CN111207377B - Steam boiler - Google Patents
Steam boiler Download PDFInfo
- Publication number
- CN111207377B CN111207377B CN202010189103.2A CN202010189103A CN111207377B CN 111207377 B CN111207377 B CN 111207377B CN 202010189103 A CN202010189103 A CN 202010189103A CN 111207377 B CN111207377 B CN 111207377B
- Authority
- CN
- China
- Prior art keywords
- flow
- pipe
- square
- hole
- ascending pipe
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B21/00—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically
- F22B21/02—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically built-up from substantially straight water tubes
- F22B21/04—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically built-up from substantially straight water tubes involving a single upper drum and a single lower drum, e.g. the drums being arranged transversely
- F22B21/08—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically built-up from substantially straight water tubes involving a single upper drum and a single lower drum, e.g. the drums being arranged transversely the water tubes being arranged sectionally in groups or in banks, e.g. bent over at their ends
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B37/00—Component parts or details of steam boilers
- F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
- F22B37/10—Water tubes; Accessories therefor
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- 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; the type of the flow stabilizers arranged adjacently is different. The large holes and the small holes are uniformly distributed on the whole cross section through the uniform distribution of the square holes and the regular octagonal holes, and the separation effect is better through the position change of the large holes and the small holes of the adjacent flow stabilizing devices.
Description
The application is a divisional application aiming at 20 days 06 and 8 months in 2018, application number 201810632533X, and invention name design method of a flow stabilizer and a steam boiler with optimized pipe diameter.
Technical Field
The invention relates to a project which entrusts colleges and universities to research and develop. 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 the low level to the high level is called the "uptake circuit", while the circuit that receives heat and moves the fluid from the high level to the 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 descending heated tubes provide the entire 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.
On the other hand, in the section from the outlet of the ascending pipe to the upper drum, because the space of the section is suddenly enlarged, the change of the space can cause the gas to rapidly flow out and gather upwards, so the change of the space can cause the gathered vapor phase (vapor mass) to enter the upper drum from the position of the ascending pipe, the vapor mass moves rapidly upwards from the position of the connecting pipe due to the poor liquid density of the vapor (vapor), and the original space position of the vapor mass is pushed by the liquid of the vapor mass away from the wall surface and also rapidly rebounds and impacts the wall surface to form an impact phenomenon. The more discontinuous the gas (vapor) liquid phase, the larger the mass of gas is gathered and the greater the impact energy. The impact phenomenon can cause larger noise vibration and mechanical impact, and damage to equipment.
Various riser devices have been devised in the previous applications to solve the above problems, such as 2017102546447 multitubular, but such devices have been found in operation that the space a formed between the three tubes is relatively small because the tubes are tightly joined together, and because the space a is formed by the convex arcs of the three tubes, most of the area of the space a is narrow, making it difficult for the fluid to enter and pass through, making a fluid short circuit, thereby affecting the heat exchange of the fluid and failing to achieve a good flow stabilizing effect. And also, since a plurality of tubes of the above-described structure are combined together, the manufacturing is difficult. For example, the 2017102666326 structure solves the fluid short circuit phenomenon, but has a problem that the flow area is greatly reduced, resulting in an increase in flow resistance. For example, 2017102949490, the annular flow stabilizer in the annular structure has an annular structure, which results in uneven circumferential separation of the annular space of the flow stabilizer as a whole, and because of the annular structure, the four included angles of the annular space have acute angles smaller than 90 degrees, which may cause the problem of short circuit of fluid flow at the acute angle smaller than 90 degrees.
There is no relevant research on the design of the relationship between the distance between the flow stabilizers and the distance between the ascending tube and the descending tube. And the above relationship is also extremely important for heat exchange and vapor-liquid flow stabilization. The present inventors have studied the above-mentioned relationship.
In view of the above problems, the present invention is an improvement on the basis of the above invention, and provides a new steam boiler and a design method thereof, so as to solve the problem of low heat absorption efficiency of the ascending pipe.
Disclosure of Invention
The present invention provides a new steam boiler, thereby solving the technical problems occurring in the prior art.
In order to achieve the purpose, the technical scheme of the invention is as follows:
a design method of a steam boiler comprises an upper drum, a lower drum, an ascending pipe and a descending pipe which are connected between the upper drum and the lower drum, and is characterized in that a flow stabilizing device is arranged in the ascending pipe, and the design method comprises the following steps: along with the increase of the ascending pipe diameter, the interval between the adjacent flow stabilizers is continuously reduced.
Preferably, the distance between the adjacent flow stabilizers is reduced to a smaller extent along with the increase of the pipe diameter of the ascending pipe.
Preferably, the steam boiler comprises an upper drum, a lower drum, an ascending pipe and a descending pipe which are connected between the upper drum and the lower drum, and is characterized in that a flow stabilizer is arranged in the ascending pipe, the flow stabilizer is of a sheet structure, and the sheet structure is arranged on the cross section of the ascending pipe; the flow stabilizer consists of a square through hole and a regular octagonal through hole, the side length of the square through hole is equal to that of the regular octagonal through hole, four sides of the square through hole are respectively sides of four different regular octagonal through holes, and four mutually spaced sides of the regular octagonal through hole are respectively sides of four different square through holes; the design method comprises the following steps: along with the increase of the pipe diameter of the ascending pipe, the side length of the square through hole is continuously increased.
Preferably, but the side length of the square through hole is increased by a smaller and smaller range along with the increase of the pipe diameter of the ascending pipe.
Preferably, a gap is formed in the inner wall of the ascending pipe, and the outer end of the flow stabilizer is arranged in the gap.
Preferably, the ascending pipe is formed by welding a multi-section structure, and a flow stabilizer is arranged at the joint of the multi-section structure.
Preferably, a plurality of flow stabilizers are arranged in the ascending pipe, the distance between every two adjacent flow stabilizers is M1, the side length of each square through hole is B1, and the side length of the ascending pipe is B2, so that the following requirements are met:
M1/B2=a*Ln(B1/B2) +b
wherein a, b are parameters, wherein 1.69< a <1.70,4.86< b < 4.87;
11<B2<46mm；
1．9<B1<3.2mm；
15<M1<31mm。
preferably, a =1.692 and b = 4.863.
Preferably, a is smaller and B is smaller as B1/B2 is increased.
Preferably, the flow stabilizer comprises at least one of a square central flow stabilizer with a square through hole in the center of the riser pipe and a regular octagonal central flow stabilizer with a regular octagonal through hole in the center of the riser pipe.
Preferably, the adjacently arranged flow stabilizers are of different types.
Preferably, a plurality of flow stabilizers are arranged in the ascending tube, the distance from the inlet of the ascending tube is H, the distance between every two adjacent flow stabilizers is S, and S = F1(H) The following requirements are met:
S’<0, S”>0。
preferably, a plurality of flow stabilizers are arranged in the ascending pipe, the distance from the ascending pipe inlet is H, the length of each flow stabilizer is C, and C = F2(H) The following requirements are met:
C’>0, C”>0。
preferably, a plurality of flow stabilizers are arranged in the ascending pipe, the distance from the ascending pipe inlet is H, the side length of a square through hole of each flow stabilizer is D, and D = F3(H) The following requirements are met:
D’<0, D”>0。
preferably, the inner wall of the ascending tube is provided with a groove, the housing of the flow stabilizer is arranged in the groove, and the inner wall of the housing is aligned with the inner wall of the ascending tube.
Compared with the prior art, the invention has the following advantages:
1) the invention provides a design method of a steam boiler with a new-type structure flow stabilizer, and the boiler designed by the method strengthens heat transfer when gas-liquid two-phase flow exists in an ascending pipe, and simultaneously weakens the vibration of the ascending pipe and reduces the noise level.
2) The invention provides a novel flow stabilizer with a novel structure combining a square through hole and a regular octagon through hole, wherein the included angles formed by the edges of the formed square hole and the regular octagon hole are both larger than or equal to 90 degrees through the square and the regular octagon, so that fluid can fully flow through each position of each hole, and the short circuit of the fluid flow is avoided or reduced. The two-phase fluid is separated into the liquid phase and the gas phase by the flow stabilizer with the novel structure, the liquid phase is divided into small liquid masses, the gas phase is divided into small bubbles, the backflow of the liquid phase is inhibited, the gas phase is enabled to flow smoothly, the flow stabilizing effect is achieved, the vibration and noise reducing effect is achieved, and the heat exchange effect is improved. Compared with the current stabilizer in the prior art, the current stabilizer further improves the current stabilizing effect, strengthens heat transfer and is simple to manufacture.
3) According to the invention, through reasonable layout, the square and regular octagonal through holes are uniformly distributed, so that the fluid on the whole cross street is uniformly divided, and the problem of nonuniform division of the annular structure along the circumferential direction in the prior art is avoided.
4) The large holes and the small holes are uniformly distributed on the whole cross section through the uniform distribution of the square holes and the regular octagonal holes, and the separation effect is better through the position change of the large holes and the small holes of the adjacent flow stabilizing devices.
5) According to the invention, the flow stabilizer is of a sheet structure, so that the flow stabilizer is simple in structure and low in cost.
6) According to the invention, the optimal relation size of the parameters is researched by setting the regular changes of the parameters such as the distance between the adjacent flow stabilizers, the side length of the hole of the flow stabilizer, the pipe diameter of the ascending pipe, the pipe spacing and the like in the height direction of the ascending pipe, so that the flow stabilizing effect is further achieved, the noise is reduced, and the heat exchange effect is improved.
7) According to the invention, through carrying out extensive research on the heat exchange rule caused by the change of each parameter of the annular flow stabilizer, the optimal relational expression of the vibration and noise reduction effects is realized under the condition of meeting the flow resistance.
Drawings
FIG. 1 is a schematic view of the steam boiler configuration of the present invention;
FIG. 2 is a schematic view of another embodiment of the steam boiler structure of the present invention;
FIG. 3-1 is a schematic cross-sectional view of a flow stabilizer of the present invention;
fig. 3-2 are schematic diagrams of another embodiment of a flow stabilizer cross-section of the present invention;
FIG. 4 is a schematic view of the arrangement of the flow stabilizers of the present invention within the riser;
FIG. 5 is a schematic view of the cross-sectional arrangement of the flow stabilizer of the present invention within the riser.
In the figure: 1. the device comprises an upper boiler barrel, 2, a lower boiler barrel, 3, an ascending pipe, 4, a flow stabilizer, 41 shells, 42 pipes, 5, a descending pipe, 6, a descending pipe, 7, a lower boiler barrel, 8, 9, an ascending pipe, 10 hearth combustion chambers, 11 outlet headers and 12 flues.
Detailed Description
The following detailed description of embodiments of the invention refers to the accompanying drawings.
In this document, "/" denotes division and "×", "denotes multiplication, referring to formulas, if not specifically stated.
A steam boiler as described in fig. 1, comprising 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. 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 rising pipe 3 boils the liquid inside the pipe, thereby creating a two-phase mixture of water and steam. 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 in 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 reaches the lower drum 7 of the furnace through the downcomer 6. The liquid entering a lower drum 7 is distributed to furnace tubes 8 connected to the lower drum 7. The furnace tubes are heated by the combustion of fuel in the furnace firebox 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 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.
For the boiler evaporator tube bundle, the furnace walls and the convection walls to be selectively subjected to the combustion gas flow, it is necessary to ensure a critical heat input so that the fluid flows substantially circularly in all the tubes in the loop of the tube bundle and the convection walls without flow instabilities.
A flow stabilizer 4 is arranged in the ascending pipe 3 and/or the ascending pipe 8 and/or the ascending pipe 9, the flow stabilizer 4 is shown in figure 3, and the structure of the flow stabilizer 4 is shown in figures 3-1 and 3-2. The flow stabilizer 4 is a sheet structure which is arranged on the cross section of the ascending pipe 3; the flow stabilizer 4 is composed of a square structure and a regular octagonal structure, so that a square through hole 41 and a regular octagonal through hole 42 are formed. The side length of the square through-hole 41 is equal to the side length of the regular octagonal through-hole 42 as shown in fig. 1, the four sides 43 of the square through-hole are the sides 43 of four different regular octagonal through-holes, respectively, and the four mutually spaced sides 43 of the regular eight deformed through-hole are the sides 43 of four different square through-holes, respectively.
The invention adopts the current stabilizer with a novel structure, and has the following advantages:
1) the invention provides a novel flow stabilizer with a novel structure combining a square through hole and a regular octagon through hole, wherein the included angles formed by the edges of the formed square hole and the regular octagon hole are both larger than or equal to 90 degrees through the square and the regular octagon, so that fluid can fully flow through each position of each hole, and the short circuit of the fluid flow is avoided or reduced. The two-phase fluid is separated into the liquid phase and the gas phase by the flow stabilizer with the novel structure, the liquid phase is divided into small liquid masses, the gas phase is divided into small bubbles, the backflow of the liquid phase is inhibited, the gas phase is enabled to flow smoothly, the flow stabilizing effect is achieved, the vibration and noise reducing effect is achieved, and the heat exchange effect is improved. Compared with the current stabilizer in the prior art, the current stabilizer further improves the current stabilizing effect, strengthens heat transfer and is simple to manufacture.
2) According to the invention, through reasonable layout, the square and regular octagonal through holes are uniformly distributed, so that the fluid on the whole cross street is uniformly divided, and the problem of nonuniform division of the annular structure along the circumferential direction in the prior art is avoided.
3) According to the invention, the large holes and the small holes are uniformly distributed on the whole cross section through the uniform distribution of the square holes and the regular octagonal through holes at intervals, and the separation effect is better through the position change of the large holes and the small holes of the adjacent flow stabilizers.
4) According to the invention, the flow stabilizer is of a sheet structure, so that the flow stabilizer is simple in structure and low in cost.
By arranging the annular flow stabilizing device, the invention is equivalent to increase the internal heat exchange area in the ascending pipe, thereby strengthening the heat exchange and improving the heat exchange effect.
The invention divides the gas phase and the liquid phase at all cross section positions of all the ascending pipes, thereby realizing the contact area of the gas-liquid interface and the gas phase boundary layer on the whole ascending pipe section and the cooling wall surface and enhancing the disturbance, greatly reducing the noise and the vibration and strengthening the heat transfer.
The later-mentioned rising pipes are all at least one of the rising pipe 3, the rising pipe 8, and the rising pipe 9.
By arranging the square and octagonal flow stabilizing devices, the invention is equivalent to adding the inner fins in the ascending pipe 3, thereby strengthening the heat exchange and improving the heat exchange effect.
The invention divides the vapor-liquid two phases at all cross section positions of the ascending pipe 3, thereby realizing the contact area of the vapor-liquid interface and the vapor phase boundary layer on the whole ascending pipe section and the cooling wall surface, enhancing disturbance, greatly reducing noise and vibration and strengthening heat transfer.
Preferably, the flow stabilizers comprise two types, as shown in fig. 3-1, the first type being a square central flow stabilizer, the square being located in the center of the riser or downcomer as shown in fig. 3-2. The second is a regular octagonal central flow stabilizer, the regular octagon being located in the center of the riser or downcomer, as shown in fig. 3-1. Preferably, the two types of flow stabilizers are arranged adjacently, i.e. the types of flow stabilizers arranged adjacently are different. Namely, the regular octagonal central current stabilizer is adjacent to the square central current stabilizer, and the square central current stabilizer is adjacent to the regular octagonal central current stabilizer. According to the invention, the square holes and the regular octagon holes are uniformly distributed at intervals, so that the large holes and the small holes are uniformly distributed on the whole cross section, and through the position change of the large holes and the small holes of the adjacent flow stabilizing devices, the fluid passing through the large holes next passes through the small holes, and the fluid passing through the small holes next passes through the large holes to be further separated, so that the mixing of vapor and liquid is promoted, and the separating and heat exchanging effects are better.
Preferably, said riser 3 has a square cross-section.
Preferably, the pipe diameter of the rising pipe 3 is continuously increased in the direction of 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 by 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, a plurality of flow stabilizers are provided in the rising pipe 3 along the flow direction of the fluid in the rising pipe 3 (i.e., the height direction of fig. 3)And 4, the distance between adjacent flow stabilizers is shorter and shorter from the inlet of the ascending pipe to the outlet of the ascending pipe. Setting the distance from the inlet of the ascending pipe to be H, and the distance between adjacent flow stabilizers to be S, S = F1(H) I.e. S is a function with distance H as a variable, S' is the first derivative of S, satisfying the following requirements:
S’<0;
the main reason is that the gas in the ascending pipe carries liquid in the ascending process, the ascending pipe is continuously heated in the ascending process, so that more and more gas in gas-liquid two-phase flow is caused, the gas phase in the gas-liquid two-phase flow is increased, the heat exchange capacity in the ascending pipe is relatively weakened along with the increase of the gas phase, and the vibration and the noise are also continuously increased along with the increase of the gas phase. The distance between adjacent flow stabilizers needs to be set shorter and shorter.
In addition, the section from the outlet of the ascending pipe 8 to the outlet header 11 and the section from the ascending pipes 9 and 3 to the upper drum 1 are also provided, because the space of the section is suddenly enlarged, the change of the space can cause the gas to rapidly flow out and gather upwards, so the change of the space can cause the gathered vapor phase (vapor mass) to enter the condensation header from the position of the ascending pipe, the vapor mass moves upwards rapidly away from the position of the connecting pipe due to the poor liquid density of the gas (vapor), and the original space position of the vapor mass is pushed away from the liquid of the wall surface by the vapor mass and simultaneously rebounds back rapidly and impacts the wall surface to form an impact phenomenon. The more discontinuous the gas (vapor) liquid phase, the larger the gas mass accumulation and the larger the water hammer energy. The impact phenomenon can cause larger noise vibration and mechanical impact, and damage to equipment. Therefore, in order to avoid the phenomenon, the distance between adjacent flow stabilizers is set to be shorter and shorter, so that the gas phase and the liquid phase are separated continuously in the fluid conveying process, and vibration and noise are reduced to the maximum extent.
Through the experiment discovery, through foretell setting, both can reduce vibrations and noise to the at utmost, can improve the heat transfer effect simultaneously.
It is further preferred that the distance between adjacent flow stabilizers increases progressively from the inlet of the riser to the outlet of the riser. I.e. S "is the second derivative of S, the following requirements are met:
S”>0;
through the experiment, the vibration and the noise of about 9 percent can be further reduced, and the heat exchange effect of about 7 percent is improved.
Preferably, the length of each flow stabilizer 4 remains constant.
Preferably, other parameters of the flow stabilizer (e.g., tube diameter, etc.) are kept constant except for the distance between adjacent flow stabilizers 4.
Preferably, a plurality of flow stabilizers are arranged in the ascending pipe along the flowing direction of the fluid in the ascending pipe (namely, along the extending direction of the ascending pipe), and the side length of the square through hole of each flow stabilizer in different flow stabilizers 4 is smaller and smaller from the inlet of the ascending pipe to the outlet of the ascending pipe. I.e. the tube diameter of the flow stabilizer is D, D = F3(X), D' is the first derivative of D, and the following requirements are met:
D’<0;
preferably, the side length of the square through hole of the flow stabilizer is gradually increased from the inlet of the ascending pipe to the outlet of the ascending pipe. Namely, it is
D' is the second derivative of D, and meets the following requirements:
D”>0。
for example, the distance between adjacent flow stabilizers may vary equally.
Preferably, the length of the flow stabilizers and the distance between adjacent flow stabilizers remain constant.
Preferably, other parameters of the flow stabilizer (e.g., length, distance between adjacent flow stabilizers, etc.) are maintained constant, except for the diameter of the tube of the flow stabilizer.
Further preferably, as shown in fig. 4, a slit is provided inside the rising pipe, and the housing 42 of the flow stabilizer 4 is provided inside the slit.
Preferably, the ascending pipe is formed by welding a multi-section structure, and a flow stabilizer 4 is arranged at the joint of the multi-section structure. This way the riser pipe provided with flow stabilizers can be manufactured simply and at a reduced cost.
Through analysis and experiments, the distance between the flow stabilizers cannot be too large, the damping and noise reduction effects are poor due to too large distance, the resistance is too large due to too small distance, and the side length of the square cannot be too large or too small, so that the damping and noise reduction effects are poor or the resistance is too large, so that the damping and noise reduction effects are optimized under the condition that normal flow resistance (the total pressure bearing is less than 2.5MPa or the on-way resistance of a single ascending pipe is less than or equal to 5 Pa/M) is preferentially met through a large number of experiments, and the optimal relation of each parameter is arranged.
Preferably, the distance between adjacent flow stabilizers is M1, the side length of a square through hole is B1, the riser is a square section, and the side length of the square section of the riser is B2, so that the following requirements are met:
M1/B2=a*Ln(B1/B2) +b
wherein a, b are parameters, wherein 1.69< a <1.70,4.86< b < 4.87;
11<B2<46mm；
1．9<B1<3.2mm；
15<M1<31mm。
preferably, a =1.692 and b = 4.863.
Further preferably, a is smaller and B is larger as B1/B2 is increased.
Preferably, the side length B1 of the square through hole is the average of the inner side length and the outer side length of the square through hole, and the side length B2 of the square cross section of the ascending tube is the average of the inner side length and the outer side length of the ascending tube.
Preferably, the outer length of the square through hole is equal to the inner length of the square section of the riser.
Preferably, as B2 increases, B1 also increases. However, as B2 increases, the magnitude of the increase in B1 becomes smaller and smaller. The change of the rule is obtained through a large amount of numerical simulation and experiments, and the heat exchange effect and the noise are further improved and reduced through the change of the rule.
Preferably, as B2 increases, M1 decreases. However, as B2 increases, the magnitude of the decrease in M1 becomes smaller and smaller. The change of the rule is obtained through a large amount of numerical simulation and experiments, and the heat exchange effect and the noise are further improved and reduced through the change of the rule.
Learn through analysis and experiment, the interval of tedge also satisfies certain requirement, for example can not too big or undersize, no matter too big or undersize can lead to the heat transfer effect not good, because set up current stabilizer in this application tedge moreover, consequently current stabilizer also has certain requirement to the tedge interval. Therefore, through a large number of experiments, under the condition that the normal flow resistance (the total pressure bearing is less than 2.5MPa, or the on-way resistance of a single ascending pipe is less than or equal to 5 Pa/M) is preferentially met, the damping and noise reduction are optimized, and the optimal relation of each parameter is arranged.
The distance between adjacent flow stabilizers is M1, the side length of a square is B1, the ascending pipe is a square section, the side length of the ascending pipe is B2, and the distance between the centers of the adjacent ascending pipes is M2, so that the following requirements are met:
M2/B2=d*(M1/B2)2+e+f*(M1/B2)3-h*(M1/B2)；
wherein d, e, f, h are parameters,
1.249<d<1.252,1.495<e<1.510,0.39<f<0.40,0.920<h<0.930；
11<B2<46mm；
1．9<B1<3.2mm；
15<M1<31mm。
16<M2<76mm。
the spacing between the centers of adjacent risers of M2 is referred to as the distance between the centerlines of the risers.
Further preferably, d =1.2511, e =1.508, f =0.396, h = 0.923;
preferably, d, e, f are larger and h is smaller as M1/B2 is increased.
Preferably, as B2 increases, M2 increases, but as B2 increases, the magnitude of the increase in M2 becomes smaller and smaller. The change of the rule is obtained through a large amount of numerical simulation and experiments, and the heat exchange effect can be further improved through the change of the rule.
Preferably, a flow stabilizer 4 is also arranged in the downcomer. The optimization of the arrangement of the spacing between the downcomers is the same as for the risers.
Preferably, the riser or downcomer length L is between 4000-5500 mm. More preferably, 4200 and 4800 mm.
By optimizing the optimal geometric dimension of the formula, the optimal effect of shock absorption and noise reduction can be achieved under the condition of meeting the normal flow resistance.
For other parameters, such as the wall thickness of the pipe and the wall thickness of the shell, the parameters are set according to normal standards.
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, that is, the data can be corrected by increasing the correction coefficient c
c* M1/B2=a*Ln(B1/B2) +b；c=1/sin(A)mWherein 0.09<m<0.11, preferably m = 0.10.
20 < a <80, preferably 40-60.
Preferably, the pipe diameter of the ascending pipe is larger than that of the descending pipe. The resistance of the descending pipe is mainly increased, and the resistance of the ascending pipe is reduced, so that steam flows from the evaporation part more easily, and the loop heat pipe forms circulation better.
Preferably, said downcomer is square in cross-section.
Preferably, the diameter of the downcomer decreases continuously in the direction of fluid flow. The main reasons are as follows: 1) because along with the continuous flow of fluid, liquid is the condensation that is continuous in the downcomer to make the fluid volume littleer and smaller, pressure is also littleer and smaller, consequently satisfies the change of the fluid volume that constantly increases and pressure through reducing the pipe diameter, thereby makes pressure distribution even on the whole, and the heat transfer is even. 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, and by means of 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 with reference to the preferred embodiments, it is not limited thereto. Various changes and modifications may be effected therein 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 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; the flow stabilizer consists of a square through hole and a regular octagonal through hole, the side length of the square through hole is equal to that of the regular octagonal through hole, four sides of the square through hole are respectively sides of four different regular octagonal through holes, and four mutually spaced sides of the regular octagonal through hole are respectively sides of four different square through holes; the flow stabilizing device comprises a square central flow stabilizing device, a square through hole is positioned in the center of the ascending pipe, and a regular octagonal central flow stabilizing device is positioned in the center of the ascending pipe; the types of the flow stabilizers arranged adjacently are different; along with the increase of the pipe diameter of the ascending pipe, the side length of the square through hole is continuously increased.
2. A steam boiler according to claim 1, characterized in that the increasing tube diameter of the riser tube is of increasing magnitude in the direction of the fluid flow.
3. A steam boiler according to claim 1, characterized in that the cross-section of the riser is square.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010189103.2A CN111207377B (en) | 2018-06-20 | 2018-06-20 | Steam boiler |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810632533.XA CN110285399B (en) | 2018-06-20 | 2018-06-20 | Flow stabilizer and design method of steam boiler with optimized pipe diameter |
| CN202010189103.2A CN111207377B (en) | 2018-06-20 | 2018-06-20 | Steam boiler |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810632533.XA Division CN110285399B (en) | 2018-06-20 | 2018-06-20 | Flow stabilizer and design method of steam boiler with optimized pipe diameter |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN111207377A CN111207377A (en) | 2020-05-29 |
| CN111207377B true CN111207377B (en) | 2021-05-25 |
Family
ID=68001150
Family Applications (3)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010189103.2A Active CN111207377B (en) | 2018-06-20 | 2018-06-20 | Steam boiler |
| CN202010189094.7A Active CN111207376B (en) | 2018-06-20 | 2018-06-20 | Design method of steam boiler with variable ascending pipes |
| CN201810632533.XA Active CN110285399B (en) | 2018-06-20 | 2018-06-20 | Flow stabilizer and design method of steam boiler with optimized pipe diameter |
Family Applications After (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010189094.7A Active CN111207376B (en) | 2018-06-20 | 2018-06-20 | Design method of steam boiler with variable ascending pipes |
| CN201810632533.XA Active CN110285399B (en) | 2018-06-20 | 2018-06-20 | Flow stabilizer and design method of steam boiler with optimized pipe diameter |
Country Status (1)
| Country | Link |
|---|---|
| CN (3) | CN111207377B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114608000B (en) * | 2021-05-27 | 2023-03-03 | 中北大学 | Bending tube steam boiler with intelligent elastic control change |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3106822C2 (en) * | 1981-02-24 | 1982-12-23 | Hans 7614 Gengenbach Schneekloth | Distribution pipe |
| CN201224686Y (en) * | 2008-03-28 | 2009-04-22 | 吉林省四平锅炉制造有限公司 | Vapor generation apparatus for cyclically heating sewerage |
| CN102635842A (en) * | 2012-04-16 | 2012-08-15 | 南京工业大学 | Separated type fin plate steam generator |
| CN103426486A (en) * | 2013-08-06 | 2013-12-04 | 华北电力大学 | Natural circulation multi-functional gas lifting device |
| CN106949449A (en) * | 2017-04-21 | 2017-07-14 | 青岛金玉大商贸有限公司 | A kind of steam boiler |
| 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 |
| CN107143837A (en) * | 2017-04-18 | 2017-09-08 | 青岛金玉大商贸有限公司 | A kind of damping steam boiler |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101460785A (en) * | 2006-06-08 | 2009-06-17 | 贝卡尔特股份有限公司 | Heat exchanger and heating apparatus provided therewith |
| KR20070060065A (en) * | 2007-05-28 | 2007-06-12 | 김병두 | A furnace of a pulverized coal boiler for power station |
| US10724734B2 (en) * | 2017-02-02 | 2020-07-28 | Superior Boiler, LLC | Multiple pass flexible water tube boiler |
| CN107084380B (en) * | 2017-04-18 | 2018-06-19 | 何洪兴 | A kind of steam boiler |
| CN107084381B (en) * | 2017-04-21 | 2018-11-16 | 青岛金玉大商贸有限公司 | A kind of damping steam boiler |
-
2018
- 2018-06-20 CN CN202010189103.2A patent/CN111207377B/en active Active
- 2018-06-20 CN CN202010189094.7A patent/CN111207376B/en active Active
- 2018-06-20 CN CN201810632533.XA patent/CN110285399B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3106822C2 (en) * | 1981-02-24 | 1982-12-23 | Hans 7614 Gengenbach Schneekloth | Distribution pipe |
| CN201224686Y (en) * | 2008-03-28 | 2009-04-22 | 吉林省四平锅炉制造有限公司 | Vapor generation apparatus for cyclically heating sewerage |
| CN102635842A (en) * | 2012-04-16 | 2012-08-15 | 南京工业大学 | Separated type fin plate steam generator |
| CN103426486A (en) * | 2013-08-06 | 2013-12-04 | 华北电力大学 | Natural circulation multi-functional gas lifting device |
| 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 |
| CN107143837A (en) * | 2017-04-18 | 2017-09-08 | 青岛金玉大商贸有限公司 | A kind of damping 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 |
Also Published As
| Publication number | Publication date |
|---|---|
| CN110285399A (en) | 2019-09-27 |
| CN111207376B (en) | 2021-05-25 |
| CN111207377A (en) | 2020-05-29 |
| CN111207376A (en) | 2020-05-29 |
| CN110285399B (en) | 2020-04-17 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN108895424B (en) | Design method of inclined multi-tube steam boiler | |
| CN111412763B (en) | Design method for internal size of vapor-liquid two-phase flow heat exchange tube | |
| CN111207376B (en) | Design method of steam boiler with variable ascending pipes | |
| CN109882821B (en) | Ascending pipe spacing optimization design method | |
| CN110186023B (en) | Design method of steam boiler | |
| CN109882822B (en) | Design method of steam boiler with different diameters of ascending pipe and descending pipe | |
| CN109945148B (en) | Steam boiler | |
| CN110067993B (en) | Steam boiler with variable pipe diameter of downcomer | |
| CN114076301B (en) | Linear temperature-uniforming plate steam boiler | |
| CN113623629B (en) | Steam boiler with complementary temperature-equalizing plates | |
| CN114608000B (en) | Bending tube steam boiler with intelligent elastic control change | |
| CN113669711B (en) | Arc-shaped plate steam boiler with quantity-controlled temperature-equalizing plates | |
| CN114608001B (en) | Steam boiler of intelligent control pitch-row change | |
| CN113669712B (en) | Steam boiler with ascending pipe and temperature equalizing plate spacing control function | |
| CN109855449B (en) | Shell-and-tube heat exchanger for generating steam | |
| CN110864566B (en) | Design method for balanced flow of heat exchanger with variable pipe diameter | |
| CN109974490B (en) | Design method of ascending pipe of loop heat pipe | |
| CN109916206B (en) | Loop heat pipe |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| TA01 | Transfer of patent application right | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20210425 Address after: Room 602, 2 Sanhua Road, Qixing street, Xinchang County, Shaoxing City, Zhejiang Province Applicant after: Shaoxing Mingliang Technology Information Consulting Co.,Ltd. Address before: 266071 Unit 102, Building 1, 16 Gutian Road, Southern District, Qingdao City, Shandong Province Applicant before: QINGDAO JINYUDA COMMERCE AND TRADE Co.,Ltd. |
|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20230413 Address after: 312570 shanjieling village, Shaxi Town, Xinchang County, Shaoxing City, Zhejiang Province Patentee after: Xinchang Shengye Machinery Co.,Ltd. Address before: Room 602, 2 Sanhua Road, Qixing street, Xinchang County, Shaoxing City, Zhejiang Province Patentee before: Shaoxing Mingliang Technology Information Consulting Co.,Ltd. |