Oil-gas mixing homogenizer

Abstract

The invention discloses an oil-gas mixing homogenizer, which belongs to the technical field of gas-liquid mixers, and comprises a liquid pipe which is divided into a ventilation area and a mixing area, the first end of the breather pipe header pipe is located on the outer side of the liquid pipe, and the second end penetrates through the pipe wall of the liquid pipe, extends into the liquid pipe and is provided with a dispersion plate; the plurality of ventilation pipe branch pipes are uniformly distributed on the dispersion plate, the first ends penetrate through the dispersion plate and are communicated with the ventilation pipe header pipe, and the second ends are located in the ventilation area and extend in the axial direction of the ventilation pipe header pipe; wherein the ventilation pipe branch pipes are identical in structure and are all circular-truncated-cone-shaped pipelines, a plurality of small holes are formed in the pipe walls of the ventilation pipe branch pipes, variable-pitch spiral blades are arranged on the outer surfaces of the ventilation pipe branch pipes, and the large ends and the small ends of at least part of the ventilation pipe branch pipes are alternately arranged. The circular truncated cone-shaped design enables the diameter of the pipeline to be gradually changed, a unique flow field characteristic is formed in cooperation with the variable-diameter spiral blade, turbulent flow and shearing force are enhanced, and gas-liquid mixing is promoted.

Description

Technical Field

[0001] This invention belongs to the technical field of gas-liquid mixers, and more specifically, relates to an oil-gas mixing homogenizer. Background Technology

[0002] Oil-gas mixing homogenizers are widely used in chemical, wastewater treatment, food processing, and bioreactor fields. Their core function is to promote mass transfer, reaction, or dissolution through efficient gas-liquid contact. However, traditional ventilation pipes are standard cylindrical pipes. The flow field distribution inside the cylindrical pipe is relatively uniform, making it difficult to form sufficient turbulence and shear force, resulting in insufficient gas-liquid contact and low mixing efficiency. Summary of the Invention

[0003] To solve the above problems, the present invention adopts the following technical solution:

[0004] An oil-gas mixing homogenizer, comprising:

[0005] The liquid pipe is divided into a venting zone and a mixing zone;

[0006] A venting manifold, the first end of which is located outside the liquid pipe, and the second end which penetrates the wall of the liquid pipe and extends into the interior of the liquid pipe, and is provided with a dispersion plate;

[0007] Multiple ventilation pipe branches are evenly distributed on the dispersion plate, and the first end of each branch penetrates the dispersion plate and is connected to the main ventilation pipe, and the second end is located in the ventilation area and extends along the axial direction of the main ventilation pipe.

[0008] Among them, multiple ventilation pipe branches have the same structure, all of which are frustum-shaped pipes. Each ventilation pipe branch has multiple small holes on its pipe wall and variable pitch helical blades on its outer surface. At least some of the ventilation pipe branches have alternating large and small ends.

[0009] Furthermore, the plurality of said ventilation tube branches include:

[0010] The first ventilator branch pipe has a first end that passes through the center of the dispersion plate and is connected to the main ventilator pipe, and a second end that is located in the ventilation area and extends along the axial direction of the main ventilator pipe.

[0011] Multiple second ventilation pipe branches are evenly distributed around the outer periphery of the first ventilation pipe branch. The first end of each second ventilation pipe branch penetrates the dispersion plate and is connected to the main ventilation pipe. The second end of each branch is located in the ventilation area and extends along the axial direction of the main ventilation pipe.

[0012] The first ventilator branch pipe and the second ventilator branch pipe have the same structure, both being frustum-shaped pipes. Both the first ventilator branch pipe and the second ventilator branch pipe have multiple small holes on their pipe walls and spiral blades on their outer surfaces. The large and small ends of two adjacent second ventilator branch pipes are arranged alternately.

[0013] Furthermore, the spatial geometry of the helical blade is obtained according to the following:

[0014] Pitch P(z) refers to the distance that the helix travels 360° along the axis when it rotates one revolution at the axial position z.

[0015] Define a function P(z) for pitch variation. The pitch variation method uses a downward-opening parabola with Z = L / 2 as the axis of symmetry.

[0016] P(z)=a(zL / 2) 2 +P max

[0017] In the above formula, 'a' is the parabola coefficient; a negative value indicates the parabola opens downwards.

[0018] (zL / 2) represents the midpoint, z mid =L / 2 is the axis of symmetry, P max It is the vertex value of the parabola;

[0019] Determine the coefficient a: using the boundary conditions z = 0 and z = L; P(z) = P min ;

[0020] The final parabolic function is:

[0021] P(z) = 4(P min -P max ) / L 2 *(zL / 2) 2 +P max ;

[0022] Spiral equation: In three-dimensional space, the coordinates of a point on the blade edge are described by a parametric equation with the ventilator axis as the center, where θ is the rotation angle;

[0023] x(θ, z) = r(z) * cos(θ)

[0024] y(θ, z) = r(z)*sin(θ)

[0025] z(θ, z) = z

[0026] In the above formula, r is the outer radius of the helical blade;

[0027] z is the axis of center line;

[0028] θ is the angle between a point on the spiral and the x-axis;

[0029] The relationship between angle θ and axial position z is determined by the pitch, and the definition of pitch P(z) means:

[0030] dθ / dz = 2π / P(z);

[0031] Therefore, for a given axial position z, the cumulative rotation angle θ(z) is obtained by integration:

[0032]

[0033] In the formula, ζ is the integral dummy variable, representing the axial path from the starting point to the current position;

[0034] P(ζ) is the axial length of one revolution of the helix at position ζ;

[0035] Where θ0 is the initial angle at z = 0.

[0036] Furthermore, the multiple holes are not uniformly arranged.

[0037] Furthermore, the axial position of the small hole is obtained according to the following:

[0038] First, the position of the center of the orifice along the axis of the vent pipe is determined as follows:

[0039] z K (K = 1, 2, 3, ..., N), 0 ≤ z K ≤L;

[0040] The spacing changes linearly with z, first increasing and then decreasing. Let z... mid The position where the spacing is maximized, such as z. mid =L / 2;

[0041] ΔS(z)=ΔS min +(ΔS max -ΔS min )*(z / z mid ), 0≤z≤z mid

[0042] ΔS(z)=ΔS max -(ΔS max -ΔS min ) / (L / z mid )*(zz mid ),z mid ≤z≤L

[0043] If z mid = L / 2, then the denominator is L / 2;

[0044] According to the defined spacing sequence {ΔSK This allows us to calculate the position of each hole;

[0045] Axial position of the small hole z K :

[0046] z {k} =z {k-1} +(ΔS {k-1} +ΔS k ) / 2;

[0047] In the above formula: ΔS is the spacing between the small holes, and L is the shaft length.

[0048] Furthermore, both the liquid inlet and the mixing outlet of the liquid pipe are constricted openings.

[0049] Furthermore, there are eight second ventilation tube branches, each connected to the middle first ventilation tube branch via a bracket.

[0050] The beneficial effects of this invention are:

[0051] The frustum-shaped design of this invention creates a gradual change in pipe diameter, which, combined with variable-diameter helical blades, forms unique flow field characteristics, enhances turbulence and shear force, and promotes gas-liquid mixing.

[0052] The variable pitch design of this invention subjectes the liquid to rotation and disturbance of varying intensities during flow. Compared to a fixed pitch design, it can better adapt to different flow rates and optimize gas-liquid contact.

[0053] In this invention, multiple second vent pipes with alternating large and small ends are installed to form a complex three-dimensional flow field, increasing the chance of gas-liquid contact and improving the mixing effect.

[0054] The non-uniform distribution of the orifices in this invention can optimize the injection position and intensity of the gas, avoid bubble coalescence or uneven local mixing, and improve the uniformity and efficiency of gas-liquid contact. Attached Figure Description

[0055] Figure 1 This is a schematic diagram of the overall structure of an oil-gas mixing homogenizer according to the present invention. Figure 1 ;

[0056] Figure 2 for Figure 1 Internal structure diagram;

[0057] Figure 3 This is a schematic diagram of the vent pipe branch structure of an oil-gas mixing homogenizer according to the present invention;

[0058] Figure 4 for Figure 3 Schematic diagram of the BB cross section;

[0059] Figure 5 for Figure 3 Schematic diagram of the CC section;

[0060] Figure 6 This is a schematic diagram of the overall structure of an oil-gas mixing homogenizer according to the present invention. Figure 2 ;

[0061] Figure 7 for Figure 6 Schematic diagram of the FF section;

[0062] Figure 8 for Figure 6 Schematic diagram of the cross-section of GG in China;

[0063] Figure 9 This is a schematic diagram of the overall structure of an oil-gas mixing homogenizer according to the present invention. Figure 3 ;

[0064] Figure 10 This is a schematic diagram of the overall structure of an oil-gas mixing homogenizer according to the present invention. Figure 4 ;

[0065] Figure 11 This is a schematic diagram of the overall structure of an oil-gas mixing homogenizer according to the present invention. Figure 5 ;

[0066] Figure 12 This is a schematic diagram of the partitioning of an oil-gas mixing homogenizer according to the present invention.

[0067] In the diagram: 1. Liquid pipe; 2. Main vent pipe; 3. First vent pipe branch pipe; 4. Second vent pipe branch pipe; 5. Orifice; 6. Spiral blade; 7. Support; 8. Ventilation zone; 9. Mixing zone; 10. Liquid inlet; 11. Mixing outlet. Detailed Implementation

[0068] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0069] Example 1

[0070] refer to Figures 1 to 12 An oil-gas mixing homogenizer, comprising:

[0071] Liquid pipe 1 is divided into a ventilation zone 8 and a mixing zone 9.

[0072] Vent pipe 2, the first end of vent pipe 2 is located outside the liquid pipe 1, the second end penetrates the pipe wall of the liquid pipe 1 and extends into the interior of the liquid pipe 1, and is provided with a dispersion plate;

[0073] Multiple ventilation pipe branches are evenly distributed on the dispersion plate, and the first end of each branch penetrates the dispersion plate and is connected to the main ventilation pipe 2. The second end of each branch is located in the ventilation area and extends along the axial direction of the main ventilation pipe 2.

[0074] Among them, multiple ventilation pipe branches have the same structure, all of which are frustum-shaped pipes. The pipe walls of each ventilation pipe branch are provided with multiple small holes 5, and the outer surface of each branch is provided with variable pitch spiral blades 6.

[0075] At least some of the ventilation tube branches have alternating large and small ends.

[0076] In practice, the non-standard cylindrical design, with the pipe diameter gradually changing from one end to the other, and the size of the spiral blades also changing accordingly, can further enhance the fluid disturbance and mixing effect.

[0077] The frustum-shaped design of this invention creates a gradual change in pipe diameter, which, combined with variable-diameter helical blades, forms unique flow field characteristics, enhances turbulence and shear force, and promotes gas-liquid mixing.

[0078] In practice, the ventilation zone is three-fifths of the liquid pipe 1, serving as the core mixing zone, while the mixing zone is two-fifths of the liquid pipe 1, serving as a space for further mixing. This allows the gas and liquid to continue interacting on the basis of the turbulence formed in the core zone, reducing bubble size, improving mixing uniformity, and achieving phased optimization of the gas-liquid mixing process, thereby improving mixing efficiency and the adaptability of the device. This zoning design helps to optimize the gas-liquid contact and mixing process at different stages. The ventilation zone focuses on gas distribution, while the mixing zone focuses on turbulent mixing, resulting in a clear structure and well-defined functions.

[0079] In this embodiment, the multiple ventilation tube branches include:

[0080] The first ventilator branch pipe 3 has its first end passing through the center of the dispersion plate and connected to the main ventilator pipe 2, and its second end located in the ventilation area and extending along the axial direction of the main ventilator pipe 2.

[0081] Multiple second ventilation pipe branches 4 are evenly distributed around the outer periphery of the first ventilation pipe branch 3. The first end of the second ventilation pipe branch 4 passes through the dispersion plate and is connected to the main ventilation pipe 2. The second end is located in the ventilation area and extends along the axial direction of the main ventilation pipe 2.

[0082] Among them, the ventilation pipe branch pipe and the second ventilation pipe branch pipe 4 have the same structure, both being frustum-shaped pipes. Both the first ventilation pipe branch pipe 3 and the second ventilation pipe branch pipe 4 have multiple small holes 5 on their pipe walls and spiral blades 6 on their outer surfaces. The large and small ends of two adjacent second ventilation pipe branch pipes 4 are arranged alternately.

[0083] In this invention, multiple second vent pipes with alternating large and small ends are installed to form a complex three-dimensional flow field, increasing the chance of gas-liquid contact and improving the mixing effect.

[0084] The present invention uses multiple second ventilation pipe branches arranged in a staggered manner (circumferentially offset) to avoid the formation of a fixed "air column" or channel in the circumferential direction of the gas jet. The staggered arrangement allows the gas jet point to cover the entire circumference and forms a complex angle with the flow direction of the spiral blade, which promotes the three-dimensional dispersion of gas in the liquid vortex.

[0085] In this embodiment, the dispersion plate is rotatably and sealed to the main vent pipe 2.

[0086] Example 2

[0087] To improve practicality, this embodiment provides a variable pitch method.

[0088] In this embodiment, the spatial geometry of the helical blade 6 is obtained according to the following:

[0089] Pitch P(z) refers to the distance that the helix travels 360° along the axis when it rotates one revolution at the axial position z.

[0090] Define the pitch variation function P(z). Common pitch variation methods are segmented or parabolic variation. Here, we use the standard parabolic variation equation. Using the parabolic equation, we can precisely control the pitch variation blade.

[0091] The variable pitch method uses a downward-opening parabola with z = L / 2 as the axis of symmetry;

[0092] P(z)=a(zL / 2) 2 +P max ;

[0093] In the above formula, 'a' is the parabola coefficient; a negative value indicates the parabola opens downwards.

[0094] Where (zL / 2) represents the midpoint, z mid =L / 2 is the axis of symmetry, P max It is the vertex value of the parabola;

[0095] Determine the coefficient a: using the boundary conditions z = 0 and z = L; P(z) = P min ;

[0096] The final parabolic function is:

[0097] P(z) = 4(P min -P max ) / L 2 *(zL / 2) 2 +P max ;

[0098] Spiral equation: In three-dimensional space, the coordinates of a point on the blade edge are described by a parametric equation with the ventilator axis as the center, where θ is the rotation angle;

[0099] x(θ, z) = r(z) * cos(θ)

[0100] y(θ, z) = r(z)*sin(θ)

[0101] z(θ, z) = z

[0102] In the above formula, r is the outer radius of the helical blade;

[0103] z is the axis of center line;

[0104] θ is the angle between a point on the spiral and the x-axis;

[0105] The key point is that the relationship between angle θ and axial position z is determined by the pitch, and the definition of pitch P(z) means:

[0106] dθ / dz = 2π / P(z);

[0107] Therefore, for a given axial position z, the cumulative rotation angle θ(z) is obtained by integration:

[0108]

[0109] In the formula, ζ is the integral dummy variable, representing the axial path from the starting point to the current position;

[0110] P(ζ) is the axial length of one revolution of the helix at position ζ;

[0111] Where θ0 is the initial angle at z = 0.

[0112] This equation connects the spatial geometry of the blade with the pitch function P(z) and the radius r(z) of the frustum.

[0113] The variable pitch design of this invention subjectes the liquid to rotation and disturbance of varying intensities during flow. Compared to a fixed pitch design, it can better adapt to different flow rates and optimize gas-liquid contact.

[0114] In this embodiment, the helical blade 6 is disposed inside the branch pipe of the vent pipe, and its pitch is variable, which can guide the liquid to form a complex flow trajectory, enhance the turbulence effect, and promote gas-liquid mixing. In this embodiment, the multiple small holes 5 are not uniformly arranged.

[0115] In this embodiment, the arrangement order and spacing of the orifices can optimize gas distribution, avoid local airflow concentration, and improve the uniformity of gas-liquid mixing.

[0116] Example 3

[0117] To improve practicality, this embodiment provides a method for arranging the small holes.

[0118] In this embodiment, the axial position of the small hole 5 is obtained as follows:

[0119] First, the position of the center of orifice 5 along the axis of the vent pipe is as follows:

[0120] z K (K = 1, 2, 3, ..., N), 0 ≤ z K ≤L;

[0121] The spacing changes linearly with z, first increasing and then decreasing; let z mid The position where the spacing is maximized, such as z. mid =L / 2;

[0122] ΔS(z)=ΔS min +(ΔS max -ΔS min )*(z / z mid ), 0≤z≤z mid

[0123] ΔS(z)=ΔS max -(ΔS max -ΔS min ) / (L / z mid )*(zz mid ),z mid ≤z≤L

[0124] If z mid = L / 2, then the denominator is L / 2;

[0125] According to the defined spacing sequence {ΔS K This allows us to calculate the position of each hole;

[0126] Axial position z of small hole 5 K :

[0127] z {k} =z {k-1} +(ΔS {k-1} +ΔS k ) / 2;

[0128] In the above formula: ΔS is the spacing between the small holes 5, and L is the shaft length.

[0129] The non-uniform distribution of the orifices in this invention can optimize the injection position and intensity of the gas, avoid bubble coalescence or uneven local mixing, and improve the uniformity and efficiency of gas-liquid contact.

[0130] The present invention combines a frustum-shaped ventilation pipe, a variable pitch helical blade, and a non-uniform distribution of small holes, which can significantly improve mixing efficiency and applicability.

[0131] In practice, variable diameter pipes and variable pitch blades can adapt to different fluid conditions, enhance turbulence and gas-liquid contact efficiency, and may be superior to existing technologies in terms of energy consumption, mixing uniformity or applicability. They can be applied to a variety of scenarios (such as chemical industry, sewage treatment, food processing, etc.), and have strong market potential, especially in situations requiring efficient gas-liquid mixing.

[0132] In this embodiment, both the liquid inlet 10 and the mixing outlet 11 of the liquid pipe 1 are constricted outlets.

[0133] In this embodiment, there are eight second ventilation tube branches 4, which are connected to the middle first ventilation tube branch 3 via brackets 7.

[0134] In this embodiment, nine venting pipes are arranged inside the liquid pipe, which increases the gas-liquid contact area and helps to improve mixing efficiency.

[0135] The present invention has the following synergistic effects and benefits:

[0136] (1) Achieving dynamic shear-enhanced bubble breakage: Gas is ejected from the variable-pitch misaligned orifice and immediately encounters a liquid shear flow generated by the variable-pitch blades, where the direction and intensity are changing. This dynamic shear environment is extremely conducive to efficiently breaking the injected gas jet or initial bubble into smaller microbubbles. The smaller bubbles have a larger specific surface area, accelerating mass transfer (dissolution or reaction).

[0137] (2) Three-dimensional turbulent enhanced mixing: The swirling flow (circumferential motion) generated by the blades, the jet introduced by the orifice injection (radial / axial disturbance), and the axial secondary flow caused by the staggered arrangement of the large and small ends superimpose and interfere with each other. This coupling of multidimensional disturbances can generate three-dimensional turbulence with high intensity and rich scale (large eddies break into small eddies). Turbulent vortices are the main carriers of mixing (momentum and mass transfer).

[0138] (3) Continuous disturbance inhibits phase separation: Bubbles tend to migrate (aggregate) towards the low-pressure center in the swirling flow, or float in the gravitational field. However, the continuous change in rotational speed caused by the variable pitch, the local disturbance caused by the non-uniform gas injection, and the abrupt change in the flow channel caused by the reverse diameter of adjacent vent pipes all continuously break the aggregation tendency and stable motion trajectory of the bubbles, forcing the bubbles to repeatedly disperse, recombine, and redisperse in the liquid, which greatly prolongs the gas-liquid contact time and path.

[0139] (4) Scale Coupling: The macroscopic swirling flow and channel changes generated by the blades (large-scale vortices) interact with the small-scale jetting and microbubble breaking (small-scale vortices). Large-scale vortices transfer energy to small-scale vortices, and small-scale vortices dissipate energy to complete fine mixing. The design of variable pitch and variable aperture helps to optimize the occurrence location and intensity of disturbances at different scales.

[0140] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention are included within the scope of protection of the present invention.

Claims

1. An oil-gas mixing homogenizer, characterized in that, include: The liquid pipe is divided into a venting zone and a mixing zone; A venting manifold, the first end of which is located outside the liquid pipe, and the second end which penetrates the wall of the liquid pipe and extends into the interior of the liquid pipe, and is provided with a dispersion plate; Multiple ventilation pipe branches are evenly distributed on the dispersion plate, and the first end of each branch penetrates the dispersion plate and is connected to the main ventilation pipe, and the second end is located in the ventilation area and extends along the axial direction of the main ventilation pipe. Among them, multiple ventilation pipe branches have the same structure, all of which are frustum-shaped pipes. Each ventilation pipe branch has multiple small holes on its pipe wall and variable pitch helical blades on its outer surface. At least some of the ventilation pipe branches have alternating large and small ends.

2. The oil-gas mixing homogenizer according to claim 1, characterized in that, The multiple ventilation tube branches include: The first ventilator branch pipe has a first end that passes through the center of the dispersion plate and is connected to the main ventilator pipe, and a second end that is located in the ventilation area and extends along the axial direction of the main ventilator pipe. Multiple second ventilation pipe branches are evenly distributed around the outer periphery of the first ventilation pipe branch. The first end of each second ventilation pipe branch penetrates the dispersion plate and is connected to the main ventilation pipe. The second end of each branch is located in the ventilation area and extends along the axial direction of the main ventilation pipe. The first ventilator branch pipe and the second ventilator branch pipe have the same structure, both being frustum-shaped pipes. Both the first ventilator branch pipe and the second ventilator branch pipe have multiple small holes on their pipe walls and spiral blades on their outer surfaces. The large and small ends of two adjacent second ventilator branch pipes are arranged alternately.

3. The oil-gas mixing homogenizer according to claim 1, characterized in that, The spatial geometry of the helical blade is obtained according to the following: Pitch refers to the distance that the helix travels 360° along the axis when it rotates one revolution at the axial position z. Define a function P(z) for pitch variation. The pitch variation method uses a downward-opening parabola with z = L / 2 as the axis of symmetry. P(z)=a(z-L / 2) 2 +P max ; In the above formula, 'a' is the parabola coefficient; a negative value indicates the parabola opens downwards. (zL / 2) represents the midpoint, z mid =L / 2 is the axis of symmetry, P max It is the vertex value of the parabola; Determine the coefficient a: using the boundary conditions z = 0 and z = L; P(z) = P min ; The final parabolic function is: P(z)=4(P min -P max ) / L 2 *(z-L / 2) 2 +P max ; Spiral equation: In three-dimensional space, the coordinates of a point on the blade edge are described by a parametric equation with the ventilator axis as the center, where θ is the rotation angle; x(θ, z) = r(z) * cos(θ) y(θ, z) = r(z)*sin(θ) z(θ, z) = z In the above formula, r is the outer radius of the helical blade; z is the axis of center line; θ is the angle between a point on the spiral and the x-axis; The relationship between angle θ and axial position z is determined by the pitch, and the definition of pitch P(z) means: dθ / dz = 2π / P(z); Therefore, for a given axial position z, the cumulative rotation angle θ(z) is obtained by integration: In the formula, ζ is the integral dummy variable, representing the axial path from the starting point to the current position; P(ζ) is the axial length of one revolution of the helix at position ζ; Where θ0 is the initial angle at z = 0.

4. The oil-gas mixing homogenizer according to claim 1, characterized in that, The multiple holes are not uniformly arranged.

5. An oil-gas mixing homogenizer according to claim 5, characterized in that, The axial position of the small hole is obtained as follows: First, the position of the center of the orifice along the axis of the vent pipe is determined as follows: z K (K=1,2,3,....,N),0≤z K ≤L; The spacing changes linearly with z, first increasing and then decreasing. Let z... mid The position where the spacing is maximized, such as z. mid =L / 2; ΔS(z)=ΔS min +(ΔS max -ΔS min )*(z / z mid ),0≤z≤z mid ΔS(z)=ΔS max -(ΔS max -ΔS min ) / (L / z mid )*(z-z mid ),z mid ≤z≤L If z mid = L / 2, then the denominator is L / 2; According to the defined spacing sequence {ΔS K This allows us to calculate the position of each hole; Axial position of the small hole z K : z {k} =z {k-1} +(ΔS {k-1} +ΔS k ) / 2; In the above formula: ΔS is the spacing between the small holes, and L is the shaft length.

6. The oil-gas mixing homogenizer according to claim 1, characterized in that, Both the liquid inlet and the mixing outlet of the liquid pipe are constricted openings.

7. An oil-gas mixing homogenizer according to claim 2, characterized in that, There are eight second ventilation tube branches, each connected to the middle first ventilation tube branch via a bracket.

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