Centrifugal wind wheel and fresh air module

Abstract

The utility model provides a centrifugal wind wheel and a fresh air module. The centrifugal wind wheel comprises a tail disc and a fan, the fan blades are arranged on the tail disc; the fan blade is provided with a first section extending out of the tail disc in the radial direction, and a sawtooth structure is arranged at the end, close to the tail disc, of the first section. The centrifugal wind wheel aims at solving the technical problem that in the prior art, noise is large due to flow field instability of a centrifugal wind wheel.

Description

Technical Field

[0001] This application relates to the technical field of fresh air, and particularly to a centrifugal impeller and a fresh air module. Background Art

[0002] With the improvement of living standards, people's requirements for indoor air quality are getting higher and higher. Fresh air air conditioners can improve indoor air quality, so they are favored by consumers. However, with the popularization of fresh air air conditioners, many problems of fresh air fans have also emerged. Problems such as high fresh air noise and insufficient fresh air volume in fresh air air conditioners have always been common problems of fresh air fans in fresh air air conditioners, seriously affecting the user experience.

[0003] In the prior art, due to the single-stage single-suction mode of the fresh air module, outdoor fresh air only enters the lower volute from the side of the guide ring to do work; however, there is a technical problem in the prior art that the centrifugal impeller has high noise caused by unstable flow field. Summary of the Utility Model

[0004] The main purpose of this application is to provide a centrifugal impeller and a fresh air module, aiming to solve the technical problem that the centrifugal impeller in the prior art has high noise caused by unstable flow field.

[0005] In a first aspect, this application provides a centrifugal impeller, including:

[0006] A trailing disk; and

[0007] Blades, the blades are arranged on the trailing disk; the blades have a first section extending radially out of the trailing disk, and a serrated structure is formed at one end of the first section close to the trailing disk.

[0008] Optionally, there are multiple blades; multiple serrated structures are arranged on the first section of each blade, and the multiple serrated structures on each blade are continuously arranged along the extending direction of the first section of the blade.

[0009] Optionally, while the first section extends radially out of the trailing disk, it bends circumferentially towards the inner side of the trailing disk.

[0010] Optionally, the serrated structure includes a first inner tooth surface, a second inner tooth surface and a tooth bottom, and the first inner tooth surface and the second inner tooth surface intersect at the tooth bottom; the first inner tooth surface and the second inner tooth surface are arranged at an angle.

[0011] Optionally, the serrated structure further includes a first tooth top and a second tooth top arranged at intervals along the extending direction of the first section;

[0012] The first inner tooth surface is formed by extending from the first tooth top towards the tooth bottom into the interior of the blade;

[0013] The second inner tooth surface is formed by extending from the second tooth top towards the tooth bottom into the interior of the wind blade. Optionally, the first spacing distance between the first tooth top and the second tooth top is 1-2 mm; and / or

[0014] The second spacing distance between the first tooth top and the tooth bottom and the third spacing distance between the second tooth top and the tooth bottom are 2-3 mm.

[0015] Optionally, the included angle between the first inner tooth surface and the second inner tooth surface is 30-35°.

[0016] Optionally, the ratio of the radius of the trailing disc to the distance from the radial outer edge of the wind blade to the center of the trailing disc is 0.8:1 to 0.9:1.

[0017] Optionally, the centrifugal wind wheel further includes a front disc. The trailing disc and the front disc are arranged at an axial interval, and both axial ends of the wind blade are respectively connected to the trailing disc and the front disc;

[0018] The projection of the wind blade in the axial direction is located within the front disc.

[0019] In a second aspect, an embodiment of the present application further provides a fresh air module, including the centrifugal wind wheel as described above.

[0020] In the technical solution of the embodiment of the present application, the wind blade has a first section that radially extends out of the trailing disc, so as to increase the diffusing pressure capacity of the bottom of the wind blade, thereby reducing the difference in work efficiency between the top, middle and bottom of the wind blade; and, a serrated structure is configured at one end of the first section close to the trailing disc, further suppressing the large-scale vortices generated by the separation of the bottom-side airflow, effectively improving the airflow state, reducing flow separation, reducing the vortex intensity, reducing the interaction between the vortex and the cavity wall surface, achieving the purpose of noise reduction and also improving the boosting performance of the centrifugal wind wheel. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the prior art, the following will briefly introduce the drawings required for use in the description of the embodiments or the prior art. Obviously, the drawings in the following description are only some embodiments of the present application. For those of ordinary skill in the art, other drawings can be obtained based on the structures shown in these drawings without creative efforts.

[0022] Figure 1 It is a schematic structural diagram of the centrifugal wind wheel provided by the embodiment of the present application from a perspective;

[0023] Figure 2 is Figure 1 a partial enlarged view of part A in;

[0024] Figure 3Schematic diagram of the sawtooth structure on the blade of the centrifugal impeller provided by the embodiment of the present application;

[0025] Figure 4 Schematic diagram of the structure of the centrifugal impeller provided by the embodiment of the present application from another perspective;

[0026] Figure 5 Schematic diagram of the structure of the fresh air module provided by the embodiment of the present application.

[0027] List of reference numerals

[0028] 10 Fresh air module 122 Sawtooth structure 100 Centrifugal impeller 123 Second section 200 Volute 1221 First internal tooth surface 110 Tail plate 1222 Second internal tooth surface 120 Blade 1223 Tooth bottom 130 Front plate 1224 First tooth tip 121 First section 1225 Second tooth tip Detailed implementation manners

[0029] Next, the technical solutions in the embodiments of the present application will be clearly and completely described with reference to the accompanying drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, rather than all the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments in the present application without creative efforts shall fall within the protection scope of the present application.

[0030] It should be noted that all directional indications (such as up, down, left, right, front, back...) in the embodiments of the present application are only used to explain the relative positional relationship and movement conditions between components in a specific posture (as shown in the drawings). If the specific posture changes, the directional indications will also change accordingly.

[0031] In the present application, unless otherwise clearly defined and limited, terms such as "connection" and "fixation" should be understood in a broad sense. For example, "fixation" can be a fixed connection, a detachable connection, or integrated; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the internal communication of two components or the interaction relationship between two components, unless otherwise clearly limited. For those of ordinary skill in the art, the specific meanings of the above terms in the present application can be understood according to specific circumstances.

[0032] In addition, if the descriptions such as "first" and "second" are involved in the embodiments of the present application, the descriptions of "first", "second", etc. are only for descriptive purposes and cannot be construed as indicating or implying their relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include at least one such feature. In addition, the meaning of "and / or" appearing throughout the text includes three parallel scenarios. Taking "A and / or B" as an example, it includes Scenario A, or Scenario B, or the scenario where both A and B are satisfied simultaneously. In addition, the technical solutions between the various embodiments can be combined with each other, but it must be based on the ability of those of ordinary skill in the art to implement. When the combination of technical solutions results in contradictions or cannot be implemented, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection required by the present application.

[0033] Due to the single-stage single-suction mode of the fresh air module, the outdoor fresh air only enters the lower volute from the side of the guide ring to do work, resulting in higher work efficiency at the top and middle of the impeller, while the work efficiency at the bottom of the impeller is poor. Moreover, because the conventional impeller trailing disk blocks the impeller at the lower side, the flow field at the bottom of the fan is prone to flow field instability, flow separation, and the formation of problems such as vortices and secondary flows, resulting in air volume loss and the generation of aerodynamic separation noise. And because the flow field at the bottom of the impeller is chaotic, the volute has insufficient pressure increase and there is no large pressure gradient with the outside atmospheric pressure, so the backflow phenomenon is likely to occur. In addition, vortices shed at the trailing edge of the blade and vortices generated by boundary layer separation are formed to generate large noise.

[0034] Referring to Figure 1 and Figure 2 As shown, an embodiment of the present application provides a centrifugal impeller 100, including:

[0035] A trailing disk 110; and

[0036] An impeller 120, the impeller 120 is provided on the trailing disk 110; the impeller 120 has a first section 121 extending radially out of the trailing disk 110, and a serrated structure 122 is formed at one end of the first section 121 close to the trailing disk 110.

[0037] In the technical solution of the embodiment of the present application, the impeller 120 has a first section 121 extending radially out of the trailing disk 110 to increase the pressure-increasing ability of the bottom of the impeller 120 to do work, so as to reduce the difference in work efficiency between the top, middle and bottom of the impeller 120; and, a serrated structure 122 is formed at one end of the first section 121 close to the trailing disk 110, further suppressing the large-scale vortices generated by the separation of the bottom-side airflow, effectively improving the airflow state, reducing flow separation, reducing the vortex intensity, reducing the interaction between the vortices and the cavity wall surface, achieving the purpose of noise reduction and improving the pressure-increasing performance of the centrifugal impeller 100.

[0038] Through the noise comparison between the centrifugal impeller 100 of the embodiment of the present application and the centrifugal impeller 100 with a common structure, the noise generated by the centrifugal impeller 100 of the embodiment of the present application is lower than that of the common centrifugal impeller at the same rotational speed: the noise value in the 550-740 Hz medium and low frequency band with poor sound quality decreases by an average of 1.5 dB(A), and can be reduced by about 2-3 dB(A) at most, and the overall noise sound quality is improved.

[0039] It should be noted that the centrifugal impeller 100 has a radial direction, a circumferential direction, and an axial direction. The tail plate 110 of the centrifugal impeller 100 is a disc structure. The radial direction of the tail plate 110 is the radial direction of the centrifugal impeller 100, the circumferential direction of the tail plate 110 is the circumferential direction of the centrifugal fan, and the axial direction of the tail plate 110 is the axial direction of the centrifugal impeller 100. The tail plate 110 of the centrifugal impeller 100 is used to connect the drive shaft of the motor.

[0040] In the technical solution of the embodiment of the present application, as Figure 1 and Figure 4 shown, the centrifugal impeller 100 includes a plurality of blades 120, and the plurality of blades 120 are arranged at intervals in the circumferential direction. The structure of each blade 120 can adopt the structure of the blade 120 in the foregoing embodiment, that is: each blade 120 has a first section 121 extending radially out of the tail plate 110, and a sawtooth structure 122 is constructed at one end of the first section 121 close to the tail plate 110.

[0041] In the technical solution of the embodiment of the present application, the blade 120 further includes a second section 123, the second section 123 is connected to the tail plate 110, and the first section 121 and the second section 123 are integrally formed. The first section 121 extends radially out of the tail plate 110 from one end of the second section 123 away from the center of the tail plate 110.

[0042] As an alternative implementation manner of the above embodiment, a plurality of the sawtooth structures 122 are provided on the first section 121 of each blade 120, and the plurality of sawtooth structures 122 on each blade 120 are arranged continuously along the extending direction of the first section 121 of the blade 120 where they are located. The continuous arrangement of the sawtooth structures 122 along the extending direction of the first section 121 helps to suppress the separation of the airflow at the bottom of the blade 120 to form large-scale vortices, and instead forms small-scale vortices, improves the airflow state, reduces the flow separation, reduces the vortex intensity, reduces the interaction between the vortex and the cavity wall surface, and achieves the purpose of reducing noise.

[0043] As Figure 3Illustrates the arrangement of three serrated structures 122, which are connected end to end to form a continuously arranged serrated structure 122. In a specific embodiment, the number of serrated structures 122 is not specifically limited. Two adjacent serrated structures 122 are connected end to end to form a continuous pointed or wavy structure at one end of the first segment 121 near the end plate 110.

[0044] In some embodiments, the serrated structures 122 are evenly arranged, which helps to form a stable flow field. For example, as Figure 3 shown.

[0045] As an alternative implementation of the above embodiment, as Figure 4 shown, while the first segment 121 extends radially out of the end plate 110, it bends circumferentially towards the inside of the end plate 110. Such a setting helps to increase the diffuser capacity of the bottom of the blade 120 to do work, and effectively improves the bottom separation flow and vortex field, etc.

[0046] As an alternative implementation of the above embodiment, as Figure 3 shown, the serrated structure 122 includes a first inner tooth surface 1221, a second inner tooth surface 1222 and a tooth bottom 1223. The first inner tooth surface 1221 and the second inner tooth surface 1222 intersect at the tooth bottom 1223; the first inner tooth surface 1221 and the second inner tooth surface 1222 are arranged at an angle. The first inner tooth surface 1221 and the second inner tooth surface 1222 are inclined with respect to the tooth bottom 1223 and are arranged at an angle, thereby forming a tooth groove, which can suppress the large-scale vortices generated by the separation of the bottom-side airflow and improve the airflow state.

[0047] In some embodiments, the first inner tooth surface 1221 and the second inner tooth surface 1222 can be planes. In some other embodiments, the first inner tooth surface 1221 and the second inner tooth surface 1222 can also be curved surfaces, as long as the first inner tooth surface 1221 and the second inner tooth surface 1222 intersect at the tooth bottom 1223. At this time, the angle between the first inner tooth surface 1221 and the second inner tooth surface 1222 can be defined as: the angle between the tangent line of the first inner tooth surface 1221 passing through the tooth bottom 1223 and the tangent line of the second inner tooth surface 1222 passing through the tooth bottom 1223.

[0048] As an alternative implementation of the above embodiment, as Figure 3As shown, the serrated structure 122 further includes a first tooth tip 1224 and a second tooth tip 1225 that are spaced apart along the extending direction of the first segment 121; the first inner tooth surface 1221 extends from the first tooth tip 1224 towards the tooth bottom 1223 into the interior of the blade 120; the second inner tooth surface 1222 extends from the second tooth tip 1225 towards the tooth bottom 1223 into the interior of the blade 120. The first inner tooth surface 1221 extends from the first tooth tip 1224 towards the tooth bottom 1223, and the second inner tooth surface 1222 extends from the second tooth tip 1225 towards the tooth bottom 1223. Since the first tooth tip 1224 and the second tooth tip 1225 are spaced apart along the extending direction and the first tooth surface and the second inner tooth surface 1222 are compared with the tooth bottom 1223, an included angle is formed between the first tooth surface and the second tooth surface, and thus a tooth groove is formed. This tooth groove can suppress the large-scale vortices generated by the separation of the bottom-side airflow and improve the airflow state.

[0049] In the embodiment, the serrated structures 122 are continuously arranged. In two adjacent serrated structures 122, the first tooth tip 1224 of one of them is the second tooth tip 1225 of its adjacent serrated structure 122. In the embodiment, in Figure 3 the perspective shown (in the plane), the first tooth tip 1224 and the second tooth tip 1225 can be sharp points (in the three-dimensional perspective, the first tooth tip 1224 and the second tooth tip 1225 are straight lines), or can be curves (in the three-dimensional perspective, the first tooth tip 1224 and the second tooth tip 1225 are arc surfaces).

[0050] As an alternative implementation of the above embodiment, as Figure 3 shown, the first spacing distance h1 between the first tooth tip 1224 and the second tooth tip 1225 is 1 - 2 mm. And / or the second spacing distance h2 between the first tooth tip 1224 and the tooth bottom 1223 and the third spacing distance h3 between the second tooth tip 1225 and the tooth bottom 1223 are 2 - 3 mm.

[0051] For example, in Figure 3 the perspective shown (in the plane), the first tooth tip 1224 and the second tooth tip 1225 can be sharp points (in the three-dimensional perspective, the first tooth tip 1224 and the second tooth tip 1225 are straight lines). At this time, the distance between two adjacent sharp points is the first spacing distance h1; the distances from the two sharp points to the tooth bottom 1223 are the second spacing distance h2 and the third spacing distance h3 respectively.

[0052] For example, the first tooth crest 1224 and the second tooth crest 1225 can be straight lines or curves (in a three-dimensional perspective, the first tooth crest 1224 and the second tooth crest 1225 are arc surfaces). In this structure, the distance between the point on the first tooth crest 1224 that is farthest from the center of the tail plate 110 and the point on the second tooth crest 1225 that is farthest from the center of the tail plate 110 is the first interval distance h1; the distance between the point on the first tooth crest 1224 that is farthest from the center of the tail plate 110 and the tooth bottom 1223 is the second interval distance h2, and the distance between the point on the second tooth crest 1225 that is farthest from the center of the tail plate 110 and the tooth bottom 1223 is the third interval distance h3.

[0053] In an embodiment, the first interval distance h1 can be understood as the tooth width of the sawtooth structure 122, and is set to 1 mm, 1.2 mm, 1.4 mm, 1.5 mm, 1.6 mm, 1.8 mm, or 2 mm. The second interval distance h2 and the third interval distance h3 are the tooth heights of the sawtooth structure 122, which are 2 mm, 2.2 mm, 2.4 mm, 2.5 mm, 2.6 mm, 2.8 mm, or 3 mm.

[0054] The setting of the above parameters can help reduce the formation of large vortices and reduce the vortex intensity.

[0055] As an alternative implementation of the above embodiment, as Figure 3 shown, the angle between the first inner tooth surface 1221 and the second inner tooth surface 1222 is 30 - 35°. In some embodiments, the first inner tooth surface 1221 and the second inner tooth surface 1222 can be planes. In other embodiments, the first inner tooth surface 1221 and the second inner tooth surface 1222 can also be curved surfaces, as long as the first inner tooth surface 1221 and the second inner tooth surface 1222 intersect at the tooth bottom 1223. At this time, the angle between the first inner tooth surface 1221 and the second inner tooth surface 1222 can be defined as: the angle between the tangent line of the first inner tooth surface 1221 passing through the tooth bottom 1223 and the tangent line of the second inner tooth surface 1222 passing through the tooth bottom 1223. For example, the angle between the first inner tooth surface 1221 and the second inner tooth surface 1222 is 30°, 30.5°, 31°, 31.5°, 32°, 32.5°, 33°, 33.5°, 34°, 34.5°, or 35°. The setting of the above parameters can help reduce the formation of large vortices and reduce the vortex intensity.

[0056] As an alternative implementation of the above embodiment, as Figure 4 shown, the ratio of the radius of the tail plate 110 to the distance from the radial outer edge of the wind blade 120 to the center of the tail plate 110 is 0.8:1 to 0.9:1. In the embodiment, it can maximize the diffuser capacity and improve the bottom flow while ensuring the strength of the wind blade 120.

[0057] The radially outer edge of the wind blade 120 is understood as the point on the wind blade 120 that is farthest from the center of the tail plate 110. For example, the ratio of the radius of the tail plate 110 to the distance from the radially outer edge of the wind blade 120 to the center of the tail plate 110 is 0.8:1, 0.82:1, 0.84:1, 0.85:1, 0.86:1, 0.88:1 or 0.9:1.

[0058] As an alternative embodiment of the above embodiment, the centrifugal impeller 100 further includes a front disk 130. The tail plate 110 and the front disk 130 are arranged at intervals along the axial direction. The two axial ends of the wind blade 120 are respectively connected to the tail plate 110 and the front disk 130. The projection of the wind blade 120 in the axial direction is located within the front disk 130. Airflow axially enters the centrifugal impeller 100 through the front disk 130. The projection of the wind blade 120 in the axial direction is located within the front disk 130, that is, the wind blade 120 radially extends out of the tail plate 110, but it does not extend out of the front disk 130, avoiding air leakage at the blade tip and causing a decrease in air volume.

[0059] In the prior art, outdoor fresh air only enters the lower volute 200 from the side of the guide ring to do work, resulting in higher work efficiency at the top and middle of the wind blade 120, while the work efficiency at the bottom of the wind blade 120 is poor. Through the technical solution of the present application, by extending the wind blade 120 out of the bottom of the tail plate 110, the pressure-increasing ability at the bottom of the wind blade 120 is increased, and the work efficiency at the bottom of the wind blade 120 is improved, so that the work efficiencies at the top, middle and bottom of the wind blade 120 are close, and the internal flow field of the centrifugal impeller 100 is improved.

[0060] As Figure 5 shown, an embodiment of the present application also proposes a fresh air module 10, including a centrifugal impeller 100. The centrifugal impeller 100 adopts a part or all of the technical solutions of the foregoing embodiment, so the fresh air module 10 has part or all of the technical advantages of the foregoing embodiment. The fresh air module 10 further includes a volute 200, and the centrifugal impeller 100 is rotatably arranged in the volute 200. A fresh air pipe and an air outlet (or exhaust pipe) are connected to the volute 200. The fresh air pipe communicates with the outdoor environment, and the air outlet (or exhaust pipe) communicates with the outdoor environment. The fresh air module 10 further includes a motor, and the motor is installed on the volute 200 and is used to drive the centrifugal impeller 100 to rotate. When the centrifugal impeller 100 rotates driven by the motor, the outdoor fresh air inhaled from the fresh air pipe will enter the centrifugal impeller 100 from the meridian plane of the wind blade 120, do work and finally realize the increase of the total pressure of the gas, and introduce the outdoor fresh air into the indoor environment through the air outlet (or exhaust pipe).

[0061] Further, in the embodiment, the fresh air module 10 further includes a filter screen, which is arranged upstream of the centrifugal air impeller 100 in the volute 200 to filter outdoor air. In some embodiments, the fresh air module 10 further includes sound-absorbing cotton, which is arranged in the volute 200 to reduce noise.

[0062] The above are only alternative embodiments of the present application, and thus do not limit the patent scope of the present application. Any equivalent structural transformation made under the application concept of the present application by using the content of the specification and drawings of the present application, or any direct / indirect application in other related technical fields is included in the patent protection scope of the present application.

Claims

1. A centrifugal wind wheel, characterized in that: include: end of trading; as well as A fan blade, wherein the fan blade is arranged on the tail plate; The fan blade has a first section extending radially out of the tail disk, and one end of the first section close to the tail disk is configured with a sawtooth structure.

2. The centrifugal wind wheel according to claim 1, characterized in that: There are a plurality of the fan blades; a plurality of the sawtooth structures are arranged on the first section of each of the fan blades, and the plurality of sawtooth structures on each of the fan blades are continuously arranged along the extension direction of the first section of the fan blade.

3. The centrifugal wind wheel according to claim 1 or 2, characterized in that: The first section extends out of the tail disc in the radial direction and bends toward the inner side of the tail disc in the circumferential direction.

4. The centrifugal wind wheel according to claim 1, characterized in that: The sawtooth structure includes a first inner tooth surface, a second inner tooth surface and a tooth bottom, wherein the first inner tooth surface and the second inner tooth surface intersect at the tooth bottom; and the first inner tooth surface and the second inner tooth surface are arranged at an angle.

5. The centrifugal wind wheel according to claim 4, characterized in that: The sawtooth structure further includes a first tooth top and a second tooth top arranged at intervals along the extending direction of the first section; The first inner tooth surface is formed by extending from the first tooth top toward the tooth bottom toward the inside of the fan blade; The second inner tooth surface is formed by extending from the second tooth top toward the tooth bottom toward the inside of the fan blade.

6. The centrifugal wind wheel according to claim 5, characterized in that: A first spacing distance between the first tooth top and the second tooth top is 1-2 mm; and / or A second spacing distance between the first tooth top and the tooth bottom and a third spacing distance between the second tooth top and the tooth bottom are 2-3 mm.

7. The centrifugal wind wheel according to any one of claims 4 to 6, characterized in that: The included angle between the first inner tooth surface and the second inner tooth surface is 30-35°.

8. The centrifugal wind wheel according to claim 1, characterized in that: The ratio of the radius of the tail disc to the distance from the radial outer edge of the fan blade to the center of the tail disc is 0.8:1 to 0.9:

1.

9. The centrifugal wind wheel according to claim 1, characterized in that: The centrifugal wind wheel further comprises a front disk, the tail disk and the front disk are arranged axially at intervals, and the axial ends of the wind blade are respectively connected to the tail disk and the front disk; The projection of the fan blade in the axial direction is located inside the front disk.

10. A fresh air module, characterized in that: It comprises the centrifugal wind wheel according to any one of claims 1 to 9.

Images