exchanger body (6) and outside the flue gas;
the flue gas is introduced through the flue gas inlet (1), flows through the flue gas runner (5) through the flue gas runner inlet (51), is cooled by a heat exchange medium introduced into the heat exchange tube (3) and/or the pouring gas runner (2), and is discharged from the flue gas outlet (4) through the flue gas runner outlet (52);
the channel stroke of each flue gas channel (5) is similar, and the number of the heat exchange tubes in each flue gas channel (5) is similar.
2. The heat exchanger according to claim 1, characterized in that the heat exchanger body (6) is of axially symmetrical construction.
3. The heat exchanger according to claim 1, characterized in that the cast gas channel (2) is of solid construction, or of shell construction;
when the pouring gas channel (2) is of a shell structure, a heat exchange medium can be introduced into the pouring gas channel (2), and the heat exchange medium flows along the axial direction and exchanges heat with flue gas flowing in the flue gas channel (5).
4. The heat exchanger according to claim 1, characterized in that all flue gas channel inlets (51) of the flue gas channel (5) merge into the flue gas inlet (1), and all flue gas channel outlets (52) merge into the flue gas outlet (4);
the flue gas channels (5) are not communicated with each other and are independent gas channels.
5. A heat exchanger according to claim 1, characterized in that the heat exchange tubes (3) are evenly distributed in the heat exchanger body (6);
when the heat exchanger main body (6) is in an axially symmetrical structure, the heat exchange tubes (3) are symmetrically arranged in the heat exchanger main body (6) along the symmetrical axis of the heat exchange tubes.
6. A heat exchanger according to claim 1, characterized in that the width of the flue gas channel (5) near both sides of the heat exchange tube (3) is not greater than the maximum radial width of the heat exchange tube (3), the flue gas channel (5) passing through the heat exchange tube (3) is partially expanded to form an annular channel surrounding the heat exchange tube (3), and the flue gas is divided as it passes through the heat exchange tube (3) and is in integral contact with the heat exchange tube (3).
7. The heat exchanger of claim 1,
the width of the flue gas channel (5) along the way is unchanged, and the section of the flue gas channel part on the periphery of the heat exchange tube (3) is gradually reduced along the flow direction of the flue gas; or
The sections of the flue gas flow channel parts on the periphery of the heat exchange tubes (3) are the same, and the width of the flue gas flow channel (5) is gradually reduced along with the flow direction of flue gas; or
The section of the flue gas runner part at the periphery of the heat exchange tube (3) and the width of the flue gas runner (5) are gradually reduced along with the flow direction of the flue gas.
8. A heat exchanger according to claim 1, characterized in that the path of the heat exchange tube (3) is a straight line or a curved line, and the heat exchange medium in the heat exchange tube (3) exchanges heat with the flue gas in the flue gas channel (5) through heat conduction or heat radiation.
9. A heat exchange method is characterized in that the method comprises the steps of enabling flue gas to pass through flue gas channels uniformly distributed in a heat exchanger, cooling and discharging the cooled flue gas out of the heat exchanger;
the heat exchanger is the heat exchanger for flue gas heat exchange according to any one of claims 1 to 8.
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|---|---|---|---|---|
| CN1573273A (en) * | 2003-06-11 | 2005-02-02 | 臼井国际产业株式会社 | Gas cooling apparatus |
| CN106017154A (en) * | 2016-06-25 | 2016-10-12 | 湖州鼎诚环保科技有限公司 | Heat exchange equipment used for flue gas desulfurization |
| CN109253639A (en) * | 2018-07-25 | 2019-01-22 | 浙江森田新材料有限公司 | A kind of production anhydrous hydrofluoric acid tubular heat exchanger and manufacturing method |
| CN210014683U (en) * | 2019-03-29 | 2020-02-04 | 王磊 | Gas flow passage heat exchanger |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US20030111209A1 (en) * | 1999-01-20 | 2003-06-19 | Hino Motors, Ltd. | EGR cooler |
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Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1573273A (en) * | 2003-06-11 | 2005-02-02 | 臼井国际产业株式会社 | Gas cooling apparatus |
| CN106017154A (en) * | 2016-06-25 | 2016-10-12 | 湖州鼎诚环保科技有限公司 | Heat exchange equipment used for flue gas desulfurization |
| CN109253639A (en) * | 2018-07-25 | 2019-01-22 | 浙江森田新材料有限公司 | A kind of production anhydrous hydrofluoric acid tubular heat exchanger and manufacturing method |
| CN210014683U (en) * | 2019-03-29 | 2020-02-04 | 王磊 | Gas flow passage heat exchanger |
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Effective date of registration: 20220119 Address after: 214000 room 2022, building 10, first financial street, Wuxi Economic Development Zone, Wuxi City, Jiangsu Province Patentee after: Jiangsu Xinbo Energy Technology Co.,Ltd. Address before: 215500 building 11, 208 Huangpujiang Road, Changshu hi tech Industrial Development Zone, Changshu City, Suzhou City, Jiangsu Province Patentee before: SUZHOU BOEHMER THERMAL ENERGY PRODUCTS Co.,Ltd. |