Combined impeller and turbine

Abstract

The utility model discloses a combined impeller and a turbine, belongs to the technical field of turbines, and adopts the main technical scheme that the combined impeller comprises a rotating part and a driving part, the multiple layers of blades are installed on the rotating part, the blades in part of layers are composite blades, the blades in part of layers are axial flow blades, and the blade layers with the axial flow blades are arranged adjacently; the length of the projection of the blade root chord D of each axial flow blade on the axis of the impeller is the projection length H, and the distance between adjacent layers with the axial flow blades is 1 / 5H-1 / 3H. The turbine solves the problems that when fluid passes through an existing turbine, large air volume and high air pressure can not be provided at the same time in a small space size, and turbulence and too large noise are generated at the same time.

Description

Technical Field

[0001] The utility model relates to the technical field of turbines, and in particular mainly to a combined impeller and turbine. Background Art

[0002] Axial-flow turbines are widely favored for their high flow and low pressure characteristics in industrial applications, especially in wind power generation and ventilation systems, while centrifugal turbines, with their expertise in providing high pressure and low flow, play a key role in specific applications such as compressors to increase fluid pressure and lift fluids from low to high. As industry's requirements for fluid mechanical performance increase, single-function turbines are no longer sufficient to meet diverse application requirements, which has prompted the industry to begin researching a new turbine design that aims to achieve both high flow and high pressure.

[0003] Combined turbine technology is an innovative fluid machinery design that combines the advantages of axial flow and centrifugal turbines to provide high flow and high pressure at the same time, meeting the diverse and complex needs of fluid power systems in industrial applications. This technology is widely used in wind power generation, gas compression, fluid transportation, ventilation systems and other fields. It not only improves energy conversion efficiency and reduces energy consumption, but also enhances system reliability and stability. It is one of the key technologies for modern industry to pursue high efficiency, environmental protection and sustainable development.

[0004] Although the combined turbine technology performs well in fluid power conversion, there are still some problems that need to be solved, especially in turbulence and noise control. The generation of turbulence will reduce the efficiency of the turbine and increase maintenance costs; in addition, the turbine may generate high noise during operation, which not only causes discomfort to the operator, but also may cause interference to the surrounding environment.

[0005] In view of this, it is necessary to improve the existing turbine. Utility Model Content

[0006] In view of the shortcomings of the prior art, the utility model provides a combined impeller and turbine, which can provide large air volume and high air pressure in a small space, and solve the problem of turbulence and excessive noise generated by the existing turbine when the fluid passes through. It is achieved through the following technical solutions:

[0007] The utility model discloses a combined impeller, comprising: a rotating part; a plurality of layers of blades mounted on the rotating part, wherein the blades of some layers are composite blades, the blades of some layers are axial flow blades, and the blade layers with axial flow blades are arranged adjacent to each other; the length of the projection of the blade root chord D of the axial flow blade on the impeller axis is the projection length H, and the spacing between adjacent layers with the axial flow blades is 1 / 5H to 1 / 3H.

[0008] Preferably, the combined impeller is provided with three layers of blades, the first layer includes multiple first blades, the second layer includes multiple second blades, and the third layer includes multiple third blades. The first blades and the second blades are axial flow blades, and the interlayer spacing between the first blades and the second blades is 1 / 5H to 1 / 3H.

[0009] Preferably, the interlayer distance between the second blade and the third blade is 1 / 3H to 1 / 2H.

[0010] Preferably, the third blade is a composite blade.

[0011] Preferably, each layer of the impeller is provided with 3 to 23 blades, and the blades of each layer are evenly arranged at equal intervals along a circular path around the axis of the impeller.

[0012] Preferably, an axial hole is provided on the rotating part, and the axial hole penetrates the rotating part along the axial direction of the rotating part.

[0013] The utility model also discloses a turbine, comprising the combined impeller, and also comprising: a volute; a front cone, the front cone being installed in the volute; a rotating member, the rotating member being installed on the front cone; the combined impeller being installed on the rotating member; a tail cone, the tail cone being installed in the volute, and the tail cone corresponding to the impeller.

[0014] Preferably, a front guide vane is provided in the volute casing, and a plurality of the front guide vanes are provided.

[0015] Preferably, a rear guide vane is provided in the volute casing, and a plurality of the rear guide vanes are provided.

[0016] The beneficial effects of this application are:

[0017] (1) The fluid will enter the turbine from the first channel in the input section, and the front guide vane will change the axial flow state of the fluid into a rotating state around the axis to ensure that the fluid enters the impeller in the correct direction and angle.

[0018] (2) When entering the acceleration section, the velocity of the fluid can be increased by passing through the first blade and the second blade to generate a larger flow rate. At the same time, a suitable spacing is set between each layer, so that the fluid flows more smoothly in the combined impeller, the generation of turbulence is reduced, the fluid delivery efficiency is improved, and the noise is reduced.

[0019] (3) When entering the pressurization section, the fluid is pressurized and pushed out by the third blade, so that the fluid has a high pressure and high flow rate, allowing the fluid to be smoothly pushed out of the diffuser section. When passing through the diffuser section, the cross-sectional area is increased, which helps the fluid to diffuse smoothly, reducing the pressure fluctuation caused by excessive flow rate, thereby reducing noise, and finally flowing out of the output section.

[0020] In summary, the utility model solves the problem of turbulence and excessive noise generated by the existing turbine when fluid passes through. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] The drawings described herein are used to provide a further understanding of the present application and constitute a part of the present application. The illustrative embodiments of the present application and their descriptions are used to explain the present application and do not constitute an improper limitation on the present application. In the drawings:

[0022] Figure 1 It is an exploded view of the utility model;

[0023] Figure 2 It is a cross-sectional view of the combined impeller of the utility model;

[0024] Figure 3 It is a structural schematic diagram of the combined impeller of the utility model;

[0025] Figure 4 It is a schematic diagram of the overall structure of the volute of the utility model;

[0026] Figure 5 It is a cross-sectional view of the overall structure of the utility model.

[0027] Description of reference numerals:

[0028] 1. Combined impeller; 11. First blade; 12. Second blade; 13. Third blade; 14. Rotating part; 141. Shaft hole; 142. Accelerating part; 143. Pressurizing part;

[0029] 2. volute; 21. first channel; 22. front guide vane; 23. rear guide vane; 24. input section; 25. acceleration section; 26. pressurization section; 27. expansion section; 28. output section; 29. ​​second channel;

[0030] 3. Front cone; 4. Rotating part; 5. Tail cone. DETAILED DESCRIPTION

[0031] The following will disclose multiple embodiments of the present invention with drawings. For the purpose of clear description, many practical details will be described together in the following description. However, it should be understood that these practical details should not be used to limit the present invention. In other words, in some embodiments of the present invention, these practical details are not necessary. In addition, in order to simplify the drawings, some conventional structures and parts will be depicted in a simple schematic manner in the drawings.

[0032] It should be noted that all directional indications such as up, down, left, right, front, back... in the embodiments of the present invention are only used to explain the relative position relationship, movement status, etc. between the components in a certain specific posture as shown in the accompanying drawings. If the specific posture changes, the directional indication will also change accordingly.

[0033] In addition, in the present utility model, the descriptions of "first", "second", etc. are only used for descriptive purposes, and do not specifically refer to the order or sequence, nor are they used to limit the present utility model. They are only used to distinguish between parts or operations described with the same technical terms, and cannot be understood as indicating or implying their relative importance or implicitly indicating the number of technical features indicated. Therefore, the features defined as "first" and "second" may explicitly or implicitly include at least one of the features. In addition, the technical solutions between the various embodiments can be combined with each other, but they must be based on the ability of ordinary technicians in this field to implement them. When the combination of technical solutions is contradictory or cannot be implemented, it should be deemed that such a combination of technical solutions does not exist and is not within the scope of protection required by the present utility model.

[0034] In order to further understand the content, features and effects of the present invention, the following embodiments are given as examples and described in detail with reference to the accompanying drawings:

[0035] Reference Figure 2 and Figure 3 , is a combined impeller 1 disclosed in the utility model, comprising: a rotating part 14; a plurality of layers of blades installed on the rotating part 14; the blades of some layers are composite blades, and the blades of some layers are axial flow blades. In this embodiment, the combined impeller 1 is a rotating body, and the combined impeller 1 has three layers of blades arranged in sequence along the axial direction, the first layer includes a plurality of first blades 11, the second layer includes a plurality of second blades 12, and the third layer includes a plurality of third blades 13.

[0036] Specifically, an axial hole 141 is opened on the rotating part 14 for connecting the rotating shaft. The axial hole 141 passes through the rotating part 14 along the axial direction of the rotating part 14. The rotating part 14 includes an accelerating part 142 and a pressurizing part 143 that are integrally connected. The accelerating part 142 is a rod-shaped structure. The first blade 11 and the second blade 12 are fixedly connected to the side wall of the accelerating part 142. The diameter of one end of the pressurizing part 143 away from the accelerating part 142 is larger than the diameter of the other end. The end of the pressurizing part 143 connected to the accelerating part 142 is equal to the diameter of the accelerating part 142. The side wall of the pressurizing part 143 is an arc-shaped structure. The third blade 13 is fixedly connected to the side wall of the pressurizing part 143. The radial length of the third blade 13 is larger than the radial length of the first blade 11 or the second blade 12.

[0037] Reference Figure 2 and Figure 3The first blade 11 and the second blade 12 are axial flow blades. The axial flow blades make the fluid direction along the axial direction and are used to increase the flow velocity of the fluid. The third blade 13 is a composite blade, that is, a mixed flow blade. Specifically, the composite blade includes an axial flow section and a centrifugal section; the third blade 13 is used to increase the flow velocity and pressure of the fluid, reduce fluid disturbance, and flow to the diffuser section.

[0038] Reference Figure 2 and Figure 3 , 3 to 23 blades are provided on each layer of the combined impeller 1, preferably 7 blades, the blades are evenly arranged along the circumferential direction of the outer wall of the rotating part 14 at equal intervals, the length of the projection of the blade root chord D of the axial flow blade on the impeller axis is the projection length H, the spacing between the first blade 11 and the second blade 12 is set to 1 / 5H to 1 / 3H, and the spacing between the second blade 12 and the third blade 13 is set to 1 / 3H to 1 / 2H. It has been verified through experiments that turbulence can be reduced, thereby reducing energy consumption.

[0039] Another embodiment of the present application further provides a turbine, comprising the combined impeller 1 in the above embodiment;

[0040] Reference Figure 1 and Figure 5 The turbine further comprises a volute 2, a front cone 3, a rotating member 4, and a tail cone 5, wherein the front cone 3 is mounted in the volute 2, the rotating member 4 is mounted on the front cone 3, the combined impeller 1 is mounted on the rotating member 4, the tail cone 5 is mounted in the volute 2, and the tail cone 5 is connected to the combined impeller 1; the front cone 3, the rotating member 4, the combined impeller 1 and the tail cone 5 are all coaxially arranged inside the volute 2. When the turbine is working, the rotating member 4 drives the combined impeller 1 to work through the bearing rotation, the fluid enters the volute 2 from the front cone 3, and the fluid is guided, accelerated, pressurized and expanded by the front cone 3, the combined impeller 1 and the tail cone 5, and finally flows out.

[0041] Reference Figure 4The volute 2 includes a first passage 21, a front guide vane 22, a rear guide vane 23, an input section 24, an acceleration section 25, a pressurizing section 26, a diffuser section 27, a second passage 29 and an output section 28; the input section 24 is a flared bowl-shaped structure, and its side wall is an arc-shaped structure convex outward. Both ends of the input section 24 are provided with circular openings, and the openings at both ends of the input section 24 have different diameters, and the end with a smaller diameter is the small end. The small end opening of the input section 24 is integrally connected with one end of the acceleration section 25. The acceleration section 25 is a cylindrical structure and both ends of the acceleration section 25 are also provided with openings. The acceleration portion 142 is arranged in the acceleration section 25, and the pressurizing section 26 is a flared bowl-shaped structure. The pressure section 26 has a horn-shaped structure, and its side wall is an arc-shaped structure protruding outward. Both ends of the pressure section 26 are provided with circular openings. The opening diameters of the two ends of the pressure section 26 are different. The end with a smaller diameter is the small end. The small end of the pressure section 26 is connected integrally with the other end of the acceleration section 25. The pressure section 143 is arranged in the pressure section 26. The diffuser section 27 is a trumpet-shaped structure. Both ends of the diffuser section 27 are provided with openings. The opening diameters of the two ends of the diffuser section 27 are different. The end with a larger diameter is the large end. The large end of the diffuser section 27 is connected integrally with the large end of the pressure section 26. The output section 28 is a cylindrical structure, both ends are provided with openings, and the small end of the diffuser section 27 is connected integrally with one end of the output section 28.

[0042] Specifically, a plurality of front guide vanes 22 are provided in the volute 2, and the front guide vanes 22 are arc-shaped blades. The front guide vanes 22 are arranged inside the input section 24 of the volute 2, and the front guide vanes 22 are fixedly connected to the input section 24. The plurality of front guide vanes 22 are evenly arranged at equal intervals around the axial direction of the input section 24.

[0043] Specifically, the front cone 3 is arranged inside the input section 24. The front cone 3 is a rotating body. The outer wall of the front cone 3 is arc-shaped and corresponds to the outer shell shape of the input section 24. In the installed state, a channel is formed between two adjacent front guide plates 22 and the front cone 3, which is the first channel 21. The first channel 21 is used for drainage, so that the fluid can enter the acceleration section 25 from the first channel 21.

[0044] Reference Figure 1 The volute 2 is provided with a plurality of rear guide vanes 23, which are arc-shaped blades. The rear guide vanes 23 are arranged inside the diffuser section 27, and the rear guide vanes 23 are fixedly connected to the diffuser section 27. The plurality of rear guide vanes 23 are evenly arranged at equal intervals around the axial direction of the diffuser section 27.

[0045] Specifically, the tail cone 5 is arranged inside the diffusion section 27. The tail cone 5 is a cone structure. The side wall of the tail cone 5 is fixedly connected to the rear guide vane 23. The large end of the tail cone 5 is connected to the large end of the pressurizing part 143. In the installed state, a channel is formed between two adjacent rear guide vanes 23 and the tail cone 5, which is the second channel 29. The fluid enters the output section 28 from the second channel 29. As the cross-sectional area of ​​the second channel 29 gradually increases, the fluid is diffused.

[0046] The following experiment 1 is used to further illustrate the size or parameter limitations of each part of the impeller structure and the technical effects that can be achieved.

[0047] Experiment 1:

[0048] The above-mentioned turbine of the utility model is numerically simulated using the Reynolds time-averaged NS equations and the turbulence model. The mass-weighted average turbulent kinetic energy and turbulent dissipation rate method is adopted in the study to analyze the distribution law of turbulent kinetic energy and turbulent dissipation rate along the radius. The turbine of the utility model is taken as experimental example 1, and then experimental examples 2 to 5 are taken, and turbulence tests are carried out on them according to the above-mentioned standards, wherein the difference between the experimental examples is only the different spacing between the layers.

[0049] The test results are shown in Table 1 and Table 2:

[0050] Table 1 Impeller turbulence test results 1

[0051]

[0052] Note: When the Reynolds number is greater than 4000, it is a turbulent state.

[0053] Table 2 Impeller turbulence test results 2

[0054]

[0055] Note: When the Reynolds number is greater than 4000, it is a turbulent state.

[0056] It can be seen from Table 1 that in Example 1, the spacing between the first blade and the second blade is 1 / 5H to 1 / 3H, the spacing between the second blade and the third blade is 1 / 3H to 1 / 2H, and the Reynolds number is 2235 to 2302; in Example 2, the spacing between the first blade and the second blade is 1 / 7H to 1 / 5H, the spacing between the second blade and the third blade is 1 / 3H to 1 / 2H, and the Reynolds number is 4034 to 4147; in Example 3, the spacing between the first blade and the second blade is 1 / 3H to 1 / 2H, the spacing between the second blade and the third blade is 1 / 3H to 1 / 2H, and the Reynolds number is 3857 to 3987.

[0057] It can be seen from Table 2 that in Example 1, the spacing between the first blade and the second blade is 1 / 5H to 1 / 3H, the spacing between the second blade and the third blade is 1 / 3H to 1 / 2H, and the Reynolds number is 2235 to 2302; in Example 4, the spacing between the first blade and the second blade is 1 / 5H to 1 / 3H, the spacing between the second blade and the third blade is 1 / 5H to 1 / 3H, and the Reynolds number is 3987 to 4099; in Example 5, the spacing between the first blade and the second blade is 1 / 5H to 1 / 3H, the spacing between the second blade and the third blade is 1 / 2H to 1H, and the Reynolds number is 4143 to 4264. This shows that the spacing between the first blade and the second blade is 1 / 5H to 1 / 3H, and the spacing between the second blade and the third blade is 1 / 3H to 1 / 2H can reduce the generation of turbulence, thereby reducing energy consumption.

[0058] The beneficial effects of the utility model are as follows: when in use, the fluid will enter the turbine from the first channel 21 in the input section 24, and the front guide vane 22 will cause the fluid to change from an axial flow form to a rotating state around the axis, so as to ensure that the fluid enters the combined impeller 1 in the correct direction and angle; when entering the acceleration section 25, the speed of the fluid can be increased by passing through the first blade 11 and the second blade 12 to generate a larger flow rate, and at the same time, a suitable spacing is provided between each layer, so that the fluid flows more smoothly in the combined impeller 1, the generation of turbulence is reduced, the fluid transportation efficiency is improved, and thus the noise is reduced; when entering the pressurization section 26, the fluid is pressurized and pushed out by the third blade 13, so that the fluid has a high pressure and high flow rate state, so that the fluid can be smoothly pushed out of the diffuser section 27, and when passing through the diffuser section 27, the cross-sectional area is increased, which helps the fluid to diffuse smoothly, reduces the pressure fluctuation caused by the excessive flow rate, thereby reducing the noise, and finally flows out of the output section 28; the utility model solves the problem that the existing turbine generates turbulence, reduces efficiency and generates noise due to the complexity of the fluid flow.

[0059] The combined impeller and turbine technology of the utility model can be used in the field of vacuuming. By combining the two different characteristics of axial flow and centrifugal flow, it can generate high-flow and high-pressure suction, so that it can quickly vacuum and improve work efficiency. The above application scenarios include but are not limited to this field.

[0060] In order to verify the effect of the turbine protected by the present application, the turbine of the present application is combined with a drive motor, a dust hood and other mechanisms into a dust suction device, and the dust suction device is subjected to flow and pressure tests, wherein the drive motor power is selected to be 3Kw, the impeller diameter is 0.125 meters, the volute diameter is 0.13 meters, and the total length is 0.45 meters. When the drive motor speed is 24000rpm, the static pressure at the inlet end is measured to be -6300Pa, and the air flow rate at the output end is 1700 cubic meters / hour, which is equivalent to the performance effect achieved by a 9-19A centrifugal fan with a power of 5.5Kw, a volute diameter of 0.8 meters, a total length of 0.6 meters, and a speed of 2900rpm.

[0061] The above is only an embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the scope of the claims of the present invention.

Claims

1. A combined impeller, characterized in that: include: Rotating portion (14); The multi-layer blades installed on the rotating part (14) are composite blades in some layers and axial flow blades in some layers. The blade layers with axial flow blades are arranged adjacent to each other. The length of the projection of the blade root chord D of the axial flow blade on the impeller axis is the projection length H. The spacing between adjacent layers with the axial flow blades is 1 / 5H to 1 / 3H.

2. The combined impeller according to claim 1, characterized in that: The combined impeller (1) is provided with three layers of blades, the first layer comprises a plurality of first blades (11), the second layer comprises a plurality of second blades (12), and the third layer comprises a plurality of third blades (13), the first blades (11) and the second blades (12) are axial flow blades, and the interlayer spacing between the first blades (11) and the second blades (12) is 1 / 5H to 1 / 3H.

3. The combined impeller according to claim 2, characterized in that: The interlayer distance between the second blade (12) and the third blade (13) is 1 / 3H to 1 / 2H.

4. The combined impeller (1) according to claim 2, characterized in that: The third blade (13) is a composite blade.

5. The combined impeller according to claim 2, characterized in that: Each layer of the impeller is provided with 3 to 23 blades, and the blades of each layer are evenly arranged at equal intervals along a circumferential path around the axis direction of the impeller.

6. The combined impeller according to claim 1, characterized in that: The rotating part (14) is provided with an axial hole (141), and the axial hole (141) penetrates the rotating part (14) along the axial direction of the rotating part (14).

7. A turbine, characterized in that: The combined impeller (1) comprises the combined impeller (1) as claimed in any one of claims 1 to 6, and further comprises: a volute (2); A front cone (3), wherein the front cone (3) is installed in the volute (2); A rotating member (4), wherein the rotating member (4) is mounted on the front cone (3); the combined impeller (1) is mounted on the rotating member (4); A tail cone (5), wherein the tail cone (5) is installed in the volute (2), and the tail cone (5) corresponds to the combined impeller (1).

8. The turbine according to claim 7, characterized in that A front guide vane (22) is arranged in the volute (2), and a plurality of the front guide vanes (22) are arranged.

9. The turbine according to claim 7, characterized in that A rear guide vane (23) is arranged in the volute (2), and a plurality of the rear guide vanes (23) are arranged.

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