CN113623628B - Steam boiler with arc plates - Google Patents
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- CN113623628B CN113623628B CN202111126286.4A CN202111126286A CN113623628B CN 113623628 B CN113623628 B CN 113623628B CN 202111126286 A CN202111126286 A CN 202111126286A CN 113623628 B CN113623628 B CN 113623628B
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- 239000012530 fluid Substances 0.000 claims abstract description 54
- 238000005452 bending Methods 0.000 claims abstract description 34
- 230000001174 ascending effect Effects 0.000 claims abstract description 31
- 230000001154 acute effect Effects 0.000 claims description 10
- 230000000694 effects Effects 0.000 abstract description 21
- 230000000630 rising effect Effects 0.000 abstract description 18
- 239000000463 material Substances 0.000 abstract description 6
- 239000007788 liquid Substances 0.000 description 14
- 238000002156 mixing Methods 0.000 description 13
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 12
- 238000004088 simulation Methods 0.000 description 9
- 239000000203 mixture Substances 0.000 description 8
- 238000010438 heat treatment Methods 0.000 description 7
- 238000011160 research Methods 0.000 description 7
- 238000013461 design Methods 0.000 description 6
- 238000002474 experimental method Methods 0.000 description 6
- 230000008859 change Effects 0.000 description 5
- 238000001816 cooling Methods 0.000 description 5
- 238000002485 combustion reaction Methods 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 238000000926 separation method Methods 0.000 description 3
- 238000010521 absorption reaction Methods 0.000 description 2
- 238000012937 correction Methods 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000005457 optimization Methods 0.000 description 2
- 239000011555 saturated liquid Substances 0.000 description 2
- 230000005514 two-phase flow Effects 0.000 description 2
- 230000003139 buffering effect Effects 0.000 description 1
- 239000000567 combustion gas Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 238000012827 research and development Methods 0.000 description 1
- 229920006395 saturated elastomer Polymers 0.000 description 1
- 238000009991 scouring Methods 0.000 description 1
- 238000003756 stirring Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B31/00—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus
- F22B31/08—Installation of heat-exchange apparatus or of means in boilers for heating air supplied for combustion
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention provides a steam boiler which comprises an upper boiler barrel, a lower boiler barrel, an ascending pipe and a descending pipe, wherein the ascending pipe and the descending pipe are connected between the upper boiler barrel and the lower boiler barrel, a temperature-equalizing plate extending from the inner wall of the ascending pipe to the center of the ascending pipe is arranged in the ascending pipe, the temperature-equalizing plate comprises a first bending wall and a second bending wall, the first bending wall and the second bending wall extend in a bending way towards the flowing direction of fluid, and a plurality of temperature-equalizing plates are arranged on the inner wall of the ascending pipe along the height direction. The invention provides a steam boiler with a novel structure, flow resistance is reduced by arranging temperature equalizing plates in a rising pipe, and the temperature equalizing effect achieves basically the same effect on the aspects of reducing resistance and saving material cost.
Description
Technical Field
The invention relates to a project entrusted with colleges and universities for research and development. The invention belongs to the field of steam generation, and particularly relates to a steam boiler, belonging to the field of IPC classification number F22.
Background
The circuit that receives heat from the furnace and moves the fluid from a low level to a high level is called the "uptake circuit", while the circuit that receives heat and moves the fluid from a high level to a low level is called the "descent circuit". A circuit consists of a pipe or a set of pipes leading from a common point, such as a header or a steam drum, terminating at a common point, also such as a header or a drum.
In most natural circulation boiler designs, the heated tubes that make up the evaporator section are typically supplied with fluid flowing upward, but in multi-boiler boilers, the falling tubes of the evaporator tube bundle are not. In this type of boiler, the downheated tubes provide the full circulation flow of the riser in the furnace and in the evaporator tube bundle section.
On the one hand, the fluid in the ascending pipe is generally in a vapor-liquid two-phase flow in an upward process, so that the fluid in the ascending pipe is a vapor-liquid mixture, and the existence of the vapor-liquid two-phase flow influences the heat absorption efficiency of the ascending pipe.
The temperature of each part of the ascending pipe is not uniform, for example, the side close to the furnace is high, the side opposite to the furnace is low, the temperature of the fluid at different positions in the ascending pipe is different, and the temperature difference can cause the temperature in the ascending pipe to be non-uniform, so that the overheating or the overcooling condition can be caused, and the operation is influenced.
The invention provides a new steam boiler, which solves the problem of uneven temperature of the riser fluid.
Disclosure of Invention
The present invention provides a new steam boiler to solve the above-mentioned technical problems.
In order to achieve the purpose, the technical scheme of the invention is as follows:
a steam boiler comprises an upper drum, a lower drum, and an ascending pipe and a descending pipe which are connected between the upper drum and the lower drum, and is characterized in that a temperature equalizing plate extending from the inner wall of the ascending pipe to the center of the ascending pipe is arranged in the ascending pipe, the temperature equalizing plate comprises a first bending wall and a second bending wall, the first bending wall and the second bending wall extend from the inner wall, an acute angle formed by a tangent line of a joint of the first bending wall and the inner wall is smaller than an acute angle formed by a tangent line of a joint of the second bending wall and the inner wall, the first bending wall and the second bending wall extend in a bending way towards the fluid flowing direction, the bending direction also faces the fluid flowing direction, and the intersection point of the first bending wall and the second bending wall is positioned at the upper part of the joint of the first bending wall and the inner wall and is positioned at the upper part of the joint of the second bending wall and the inner wall.
Preferably, the first curved wall and the second curved wall are arcs of a circle, wherein the diameter of the arc of the first curved wall is smaller than the diameter of the arc of the second curved wall.
Preferably, the tangent to the first curved wall at the location of the point of intersection forms an angle of 30-60 with the axis of the riser pipe.
Compared with the prior art, the invention has the following advantages:
1) the invention provides a novel steam boiler, wherein a bent temperature-equalizing plate is arranged in a rising pipe, so that a part of fluid flows along the temperature-equalizing plate and is guided to the opposite direction, and the fluid is fully mixed with the fluid entering from the opposite direction, thereby realizing uniform temperature of the fluid, further realizing uniform temperature and prolonging the service life of products.
2) The invention further promotes the full mixing by setting the distribution change of parameters such as the size, the number angle and the like of the temperature-equalizing plate along the flowing direction of the fluid.
3) According to the invention, through carrying out extensive research on the heat exchange rule caused by the change of each parameter of the temperature-equalizing plate, the temperature-equalizing plate structure of the heat exchanger is optimized under the condition of meeting the flow resistance, so that the optimal outlet fluid temperature-equalizing effect is achieved.
4) According to the invention, through reasonable layout, the temperature equalizing plates of adjacent rows are arranged in a staggered manner, so that fluid is further fully mixed, and the temperature is uniform.
5) According to the invention, the distance of the temperature-equalizing plate is widely researched, a minimum distance formula is designed, the temperature-equalizing mixing requirement is fully met, the problems of uneven mixing and increased flow resistance are avoided, and the optimal outlet fluid temperature-equalizing effect is achieved.
Drawings
FIG. 1 is a schematic view of the construction of a steam boiler according to the present invention.
FIG. 2 is a schematic view of another embodiment of the steam boiler structure of the present invention.
FIG. 3 is an axial sectional view of a temperature equalization plate installed on the rising pipe according to the present invention.
FIG. 4 is a schematic size view of a temperature equalization plate for a riser according to the present invention.
Fig. 5 is a schematic perspective view of 1 vapor chamber per layer.
Fig. 6 is a schematic perspective view of 3 vapor chambers arranged in each layer.
Fig. 7 is a perspective view of 1 uniform temperature plate per layer.
Fig. 8 is an exploded perspective view of the riser side of fig. 7.
In the figure: 1. the boiler comprises an upper boiler barrel, a lower boiler barrel, a heating pipe, a cooling plate, a temperature equalizing plate, a cooling pipe, a heating pipe, a cooling pipe, a heating chamber, a heating pipe, a cooling pipe, a heating chamber, a heating pipe, a cooling pipe, a heating; 41 first curved wall, 42 second curved wall, 43.
Detailed Description
The following detailed description of embodiments of the invention refers to the accompanying drawings.
In this document, "/" refers to a formula, and "×", "" refers to a division, and "x" refers to a multiplication, unless otherwise specified.
The steam boiler as shown in fig. 1 comprises an upper drum 1 and a lower drum 2, and the upcomers 3 and the downcomers 5 connect the upper drum 1 and the lower drum 2. Water enters the downcomer 5 from the upper drum 1. The water flows down in the downcomer and is collected in the lower drum 2. The rising pipes 3 of the boiler are heated by the combustion of fuel in the furnace combustion chamber 10. The heat absorbed by the riser 3 boils the liquid in the tube, thereby creating a two-phase mixture of water and vapor. The two-phase mixture in the riser 3 reaches the upper drum 1. Subcooled liquid discharged from a water supply pipe (not shown) in the upper drum 1 and saturated liquid discharged from the separation device are mixed together to form subcooled liquid, and the subcooled liquid flows out of the upper drum 1 into the downcomer 5, and a flow cycle is completed according to such a flow.
A steam boiler according to another embodiment, further illustrated in fig. 2, comprises an upper drum 1 and a lower drum 2, said upcomers 3 and downcomers 5 connecting the upper drum 1 and the lower drum 2. From the upper drum 1, the water enters the downcomer 5 of the heated evaporator tube bundle in the furnace inner flue 12. The water flows down the downcomer and is collected in the lower drum 2. The temperature of the water entering the lower drum 2 increases as the downcomer 5 absorbs heat. Depending on how much heat is absorbed, the water in the lower drum 2 may be subcooled or saturated. A portion of the fluid (typically steam-water mixture) leaving the lower drum 2 flows upwards into the riser tubes 3 of the evaporator tube bundle. The liquid flowing upwards into the riser 3 absorbs heat and enters the upper drum 1.
A portion of the fluid leaving the lower drum 2 passes through the downcomer 6 to the lower drum 7 of the furnace. The liquid entering a lower drum 7 is distributed to the furnace tubes 8 connected to the lower drum 7. The burner tubes are heated by the combustion of fuel in the furnace chamber 10. The heat absorbed by the furnace tube 8 boils the liquid in the furnace tube 8, thereby producing a two-phase mixture of water and steam. The two-phase mixture in the furnace tube 8 reaches the upper drum 1 through the furnace tube 8 directly connected with the upper drum 1, the furnace tube 8 at the moment is also an ascending tube, or an outlet header 11 is arranged between the lower drum 7 and the upper drum 1, and the two-phase mixture is conveyed to the upper drum 1 from the outlet header 11 of the hearth loop through the middle ascending tube 9. An internal separation device in the upper drum 1 separates the two-phase mixture into steam and water. Subcooled liquid is formed by mixing subcooled liquid discharged from a water supply pipe (not shown) in the upper drum 1 with saturated liquid discharged from the separation device, and the subcooled liquid flows out of the upper drum 1 into the downcomer 5, completing a flow cycle according to this flow.
For the boiler steam boiler evaporator tube bundle, the furnace wall of the furnace and the furnace wall of the furnace selected to be subjected to the scouring of the combustion gas stream, it is desirable to ensure a critical heat input so that the fluid flows sufficiently upwardly in all the tubes in the tube bundle and furnace wall circuit without flow instabilities.
As a modification, as shown in FIG. 3, a temperature equalizing plate 4 extending from an inner wall 51 of the rising pipe to the center of the rising pipe is arranged in the rising pipe 3 and/or the rising pipe 8 and/or the rising pipe 9, the temperature equalizing plate 4 comprises a first curved wall 41 and a second curved wall 42 extending from the inner wall, wherein an acute angle formed by a tangent line at the connection position of the first curved wall 41 and the inner wall 51 and the inner wall is smaller than an acute angle formed by a tangent line at the connection position of the second curved wall 42 and the inner wall, the first curved wall 41 and the second curved wall 42 extend in a curved manner towards the fluid flow direction, the curved direction is also towards the fluid flow direction, and an intersection point 43 of the first curved wall 41 and the second curved wall 42 is positioned at the upper part of the connection position of the first curved wall 41 and the inner wall 51 and is positioned at the upper part of the connection position of the second curved wall 42 and the inner wall. The shape of the temperature equalization plate 4 is a shape formed by rotating the first curved wall 41 and the second curved wall 42 and the inner wall along the riser axis.
According to the invention, the temperature equalizing plate is arranged in the ascending pipe, so that a part of fluid flows along the temperature equalizing plate and is guided to the opposite direction, and the fluid is fully mixed with the fluid entering from the opposite direction, thus the temperature of the fluid is uniform, the requirement of further heat exchange is met, and the service life of a product is prolonged.
The temperature equalizing plate is respectively provided with the first bending wall and the second bending wall, so that the fluid disturbance effect is better, the area of the temperature equalizing plate contacting with the inner wall is increased, and the stability is improved. And through setting up the second crooked wall, make the fluid of coming from opposite direction also can follow the crooked direction of second crooked wall direction motion, increase the buffering, reduce flow resistance.
The later-mentioned rising pipes are all at least one of the rising pipe 3, the rising pipe 8, and the rising pipe 9.
Preferably, the first curved wall 41 and the second curved wall 42 are circular arcs, wherein the diameter of the circular arc of the first curved wall 41 is smaller than the diameter of the circular arc of the second curved wall 42.
The first wall and the second wall are in the shape of circular arcs, so that the fluid flow resistance is smaller, and the fluid flows to the opposite side easily to be mixed.
Preferably, the tangent to the first curved wall 41 at the location of the point of intersection 43 forms an angle of 30-60 deg., preferably 45 deg., with the axis of the riser tube. By providing this angle, the fluid can be quickly directed to the opposite upper position, and the flow resistance can be further reduced.
Preferably, as shown in fig. 3, a plurality of temperature-equalizing plates 4 are provided on the inner wall of the riser in the height direction, and the temperature-equalizing plates of adjacent layers are staggered. Through the staggered distribution of the temperature equalizing plates in adjacent rows, the fluids can fully move to opposite positions mutually in the ascending pipe, and the full and uniform mixing is ensured. Fig. 3 shows that one vapor chamber is provided for each layer. Of course, a plurality of temperature equalization plates can be arranged on each layer, for example, 3 temperature equalization plates can be arranged.
Preferably, the distance between the intersection point and the inner wall of the riser is 0.3 to 0.5 times, preferably 0.4 times the diameter of the riser. With this arrangement, the air has less flow resistance on thorough mixing.
Preferably, the length of the first curved wall is greater than the length of the second curved wall.
Preferably, the total radian of the circular arc connecting the uniform temperature plate and the inner wall in the same layer is 150-180 degrees. This parameter set ensures thorough mixing while meeting the resistance requirements. For example, fig. 3, 5, and 7 show one block per layer of vapor chamber, which has a total arc of 150 and 180 degrees. Of course, multiple temperature equalization plates can be arranged on each layer, for example, three plates are arranged on each layer in the figure 5, and the total arc is 150 and 180 degrees.
Preferably, the temperature-equalizing plates on the layer A are arranged in a plurality of blocks, intervals are arranged among the temperature-equalizing plates on the layer A, the temperature-equalizing plates on the layer A are arranged at equal intervals, the layer B is an adjacent layer of the layer A, and the temperature-equalizing plates on the layer B are arranged at the intervals of the layer A when viewed from the flowing direction. Through the complementation of the positions of the temperature equalizing plates of the adjacent layers, the fluids can fully move to the opposite positions mutually in the ascending pipe, and the full and uniform mixing is ensured. It should be noted that, here, the layer a and the layer B are not specifically specified, A, B is only used as a distinction and is used as an adjacent layer.
Preferably, a plurality of temperature equalization plates are provided on the inner wall of the rising pipe along the height direction, and the distribution density of the temperature equalization plates becomes smaller along the height direction. Because the mixing degree of the fluid is better and better along with the continuous movement of the fluid, the distribution density is required to be smaller and smaller so as to reduce the flow resistance, and the temperature equalizing effect achieves the basically same effect on the aspects of reduced resistance and material cost saving.
Preferably, the distribution density of the temperature equalization plates is increased in a smaller and smaller range along the height direction. The effect is obtained through a large number of numerical simulation and experimental research results, and the research finds that the rule accords with the rule of fluid motion, and the temperature equalizing effect achieves the basically same effect on the aspects of further reduction of resistance and saving of material cost.
Preferably, a plurality of temperature equalization plates are provided on the inner wall of the rising pipe along the height direction, and the size of the temperature equalization plates becomes smaller along the height direction. Because the mixing degree of the fluid is better and better along with the continuous movement of the fluid, the size is required to be smaller and smaller to reduce the flow resistance, and the temperature equalizing effect achieves the same effect in the aspects of reducing the resistance and saving the material cost.
Preferably, a plurality of temperature equalization plates are provided on the inner wall of the rising pipe along the height direction, and the size of the temperature equalization plates is gradually reduced along the height direction. The effect is obtained through a large number of numerical simulation and experimental research results, the research finds that the rule accords with the rule of fluid motion, and the temperature equalizing effect achieves basically the same effect on the aspects of further reduction of resistance and material cost saving.
Through a large amount of numerical simulation and experimental research discovery, the angle and the size of samming board have very big influence to heat transfer and misce bene, samming board and inner wall contained angle are littleer, can lead to the mixed effect variation, and lead to the samming board oversize, influence the flow resistance, the contained angle is bigger than normal, it is not good to lead to stirring the fluid effect, the resistance grow, the mixed effect variation, the interval of samming board is too big, can lead to the vortex effect not good, the interval undersize can lead to increasing the movement resistance, therefore this application has obtained nearest samming board structure size optimization relation through a large amount of data simulation and experiments.
Preferably, the length L2 of the first line between the connection point of the first curved wall and the inner wall and the intersection point 43, the length L1 of the second line between the connection point of the second curved wall and the inner wall and the intersection point 43, the acute angle between the first line and the inner wall is a2, the acute angle between the second line and the inner wall is a1, the distance S between the adjacent temperature equalization plate structures on the same side along the flowing direction of the fluid, that is, the distance between the center points of the adjacent temperature equalization plates on the inner wall, the center point being the middle point of the connection line of the connection points of the first curved wall, the second curved wall and the inner wall, meets the following requirements:
n = a-b × ln (M), wherein N = (L1+ L2)/S, M = sin (a2)/sin (a 1); ln is a function of the logarithm of the number,
0.2697<a<0.2699，0.0830<b<0.0832；
preferably, 0.25< M <0.75,0.29< N <0.36,45< a1<75 °, 15< a2<45 °,400< S <550mm, 70< L2<130mm, 30< L1<90 mm.
The optimal design requirements of the structure of the temperature equalization plate can be met by the above formulas. The structural optimization formula is a main improvement point of the invention, is the most optimized formula which is researched by a large number of numerical simulations and experiments, and is not common knowledge in the field.
Further preferably, a =0.2698 and b = 0.0831.
Preferably, in the case that the included angle formed by the ascending pipe and the horizontal plane is A, the data can be corrected by increasing a correction coefficient c, namely
c* N=a-b*Ln(M)；c=1/sin(A) m Wherein 0.09<m<0.11, preferably m = 0.10.
20< a <80, preferably 40-60.
The data simulation and the experiment find that the distance between the temperature-uniforming plates must be larger than a certain distance, otherwise, the fluid can be guided to the opposite direction through the previous temperature-uniforming plate, but if the distance between the temperature-uniforming plates is too small, the fluid can flow in the opposite direction, the whole pipeline is not fully filled, the temperature-uniforming plates are arranged at the moment, the mixing effect cannot be achieved, the temperature-uniforming plates only play the role of a baffle plate, the mixing guiding effect is not achieved, and only the flow resistance can be increased. Therefore, the design scheme of the minimum distance of the temperature-equalizing plate is provided through a large amount of research, and the design of the temperature-equalizing plate has certain guiding significance.
The vertical point of the intersection point 43 on the inner wall, the line formed by the intersection point and the vertical point is a third line, the distance between the connecting point of the first bending wall and the inner wall and the vertical point is H, the acute angle formed by the first line and the third line is A3, the acute angle formed by the tangent of the first bending wall at the intersection point and the axis of the riser pipe is A4, the inner pipe diameter of the riser pipe is R, and the distance S is designed in the following way:
(S/H)>a+b*Ln (T)，(S/R) 2 >c+d*Ln (T)；
wherein T = sin (A3)/sin (a4), 2.66< a <2.68,17.1< b <17.2, 1.976< c <1.978, 3.425< d <3.426,
30< A3<70 °, 20< a4<60 °; preferably 1.07< T < 1.30;
preferably, a =2.67, b =17.15, c =1.977, d = 3.4255;
according to the invention, through a large amount of experiments and numerical simulation, the minimum design distance of the temperature equalizing plate is obtained, and the resistance is reduced through the design distance, and meanwhile, the full mixing can be realized.
Preferably, in the case that the included angle formed by the ascending pipe and the horizontal plane is A, the correction coefficients d and f can be increased to correct the data, namely
( (S/H)/d)>a+b*Ln (T)； ((S/R) 2 /f)>c+d*Ln (T)；
d=sin(A) n Wherein 0.085<n<0.098, preferably n = 0.092. f = sin (A) k Wherein 0.076<k<0.078, preferably k =0.077
20< a <80, preferably 40-60.
Preferably, the pipe diameter of the rising pipe 3 is continuously increased in the direction of the fluid flow. The main reasons are as follows: 1) by increasing the pipe diameter of the ascending pipe, the flowing resistance can be reduced, so that the vapor evaporated in the ascending pipe continuously moves towards the direction of increasing the pipe diameter, and the circulating flow of the loop heat pipe is further promoted. 2) Because the liquid is continuously evaporated in the ascending pipe along with the continuous flowing of the fluid, the volume of the steam is larger and larger, and the pressure is also larger and larger, the change of the volume and the pressure of the steam which are continuously increased is met by increasing the pipe diameter, and the pressure is uniformly distributed on the whole. 3) By increasing the pipe diameter of the ascending pipe, the impact phenomenon caused by the increase of the volume of the steam outlet can be reduced.
Preferably, the pipe diameter of the rising pipe 3 is continuously increased with an increasing magnitude along the direction of fluid flow. The amplitude change of the pipe diameter is a result obtained by a large number of experiments and numerical simulation of the applicant, and through the arrangement, the circulating flow of the loop heat pipe can be further promoted, the pressure is integrally uniform, and the impact phenomenon is reduced.
Preferably, the pipe diameter of the riser is greater than the pipe diameter of the downcomer. The resistance of the downcomer is mainly increased, and the resistance of the riser is reduced, so that the steam flows from the evaporation part more easily, and the loop heat pipe forms circulation better.
Preferably, the diameter of the downcomer decreases continuously in the direction of fluid flow. The main reasons are as follows: 1) because steam is continuously condensed in the descending pipe along with the continuous flowing of the fluid, the volume of the fluid is smaller and smaller, and the pressure is also smaller and smaller, the continuously increased volume and pressure changes of the fluid are met by reducing the pipe diameter, so that the pressure distribution is uniform on the whole, and the heat exchange is uniform. 2) Through the reduction of the pipe diameter of the heat absorption pipe, materials can be saved, and the cost is reduced.
Preferably, the pipe diameter of the downcomer is continuously reduced to a greater and greater extent in the direction of fluid flow. The amplitude change of the pipe diameter is a result obtained by a large number of experiments and numerical simulation of the applicant, and through the arrangement, the circulating flow of the loop heat pipe can be further promoted, and the pressure is integrally uniform.
Although the present invention has been described in connection with the preferred embodiments, it is not limited thereto. Various changes and modifications may be effected by one skilled in the art without departing from the spirit and scope of the invention, as defined in the appended claims.
Claims (3)
1. A steam boiler comprises an upper drum, a lower drum, and an ascending pipe and a descending pipe which are connected between the upper drum and the lower drum, and is characterized in that a temperature-equalizing plate extending from the inner wall of the ascending pipe to the center of the ascending pipe is arranged in the ascending pipe, the temperature-equalizing plate comprises a first bending wall and a second bending wall which extend from the inner wall, wherein an acute angle formed by a tangent line at the joint of the first bending wall and the inner wall is smaller than an acute angle formed by a tangent line at the joint of the second bending wall and the inner wall, the first bending wall and the second bending wall bend and extend towards the fluid flow direction, the bending direction also faces towards the fluid flow direction, the intersection point of the first bending wall and the second bending wall is positioned at the upper part of the joint of the first bending wall and the inner wall, and is positioned at the upper part of the joint of the second bending wall and the inner wall; along the direction of height, the riser inner wall sets up a plurality of temperature-uniforming plates, and along the direction of height, the distribution density of temperature-uniforming plate is littleer and more.
2. A steam boiler according to claim 1, characterized in that the first curved wall and the second curved wall are circular arcs, wherein the circular arc diameter of the first curved wall is smaller than the circular arc diameter of the second curved wall.
3. A steam boiler according to claim 1, characterized in that the tangent to the first curved wall at the location of the intersection forms an angle of 30-60 ° with the axis of the riser.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011211310X | 2020-11-03 | ||
| CN202011211310 | 2020-11-03 |
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| Publication Number | Publication Date |
|---|---|
| CN113623628A CN113623628A (en) | 2021-11-09 |
| CN113623628B true CN113623628B (en) | 2022-07-26 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202111126286.4A Expired - Fee Related CN113623628B (en) | 2020-11-03 | 2021-09-26 | Steam boiler with arc plates |
| CN202111126296.8A Expired - Fee Related CN113623629B (en) | 2020-11-03 | 2021-09-26 | Steam boiler with complementary temperature-equalizing plates |
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| CN202111126296.8A Expired - Fee Related CN113623629B (en) | 2020-11-03 | 2021-09-26 | Steam boiler with complementary temperature-equalizing plates |
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| CN108332179A (en) * | 2017-08-02 | 2018-07-27 | 青岛金玉大商贸有限公司 | A kind of steam boiler |
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2021
- 2021-09-26 CN CN202111126286.4A patent/CN113623628B/en not_active Expired - Fee Related
- 2021-09-26 CN CN202111126296.8A patent/CN113623629B/en not_active Expired - Fee Related
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1003013A (en) * | 1962-05-28 | 1965-09-02 | Patterson Kelley Co | Heat exchange device |
| CN2854484Y (en) * | 2005-12-15 | 2007-01-03 | 苏州新太铜高效管有限公司 | Heat-exchange pipe for evaporimeter |
| CN107143838A (en) * | 2017-04-18 | 2017-09-08 | 青岛金玉大商贸有限公司 | A kind of constant-current stabilizer steam boiler |
| CN106949449A (en) * | 2017-04-21 | 2017-07-14 | 青岛金玉大商贸有限公司 | A kind of steam boiler |
| CN108332179A (en) * | 2017-08-02 | 2018-07-27 | 青岛金玉大商贸有限公司 | A kind of steam boiler |
| CN108332181A (en) * | 2017-08-02 | 2018-07-27 | 青岛金玉大商贸有限公司 | A kind of steam boiler |
Also Published As
| Publication number | Publication date |
|---|---|
| CN113623629B (en) | 2022-12-27 |
| CN113623629A (en) | 2021-11-09 |
| CN113623628A (en) | 2021-11-09 |
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