CN221003211U - High-speed blower motor with noise reduction structure - Google Patents
High-speed blower motor with noise reduction structure Download PDFInfo
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- CN221003211U CN221003211U CN202322976562.7U CN202322976562U CN221003211U CN 221003211 U CN221003211 U CN 221003211U CN 202322976562 U CN202322976562 U CN 202322976562U CN 221003211 U CN221003211 U CN 221003211U
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- 210000000214 mouth Anatomy 0.000 claims description 3
- 230000003068 static effect Effects 0.000 abstract description 7
- 238000000926 separation method Methods 0.000 abstract description 3
- 238000009434 installation Methods 0.000 description 16
- 238000000034 method Methods 0.000 description 6
- 230000009471 action Effects 0.000 description 5
- 238000005452 bending Methods 0.000 description 5
- 239000012530 fluid Substances 0.000 description 4
- 230000000903 blocking effect Effects 0.000 description 3
- 230000003993 interaction Effects 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000013016 damping Methods 0.000 description 2
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Abstract
The utility model discloses a high-speed blower motor with a noise reduction structure.A wind channel penetrating through an upper wind channel shell and a lower wind channel shell is formed in a wind channel shell, a support bearing is arranged in a bearing shell, a rotating shaft center is arranged in a rotor of a rotating assembly, and a rotating impeller is arranged at the top end position of a rotating shaft core; the impeller blades of the rotary impeller adopt a curved and swept combined structure, the front edges of the impeller blades are of a backward curved structure, and the rear edges of the blades adopt a forward curved structure; the air duct is also internally provided with a plurality of shell guide vanes, and the axial distance between the vane tail edge line of the impeller vane and the vane tip position of the front edge line of the shell guide vanes is larger than the axial distance between the vane root positions of the impeller vane tail edge line and the front edge line of the shell guide vanes. The impeller structure adopting the curved and swept combined structure can effectively inhibit tip clearance separation vortex from being broken and expanded in a blade runner and downstream of the blade, reduces the broadband noise of the tip and wake vortex shedding, and reduces the interference noise of the moving blade and the static blade. The radial distribution of the air flow in the air duct is more uniform, and dynamic and static interference noise is reduced.
Description
Technical Field
The utility model belongs to the technical field of motor noise reduction structures, and relates to a high-speed blower motor with a noise reduction structure.
Background
The motor speed of the existing high-speed blower is higher and higher, and along with the further improvement of the sound quality requirement of the market, the dynamic balance control and pneumatic noise level requirements of the impeller are also tightened, otherwise, the high-frequency sound caused by poor dynamic balance of the motor blade and the overall noise of the flow noise become more obvious along with the improvement of the rotating speed; based on this, we need to design impeller air channels synchronously so that the sound quality meets the increasingly demanding requirements of the market.
Disclosure of utility model
In order to solve the technical problems, the utility model adopts the following technical scheme:
A high speed blower motor with noise reduction structure, comprising: the mechanism comprises an air duct shell and a mechanism shell which is arranged concentrically with the air duct shell;
An air duct penetrating the upper air duct shell and the lower air duct shell is formed in the air duct shell, the top end of the mechanism shell is arranged in the air duct, and a rotating assembly and a bearing shell arranged at the upper end of the rotating assembly are arranged in the mechanism shell;
The bearing shell is internally provided with a supporting bearing, the rotor of the rotating assembly is internally provided with a rotating shaft center, the top end of the rotating shaft center penetrates through the supporting bearing and extends into the air duct, and the top end position of the rotating shaft core is provided with a rotating impeller;
the impeller blades of the rotary impeller adopt a curved and swept combined structure, the front edges of the impeller blades are of a backward curved structure, and the rear edges of the blades adopt a forward curved structure;
The chord length of the blade tip position of the impeller blade and the chord length of the spanwise position of the middle section of the impeller blade are respectively 1.042:1 and 1.016:1, a step of;
The air duct is also internally provided with a plurality of shell guide vanes, and the axial distance between the vane tail edge line of the impeller vane and the vane tip position of the front edge line of the shell guide vanes is larger than the axial distance between the vane root positions of the impeller vane tail edge line and the front edge line of the shell guide vanes.
As a further scheme of the utility model: the number of impeller blades of the rotary impeller is 17, the installation angle of the impeller blades at the blade inlet blade root is 21.1 degrees, the installation angle of the impeller blades at the blade inlet blade tip is 13.3 degrees, the installation angle of the impeller blades at the blade outlet blade root is 63.9 degrees, and the installation angle of the impeller blades at the blade outlet blade tip is 40.8 degrees.
As a further scheme of the utility model: the number of blades of the shell guide vane is 15, the installation angle at the blade root of the guide vane inlet of the shell guide vane is 47.8 degrees, the installation angle at the blade tip of the guide vane inlet is 22.3 degrees, the installation angle at the blade root of the blade outlet is 82.7 degrees, and the installation angle at the blade tip of the blade outlet is 76.4 degrees; the chord length of the casing guide vane is 3.45mm.
As a further scheme of the utility model: the arc length of the blade root of the impeller blade is 4.988mm, the arc length of the spanwise position of the middle section of the impeller blade is 5.186mm, and the arc length of the blade tip position is 5.034mm.
As a further scheme of the utility model: the air duct shell adopts a short air duct structural design.
As a further scheme of the utility model: a narrow-hole acoustic resonant cavity is arranged on the inner wall of the air duct corresponding to the middle position of the axial chord length of the impeller blade; the narrow-hole acoustic resonant cavity is arranged along the circumference of the inner wall of the air duct in a square mode, and is of a narrow oral cavity groove structure with a T-shaped cross section.
As a further scheme of the utility model: the inner wall of the air duct adopts a chamfer structural design.
As a further scheme of the utility model: the lower edge of the outer wall of the air duct shell adopts a chamfer structural design.
The utility model has the beneficial effects that: the impeller structure in the form of a curved-swept combined structure can effectively inhibit tip clearance separation vortex from being broken and expanded in a blade runner and at the downstream of the blade, so that the falling broadband noise of the tip and wake vortex is reduced, meanwhile, the intensity of turbulent wave at the tail edge of the blade is reduced, and the axial force of the turbulent wave on random pulsation of the tip area of the blade is also reduced according to the force interaction principle, namely the blade vibration noise caused by strong airflow disturbance of tip secondary flow to the blade is reduced; meanwhile, the impact speed between the blades and the lower shell guide vanes is reduced, the uniformity of radial distribution of air flow between the rotating impeller and the shell guide vanes is improved, and the interference noise of the moving and static blades is reduced. The radial distribution of the air flow in the air duct is more uniform, and dynamic and static interference noise is reduced.
By adopting the short air duct structure, the weight of the air duct shell is reduced as a whole, the natural resonance frequency of the long air duct is improved, the first-order resonance between the rotor component and the air duct shell at high rotating speed is avoided, and the sound quality is improved.
And through the narrow-hole acoustic resonant cavity arranged in the inner wall of the air duct, vibration caused by the action of sound waves is blocked, and meanwhile, a considerable part of sound energy is lost due to heat consumption due to friction and damping of the cavity wall. At the same time, the narrow bore acoustic resonator has the property of blocking pressure variations on the suction and pressure surfaces of nearby blade tips, and therefore noise is reduced as gas passes through the narrow bore acoustic resonator.
Drawings
Fig. 1 is a schematic diagram of the structure of the present utility model.
Fig. 2 is a schematic structural view of the airway housing of the present utility model.
Fig. 3 is a schematic view of the structure of the rotary impeller of the present utility model.
Fig. 4 is a schematic view of still another construction of the airway housing of the present utility model.
Detailed Description
The technical solutions of the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it should be understood that the described embodiments are only some embodiments of the present application, but not all embodiments, and the present application is not limited by the exemplary embodiments described herein. All other embodiments, which can be made by those skilled in the art based on the embodiments of the application without making any inventive effort, are intended to be within the scope of the application.
In the description of the present utility model, it should be understood that the terms "length," "width," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like indicate orientations or positional relationships based on the orientation or positional relationships shown in the drawings, merely to facilitate describing the present utility model and simplify the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the present utility model.
Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present utility model, the meaning of "a plurality" is two or more, unless explicitly defined otherwise.
In the embodiments of the present utility model, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured" and the like are to be construed broadly and include, for example, either permanently connected, removably connected, or integrally formed; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communicated with the inside of two elements or the interaction relationship of the two elements. The specific meaning of the above terms in the present utility model can be understood by those of ordinary skill in the art according to the specific circumstances.
The present utility model provides referring to fig. 1 to 4, in an embodiment of the present utility model, a high-speed blower motor with a noise reduction structure, comprising: the air duct shell 5 and the mechanism shell 2 which is arranged concentrically with the air duct shell 5;
an air duct 52 penetrating the upper air duct shell 5 and the lower air duct shell 5 is formed in the air duct shell 5, the top end of the mechanism shell 2 is arranged in the air duct 52, and the mechanism shell 2 is internally provided with a rotating assembly 1 and a bearing shell 8 arranged at the upper end of the rotating assembly 1;
The bearing housing 8 is internally provided with a support bearing 3, the rotor of the rotating assembly 1 is internally provided with a rotating shaft core 7, the top end of the rotating shaft core 7 passes through the support bearing 3 and extends into the air duct 52, and the top end position of the rotating shaft core 7 is provided with a rotating impeller 6;
The impeller blades 61 of the rotary impeller 6 adopt a bending and sweeping combined structure, the front edges of the impeller blades 61 are of a backward bending structure, and the rear edges of the blades adopt a forward bending structure; the chord length of the blade tip position of the impeller blade 61, the chord length of the middle-span position of 50% of the impeller blade 61, and the chord length ratio of the blade root position are respectively 1.042:1 and 1.016:1, a step of;
The air duct 52 is also internally provided with a plurality of shell guide vanes 9, and the axial distance between the blade tail edge line of the impeller blades 61 and the blade tip position of the front edge line of the shell guide vanes 9 is larger than the axial distance between the blade root positions, so that the radial distribution of air flow in the air duct 52 between the impeller blades 61 and the shell guide vanes 9 is more uniform, and dynamic and static interference noise is reduced.
The blade front edge structure in the backward bending mode can realize that the flow velocity of fluid at the blade tip position is increased by the centrifugal force generated by the fluid passing through the surface of the blade, but the streamline near the blade tail edge is more concentrated, so that the blade tip clearance separation vortex can be effectively restrained from being broken and expanded in the blade runner and downstream of the blade, the falling broadband noise of the blade tip and the wake vortex is reduced, meanwhile, the intensity of turbulent wave at the blade tail edge is reduced, and the axial force of the turbulent wave on random pulsation of the blade tip region of the blade is also reduced according to the interaction principle of the force, namely the blade vibration noise caused by the strong airflow disturbance of the blade tip secondary flow to the blade is reduced;
The front-bending type blade trailing edge structure can realize that centrifugal force generated when fluid passes through the surface of the blade reduces the fluid speed at the position of the tip of the tail edge blade, reduces the impact speed between the impeller blade 61 and the lower shell guide vane 9, improves the uniformity of radial distribution of air flow between the rotating impeller 6 and the shell guide vane 9, and reduces the interference noise of the moving and static blades.
Preferably, the number of impeller blades 61 of the rotary impeller 6 is 17, the installation angle of the impeller blades 61 at the blade inlet blade root is 21.1 degrees, the installation angle of the impeller blades at the blade inlet blade tip is 13.3 degrees, the installation angle of the impeller blades at the blade outlet blade root is 63.9 degrees, and the installation angle of the impeller blades at the blade outlet blade tip is 40.8 degrees;
The number of blades of the shell guide vane 9 is 15, the installation angle at the inlet blade root of the guide vane of the shell guide vane 9 is 47.8 degrees, the installation angle at the inlet blade tip of the guide vane is 22.3 degrees, the installation angle at the outlet blade root of the blade is 82.7 degrees, and the installation angle at the outlet blade tip of the blade is 76.4 degrees; the chord length of the casing vane 9 is 3.45mm.
Further, the root arc length of the impeller blade 61 is 4.988mm, the arc length of the middle section spanwise position of the impeller blade 61 is 5.186mm, and the tip arc length is 5.034mm; the impeller blade 61 structure can place the maximum work load in the middle of the blade, and the smaller work load is placed in the blade root and the blade tip area, so that the blocking strength of the blade root area and the overall secondary flow strength of the blade tip area are reduced, the flow efficiency is improved, and the broadband noise level of the blade tip is also reduced.
Further, the air duct housing 5 adopts the structure design of the short air duct 52, so that the weight of the air duct housing 5 can be reduced as a whole, compared with the natural resonance frequency of the long air duct 52, the air duct housing 5 is beneficial to avoiding first-order resonance between the rotor component and the air duct housing 5 at a high rotating speed, and the sound quality is improved.
Further, a narrow-hole acoustic resonant cavity 51 is arranged on the inner wall of the air duct 52 at a middle position corresponding to the axial chord length of the impeller blade 61; the narrow-hole acoustic resonant cavity 51 is arranged along the circumference of the inner wall of the air duct 52 in a square manner, and the narrow-hole acoustic resonant cavity 51 is of a narrow oral cavity groove structure with a T-shaped cross section; during the high-speed rotation of the impeller 6, when the tip sound waves of the impeller blades 61 originate from the tip leading edge and develop and expand downstream to the narrow-hole acoustic resonance chamber 51, the small-hole aperture and the gas in the cavity move back and forth under the action of the sound waves, and the moving gas has a certain mass inertia, which hinders the vibration caused by the sound waves, and at the same time, a considerable part of the sound energy is lost due to heat loss due to friction and damping of the chamber walls. Meanwhile, the narrow bore acoustic resonator 51 has a characteristic of blocking pressure variations of the suction side and the pressure side of the nearby blade tip, and thus noise is reduced when gas passes through the narrow bore acoustic resonator 51.
Further, the inner wall of the air duct 52 adopts a chamfer structure design, so that the effect of reducing the turbulent flow impact of the blunt body of the incoming flow on the upper end part of the shell can be realized, the airflow streamline on the outer edge of the impeller blade 61 of the rotary impeller 6 is more uniform and smooth, the turbulent flow impact noise of the front edge area of the blade tip is reduced, meanwhile, the flow velocity of the front edge area of the blade tip is reduced due to the existence of chamfer, the streamline deflects towards the rotation center of the rotary impeller 6, the radial distribution of the airflow is more uniform, and the incoming flow BPF noise level is reduced;
Further, the lower edge of the outer wall of the air duct shell 5 adopts a chamfer structural design, so that high-speed jet flow Cheng Liuxian of the outside static air of the air duct shell 5, which is merged into the outlet of the air duct 52, is smoother, and local outflow broadband noise is reduced.
It is further noted that relational terms such as first and second, and the like are used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Moreover, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising one does not exclude the presence of other like elements in a process, method, article, or apparatus that comprises an element.
The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the present application. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the application. Thus, the present application is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (8)
1. A high speed blower motor having a noise reducing structure, comprising: the mechanism comprises an air duct shell and a mechanism shell which is arranged concentrically with the air duct shell;
An air duct penetrating the upper air duct shell and the lower air duct shell is formed in the air duct shell, the top end of the mechanism shell is arranged in the air duct, and a rotating assembly and a bearing shell arranged at the upper end of the rotating assembly are arranged in the mechanism shell;
The bearing shell is internally provided with a supporting bearing, the rotor of the rotating assembly is internally provided with a rotating shaft center, the top end of the rotating shaft center penetrates through the supporting bearing and extends into the air duct, and the top end position of the rotating shaft core is provided with a rotating impeller;
the impeller blades of the rotary impeller adopt a curved and swept combined structure, the front edges of the impeller blades are of a backward curved structure, and the rear edges of the blades adopt a forward curved structure;
The chord length of the blade tip position of the impeller blade and the chord length of the spanwise position of the middle section of the impeller blade are respectively 1.042:1 and 1.016:1, a step of;
The air duct is also internally provided with a plurality of shell guide vanes, and the axial distance between the vane tail edge line of the impeller vane and the vane tip position of the front edge line of the shell guide vanes is larger than the axial distance between the vane root positions of the impeller vane tail edge line and the front edge line of the shell guide vanes.
2. The high-speed blower motor with noise reduction structure according to claim 1, wherein the number of impeller blades of the rotary impeller is 17, the blade inlet blade root mounting angle of the impeller blades is 21.1 °, the blade inlet blade tip mounting angle is 13.3 °, the blade outlet blade root mounting angle is 63.9 °, and the blade outlet blade tip mounting angle is 40.8 °.
3. The high-speed blower motor with noise reduction structure according to claim 1, wherein the number of blades of the casing guide vane is 15, the mounting angle at the inlet blade root of the casing guide vane is 47.8 °, the mounting angle at the inlet blade tip of the guide vane is 22.3 °, the mounting angle at the outlet blade root of the blade is 82.7 °, and the mounting angle at the outlet blade tip of the blade is 76.4 °; the chord length of the casing guide vane is 3.45mm.
4. The high speed blower motor with noise reduction structure of claim 1, wherein the root of the impeller blade has an arc length 4.988mm, the midsection of the impeller blade has an arc length 5.186mm, and the tip has an arc length 5.034mm.
5. The high speed blower motor with noise reduction structure according to claim 1, wherein the duct housing is of a short duct design.
6. The high-speed blower motor with noise reduction structure according to claim 1, wherein a narrow-hole acoustic resonant cavity is arranged on the inner wall of the air duct at a middle position corresponding to the axial chord length of the impeller blade; the narrow-hole acoustic resonant cavity is arranged along the circumference of the inner wall of the air duct in a square mode, and is of a narrow oral cavity groove structure with a T-shaped cross section.
7. The high-speed blower motor with noise reduction structure according to claim 1, wherein the inner wall of the air duct is designed in a chamfer structure.
8. The high-speed blower motor with noise reduction structure according to claim 1, wherein the lower edge of the outer wall of the air duct housing is designed in a chamfer structure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202322976562.7U CN221003211U (en) | 2023-11-04 | 2023-11-04 | High-speed blower motor with noise reduction structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202322976562.7U CN221003211U (en) | 2023-11-04 | 2023-11-04 | High-speed blower motor with noise reduction structure |
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| Publication Number | Publication Date |
|---|---|
| CN221003211U true CN221003211U (en) | 2024-05-24 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202322976562.7U Active CN221003211U (en) | 2023-11-04 | 2023-11-04 | High-speed blower motor with noise reduction structure |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN221003211U (en) |
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2023
- 2023-11-04 CN CN202322976562.7U patent/CN221003211U/en active Active
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