Blade type spiral flow spiral flow generator based on bionic non-smooth surface

Abstract

The utility model discloses a blade type spiral flow spiral flow generator based on a bionic non-smooth surface. The blade type spiral flow spiral flow generator is divided into a mandrel part and a front cone part. The main body of the core shaft part is a core shaft, the core shaft is a solid cylinder, a plurality of spiral blades are arranged on the excircle surface of the core shaft in parallel, a plurality of grooves are distributed in each spiral blade side by side in the radial direction, and all the grooves face the front cone direction; the main body of the front cone part is called a front cone section, and a plurality of ribs are longitudinally arranged on the conical surface of the front cone section. The utility model belongs to the technical field of fluid machinery, and solves the problems of low fluid conveying efficiency and lower material mixing property caused by unsatisfactory structure arrangement of a spiral flow spiral flow generator in the prior art, and the grooves not only increase the contact surface between the blades and the materials, promote the full mixing of the materials, but also enhance the stirring uniformity and efficiency; in addition, the shape and arrangement of the grooves ingeniously guide the materials to flow in the spiral line direction, the conveying resistance is reduced, and the overall conveying performance is improved.

Description

TECHNICAL FIELD

[0001] The utility model belongs to the field of fluid machinery, and relates to a blade type spiral flow whirl generator based on a bionic non-smooth surface. BACKGROUND

[0002] Gas-liquid two-phase spiral flow refers to the spiral flow pattern of gas and liquid two fluids in the pipeline or equipment. This unique flow state frequently occurs in power, chemical, nuclear energy, refrigeration, petroleum, metallurgy and other industrial fields, and is the most common and complex two-phase flow system. In the application of gas-liquid two-phase spiral flow, it shows significant advantages in gas-liquid separation, heat transfer enhancement and other fields, and plays an important role in the oil and gas exploitation industry, such as water drainage and gas recovery in gas wells, transportation of hydrates and measurement of wet gas. Because the shape and distribution of the phase interface change with time and space during two-phase flow, and there is a significant speed difference between the two phases, the two-phase flow process is much more complex than single-phase flow.

[0003] The existing spiral flow whirl generator is applied in gas-liquid two-phase spiral flow, but due to the limitation of the structure, the fluid conveying efficiency is low, and the mixing of the material is also low, which needs to be further improved and perfected. INVENTION CONTENTS

[0004] The utility model discloses a blade type spiral flow whirl generator based on a bionic non-smooth surface, which solves the problem of low fluid conveying efficiency and low mixing of materials caused by the unsatisfactory structure of the spiral flow whirl generator in the prior art.

[0005] The technical scheme adopted by the utility model is that the blade type spiral flow whirl generator based on a bionic non-smooth surface is divided into two parts, namely a core shaft part and a front cone part.

[0006] The main body of the core shaft part is a core shaft, which is a solid cylinder. A plurality of spiral blades are arranged in parallel on the outer circular surface of the core shaft. Each spiral blade has a plurality of grooves distributed in the radial direction. All the grooves are directed towards the front cone.

[0007] The main body of the front cone part is called a front cone section. A plurality of ribs are arranged longitudinally on the conical surface of the front cone section. No rib is arranged within a certain range of the front and rear ends of the front cone section.

[0008] The blade type spiral flow whirl generator based on a bionic non-smooth surface of the utility model has the following characteristics:

[0009] The spiral blades are welded on the outer circular surface of the core shaft.

[0010] A plurality of grooves are formed on the spiral blades by spiral tool path. The cross section of the grooves is rectangular.

[0011] The height of the spiral blade is 25-30mm, the thickness of the spiral blade is 3-5mm, and the depth of each groove is 1-2mm.

[0012] The grooves are distributed throughout the spiral blade and extend from the inlet end to the outlet end of the spiral blade.

[0013] The front end of the front cone section is spherical.

[0014] No rib is arranged in the range of 10-15mm between the front end and the rear end of the front cone section.

[0015] The adjacent distance of the ribs is 8-10mm, the protruding height of each rib is 4-5mm, the radial protrusion of the rib is spherical, and the radius of the sphere is 4-5mm.

[0016] The ribs are uniformly distributed along the generatrix of the front cone section.

[0017] The grooves on the spiral blade can significantly improve the mixing and blending effect of the materials during rotation, the grooves not only increase the contact surface between the blade and the materials, promote the full mixing of the materials, but also enhance the uniformity and efficiency of the mixing; in addition, the shape and arrangement of the grooves cleverly guide the materials to flow along the spiral line direction, reduce the conveying resistance, ensure the smooth passage of the materials, effectively prevent the materials from being blocked or stagnant, and improve the overall conveying performance. BRIEF DESCRIPTION OF DRAWINGS

[0018] Figure 1 is the overall structure schematic view of the spiral flow rotator of the utility model;

[0019] Figure 2 is the spiral direction schematic view of the spiral blade of the spiral flow rotator of the utility model;

[0020] Figure 3 is the sectional schematic view of the spiral blade with grooves of the utility model;

[0021] Figure 4 is the sectional structure schematic view of the front cone section and the rib of the utility model;

[0022] Figure 5 is the measurement result comparison curve of the structure of each measuring point of the embodiment 2;

[0023] Figure 6 is the differential pressure comparison curve of the inlet and outlet sections under different flow rate working conditions of the embodiment 3;

[0024] Figure 7 is the hydrate volume fraction result comparison graph of the sectional surface of the embodiment 4;

[0025] Figure 8is the comparison curve of the Nusselt number results of the measuring points of embodiment 6.

[0026] In the figure, 1. helical blade, 2. groove, 3. mandrel, 4. rib, 5. front cone section. DETAILED DESCRIPTION

[0027] The utility model will be described in detail below in combination with the drawings and specific embodiments.

[0028] Reference Figure 1 The structure of the utility model is that the rotator is divided into two parts, namely the mandrel part and the front cone part.

[0029] The main body of the mandrel part is the mandrel 3, which is a solid cylinder. A plurality of helical blades 1 are arranged in parallel on the outer circular surface of the mandrel 3. Each helical blade 1 has a plurality of grooves 2 distributed in parallel along the radial direction, and all the grooves 2 are directed towards the front cone direction. The main body of the front cone part is called the front cone section 5, and a plurality of ribs 4 are arranged longitudinally on the conical surface of the front cone section 5.

[0030] The helical blade 1 is welded on the outer circular surface of the mandrel 3, and the helical line structure is as shown in the figure. Figure 2 The helical blade 1 is made of stainless steel, which has the characteristics of corrosion resistance and high strength. The height of the helical blade 1 is preferably set to be twice the diameter of the mandrel 3. A larger blade height means a larger contact area between the blade and the water flow or air flow, thereby being able to generate a larger pushing force and also being able to enhance the stability of the rotator. During the fluid or material conveying process, the rotator may be affected by various external forces, and a larger blade diameter can better resist these external forces and maintain the stable operation of the rotator.

[0031] As shown in the figure, a plurality of grooves 2 are opened on the helical blade 1 by means of helical tool path, the cross section of the groove 2 is rectangular, the helical line adopts equidistant and continuous machining cutting method, and does not need to cut in and cut out. After finishing, the height L of the helical blade 1 is 25-30mm, the thickness H2 of the helical blade 1 is 3-5mm, and the depth H1 of each groove 2 is 1-2mm. Figure 3 The groove 2 extends throughout the helical blade 1 and from the inlet end to the outlet end of the helical blade 1, and is helically arranged as a whole along with the trend of the helical blade 1. In order to meet the requirements of the overall structure in mechanical properties, stability and other aspects, the depth of the groove 2 is preferably one third of the thickness of the helical blade 1.

[0032] As shown in the figure, a plurality of grooves 2 are opened on the helical blade 1 by means of helical tool path, the cross section of the groove 2 is rectangular, the helical line adopts equidistant and continuous machining cutting method, and does not need to cut in and cut out. After finishing, the height L of the helical blade 1 is 25-30mm, the thickness H2 of the helical blade 1 is 3-5mm, and the depth H1 of each groove 2 is 1-2mm.

[0033] Figure 4 ​As shown in the drawings, the front end of the front cone section 5 is spherical, the ribs 4 are made of cast iron, the surface hardness is high, and the ribs 4 can resist the wear of abrasive particles in water, the ribs 4 are welded on the conical surface of the front cone section 5 at equal intervals, and the ribs 4 are not arranged in a range of 10-15mm from the front and rear ends of the front cone section 5.

[0034] The adjacent interval a of the ribs 4 is 8-10mm, the protruding height b of each rib 4 is 4-5mm, the radial protrusion of the rib 4 is spherical, and the spherical radius R is 4-5mm.

[0035] The spiral blade 1 with the groove 2 is fixedly connected with the mandrel 3 in a welding mode considering the special spiral structure, and the fixed connection has the advantages of high structural strength.

[0036] All the ribs 4 are uniformly distributed along the generatrix of the front cone section 5.

[0037] The principle of the utility model is: the structure can effectively improve the fluid dynamics performance and reduce the flow resistance: the design and arrangement of the ribs 4 can keep the increase range of the flow resistance at a low level; meanwhile, the spiral flow induced by the ribs 4 also has good resistance characteristics, which helps to reduce the overall flow resistance and improve the fluid stability: the ribs 4 can guide the fluid to form stable spiral flow on the spiral blade 1, reduce the turbulence and vortex of the fluid, and improve the stability of the fluid.

[0038] Among the numerous bionic drag reduction technologies, the bionic non-smooth surface drag reduction technology is widely concerned due to its convenience, environmental protection and low carbon, etc. In the evolution history of hundreds of millions of years, the organism forms a self-adaptive non-smooth skin surface, which has been proved and accepted. The streamlined design of the shark body helps to reduce the separation phenomenon of the water flow passing through the body surface, but the water flow still has a separation trend at the position with the largest cross-sectional area of the body surface. To solve this problem, the shark has the largest rib size at this position, and the ribs play a role in inhibiting the separation of the water flow, indicating that the drag reduction effect at this position is the most critical. The utility model realizes the drag reduction function by arranging ribs on the front cone section of the vortex generator.

[0039] The working process of the utility model is: when working, the mixed fluid passes through the front cone section 5, passes through the ribs 4, changes the thickness of the boundary layer, thereby effectively reducing the flow resistance and improving the stability of the flow. Then the fluid continues to flow to the spiral blade 1, and since the spiral blade 1 is processed with the groove 2, the contact area of the fluid and the spiral blade 1 is increased, thereby improving the stirring characteristics and the conveying performance of the fluid; at the same time, due to the spiral structure of the spiral blade 1, the flowing form of the conveyed fluid will change to a spiral flow form after passing through the spiral blade 1, so as to achieve the purposes of high conveying efficiency and low energy consumption.

[0040] Example 1

[0041] In the natural gas hydrate transportation pipeline, in order to inhibit hydrate coalescence to block the pipeline, the structure of the preceding utility model is adopted, the swirler is divided into two parts, namely the mandrel part and the front cone part; the main body of the mandrel part is the mandrel 3, the mandrel 3 is a solid cylinder, a plurality of helical blades 1 are arranged in parallel on the outer circular surface of the mandrel 3, each helical blade 1 has a plurality of grooves 2 distributed in parallel along the radial direction, and all the grooves 2 are directed to the front cone direction; the main body of the front cone part is called the front cone section 5, and a plurality of ribs 4 are arranged longitudinally on the conical surface of the front cone section 5.

[0042] The height of the helical blade 1 is 25 mm, the thickness of the helical blade 1 is 3 mm, the depth of each groove 2 is 1 mm, the distance a between adjacent ribs 4 is 9 mm, the protruding height b of each rib 4 is 4.5 mm, the radial protrusion of the rib 4 is spherical, and the spherical radius R is 4.5 mm. The front cone section 5 is not provided with ribs 4 within a range of 12 mm from the front and rear ends. The helical blade 1 is welded to the outer circular surface of the mandrel 3, and the helical structure is as shown in Figure 2 The helical blade 1 is made of stainless steel.

[0043] Through experimental comparison, the performance comparison of the three states of the ordinary pipe flow state, the flow state after adding the ionic liquid dynamic inhibitor, and the spiral flow state after adding the swirler is shown in the following table 1.

[0044] Table 1, performance of natural gas hydrate flow control technology

[0045]

[0046] It can be seen that the spiral flow formed by the preceding swirler has obvious inhibition and improvement on the coalescence performance of natural gas hydrate, has good operating conditions, low cost, and high transportation efficiency.

[0047] Example 2

[0048] In the hydraulic transportation engineering, in order to improve the transportation efficiency and prevent the accumulation of solid particles such as silt, it is hoped to reduce the influence by generating spiral flow, therefore, the structure of the preceding utility model is adopted, the swirler is divided into two parts, namely the mandrel part and the front cone part; the main body of the mandrel part is the mandrel 3, the mandrel 3 is a solid cylinder, a plurality of helical blades 1 are arranged in parallel on the outer circular surface of the mandrel 3, each helical blade 1 has a plurality of grooves 2 distributed in parallel along the radial direction, and all the grooves 2 are directed to the front cone direction; the main body of the front cone part is called the front cone section 5, and a plurality of ribs 4 are arranged longitudinally on the conical surface of the front cone section 5.

[0049] The height of the helical blade 1 is 30mm, the thickness of the helical blade 1 is 5mm, the depth of each groove 2 is 2mm, the interval a of the adjacent ribs 4 is 10mm, the protruding height b of each rib 4 is 5mm, the radial protrusion of the rib 4 is spherical, and the spherical radius R is 5mm. The rib 4 is not arranged within a certain distance range of 15mm at the front and back ends of the front cone section 5.

[0050] The cross-sectional structure of the helical blade 1 is that a plurality of grooves 2 are opened on the blade by helical tool path, the cross section of the groove 2 is rectangular, and the helical line adopts equidistant and continuous machining cutting mode.

[0051] Through experimental exploration, the structure of the embodiment 2 is installed in the horizontal pipeline, and 13 symmetrical distributed measuring points are measured on the circular tube cross section 20cm away from the rotator. Among them, the distance of the points near the tube wall and the tube axis is 0.5cm, and the distance of the other points is 1cm. The measurement results are shown in Figure 5

[0052] As can be seen from Figure 5 , the water flow generates a circumferential flow velocity after passing through the rotator, which indicates that the water flow changes from a straight flow to a helical flow. Moreover, the circumferential flow velocity under different flow rates is distributed radially in the cross section, that is, small at the center of the pipeline and large at the edge wall, which has the symmetry of rotation. These flow velocity structure characteristics are beneficial to the suspension lifting conveying efficiency of the solid particles in the pipeline and prevent the pipeline from being blocked.

[0053] Embodiment 3

[0054] In order to reduce the energy loss of the fluid after flowing through the rotator and reduce the flow resistance, the structure of the utility model is adopted, the rotator is divided into two parts, that is, the core shaft part and the front cone part; the main body of the core shaft part is the core shaft 3, the core shaft 3 is a solid cylinder, a plurality of helical blades 1 are arranged in parallel on the outer circular surface of the core shaft 3, each helical blade 1 has a plurality of grooves 2 distributed in parallel along the radial direction, and all the grooves 2 are directed to the front cone direction; the main body of the front cone part is called the front cone section 5, and a plurality of ribs 4 are longitudinally arranged on the conical surface of the front cone section 5.

[0055] The height of the helical blade 1 is 28mm, the thickness of the helical blade 1 is 4mm, the depth of each groove 2 is 1.5mm. The interval a of the adjacent ribs 4 is 8mm, the protruding height b of each rib 4 is 4mm, the radial protrusion of the rib 4 is spherical, and the spherical radius R is 4mm. The rib 4 is not arranged within a certain distance range of 10mm at the front and back ends of the front cone section 5.

[0056] The grooves 2 are distributed throughout the helical blade 1, and extend from the inlet end to the outlet end of the helical blade 1. Overall, the grooves 2 are arranged in a helical shape along the trend of the helical blade 1.

[0057] ​The energy loss of single-phase flow fluid flowing through the rotating device is calculated by CFD numerical simulation technology. By comparing the rotating device and the rotating device without ribs in the cone section before the rotating device, the pressure difference of the inlet and outlet sections of the fluid under different flow conditions is calculated as the basis, and the data are shown in Table 1. Figure 6

[0058] As can be seen from Figure 6 , the ribs can reduce the resistance of the fluid and improve the transport efficiency and reduce energy consumption.

[0059] Example 4

[0060] In the process of natural gas pipeline transportation, the rotating device has the effect of changing the flow boundary of the pipeline, thereby changing the flow direction. This transportation method can ensure that the hydrate particles flow in the form of suspended load with the gas, avoid hydrate blockage of the pipeline, and improve the safety and economy of natural gas transportation. The rotating device is divided into two parts, namely the core shaft part and the front cone part. The main body of the core shaft part is a solid cylinder, and the outer circular surface of the core shaft is parallelly arranged with a plurality of spiral blades. Each spiral blade is distributed with a plurality of grooves in the radial direction, and all the grooves are directed to the front cone direction. The main body of the front cone part is a front cone section, and a plurality of ribs are longitudinally arranged on the conical surface of the front cone section.

[0061] The height of the spiral blade is 26mm, the thickness of the spiral blade is 3.5mm, the depth of each groove is 1.2mm, the distance between adjacent ribs is 9mm, the protruding height of each rib is 4.5mm, the radial protrusion of the rib is spherical, and the spherical radius R is 4.5mm. A certain distance is left within the range of 10-15mm of the front and rear ends of the front cone section without setting the rib.

[0062] The front end of the front cone section is spherical, the rib is made of cast iron, the surface hardness is high, and it can resist the wear of abrasive particles in water. The ribs are welded on the conical surface of the front cone section at equal intervals.

[0063] The motion of natural gas hydrate in the horizontal pipe is simulated by CFD numerical simulation technology. The cross-sectional hydrate volume fraction at 5 times and 20 times the pipe diameter after the rotating device is measured as follows Figure 7 Figure 7 As can be seen from , the hydrate particles are distributed near the pipe wall due to the centrifugal force of the spiral flow, and the mixing of gas and solid is effectively improved, which can effectively improve the transport capacity of the pipeline for solid particles, reduce the probability of pipeline blockage, and improve the transport efficiency and reduce energy consumption.

[0064] Example 5

[0065] ​In view of the problems that the long-distance conveying efficiency of the sludge water compound is low, energy consumption is high, and the pipeline is easy to be blocked, a spiral flow rotator is arranged in the pipeline in engineering, and the structure of the utility model is adopted, the rotator is divided into two parts, namely, a mandrel part and a front cone part; the main body of the mandrel part is a mandrel 3, the mandrel 3 is a solid cylinder, a plurality of spiral blades 1 are arranged in parallel on the outer circular surface of the mandrel 3, each spiral blade 1 is distributed with a plurality of grooves 2 in the radial direction, and all the grooves 2 are directed to the front cone direction; the main body of the front cone part is a front cone section 5, and a plurality of ribs 4 are arranged longitudinally on the conical surface of the front cone section 5.

[0066] The height of the spiral blade 1 is 25 mm, the thickness of the spiral blade 1 is 5 mm, the depth of each groove 2 is 2 mm, the distance a between the adjacent ribs 4 is 8 mm, the protruding height b of each rib 4 is 5 mm, the radial protrusion of the rib 4 is spherical, and the spherical radius R is 5 mm. A certain distance is left within the range of 10 mm of the front and rear ends of the front cone section 5 without setting the rib 4.

[0067] The cross-sectional structure of the spiral blade 1 is that a plurality of grooves 2 are opened on the blade by spiral feeding, the cross section of the groove 2 is rectangular, and the spiral line adopts an equal distance and continuous processing cutting method.

[0068] The front end of the front cone section 5 is spherical, the rib 4 is made of cast iron, the surface hardness is high, and the rib 4 can resist the wear of the abrasive particles in water, and the rib 4 is welded on the conical surface of the front cone section 5 at equal intervals.

[0069] The rotator with the structure of the embodiment 5 is used in the experiment, the rotator with smooth blade surface is used for comparison, the average turbulent intensity of the end surface at the positions of 5 times, 10 times, 15 times and 20 times of the pipe diameter after the rotator under the working condition of the Reynolds number of 30000 and the hydrate volume fraction of 20% is measured respectively, and the table 2 is shown.

[0070] Table 2, the average turbulent intensity of the end surface at the positions of the two structures of the rotator

[0071]

[0072] As shown in table 2, the rotator with the structure of the embodiment can increase the contact area of the fluid and the blade by distributing the grooves on the blade surface in parallel, so that the stirring is more sufficient, the solid-liquid separation effect is better, the spiral flow is more stable, and the conveying efficiency of the sludge water compound is high.

[0073] Embodiment 6

[0074] In the process of transporting natural gas hydrate, in order to improve the heat transfer between fluids, to promote the formation and stability of natural gas hydrate and optimize the efficiency and safety of transportation. By simulating the actual scene in the horizontal straight pipe inlet section, natural gas hydrate is introduced into the pipeline, and the structure of the preceding utility model is adopted, the spiral device is divided into two parts, namely the mandrel part and the front cone part; The main body of the mandrel part is the mandrel 3, which is a solid cylinder, and the outer surface of the mandrel 3 is arranged with multiple spiral blades 1, each spiral blade 1 is distributed with multiple grooves 2 in the radial direction, and all the grooves 2 are directed to the front cone direction; The main body of the front cone part is called the front cone section 5, and the rib 4 is arranged longitudinally on the conical surface of the front cone section 5.

[0075] The height of the spiral blade 1 is 30mm, the thickness of the spiral blade 1 is 3mm, the depth of each groove 2 is 1mm. The distance a between adjacent ribs 4 is 10mm, the protruding height b of each rib 4 is 4mm, the radial protrusion of the rib 4 is spherical, and the spherical radius R is 4mm. The front cone section 5 is not provided with rib 4 within the range of 13mm front and rear end. The spiral blade 1 is welded on the outer surface of the mandrel 3, and the spiral line structure is as shown in Figure 2 The spiral blade 1 is made of stainless steel.

[0076] The front end of the front cone section 5 is spherical, the rib 4 is made of cast iron, which has high surface hardness and can resist the wear of abrasive particles in water, and the rib 4 is welded on the conical surface of the front cone section 5 at equal intervals. Seven measuring points are set in the 5 to 40 times pipe diameter interval behind the spiral device, and the Nusselt number of the end surface is measured respectively, the Nusselt number represents the ratio of convective heat transfer and conductive heat transfer in the fluid, and the experimental data is as shown in Figure 8 .

[0077] From Figure 8 It can be seen that the Nusselt number of the spiral flow formed by the improved spiral device is higher, which is more conducive to the heat transfer of hydrate, so that the energy consumption is reduced.

Claims

1. A vane-type helical flow vortexer based on biomimetic non-smooth surface, characterized in that: It is divided into two parts, namely the mandrel part and the front cone part; The main body of the mandrel part is the mandrel (3), which is a solid cylinder. A plurality of helical blades (1) are arranged in parallel on the outer surface of the mandrel (3). Each helical blade (1) has a plurality of grooves (2) distributed in parallel in the radial direction. All the grooves (2) are directed towards the front cone direction. The main body of the front cone part is called the front cone section (5). A plurality of ribs (4) are arranged longitudinally on the conical surface of the front cone section (5). The front cone section (5) does not have ribs (4) within a certain range of the front and rear ends.

2. The vane-type helical flow spin generator based on a bionic non-smooth surface according to claim 1, characterized in that: The helical blade (1) is welded on the outer surface of the mandrel (3).

3. The vane-type helical flow spin generator based on a bionic non-smooth surface according to claim 1, characterized in that: A plurality of grooves (2) are formed on the helical blade (1) by helical tool path.

4. The vane-type helical flow cyclone based on bionic non-smooth surface according to claim 1, characterized in that: The height of the helical blade (1) is 25-30mm, the thickness of the helical blade (1) is 3-5mm, and the depth of each groove (2) is 1-2mm.

5. The vane-type helical flow cyclone based on bionic non-smooth surface according to claim 1, characterized in that: The grooves (2) are distributed throughout the helical blade (1) and extend from the inlet end to the outlet end of the helical blade (1).

6. The vane-type helical flow cyclone based on bionic non-smooth surface according to claim 1, characterized in that: The front end of the front cone section (5) is spherical.

7. The vane-type helical flow cyclone based on bionic non-smooth surface according to claim 1, characterized in that: The front cone section (5) does not have ribs (4) within a range of 10-15mm of the front and rear ends.

8. The vane-type helical flow cyclone based on bionic non-smooth surface according to claim 1, characterized in that: The adjacent distance of the ribs (4) is 8-10mm, the protrusion height of each rib (4) is 4-5mm, the radial protrusion of the rib (4) is spherical, and the spherical radius is 4-5mm.

9. The vane-type helical flow cyclone based on bionic non-smooth surface according to claim 1, characterized in that: The ribs (4) are uniformly distributed along the generatrix of the front cone section (5).

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