Vibration and noise reduction blade design method based on flow channel and load cooperative regulation and control, impeller and vane pump

Abstract

The invention provides a vibration and noise reduction blade design method based on flow channel and load cooperative regulation and control, an impeller and a vane pump, and the method comprises the steps: defining blade meridian plane flow channel shape determination parameters, including a rim inlet diameter, a hub inlet diameter, a rim flow channel curvature radius, a hub flow channel curvature radius, a rim outlet inclination angle and a hub outlet inclination angle; the geometric shape of the blade is determined according to the blade loads of the hub, the rim and a plurality of molded lines located between the hub and the rim at different blade heights. One purpose of the invention is to provide a vibration and noise reduction blade design method based on cooperative regulation and control of the flow channel and the load, and according to the method, the blade load distribution at different blade height positions is corrected by utilizing the curvature of the flow channel on the meridian plane of the blade, so that unsteady and non-uniform fluid excitation in an impeller can be effectively inhibited; the method has important significance on vibration and noise reduction of hydraulic machinery. The impeller is easy to implement and suitable for various types of impellers.

Description

Technical Field

[0001] This invention relates to the field of impeller design technology in hydraulic machinery equipment, and particularly to a vibration reduction and noise reduction blade design method based on the coordinated control of flow channel and load, as well as impellers and blade pumps. Background Technology

[0002] Centrifugal pumps are indispensable hydraulic machinery in production and daily life, undertaking the functions of liquid transportation and pressurization in industries such as water conservancy and hydropower, agricultural irrigation, power metallurgy, and petrochemicals. In certain operating scenarios, hydraulic machinery needs to meet the requirements of low noise and low vibration. The load distribution of the three-dimensional blades within the impeller is the main cause of unsteady and uneven flow phenomena within the channel, subsequently inducing fluid pressure pulsations. Traditional design methods often only provide a qualitative description of the distribution of blade loads at different blade heights, lacking quantitative methods for characterization.

[0003] Accordingly, this patent aims to propose a vibration reduction and noise reduction blade design method based on the coordinated control of flow channel and load, as well as an impeller and blade pump. This method can effectively reduce the flow instability caused by the curvature of the flow channel, suppress the generation of secondary flow, and reduce the non-uniformity of the impeller outlet flow. It is of great significance for vibration reduction and noise reduction of hydraulic machinery. Summary of the Invention

[0004] The present invention aims to at least partially solve one of the technical problems in the related art.

[0005] To achieve the above objectives, this invention proposes a vibration and noise reduction blade design method based on the coordinated control of flow channel and load, comprising: The parameters that determine the shape of the blade's meridional flow channel include the rim inlet diameter. Wheel hub inlet diameter rim flow channel curvature radius Hub flow channel curvature radius Flange exit inclination angle Hub outlet tilt angle ; The blade geometry is determined by the blade load on the hub, the rim, and several profile lines located at different blade heights between the two.

[0006] One objective of this invention is to propose a vibration-reducing and noise-reducing blade design method based on the coordinated regulation of flow channels and loads. This method utilizes the curvature of the flow channel on the meridional plane of the blade to correct the load distribution on the blade at different blade height positions. This effectively suppresses unsteady and non-uniform fluid excitation within the impeller, which is of great significance for vibration reduction and noise reduction in hydraulic machinery. This invention is easy to implement and applicable to various types of impellers.

[0007] Optionally, the blade load distribution is composed of the starting point, front control point, rear control point, and end point of both the hub and the rim, and the curves connecting these points, wherein the starting load and ending load of the hub and rim profiles are both set to 0.

[0008] Furthermore, the load value at the control point in front of the wheel hub is recorded as... The load value at the front control point of the wheel flange is The loads at the front control points of the hub and flange satisfy the following relationship: .

[0009] Furthermore, the load value at the control point behind the wheel hub is recorded as... The load value at the control point behind the rim is The loads at the rear control points of the hub and flange satisfy the following relationship: .

[0010] Furthermore, let δ be the relative height of the profile at different blade heights, and 0≤δ≤1, then the load at the control point before the profile at different blade heights is... ; The load value at the aforementioned control point should be controlled between 1 and 4. Within.

[0011] Furthermore, let δ be the relative height of the profile at different blade heights, and 0≤δ≤1, then the control point loads at different blade height profiles are... ; The load value at the post-control point should be controlled between 1 and 4. Within.

[0012] Furthermore, the relative streamline length of the front control point should be controlled within 5% to 40%.

[0013] Furthermore, the relative streamline length of the rear control point should be controlled within 60% to 95%.

[0014] The present invention also proposes an impeller, including a front cover plate, a rear cover plate, and a plurality of impeller blades; Multiple impeller blades are fixedly disposed between the front cover plate and the rear cover plate, and the multiple impeller blades are evenly distributed along the circumferential direction; The impeller blades are obtained according to the vibration reduction and noise reduction blade design method based on the coordinated control of flow channel and load described above.

[0015] The present invention also proposes a vane pump, comprising the impeller as described above.

[0016] Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0017] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the following description of the embodiments taken in conjunction with the accompanying drawings, wherein: Figure 1 This is a schematic diagram of the meridional flow channel of a blade according to an embodiment of the present invention; Figure 2 This is a schematic diagram of blade load distribution and three-dimensional blade according to an embodiment of the present invention; Figure 3 This is a schematic diagram of an impeller according to an embodiment of the present invention; Figure 4 This is a comparison of the pressure pulsation performance of the new impeller after redesigning the blades using the blade design method based on flow channel curvature correction according to an embodiment of the present invention, and the original impeller.

[0018] Explanation of reference numerals in the attached figures: 1. Front cover plate; 2. Rear cover plate; 3. Impeller blades. Detailed Implementation

[0019] Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain the present invention, and should not be construed as limiting the present invention.

[0020] This invention proposes a vibration and noise reduction blade design method based on the coordinated control of flow channel and load, referring to... Figures 1 to 2 Please provide a detailed explanation.

[0021] A vibration and noise reduction blade design method based on coordinated control of flow channel and load includes: The shape of the blade's meridional flow channel is determined by the following parameters, specifically including the rim inlet diameter. Wheel hub inlet diameter rim flow channel curvature radius Hub flow channel curvature radius Flange exit inclination angle Hub outlet tilt angle ; The geometry of the blade is determined by the hub, the rim, and the blade load on several profile lines located at different blade heights between them. The blade load distribution consists of the starting point, front control point, rear control point, and end point of both the hub and the rim, as well as the curves connecting these points. The starting and ending loads of the hub and rim profiles are both set to 0.

[0022] One objective of this invention is to propose a vibration-reducing and noise-reducing blade design method based on the coordinated regulation of flow channels and loads. This method utilizes the curvature of the flow channel on the meridional plane of the blade to correct the load distribution on the blade at different blade height positions. This effectively suppresses unsteady and non-uniform fluid excitation within the impeller, which is of great significance for vibration reduction and noise reduction in hydraulic machinery. This invention is easy to implement and applicable to various types of impellers.

[0023] In some embodiments, the load value at the control point in front of the wheel hub is recorded as... The load value at the front control point of the wheel flange is The loads at the front control points of the hub and flange satisfy the following relationship: .

[0024] In some embodiments, the load value at the control point behind the wheel hub is recorded as... The load value at the control point behind the rim is The loads at the rear control points of the hub and flange satisfy the following relationship: .

[0025] In some embodiments, the relative height of the profile at different blade heights is denoted as δ, and 0≤δ≤1. Then the control point loads at different blade height profiles are: .

[0026] In some embodiments, the relative height of the profile at different blade heights is denoted as δ, and 0≤δ≤1. Then, the control point loads at different blade height profiles are... ; In some embodiments, the load values ​​at both the front control point and the rear control point should be controlled within the range of 1 to 4. Within.

[0027] In some embodiments, the relative streamline length of the front control point should be controlled within 5% to 40%; the relative streamline length of the rear control point should be controlled within 60% to 95%.

[0028] The present invention also proposes an impeller, such as Figure 3 As shown, it includes a front cover plate 1, a rear cover plate 2, and multiple impeller blades 3; Multiple impeller blades 3 are fixedly disposed between the front cover plate 1 and the rear cover plate 2, and the multiple impeller blades 3 are evenly distributed between the rear cover plate 2 and the front cover plate 1 along the circumferential direction; The impeller blade 3 is obtained according to the vibration reduction and noise reduction blade design method based on the coordinated control of flow channel and load described above.

[0029] The impeller proposed in this invention employs a blade design method based on flow channel curvature correction. This method modifies the blade load distribution at different blade heights using the flow channel curvature on the meridional plane of the blade. This effectively suppresses unsteady and non-uniform fluid excitation within the impeller, playing a crucial role in vibration reduction and noise reduction for hydraulic machinery containing impellers. This invention is easy to implement and applicable to various types of impellers.

[0030] Figure 4 A comparison of the pressure pulsation performance of the impeller (new impeller) proposed according to the present invention with that of the original impeller shows that the pressure pulsation amplitude near the volute tongue of the new impeller is significantly reduced compared to the original impeller.

[0031] The present invention also proposes a vane pump, comprising the impeller as described above.

[0032] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this invention and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0033] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0034] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a connection that allows communication between them; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0035] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "over," and "on top" of the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0036] In this invention, the terms "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of the invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0037] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention.

Claims

1. A vibration reduction and noise reduction blade design method based on coordinated control of flow channel and load, characterized in that, include: The parameters that determine the shape of the blade's meridional flow channel include the rim inlet diameter. Wheel hub inlet diameter rim flow channel curvature radius Hub flow channel curvature radius Flange exit inclination angle Hub outlet tilt angle ; The blade geometry is determined by the blade load on the hub, the rim, and several profile lines located at different blade heights between the two.

2. The vibration reduction and noise reduction blade design method based on coordinated control of flow channel and load as described in claim 1, characterized in that, The blade load distribution is composed of the starting point, front control point, rear control point, and end point of the hub and rim, as well as the curves connecting these points. The starting and ending loads of the hub and rim profiles are both set to 0.

3. The vibration reduction and noise reduction blade design method based on coordinated control of flow channel and load as described in claim 2, characterized in that, Record the load value at the control point in front of the wheel hub as follows: The load value at the front control point of the wheel flange is The loads at the front control points of the hub and flange satisfy the following relationship: .

4. The vibration reduction and noise reduction blade design method based on coordinated control of flow channel and load as described in claim 2, characterized in that, Record the load value at the control point behind the wheel hub. The load value at the control point behind the rim is The loads at the rear control points of the hub and flange satisfy the following relationship: .

5. The vibration reduction and noise reduction blade design method based on coordinated control of flow channel and load as described in claim 3, characterized in that, Let δ be the relative height of the profile at different blade heights, and 0≤δ≤1. Then the load at the control point before the profile at different blade heights is... ; The load value at the aforementioned control point should be controlled between 1 and 4. Within.

6. The vibration reduction and noise reduction blade design method based on coordinated control of flow channel and load as described in claim 4, characterized in that, Let δ be the relative height of the profile at different blade heights, and 0≤δ≤1. Then, the load at the control point behind the profile at different blade heights is... ; The load value at the post-control point should be controlled between 1 and 4. Within.

7. The vibration reduction and noise reduction blade design method based on coordinated control of flow channel and load as described in claim 5, characterized in that, The relative streamline length of the front control point should be controlled within 5% to 40%.

8. The vibration reduction and noise reduction blade design method based on coordinated control of flow channel and load as described in claim 6, characterized in that, The relative streamline length of the rear control point should be controlled within 60% to 95%.

9. An impeller, characterized in that, Includes a front cover plate, a rear cover plate, and multiple impeller blades; Multiple impeller blades are fixedly disposed between the front cover plate and the rear cover plate, and the multiple impeller blades are evenly distributed along the circumferential direction; The impeller blades are obtained by the vibration reduction and noise reduction blade design method based on the coordinated control of flow channel and load as described in any one of claims 1-8.

10. A vane pump, characterized in that, Includes the impeller as described in claim 9.

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