CN109827459B - Swirl vane, swirl fan, swirl pipeline and preparation method of swirl vane - Google Patents
Swirl vane, swirl fan, swirl pipeline and preparation method of swirl vane Download PDFInfo
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Abstract
The invention discloses a swirl vane, which comprises a front edge, a back arc, a tail edge and an inner arc which are sequentially connected end to end; the swirl vanes rotate about the axis of rotation; the projection of the swirl blades on a cylindrical surface coaxial with the rotation axis forms a blade molded line, and the blade molded line is a closed curve; the intersection point of the camber line of the blade profile and the leading edge line is a leading edge point, and the intersection point of the camber line of the blade profile and the trailing edge line is a trailing edge point; the included angle between the connecting line of the leading edge point and the trailing edge point and the rotation axis is the blade mounting angle; when the radius of the cylindrical surface is gradually increased, the blade mounting angle is gradually increased, and the outlet airflow angle is gradually reduced. The swirl vane ensures that after the fluid flows through the swirl vane, the swirl vane spirals in the circumferential direction at a higher speed in the flow passage by means of a vane mounting angle which increases gradually in the radial direction and an outlet air flow angle which decreases gradually, and the pressure energy is converted into the tangential and axial kinetic energy of the fluid to the greatest extent.
Description
Technical Field
The invention relates to the field of heat exchange, in particular to a cyclone blade, a cyclone fan, a cyclone pipeline and a preparation method thereof.
Background
With the rapid development of modern industry, energy and environment problems are increasingly prominent. The world is developing clean energy and new generation energy utilization technology, and simultaneously, a new energy-saving new way is developed. The application of the enhanced heat transfer technology not only can save energy and protect the environment, but also can greatly save investment cost. In one version of energy transmission equipment, the heat exchanger is widely applied to industrial departments such as chemical industry, petroleum, power, atomic energy and the like, the heat exchange capacity of the enhanced heat exchanger is always valued by researchers, and a corresponding enhanced heat transfer technology is derived, so that the technology can effectively save energy sources and reduce investment cost. Heat exchangers of various structures and types are developed while the development of heat transfer technology is enhanced, and heat exchangers of new structures and new materials are continuously emerging. The heat exchanger is also called a heat exchanger, and is a device for transferring heat of hot fluid to cold fluid, and is also an indispensable device for transferring heat in chemical production process. The heat exchanger can be a single device, such as a heater, a cooler, a condenser and the like; but also can be a component part of certain process equipment, such as a waste heat recovery device in petrochemical industry, coal industry and the like.
The shell-and-tube heat exchanger is also called a shell-and-tube heat exchanger, and is a dividing wall type heat exchanger taking the wall surface of a tube bundle enclosed in a shell as a heat transfer surface, and the structure generally consists of the shell, the heat transfer tube bundle, a tube plate, a baffle plate (baffle plate), a tube box and other parts. At present, in the heat exchange equipment used in industrial production at home and abroad, the shell-and-tube heat exchanger still dominates, and although the shell-and-tube heat exchanger is inferior to other novel heat exchange equipment in the aspects of heat exchange efficiency, structural compactness, metal material consumption and the like, the shell-and-tube heat exchanger has the characteristics of firm structure, high operation elasticity, strong adaptability, high reliability, wide material selection range, high processing capacity, capability of bearing high temperature and high pressure and the like, so the shell-and-tube heat exchanger is still widely applied in engineering.
Enhancing heat transfer in a narrow sense refers to increasing the heat transfer coefficient between the fluid and the heat transfer surface. The main method is to reduce the thickness of the temperature boundary layer and to generate phase change of the fluid near the heat transfer surface. Various ways of enhancing heat transfer, the purpose of which is to enhance fluid instability, are generally two ways to achieve this effect, namely to change the shape of the heat transfer surface and to provide various shaped turbulizers or inserts on the heat transfer surface or in the heat transfer flow path. However, the designs of the various inserts still have shortcomings in rotating the fluid forward, and the tubular heat exchange effect still needs to be further improved.
Disclosure of Invention
The invention aims to provide a swirl vane, a swirl fan, a swirl pipeline and a preparation method thereof, which are used for solving the problems.
To achieve the purpose, the invention adopts the following technical scheme:
a swirl vane comprises a front edge, a back arc, a tail edge and an inner arc which are connected end to end in sequence; the front edge faces the air inlet direction of the cyclone fan, and the tail edge faces the air outlet direction of the cyclone fan; the swirl vanes rotate about an axis of rotation;
The projection of the swirl blades on a cylindrical surface coaxial with the rotation axis forms a blade profile; the blade molded line is a closed curve and comprises a front edge line, a back arc line, a tail edge line and an inner arc line which are connected end to end in sequence; the intersection point of the camber line of the blade profile and the leading edge line is a leading edge point, and the intersection point of the camber line of the blade profile and the trailing edge line is a trailing edge point; the included angle between the connecting line of the leading edge point and the trailing edge point and the rotation axis is a blade mounting angle;
when the radius of the cylindrical surface is gradually increased, the obtained blade mounting angle is gradually increased.
Optionally, when the radius of the cylindrical surface is gradually increased, the length of the camber line of the obtained blade profile is gradually increased.
A swirl fan comprising a plurality of swirl blades as described above;
the wheel hub is also included; the swirl blades are arranged on the hub and evenly distributed around the axis of the hub; the axis of the hub is the rotation axis, and the inner arc is fixedly connected with the hub.
Optionally, an airflow channel is formed between two adjacent swirl blades, and the cross-sectional area of the airflow channel gradually decreases from the air inlet direction to the air outlet direction.
Optionally, the two adjacent swirl blades are a first swirl blade and a second swirl blade respectively, projections of the first swirl blade and the second swirl blade on the same cylindrical surface are a first swirl blade molded line and a second swirl blade molded line respectively, and a back arc line of the first swirl blade molded line faces an inner arc line of the second swirl blade;
The projection of the airflow channel between the first swirl blade and the second swirl blade on the cylindrical surface forms an airflow channel molded line; the inner arc line of the second cyclone blade is tangent to the back arc line of the first cyclone blade through a common tangent circle, and the connecting line of the two tangent points of the common tangent circle forms an outlet of the airflow channel molded line; the tangential line of the camber line of the airflow channel molded line at the outlet of the airflow channel molded line forms an outlet airflow angle with the round surface coaxial with the axis of the hub;
The outlet air flow angle obtained gradually decreases as the radius of the cylindrical surface gradually increases.
Optionally, the tangent function of the outlet airflow angle is linear with the radius of the cylindrical surface.
Optionally, an inner arc hole matched with the inner arc in shape is formed in the hub, and the inner arc is inserted into the inner arc hole and fixedly connected with the hub.
A swirl duct in which the swirl fan described above is installed;
A plurality of back arc holes matched with the back arc shape of the cyclone blade are formed in the pipe wall of the cyclone pipe; the back arcs of the swirl blades are respectively inserted into a corresponding back arc hole and fixedly connected with the swirl pipeline.
The preparation method of the cyclone pipeline comprises the following steps:
Preparing a plurality of the swirl vanes;
splitting the cyclone tube into two parts along an axis;
Forming a plurality of inner arc holes on the hub, respectively inserting the inner arcs of the swirl blades into the corresponding inner arc holes, and welding the swirl blades and the hub;
a plurality of back arc holes are formed in the pipe wall of the cyclone pipe, back arcs of the cyclone blades are respectively inserted into the corresponding back arc holes, and the cyclone blades and the cyclone pipe are welded from the outer surface of the cyclone pipe;
And welding the swirl pipeline which is split into two parts.
Compared with the prior art, the invention has the following beneficial effects:
according to the swirl vane provided by the invention, through the gradually increased vane mounting angle, after fluid flows through the swirl vane, the swirl vane can spiral in the circumferential direction at a higher speed in the flow channel, so that the pressure energy is converted into the tangential and axial kinetic energy of the fluid to the greatest extent, the generated tangential speed can ensure the rotation of the fluid, and the generated axial speed can ensure the advance of the fluid.
Drawings
In order to more clearly illustrate the embodiments of the invention or the technical solutions of the prior art, the drawings which are used in the description of the embodiments or the prior art will be briefly described, it being obvious that the drawings in the description below are only some embodiments of the invention, and that other drawings can be obtained from these drawings without inventive faculty for a person skilled in the art.
Fig. 1 is a schematic structural diagram of a swirl vane according to an embodiment of the present invention.
Fig. 2 is a schematic view of a blade profile according to an embodiment of the present invention.
Fig. 3 is a schematic diagram of a cyclone pipeline according to an embodiment of the present invention.
FIG. 4 is a schematic diagram of the convective heat transfer coefficients of the fluid in the tube and the inner wall of the tube at different Reynolds numbers according to an embodiment of the invention.
Fig. 5 is a schematic diagram of a spiral streamline of fluid in a pipeline with a swirl fan according to an embodiment of the present invention.
Illustration of: 1. swirl vanes; 10. an axis of rotation; 11. a leading edge; 12. back arc; 13. a trailing edge; 14. an inner arc; 2. blade profile; 201. a leading edge line; 202. a back arc line; 203. a trailing edge line; 204. an inner arc line; 21. a leading edge point; 22. tail edge points; 23. blade mounting angle; 24. an outlet airflow angle; 25. an axial geometric outlet angle; 26. an airflow channel molded line; 3. a hub; 4. swirl pipes.
Detailed Description
In order to make the objects, features and advantages of the present invention more comprehensible, the technical solutions in the embodiments of the present invention are described in detail below with reference to the accompanying drawings, and it is apparent that the embodiments described below are only some embodiments of the present invention, but not all embodiments of the present invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
In the description of the present invention, it should be understood that the directions or positional relationships indicated by the terms "upper", "lower", "top", "bottom", "inner", "outer", etc. are based on the directions or positional relationships shown in the drawings, are merely for convenience of describing the present invention and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present invention. It is noted that when one component is referred to as being "connected" to another component, it can be directly connected to the other component or intervening components may also be present.
The technical scheme of the invention is further described below by the specific embodiments with reference to the accompanying drawings.
Example 1
In a first embodiment, referring to fig. 1, a swirl vane 1 is provided, where the swirl vane 1 includes a leading edge 11, a back arc 12, a trailing edge 13, and an inner arc 14 connected end to end in sequence. Wherein the leading edge 11 faces the inlet direction of the swirl fan and the trailing edge 13 faces the outlet direction of the swirl fan.
Referring to fig. 2, the swirl vanes 1 rotate about an axis of rotation 10. The projection of the swirl vane 1 on a cylindrical surface coaxial with the rotation axis 10 forms a vane profile 2, and the vane profile 2 is a closed curve and comprises a front edge line 201, a back arc line 202, a tail edge line 203 and an inner arc line 204 which are connected end to end in sequence. The intersection point of the camber line of the blade profile 2 and the leading-edge line 201 is the leading-edge point 21, and the intersection point of the camber line of the blade profile 2 and the trailing-edge line 203 is the trailing-edge point 22. The angle between the line connecting the leading edge point 21 and the trailing edge point 22 and the rotation axis 10 is the blade mounting angle 23.
Considering the rotational scattering effect of the blade channels, the obtained blade mounting angle 23 gradually increases as the radius of the cylindrical surface for projection of the swirl blade 1 gradually increases. Therefore, after the fluid flows through the swirl vane 1, the fluid can be ensured to spiral in the circumferential direction at a higher speed in the flow channel, the pressure energy is converted into the tangential and axial kinetic energy of the fluid to the greatest extent, the generated tangential speed can ensure the rotation of the fluid, and the generated axial speed can ensure the advance of the fluid.
In the present embodiment, when the radius of the cylindrical surface for projection of the swirl vane 1 is gradually increased, the length of the camber line of the obtained vane profile 2 is gradually increased. Such a streamlined design may reduce the flow resistance, i.e. such that the length of the inner arc 14 of the blade in the axial direction is smaller than the length of the back arc 12 thereof in the axial direction.
According to the embodiment, the spiral degree of the fluid is increased by controlling the installation angle of the blades, the disturbance of the fluid is enhanced, the laminar flow section is damaged, the fluid is positioned in the transition section or the turbulent flow section, the heat exchange coefficient of the fluid in the pipe and the pipe wall is increased, the fluid is continuously flushed to the pipe wall through rotational flow, and scaling can be effectively prevented.
Example two
The present embodiment provides a swirl fan including a plurality of swirl vanes 1 in the first embodiment.
Referring to fig. 3, the swirl fan further includes a hub 3. The swirl blades 1 are all arranged on the hub 3 and evenly distributed around the axis of the hub 3. The axis of the hub 3 is a rotation axis 10, and an inner arc 14 of the swirl vane 1 is fixedly connected with the hub 3. Specifically, the hub 3 is provided with an inner arc 14 molded line hole matched with the inner arc 14 in shape, and the inner arc 14 is inserted into the inner arc 14 molded line hole and fixedly connected with the hub 3.
Referring to fig. 2, two adjacent swirl blades 1 are a first swirl blade and a second swirl blade, and the projections of the first swirl blade and the second swirl blade on the same cylindrical surface are a first swirl blade profile (the swirl blade profile above the position in fig. 2) and a second swirl blade profile (the swirl blade profile below the position in fig. 2), respectively, and the camber line 202 of the first swirl blade profile faces the inner camber line 204 of the second swirl blade.
The projection of the airflow channel between the first swirl blade and the second swirl blade on the cylindrical surface forms an airflow channel molded line, and the airflow channel molded line is positioned between the first swirl blade molded line and the second swirl blade molded line. The inner arc 204 of the second swirl vane is tangent to the back arc 202 of the first swirl vane by a common tangent circle, and the two tangent points of the common tangent circle are connected to form the outlet of the airflow channel molded line. The tangential line of the central arc line of the airflow channel molded line at the outlet of the airflow channel molded line forms an outlet airflow angle between the circular surfaces coaxial with the axis of the hub. Two circular surfaces coaxial with the axis of the hub and the cylindrical surface can form a cylinder.
An airflow channel is formed between two adjacent swirl blades 1, and the cross-sectional area of the airflow channel gradually decreases from the air inlet direction to the air outlet direction.
When two adjacent blades are simultaneously intercepted by a cylindrical surface coaxial with the axis of the hub 3, two blade molded lines 2 are obtained, an airflow channel molded line 26 corresponding to an airflow channel is formed between the two blade molded lines 2, and a connecting line between tail edge points 22 of the two blade molded lines 2 forms an outlet of the airflow channel molded line 26. The camber line of the airflow channel profile 26 forms an outlet airflow angle 24 between a tangent line at the outlet of the airflow channel profile 26 and a circular surface coaxial with the axis of the hub 3. The resulting exit airflow angle 24 gradually decreases as the radius of the cylindrical surfaces used to intercept the two blades gradually increases. The tangent function of the outlet airflow angle 24 is linear with the radius of the cylindrical surface used to intercept the two blades.
The swirl vane 1 is designed to allow the fluid to spiral, and the swirl vane 1 designed in the document of the application not only deflects the fluid but also accelerates the fluid by adjusting the vane profile 2. When the mass flow rate of the fluid passing through the heat exchange tube is fixed, the average outlet air flow angle 24 degrees and the heat exchange coefficient are in a certain relation, and when the tangent function of the outlet air flow angle 24 and the radius of the cylindrical surface for intercepting two blades are in a linear relation (equal-annular-quantity torsion method) by taking a compressible gas working medium as an example, due to the fact that the circumferential speed of the circle is high, the centrifugal inertia force of the fluid is gradually increased in the radial direction, the force is balanced with the radial pressure gradient of the fluid, and at the moment, the vortex of the fluid is stronger in the area with the larger radius, and the blade profile 2 is suitable for a heat exchange unit with the large pressure and the large pipe diameter.
It will be appreciated that the outlet air flow angle 24 may also be designed in a radially non-varying twist stack which creates a non-free vortex with the axial component velocity of the air flow decreasing with increasing cylindrical surface radius, thus readily creating a turbulent zone in the region away from the hub 3 which increases heat transfer capacity but is detrimental to fluid propulsion. If a swirl fan is placed in a tubular heat exchanger, the convective heat transfer coefficient of the tubular heat exchanger increases with decreasing average outlet airflow angle 24, and in order to control the heat transfer amount of the fluid, the heat transfer coefficient may be adjusted by changing the angle of different sections of the swirl vanes 1.
In the present embodiment, the tangent to the camber line of the blade profile 2 at its trailing-edge point 22 forms an axial geometric outlet angle 25 with the rotation axis 10. The angle is selected according to practical conditions, and the preferable range is 15-30 degrees. The angle is selected to ensure that the spiral vortex exists at the outlet of the airflow channel and that the fluid has a certain tangential impact velocity. The swirling flow continuously impacts the boundary layer to enhance the mass energy exchange of the boundary layer and the main flow region, thereby improving the convective heat exchange capacity of the fluid and the pipeline.
Example III
The embodiment provides a rotational flow pipeline 4 and a preparation method thereof. The swirl duct 4 is internally provided with a swirl fan provided in the second embodiment.
Referring to fig. 3, the wall of the cyclone tube 4 is provided with a plurality of back arc 12 shaped line holes matching the shape of the back arcs 12 of the cyclone blades 1, and the back arcs 12 of the cyclone blades 1 are respectively inserted into a corresponding back arc 12 shaped line hole to be fixedly connected with the cyclone tube 4.
The preparation method of the cyclone tube 4 comprises the following steps:
Preparing a plurality of swirl vanes 1;
Dividing the swirl tube 4 into two parts along the axis;
Forming a plurality of inner arc 14 molded line holes on the hub 3, respectively inserting the inner arcs 14 of the swirl blades 1 into the corresponding inner arc 14 molded line holes, and welding the swirl blades 1 and the hub 3;
A plurality of back arc 12 molded line holes are formed in the pipe wall of the cyclone pipe 4, the back arcs 12 of the cyclone blades 1 are respectively inserted into the corresponding back arc 12 molded line holes, and the cyclone blades 1 and the cyclone pipe 4 are welded from the outer surface of the cyclone pipe 4;
The swirl tube 4 split into two parts is welded.
The swirl tube 4 may be arranged at the tube inlet location of the tube heat exchanger and later be connected to a normal tube. If the swirl pipe 4 is used for the modification of the existing tubular heat exchanger, the swirl pipe 4 may be filled and welded by cutting off the portion of the original tubular heat exchanger at a position close to the inlet. According to the demand, can prepare swirl pipe 4 pipe diameter the same, but internally mounted's swirl vane 1 molded lines are different swirl pipe 4, and whole section carries out the replacement and uses.
The smaller swirl vane 1 is milled by a numerical control five-axis machine tool, the relative precision requirement is not high, and the swirl vane 1 for low-temperature fluid can be manufactured by injection molding by a plastic mold.
The pipe diameter of the pipe heat exchanger suitable for the design is not too small, the heat exchange equipment with the pipe length not too long can be matched with a spiral pipe for use, the sustainable pushing of the vortex strength is ensured, the vortex strength of fluid can be reduced for a U-shaped pipe bundle, and a group of vortex pipes 4 can be added after the U-shaped elbow.
The preparation method of the cyclone pipeline 4 provided by the embodiment is simple, low in cost and high in manufacturing efficiency.
Example IV
In this embodiment, the effect of the swirl duct 4 in the third embodiment will be described by taking an air preheater for a certain fuel cell as an example.
The air is preheated to 650 ℃ by using flue gas with the temperature of 1050 ℃, a conventional tube type heat exchanger is adopted, the comprehensive heat transfer coefficient is 46.22W/(m 2 -K), after the cyclone pipeline 4 is added at the tube side, the comprehensive heat transfer coefficient is increased to 49.11W/(m 2 -K), the tube side convection heat transfer coefficient is increased to 90.56W/(m 2 -K) from 81.78W/(m 2 -K), and the heat transfer coefficient is increased by 10.7%, as shown in the table 1. The heat transfer coefficients of the flow measuring and calculating light pipe and the fluid in the pipe with the rotational flow pipeline 4 and the pipe wall are changed through the flow velocity of the single channel, and the heat exchange coefficient h 1 under different inlet Reynolds numbers is obtained, as shown in figure 4.
TABLE 1 analysis of Heat exchange Effect of air preheater for certain Fuel cell
The technology is also applicable to incompressible fluid, taking a water-cooled organic oil cooler as an example, the tube side dimension DN32, the number of single-pass tubes is 168, the number of regular triangles is arranged, the comprehensive heat exchange coefficient K value is 278W/(m 2 -K) before the cyclone tube 4 is added, after the cyclone tube 4 is added at the end of each tube, the heat exchange coefficient reaches 281.3W/(m 2 -K), the tube side convection heat exchange coefficient is increased from 4327W/(m 2 -K) to 4655.8W/(m 2 -K), and the 7.6% is improved; the logarithmic temperature difference was reduced from 55℃to 47℃as shown in Table 2.
Table 2 analysis of heat exchange effect of organic oil cooler
Wherein the Reynolds numberWherein ρ, v, L and μ represent density, fluid velocity, characteristic length and viscosity coefficient of the fluid respectively, ρ and μ are determined by physical properties of the working medium, v is determined by flow rate and resistance of the working medium, and L is determined by structural dimensions of the heat exchange device;
Prandtl number The relationship between the temperature boundary layer and the flow boundary layer is shown, and the influence of the physical property of the fluid on the convection heat transfer process is reflected; mu is dynamic viscosity, cp is isobaric specific heat capacity, and k is thermal conductivity;
nussel number Characterizing the ratio of the characteristic length to the thickness of the thermal boundary layer, wherein h, L and k are respectively the convection heat transfer coefficient, the characteristic length and the thermal conductivity coefficient;
In-tube turbulent forced convection heat exchange, nu=0.023 Re 0.8 PrmξtξlξR, where m=0.4 when liquid is heated or gas is cooled, m=0.3 when liquid is cooled or gas is heated, ζ t is a temperature difference correction coefficient, ζ l is a tube length correction coefficient, ζ R is a bending correction coefficient;
Total heat transfer coefficient Wherein h 1、h2 is the convective heat transfer coefficient of the fluid and the inner side and the outer side of the tube respectively, delta is the thickness of the tube wall, and lambda is the heat transfer coefficient of the tube;
Logarithmic temperature difference
Enhanced heat exchange performance evaluation indexNu and Nu 0 are the nussel numbers of the enhanced heat exchange tube and light pipe, respectively, and f 0 are the resistance coefficients of the enhanced heat exchange tube and light pipe, respectively.
In order to meet different heat exchange requirements, the swirl vanes 1 are usually required to be different, parameters such as the outlet angle, the vane number and the like of the swirl vanes 1 are regulated according to the flow speed of fluid and the length of the swirl pipeline 4, and the heat exchange coefficient is monitored through parameters such as the dimensionless factor Nu, the Planet number Pr, the Reynolds number Re and the like, so that the ideal heat exchange effect is determined to be achieved. The axial length of the swirl vane 1 is generally determined by the pipe diameter. The swirl vanes 1 in the present document are of progressively widening axial length when radially outwards, typically having a width of more than 5mm at the hub 3, the hub 3 typically taking a diameter of more than 0.1 times the diameter of the swirl tube 4.
The heat exchange mode is suitable for gas or liquid flowing in a pipe, and certain difference exists between the molded lines of the swirl vanes 1 for compressible fluid and incompressible fluid.
The cyclone pipeline 4 provided by the document can improve the heat transfer effect of tubular heat exchange, improve the heat power of the heat exchanger, reduce the size, weight and metal consumption of heat exchange equipment under the same condition, and realize heat extraction under the condition of lower temperature difference. The present document provides for the spiral propulsion of a fluid by means of swirl vanes 1, enhancing turbulence to reduce and disrupt laminar flow sections, the fluid is in the transition section or the turbulence section, and the heat exchange coefficient between the fluid in the pipe and the pipe wall is increased. Fig. 5 shows a spiral flow diagram of the fluid in the tube after passing through the swirl vanes 1. The swirl vanes 1 can also slow down the scaling phenomenon of the pipeline and reduce the cleaning frequency of the heat exchanger. The heat exchange amount of the fluid can be controlled by adjusting the swirl vanes 1 within a certain range.
The above embodiments are only for illustrating the technical solution of the present invention, and not for limiting the same; although the invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical scheme described in the foregoing embodiments can be modified or some technical features thereof can be replaced by equivalents; such modifications and substitutions do not depart from the spirit and scope of the technical solutions of the embodiments of the present invention.
Claims (9)
1. The swirl vane is characterized by comprising a front edge, a back arc, a tail edge and an inner arc which are sequentially connected end to end; the front edge faces the air inlet direction of the cyclone fan, and the tail edge faces the air outlet direction of the cyclone fan; the swirl vanes rotate about an axis of rotation;
The projection of the swirl blades on a cylindrical surface coaxial with the rotation axis forms a blade profile; the blade molded line is a closed curve and comprises a front edge line, a back arc line, a tail edge line and an inner arc line which are connected end to end in sequence; the intersection point of the camber line of the blade profile and the leading edge line is a leading edge point, and the intersection point of the camber line of the blade profile and the trailing edge line is a trailing edge point; the included angle between the connecting line of the leading edge point and the trailing edge point and the rotation axis is a blade mounting angle;
when the radius of the cylindrical surface is gradually increased, the obtained blade mounting angle is gradually increased.
2. Swirl vane according to claim 1, characterized in that the length of the camber line of the vane profile obtained increases gradually as the radius of the cylindrical surface increases gradually.
3. A swirl fan comprising a plurality of swirl vanes according to any one of claims 1 to 2;
the wheel hub is also included; the swirl blades are arranged on the hub and evenly distributed around the axis of the hub; the axis of the hub is the rotation axis, and the inner arc is fixedly connected with the hub.
4. A swirl fan according to claim 3 characterised in that an airflow channel is formed between two adjacent swirl vanes, the cross-sectional area of the airflow channel decreasing progressively from the inlet to the outlet direction.
5. The swirl fan of claim 4 wherein two adjacent swirl vanes are first and second swirl vanes, respectively, the projections of the first and second swirl vanes on the same cylindrical surface are first and second swirl vane profiles, respectively, the back arc of the first swirl vane profile being oriented toward the inner arc of the second swirl vane;
The projection of the airflow channel between the first swirl blade and the second swirl blade on the cylindrical surface forms an airflow channel molded line; the inner arc line of the second cyclone blade is tangent to the back arc line of the first cyclone blade through a common tangent circle, and the connecting line of the two tangent points of the common tangent circle forms an outlet of the airflow channel molded line; the tangential line of the camber line of the airflow channel molded line at the outlet of the airflow channel molded line forms an outlet airflow angle with the round surface coaxial with the axis of the hub;
The outlet air flow angle obtained gradually decreases as the radius of the cylindrical surface gradually increases.
6. The swirl fan of claim 5 wherein the tangent function of the outlet airflow angle is linear with the radius of the cylindrical surface.
7. A swirl fan according to claim 3 characterised in that the hub is provided with an inner arc hole matching the shape of the inner arc, the inner arc being inserted into the inner arc hole and fixedly connected to the hub.
8. A swirl duct in which a swirl fan according to claim 3 is mounted;
A plurality of back arc holes matched with the back arc shape of the cyclone blade are formed in the pipe wall of the cyclone pipe; the back arcs of the swirl blades are respectively inserted into a corresponding back arc hole and fixedly connected with the swirl pipeline.
9. A method of preparing a swirl tube according to claim 8, comprising the steps of:
Preparing a plurality of the swirl vanes;
splitting the cyclone tube into two parts along an axis;
Forming a plurality of inner arc holes on the hub, respectively inserting the inner arcs of the swirl blades into the corresponding inner arc holes, and welding the swirl blades and the hub;
a plurality of back arc holes are formed in the pipe wall of the cyclone pipe, back arcs of the cyclone blades are respectively inserted into the corresponding back arc holes, and the cyclone blades and the cyclone pipe are welded from the outer surface of the cyclone pipe;
And welding the swirl pipeline which is split into two parts.
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| CN110038401A (en) * | 2019-06-04 | 2019-07-23 | 深圳奥拓力机电科技有限公司 | Duct type air purification device |
| CN111006530A (en) * | 2019-11-18 | 2020-04-14 | 榆林学院 | Heat exchanger device and heat exchange system for inner component of crescent fan |
| CN114104297A (en) * | 2021-11-19 | 2022-03-01 | 中国商用飞机有限责任公司 | Rotational flow mixing device for air source system heat exchanger |
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