Distributing device for strengthening axial airflow transportation

Abstract

The invention belongs to the field of film evaporators, and relates to a distributor for strengthening axial airflow transportation, which comprises a cylindrical rotor and a plurality of rows of scrapers arranged on the periphery of the rotor, all the scrapers are uniformly distributed around the central axis of the rotor, and each scraper is connected with the periphery of the rotor through a support plate; the contact area of each supporting plate and the periphery of the rotor is a spiral line, each supporting plate is composed of a plurality of rectangular areas which are sequentially arranged along the spiral line, the long edge of each rectangular area is perpendicular to the periphery of the rotor, the short edge of each rectangular area coincides with the spiral line, and all the supporting plates are evenly distributed around the center axis of the rotor. According to the distributor provided by the invention, the supporting plate is obliquely arranged, so that the axial airflow conveying capacity in the distributor can be improved, the accumulation of wet steam is reduced, negative effects on the distribution uniformity of distributed feed liquid are avoided, the production efficiency is favorably improved, the energy consumption can be reduced, and the distributor has an important application prospect.

Description

TECHNICAL FIELD

[0001] The present application belongs to the field of thin film evaporators, and relates to a distributor for strengthening axial airflow transportation. BACKGROUND

[0002] The distributor is the first working area in the entire thin film evaporator system, mainly composed of support plates, scrapers and other components. Through accurate design and operation of the distributor, the feed liquid can be uniformly distributed, and through the circumferential movement of the scraper and the gravity action of the feed liquid, the feed liquid is uniformly spread to form a liquid film, thereby ensuring stable and rapid evaporation of the feed liquid during entering the evaporation area, and ensuring the improvement of production efficiency and product quality.

[0003] At present, the design of the distributor pays more attention to the development and optimization of multifunctionality to meet the requirements in different production environments and working conditions. For example, the patent application for an invention with the publication number CN117858745A discloses a large-capacity thin film evaporator for cellulose dissolution, as shown in Figure 1 and Figure 2 Each distributor area scraper is composed of a vertical plate 15 and a plurality of inclined plates 3 arranged at intervals from top to bottom. The vertical plate 15 is vertically arranged, the inner surface of the vertical plate 15 faces the rotor 2, and the outer surface of the vertical plate 15 faces away from the rotor 2. The inclined plates 3 are fixed on the outer surface of the vertical plate. The inner surface of the vertical plate 15 is connected to the outer periphery of the rotor 2 through the vertically arranged lower support steel plate 16 and the vertically arranged upper support steel plate 4, and the lower support steel plate 16 and the upper support steel plate 4 are provided with connecting grooves 14.

[0004] However, in the technical solution of the above CN117858745A, the discharge of the airflow is mainly in a spiral manner on the outer surface of the vertical plate, the axial airflow speed and the axial transportation capacity are weak, and the distributor area still has a large amount of water vapor accumulation, which has an adverse effect on the uniformity of the feed liquid distribution and the next evaporation work.

[0005] Therefore, it is necessary to develop a distributor for strengthening axial airflow transportation to improve the axial airflow transportation capacity of the distributor while not negatively affecting the uniformity of the feed liquid distribution. SUMMARY

[0006] The purpose of the present application is to solve the above-mentioned problems existing in the prior art, and to provide a distributor for strengthening axial airflow transportation.

[0007] To achieve the above-mentioned purpose, the technical scheme adopted by the present application is as follows:

[0008] The application discloses a distributor for strengthening axial airflow transportation, which comprises a cylindrical rotor and a plurality of rows of scrapers arranged on the outer periphery of the rotor, all the scrapers are uniformly distributed around the central axis of the rotor, and each of the scrapers is connected with the outer periphery of the rotor through a support plate.

[0009] The principle of the application is as follows:

[0010] The application improves the airflow channel of the distributor, so that the contact area of the support plate and the outer periphery of the rotor is a spiral line, at this time, the spiral line is at a positive angle β with the rotor axis, and then the support plate is inclined, the flow path and speed distribution of the airflow in the distributor are changed, the axial airflow speed in the distributor is improved, the airflow in the distributor can be more effectively guided to move from the bottom to the steam outlet, and when β is 35°-45°, the axial airflow speed can be considered and the film laying and overflow ratio of the distributor can be controlled in a proper range.

[0011] As a preferred technical scheme:

[0012] The application discloses a distributor for strengthening axial airflow transportation, which comprises a cylindrical rotor and a plurality of rows of scrapers arranged on the outer periphery of the rotor, all the scrapers are uniformly distributed around the central axis of the rotor, and each of the scrapers is connected with the outer periphery of the rotor through a support plate.

[0013] The application discloses a distributor for strengthening axial airflow transportation, which comprises a cylindrical rotor and a plurality of rows of scrapers arranged on the outer periphery of the rotor, all the scrapers are uniformly distributed around the central axis of the rotor, and each of the scrapers is connected with the outer periphery of the rotor through a support plate. , The application discloses a distributor for strengthening axial airflow transportation, which comprises a cylindrical rotor and a plurality of rows of scrapers arranged on the outer periphery of the rotor, all the scrapers are uniformly distributed around the central axis of the rotor, and each of the scrapers is connected with the outer periphery of the rotor through a support plate.

[0014] The application discloses a distributor for strengthening axial airflow transportation, which comprises a cylindrical rotor and a plurality of rows of scrapers arranged on the outer periphery of the rotor, all the scrapers are uniformly distributed around the central axis of the rotor, and each of the scrapers is connected with the outer periphery of the rotor through a support plate.

[0015] The distributor for strengthening axial airflow transportation has 20 rows of scrapers, and the number of scrapers in each row is 1.

[0016] The distributor for strengthening axial airflow transportation has 20 rows of scrapers, and the number of scrapers in each row is 1.

[0017] The distributor for strengthening axial airflow transportation has 20 rows of scrapers, and the number of scrapers in each row is 1.

[0018] The distributor for strengthening axial airflow transportation has 20 rows of scrapers, and the number of scrapers in each row is 1.

[0019] The distributor for strengthening axial airflow transportation has 20 rows of scrapers, and the number of scrapers in each row is 1.

[0020] The distributor for strengthening axial airflow transportation has 20 rows of scrapers, and the number of scrapers in each row is 1.

[0021] Beneficial effects:

[0022] (1) In the distributor provided by the present application, the contact area between the support plate and the outer periphery of the rotor is a spiral line, which causes the support plate of the airflow channel to be inclined, thereby not only improving the axial airflow transportation capacity inside the distributor, reducing the accumulation of wet steam, but also not affecting the uniformity of the material liquid distribution, which is beneficial to the uniform film coating of the distributor.

[0023] (2) The distributor provided by the present application not only improves the stability and production efficiency of the entire thin film evaporation process, but also is beneficial to reducing energy consumption, and has important economic value and application prospect. BRIEF DESCRIPTION OF DRAWINGS

[0024] Figure 1 is a structural diagram of a large-capacity thin film evaporator for cellulose dissolution disclosed in prior art CN117858745A;

[0025] Figure 2 is a structural diagram of a large-capacity thin film evaporator for cellulose dissolution disclosed in prior art CN117858745A;

[0026] Figure 3 is a top view of the distributor for strengthening axial airflow transportation provided by the present application;

[0027] Figure 4 is Figure 3Schematic diagram of the connection structure between the rotor and the support plate in the distributor shown;

[0028] Figure 5 yes Figure 3 A schematic diagram of the structure of the scraper of the distributor shown;

[0029] Figure 6 yes Figure 3 A schematic structural diagram of the support plate of the distributor shown;

[0030] Figure 7 yes Figure 3 Schematic diagram of the distributor with a helical line forming a positive angle β with the rotor axis;

[0031] Figure 8 This is a schematic diagram of the connection structure between the rotor and the support plate in the distributor provided in the comparative example;

[0032] Figure 9 is a graph showing the lift coefficient changing with the angle of attack α;

[0033] Figure 10 This is a cloud diagram of the distribution of liquid in the outer circle of the distributor (the area inside the scraper in the distributor is the inner circle, and the area outside the scraper is the outer circle. Red represents the area covered with liquid. The redder the color, the greater the proportion of liquid. The blue area represents the area without liquid);

[0034] Figure 11 This is the result diagram of the effect of β on velocity distribution;

[0035] Figure 12 This is the result diagram of the effect of β on the axial air flow velocity in the distributor cross section;

[0036] Figure 13 is the cloud diagram of the radial airflow velocity in the distributor cross section (β is 45°);

[0037] Figure 14 It is a cloud diagram of the overflow ratio of the distributor liquid;

[0038] Figure 15 This is the result graph of the distributor height and the average volume fraction of the feed liquid;

[0039] Figure 16 This is the result graph of the impact of β on the overflow ratio;

[0040] Figure 17 This is the result diagram of the effect of β on the proportion of outer ring liquid holdup and total liquid holdup (total liquid holdup refers to the total liquid holdup of the outer and inner rings of the distributor);

[0041] Figure 18 This is the result diagram of the effect of β on the effective cloth ratio and the material liquid drop speed;

[0042] In the figure, 1 is the support plate, 2 is the rotor, 3 is the inclined plate, 4 is the upper support steel plate, 5 is the rectangular area, 14 is the connecting groove, 15 is the vertical plate, and 16 is the lower support steel plate. DETAILED DESCRIPTION

[0043] Below in conjunction with specific embodiment, further set forth the present invention.Should be understood that these embodiments are only used to illustrate the present invention and are not used in limiting the scope of the present invention.In addition, should be understood that after reading the content taught by the present invention, those skilled in the art can make various changes or modifications to the present invention, and these equivalent forms fall equally within the scope limited by the appended claims of the application.

[0044] Examples 1-12

[0045] like Figures 3-6 The distributor for enhancing axial airflow transport shown in the figure comprises a chamber, a cylindrical rotor 2 located in the chamber, and multiple rows of scrapers arranged on the outer periphery of the rotor 2;

[0046] All scrapers are evenly distributed around the central axis of the rotor 2. Each scraper is connected to the outer periphery of the rotor 2 via a support plate 1. The contact area between each support plate 1 and the outer periphery of the rotor 2 is a spiral line. Each support plate 1 is composed of multiple rectangular areas 5 arranged in sequence along the spiral line. The long side of each rectangular area 5 is perpendicular to the outer periphery of the rotor 2, and the short side of each rectangular area 5 coincides with the spiral line. All support plates 1 are evenly distributed around the central axis of the rotor 2.

[0047] like Figure 5 Each scraper shown is composed of a vertical plate 15 and a plurality of inclined plates 3 spaced apart from each other from top to bottom. The vertical plates 15 are vertically arranged and have a V-shaped cross-section. The inner surface of the vertical plate 15 faces the rotor 2, and the outer surface of the vertical plate 15 faces away from the rotor 2. The inner surface of the vertical plate 15 is connected to the outer periphery of the rotor 2 via the support plate 1, and the inclined plates 3 are fixed to the outer surface of the vertical plate 15.

[0048] The ratio of the number of inclined plates 3 to the length of the vertical plates 15 is 4:540 mm. The inclined plates 3 are tilted and form a negative angle with the rotor axis. , The angle between all inclined plates 3 and the rotor axis is the same;

[0049] There are 20 rows of scrapers, with one scraper in each row; the distance between the scraper and the upper end of the rotor 2 is 150.5 mm, and the distance between the scraper and the lower end of the rotor 2 is 344.5 mm;

[0050] The length of the rotor 2 is 1.7 m and the circumference is 3801 mm. The length of the rectangular area 5 is 135 mm, and the thickness of the support plate 1 is 18 mm. The distance between the helix and the upper end of the rotor 2 is 1306 mm.

[0051] As shown in Figure 7 , the helical line is at a positive angle β with the rotor axis, β respectively takes values of 5°, 10°, 15°, 20°, 25°, 30°, 35°, 40°, 45°, 50°, 55°, 60°, each β value corresponds to a length value of the helical line, when β is 45°, the length of the helical line is 1824mm.

[0052] Comparative Example 1

[0053] As shown in Figure 8 , the distributor is basically the same as the embodiment, the difference is only that β is 0°, that is, the support plate 1 remains in a vertical state.

[0054] The distributors of the comparative example and the embodiment are subjected to simulation experiments.

[0055] The specific steps of the simulation experiment are as follows:

[0056] (1) The distributor is divided into a distribution area and an airflow passage area, and is defined as an outer ring and an inner ring according to the position; the area within the scraper in the distributor is the inner ring, and the area outside the scraper is the outer ring;

[0057] (2) Set the β value, and perform modeling and fluid domain construction, and then perform mesh independence verification (mesh independence verification is used to show the correctness of the simulation result, which represents that the simulation result is independent of the number of mesh division); the feed rate of the material liquid is 194 grams per second, and the rotation speed of the rotor is 90 revolutions per minute;

[0058] (3) VOF model and MRF (Multiple Reference Frame) model are used for simulation calculation, VOF model reasonably represents water vapor phase and material liquid phase in the distributor, and MRF model simulates the rotation and scraping of the distributor; wherein the control equation (continuity and momentum equation) is in the rotating reference frame, the momentum conservation equation, the relative velocity equation and the continuity equation are as follows:

[0059]

[0060]

[0061]

[0062] In the formula is the static pressure, and are the gravity and external force, is the stress tensor, is the fluid velocity vector, , is the angular velocity vector, is the position vector in the rotating coordinate system;

[0063] (4) The liquid film of the feed liquid is set. Firstly, the liquid film thickness is defined, the data is extracted from the three-dimensional model, and the average value of the uneven liquid film thickness is solved; then the viscosity of the liquid film is set, if the treated feed liquid is a non-Newtonian fluid, the average value of the viscosity is solved; finally, the heating temperature at the wall surface is defined, if the wall surface heating temperature changes, the average value is also taken and the relative humidity above the liquid film is set; when analyzing the gas-liquid two-phase, the solute of the feed liquid is cellulose, the content of NMMO in the feed liquid is 70wt%, NMMO is used instead of the feed liquid as the main phase of the simulation medium, and air is used as the secondary phase of the simulation medium; the Carreau Model in the CFD software is used to simulate the viscosity of the feed liquid (NMMO cellulose water feed liquid), and the viscosity calculation formula is as follows:

[0064]

[0065] In the formula, represents the apparent viscosity, with the unit of Pa·s; represents the zero shear viscosity, with the unit of Pa·s; represents the relaxation time, with the unit of ; represents the shear rate, with the unit of ; represents the power law index, with no unit;

[0066] (5) The air flow velocity data and the feed liquid data obtained by simulation are imported into the software CFDPOST for processing to obtain Figure 10 , Figure 13 and Figure 14 ; the air flow velocity data and the feed liquid data at different β values are extracted in the software CFDPOST, and the Figure 11 , Figure 12 , Figure 15 , Figure 16 , Figure 17 and Figure 18 are obtained by processing in the software ORIGIN.

[0067] The curve as shown in Figure 9 is the curve of the change of the lift coefficient with the attack angle recorded in the literature (Wu Bingli, Gao Yanfu. Air-cooled axial flow fan [M]. Harbin: Harbin Institute of Technology Press, 2007: 34), the vertical axis C L represents the lift coefficient, the horizontal axis α represents the attack angle, and the arrow points to the annular curve representing the air flow transport performance; on the lift curve, there is a maximum lift coefficient , and the attack angle corresponding to is called the critical attack angle , and the attack angle corresponding to the zero lift coefficient ( =0) is called the zero-lift attack angle ; when the lift coefficient reaches the maximum value , the lift and the airflow transport capacity are the strongest; when the attack angle exceeds the critical attack angle , the lift coefficient drops sharply, which is due to airflow stall and boundary layer separation, forming a flow separation point; however, Figure 9 only shows that the attack angle will affect the lift, and the attack angle corresponding to the maximum lift and airflow transport capacity is not necessarily the β value corresponding to the maximum axial airflow velocity of the distributor, because the β value corresponding to the maximum axial airflow velocity should also consider the distance from the rotor wall in the cross section of the distributor, so it is necessary to select the β value that is close to the rotor wall and has the maximum axial airflow velocity and far from the rotor wall and has the minimum axial airflow velocity;

[0068] The distributor needs to ensure uniform distribution of the slurry, providing initial conditions for the subsequent evaporation. The uniformity of the slurry distribution of the distributor mainly refers to the uniformity of the slurry distribution at the outer circle of the distributor. Within a certain range, the higher the slurry distribution uniformity, the better the slurry distribution performance, and it can improve the airflow transport rate in the evaporation stage and effectively improve the evaporation efficiency. As shown in Figure 10 , when the β of the distributor is 0° or the inclination angle of the support plate is 0°, the slurry distribution at the outer circle of the distributor is uneven.

[0069] As shown in Figure 11 , when β gradually increases, the axial airflow velocity inside the distributor also gradually increases, but if β exceeds a certain range, the axial airflow velocity will gradually decrease, so the β of the support plate should be reasonably selected. If β is too small, the effect of increasing the axial airflow velocity will not be particularly obvious. On the contrary, if β is too large, the axial airflow velocity will decrease. The radial airflow velocity and the tangential airflow velocity will affect the fluid handling capacity of the distributor. For example, the tangential airflow velocity will affect the residence time of the slurry, as well as the liquid film thickness and uniformity of the slurry in the distributor. The change in β also causes slight fluctuations in the radial airflow velocity and the tangential airflow velocity, which indicates that the change in β of the support plate has little effect on the overall distribution of the slurry. In addition, Figure 11 , when β is 35°, the axial airflow velocity reaches the maximum value, but this does not mean that this axial airflow velocity is the best axial airflow velocity, because the best axial airflow velocity of the distributor should also consider the film laying situation of the slurry and the axial airflow velocity distribution in the cross section of the distributor. A large axial airflow velocity will affect the film laying of the distributor, and Figure 11 , the axial airflow velocity does not consider the factor of being close to the rotor wall, but only considers the axial airflow velocity at the center of the distributor.

[0070] As shown in Figure 12As shown in the figure, the distribution of the axial airflow velocity in the distributor cross section tends to change regularly with the change of β. The cross section close to the rotor wall has a larger axial airflow velocity, which means that the airflow conveying capacity of the inner ring of the distributor is stronger and wet steam can be discharged from the inner ring. When the support plate is tilted close to 45°, the axial airflow velocity shows a downward trend. This downward trend means that excessive changes in β will limit further increases in the axial airflow velocity. The reason for limiting the increase in axial airflow velocity is that when β is too large, the airflow inside the distributor is suppressed, resulting in velocity separation, which weakens the airflow guidance effect.

[0071] like Figure 13 As shown in the figure, there is a larger radial air flow velocity in the cross section close to the rotor wall, which means that the air flow transport capacity of the inner ring of the distributor is stronger and the wet steam can be discharged from the inner ring of the distributor;

[0072] like Figure 14 As shown in the figure, the part above the feed inlet of the distributor is called the overflow area. In the industrial production process, when a large amount of liquid is distributed in the area above the feed inlet, it is easily sucked out by the negative pressure generated by the vacuum pump at the upper outlet. Therefore, the area occupied by the liquid in the overflow area is defined as the liquid occupation area, and the ratio of the liquid occupation area to the area of ​​the entire overflow area is defined as the overflow ratio. When the distributor is working, the liquid distribution on the outer ring of the distributor is uneven. There are two main reasons for this: first, the viscosity of the liquid is high. When the inclined plate disperses the liquid to the outer ring of the distributor, the inherent viscosity of the liquid makes it difficult to spread; second, due to the gap between the inclined plates, the liquid will gather at the front end of the inclined plate when the inclined plate moves circumferentially;

[0073] like Figure 15 As shown in the figure, in order to more intuitively understand the distribution of the liquid in the outer ring of the distributor, the liquid volume fraction of the outer ring of the distributor was statistically analyzed, and the volume fraction of the liquid in the same height area was averaged to obtain the average volume fraction of the liquid. The average volume fraction of the liquid in the outer ring of the distributor corresponding to different distributor heights was analyzed. It was observed that the average volume fraction of the liquid in the outer ring of the distributor gradually increased from top to bottom. This distribution pattern is consistent with the liquid distribution pattern of the evaporation system. Since the liquid distribution in the distributor is mainly affected by the circumferential movement of the internal scraper and the weight of the liquid, the movement of the scraper plays a leading role in the uniform distribution of the liquid.

[0074] like Figure 16As shown, the change of the overflow ratio is closely related to the change of the axial airflow velocity, the increase of the axial airflow velocity increases the upward movement speed of the slurry in the distributor, thereby increasing the risk of slurry overflow to a certain extent, however, the overflow ratio and the axial airflow velocity are not in a linear relationship, especially when the axial airflow velocity at β of 45° is increased by nearly 100% than that at β of 0°, 5° or 10°, but the change range of the overflow ratio is relatively limited, only increased by about 30%, this result shows that in the distributor, although the increase of the axial airflow velocity indeed increases the upward movement power of the slurry, but this increase does not lead to a large change of the slurry distribution at the outer circle of the distributor, that is, the increase of the axial airflow velocity in the distributor affects the slurry overflow, but does not cause a significant change of the slurry distribution at the outer circle of the distributor, therefore, in the distributor, the increase of the axial airflow transport capacity has a low adverse effect on the slurry distribution performance of the distributor;

[0075] As shown, Figure 17 with the increase of β of the distributor, the proportion of the liquid holdup at the outer circle decreases, but the total liquid holdup gradually increases with the increase of β, the increase of the total liquid holdup is because the increase of the axial airflow velocity of the distributor hinders the flow of the slurry at the outer circle of the distributor;

[0076] As shown, Figure 18 when β is small, the slurry descending speed in the distributor decreases with the increase of β, because after the increase of the axial airflow velocity in the distributor, the slurry at the outer circle of the distributor is affected by the enhanced axial airflow, thereby slowing down the slurry descending speed; when β increases to a certain value, the slurry descending speed at the outer circle of the distributor increases, because the slurry at the outer circle of the distributor is affected by the reduced axial airflow, and the slurry descending speed increases under the action of its own gravity; when β is small, the effective distribution ratio of the distributor increases with the increase of β, which shows that when the β of the distributor is appropriate, it is helpful to improve the distribution state of the slurry, because when the support plate is inclined at a certain angle, the pressure difference in the radial direction of the distributor makes part of the slurry flow from the outer circle to the inner circle, so that more slurry can stay in the inner circle, at the same time, the increase of the number of times of the slurry at the outer circle of the distributor being moved by the scraper in unit time due to the slowing down of the slurry descending speed leads to more uniform slurry distribution and lower liquid film thickness of the slurry;

[0077] In summary, the distributor of the present application can improve the axial transport capacity without affecting the film laying at the outer circle of the distributor, that is, not only the axial airflow velocity at the inner circle of the distributor is increased, but also the film laying of the slurry at the outer circle of the distributor is not affected.

Claims

1. A distributor for enhancing axial air flow transport, comprising a cylindrical rotor (2) and a plurality of rows of scrapers arranged on the outer periphery of the rotor (2), wherein all the scrapers are evenly distributed around the central axis of the rotor (2), and characterized in that: Each scraper is connected to the outer periphery of the rotor (2) through a support plate (1); the contact area between each support plate (1) and the outer periphery of the rotor (2) is a spiral line, and each support plate (1) is composed of a plurality of rectangular areas (5) arranged in sequence along the spiral line, the long side of each rectangular area (5) is perpendicular to the outer periphery of the rotor (2), and the short side of each rectangular area (5) coincides with the spiral line. All support plates (1) are evenly distributed around the central axis of the rotor (2).

2. A distributor for enhancing axial airflow transport according to claim 1, characterized in that: Each scraper is composed of a vertical plate (15) and a plurality of inclined plates (3) arranged at intervals from top to bottom; the vertical plate (15) is vertically arranged and has a V-shaped cross section, the inner surface of the vertical plate (15) faces the rotor (2), and the outer surface of the vertical plate (15) faces away from the rotor (2); the inner surface of the vertical plate (15) is connected to the outer periphery of the rotor (2) through the support plate (1), and the inclined plate (3) is fixed on the outer surface of the vertical plate (15).

3. A distributor for enhancing axial airflow transport according to claim 2, characterized in that: The ratio of the number of inclined plates (3) to the length of the vertical plates (15) is 2-5 pieces: 540 mm. The inclined plates (3) are tilted and form a negative angle with the rotor axis. , 10°-70°.

4. A distributor for enhancing axial airflow transport according to claim 3, characterized in that: The included angles between all the inclined plates (3) and the rotor axis are the same.

5. A distributor for enhancing axial airflow transport according to any one of claims 1 to 4, characterized in that: There are 20 rows of scrapers, and the number of scrapers in each row is 1.

6. A distributor for enhancing axial airflow transport according to claim 5, characterized in that: The distance between the scraper and the upper end of the rotor (2) is 150.5 mm, and the distance between the scraper and the lower end of the rotor (2) is 344.5 mm.

7. A distributor for enhancing axial airflow transport according to claim 6, characterized in that: The length of the rotor (2) is 1.7 m and the circumference is 3801 mm.

8. The distributor for enhancing axial airflow transport according to claim 7, characterized in that: The length of the rectangular area (5) is 135 mm, and the thickness of the support plate (1) is 18 mm.

9. The distributor for enhancing axial airflow transport according to claim 8, characterized in that: The distance between the helix and the upper end of the rotor (2) is 1306 mm.

10. The distributor for enhancing axial airflow transport according to claim 9, characterized in that: The helix forms a positive angle β with the rotor axis, β is 45°, and the length of the helix is ​​1824 mm.

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