CN114109924A

CN114109924A - Impeller, fan system applying same and range hood

Info

Publication number: CN114109924A
Application number: CN202010887082.1A
Authority: CN
Inventors: 胡泽元
Original assignee: Ningbo Fotile Kitchen Ware Co Ltd
Current assignee: Ningbo Fotile Kitchen Ware Co Ltd
Priority date: 2020-08-28
Filing date: 2020-08-28
Publication date: 2022-03-01
Anticipated expiration: 2040-08-28
Also published as: CN114109924B

Abstract

The invention discloses an impeller, which comprises a front ring, a rear ring, blades arranged between the front ring and the rear ring, and a middle disc arranged between the front ring and the rear ring, wherein the blades penetrate through the middle disc, the middle disc is gradually protruded towards the direction of the front ring from the position close to the edge to the middle to form a compression mold with a certain depth, one side of the middle disc, facing the rear ring, is provided with a flow guide cover, the flow guide cover comprises a conical disc section, the outer wall surface of the conical disc section is used for guiding flow, and the size of the conical disc section is gradually increased from one side, facing the rear ring, towards the direction of the middle disc. Also discloses a fan system applying the impeller and a range hood applying the fan system. Compared with the prior art, the invention has the advantages that: through setting up the kuppe, can improve the flow that gets into the air current on motor installation one side, reduce the production of air separation, swirl, avoid the air current to get into simultaneously, stagnate in the die mould intracavity of the well dish of impeller, and then reduce the loss of fan system performance, reduce fan noise.

Description

Impeller, fan system applying same and range hood

Technical Field

The invention relates to a power device, in particular to an impeller, a fan system applying the impeller and a range hood applying the fan system.

Background

The multi-wing centrifugal fan has the characteristics of high pressure, low noise and the like, so that the multi-wing centrifugal fan system is generally used as a power source in the society at present, and an impeller rotating at a high speed is utilized to complete two functions of acting and filtering in a volute. When the impeller rotates, negative pressure suction is generated in the center of the fan to suck the oil smoke below the range hood into the fan, and the oil smoke is accelerated by the fan and then is collected by the volute and guided to be discharged out of the room.

Along with the improvement of life quality of people and the forced implementation of the national standards of energy conservation and noise of household appliances, increasingly rigorous requirements are put forward on the energy conservation and low noise of the multi-wing centrifugal fan, and how to design the multi-wing centrifugal fan with lower noise is a technical problem in the industry.

In order to meet the use requirements, the aerodynamic performance of the range hood needs to be further improved, so that the multi-wing centrifugal fan with the double-air inlet structure is generally applied to the range hood. In the early days, the double-air-inlet type multi-wing centrifugal fan is only applied to a top-suction type range hood, and is also applied to a side-suction type range hood at present.

Compared with a top-suction type range hood, the installation of the double-air-inlet multi-wing centrifugal fan on the side-suction type range hood is limited by more spaces and sizes, and the obvious point is that when the double-air-inlet multi-wing centrifugal fan is installed on the side-suction type range hood, in order to avoid the interference of a motor and a range hood shell and the noise increase and abnormal sound caused by unnecessary vibration, the exposed part of the motor needs to be reduced as much as possible when the motor is installed on a fan system, so that the middle disc of the impeller of the double-air-inlet multi-wing centrifugal fan is provided with a compression mold with a certain depth so as to be beneficial to the installation of the motor. The double-air-inlet centrifugal fan disclosed in the chinese patent with the application number of 201410418400.4 comprises a volute, a double-air-inlet impeller and a motor, wherein the double-air-inlet impeller is mounted on a rotating shaft of the motor and is arranged in the volute, and the double-air-inlet impeller comprises a front end ring, a rear end ring, and a middle disc arranged between the front end ring and the rear end ring.

Disadvantageously, when the air flow enters the fan system from the motor side, the existence of the profiling with a certain depth causes large flow separation of the air flow, resulting in generation of vortex (see circled part in fig. 7), and further causing loss of fan performance and increase of fan noise.

Disclosure of Invention

The first technical problem to be solved by the present invention is to provide an impeller to reduce the generation of air flow separation and vortex and reduce noise, aiming at the defects of the prior art.

The second technical problem to be solved by the present invention is to provide a fan system using the above impeller.

The third technical problem to be solved by the invention is to provide a range hood with the fan system.

The technical scheme adopted by the invention for solving the first technical problem is as follows: an impeller, including the preceding circle, back circle, set up the blade between preceding circle and back circle, set up the well dish between preceding circle and back circle, the blade passes through the well dish, the well dish is near the position of edge and is protruding towards the direction of middle gradual preceding circle and constitute the die mould that has a certain depth, characterized in that: the air guide sleeve is arranged on one side, facing the rear ring, of the middle disc and comprises a conical disc section, wherein the outer wall surface of the conical disc section is used for guiding air, and the size of the conical disc section is gradually increased from one side, facing the rear ring, of the middle disc to the direction of the middle disc.

Preferably, for smoother flow guidance, the conical disc section is frustoconical.

In order to facilitate the connection of the air guide sleeve and the middle disc, the air flow guided by the conical disc section plays a role in buffering, the air guide sleeve further comprises a flat disc section arranged on one side of the conical disc section, which faces the middle disc, the flat disc section is annular and is fixedly connected with the middle disc, and the conical disc section is connected to the inner periphery of the flat disc section.

Preferably, the flat disc section is fixed with the part of the middle disc, which is positioned at the periphery of the profiling.

The technical scheme adopted by the invention for solving the second technical problem is as follows: a fan system using the impeller as described above, including a motor for driving the impeller, characterized in that: the motor passes through the air guide sleeve and the profiling.

Preferably, the motor comprises a motor body and an output shaft, the output shaft is fixed with the impeller, and the motor body penetrates through the air guide sleeve.

In order to reduce noise generated during operation of the fan system, the air guide sleeve further comprises a cylindrical surface section, one end of the cylindrical surface section is connected with one end of the conical disc section, the conical disc section is small in size, a certain gap is formed between the cylindrical surface section and the motor body, and a space among the air guide sleeve, the middle disc and the peripheral wall surface of the motor body forms a sound-absorbing cavity serving as a Helmholtz resonator.

In order to avoid the air flow from impacting the guide flow to generate vibration noise and avoid increasing the impeller load due to excessive thickness, the wall thickness of the guide flow cover is e, and the requirement that e is more than or equal to 0.3mm and less than or equal to 1mm is met.

In order to increase the noise reduction capability of the muffling cavity and simultaneously to enable the conical disc section to have better flow guiding characteristics, the inclination angle of the conical disc section is alpha, and the requirement that the angle is 0 degrees < alpha <90 degrees is met.

The technical scheme adopted by the invention for solving the third technical problem is as follows: a range hood, its characterized in that: a fan system as described above is applied.

Compared with the prior art, the invention has the advantages that: by arranging the air guide sleeve, the flow of air flow entering from one side of the motor installation can be improved, the generation of air flow separation and vortex is reduced, and meanwhile, the air flow is prevented from entering and stagnating in a compression cavity of a middle disc of the impeller, so that the loss of the performance of a fan system is reduced, and the noise of the fan is reduced; the combination of the middle disc, the air guide sleeve and the motor can form a Helmholtz resonator silencing cavity, and further, the sound absorption and noise reduction of the fan system are realized.

Drawings

FIG. 1 is a schematic view of a range hood according to an embodiment of the present invention;

FIG. 2 is a cross-sectional view of a range hood in accordance with an embodiment of the present invention;

FIG. 3 is a schematic view of a fan system according to an embodiment of the present disclosure;

FIG. 4 is a schematic view of an impeller according to an embodiment of the present invention;

FIG. 5 is an exploded view of an impeller according to an embodiment of the present invention;

FIG. 6 is a cross-sectional view of a hidden volute of a fan system in accordance with an embodiment of the present invention;

FIG. 7 is a schematic diagram of a simulation of the operation of a prior art wind turbine system.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar functions.

In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the present invention and to simplify the description, but are not intended to indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and that the directional terms are used for purposes of illustration and are not to be construed as limiting, for example, because the disclosed embodiments of the present invention may be oriented in different directions, "lower" is not necessarily limited to a direction opposite to or coincident with the direction of gravity. Furthermore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature.

Referring to fig. 1 and 2, a range hood includes a housing 1 and a fan system 2 disposed in the housing 1, and in this embodiment, the range hood is of a side-draft type, alternatively, any other type of range hood is also possible.

Referring to fig. 3 to 6, in the present embodiment, the fan system 2 is a centrifugal fan, and includes a volute 21, an impeller 22 disposed in the volute 21, and a motor 23 for driving the impeller 22 to rotate. The impeller 22 includes a front ring 221, a rear ring 222, and a plurality of blades 223 provided between the front ring 221 and the rear ring 222, the blades 223 being arranged at intervals in the circumferential direction of the impeller 22 (the circumferential direction of the front ring 221 or the rear ring 222). In addition, the impeller 22 further includes a center disk 224 disposed at an interval between the front ring 221 and the rear ring 222, and the blades 223 pass through the center disk 224. A wheel disc 225 is arranged in the middle of the middle disc 224, the motor 23 comprises a motor body 231 and an output shaft 232, and the output shaft 232 passes through the wheel disc 225 and is fixed with the impeller 22, so that the impeller 22 can be driven to rotate when the motor 23 is started. The middle plate 224 is formed with a profiling 2241 with a certain depth at a position close to the edge and gradually protruded towards the middle of the front ring 221 so as to facilitate the installation of the motor 23.

Impeller 22 also includes a shroud 226 disposed on a side of centerpan 224 facing aft ring 222. The air guide sleeve 226 comprises a cylindrical surface section 2261, a conical disk section 2262 and a flat disk section 2263 which are arranged in sequence and are used for guiding air on the outer wall surface, and the three sections are integrated to form the air guide sleeve 226. The cylindrical section 2261 is a hollow cylinder, one end of which is connected to one end of the conical disk section 2262, and the other end of the conical disk section 2262 is connected to the flat disk section 2263. The conical disk section 2262 is frusto-conical in shape, preferably frusto-conical in shape in this embodiment, with the size gradually increasing from the junction with the cylindrical surface section 2261 to the junction with the flat disk section 2263. The flat disk section 2263 is annular, preferably circular in shape in this embodiment, and the conical disk section 2262 is attached to the inner periphery of the flat disk section 2263. The flat disk section 2263 is secured by rivets to the portion of the center disk 224 that is located at the periphery of the profiling 2241. The motor 23 passes through the middle of the air guide sleeve 226, and the air guide sleeve 226 is arranged on the periphery of the motor body 23.

When the airflow enters the fan system 2 from the motor 23 side, the air guide sleeve 226 can play a role in guiding, so that the generation of airflow separation and vortex is reduced, and meanwhile, the airflow is prevented from entering and stagnating in the pressure type 2241 cavity of the center plate 224 of the impeller 22, thereby reducing the performance loss of the fan system 2 and reducing the noise of the fan system 2.

The space between the shroud 226, the inner disk 224, and the outer peripheral wall surface of the motor body 231 constitutes a noise canceling chamber Q1 of the helmholtz resonator. According to the helmholtz resonance principle, after sound is transmitted, sound waves close to the natural frequency of the resonator resonate with the resonator, and in the vibration process, an air column in the silencing cavity Q1 rubs against the inner wall of the silencing cavity Q1 to consume sound energy, so that sound absorption and noise reduction are performed. Meanwhile, according to the gas sound wave theory, the sound wave is the fluctuation of mechanical properties in gas, the transmission of the sound wave depends on a sound source and a propagation medium, the transmission of the sound wave is the transmission of the vibration pressure of a space gas medium, the wall surface formed by the part of the resonator muffling cavity Q1 is in a high-speed rotating state in the working process of the fan, the state of a fluid medium in the muffling cavity can be changed, the transient impedance of the sound medium of the muffling cavity can be changed, and compared with the single frequency in a static state, the inherent resonance frequency of the muffling cavity Q1 can have a wider frequency range, so that noise reduction and sound absorption can be carried out in the wider frequency range.

Further, a certain gap is provided between the cylindrical section 2261 of the air guide sleeve 226 and the motor body 231, and a hole (a neck of the hole) of the helmholtz resonator is formed, the hole is annular, the circumference of the hole is a, the width of the hole is b, the depth of the hole is t, and the volume of the corresponding sound attenuation cavity Q1 is v. The resonant frequency of the resonator is calculated by

Where f is the resonant frequency, c is the speed of sound in air, and s is the area of the hole, i.e., s-ab. The noise in the range hood is mainly concentrated between 100Hz and 1500Hz, and the part with larger noise amplitude is in the frequency range of 750Hz to 1250Hz, therefore, the resonant frequency of the resonator is better designed in the range, and b is more than or equal to 1mm and less than or equal to 4mm, and t/b is more than or equal to 0.5 and less than or equal to 5 in order to ensure that the muffling cavity Q1 of the resonator has better noise reduction characteristics.

Noting that the motor body 231 has a diameter D and an inner impeller diameter D, the fan system 2 has a limited height H (the distance between the motor 23 and the volute 21 mounting structure and the center disk 224) that can be used for adding the air guide sleeve 226. The air guide sleeve 226 has a wall thickness of e, a height of h, an outer diameter of D2 in the flat disk section 2263, an inner diameter of D1 in the flat disk section 2263, and an inclination angle of α in the conical disk section 2262. In order to avoid the air flow from impacting the air guide sleeve 226 to generate vibration noise, the wall thickness e should not be too small, and the load of the impeller 22 should be prevented from being increased due to too large thickness, preferably, e is more than or equal to 0.3mm and less than or equal to 1 mm; considering the problems of installation of the impeller 22 after the airflow guide sleeve 226 is newly added and operation interference after installation, H is not more than H-1.5 mm; the maximum value of the outer diameter D2 of the flat disc section 2263 does not influence the noise reduction characteristic of the muffling cavity Q1, and the mounting requirement on the impeller 22 is met, namely D2< D; a buffer distance is reserved before the airflow which contacts the conical disc section 2262 and is guided by the conical disc section enters the impeller flow passage, so that the reversing performance loss is reduced, and meanwhile, in consideration of the riveting installation problem, D2-D1 is selected to be not less than 20 mm. For the conical disk section 2262, the inclination angle should satisfy 0 ° < α <90 °. In order to increase the noise reduction capability of the muffling cavity Q1 of the resonator, the larger the area of the conical disk section 2262 is, the better, and in the case of determination of D1, α should be as large as possible, and at the same time, α should not be too large in order to make the conical disk section 2262 have better flow guiding characteristics; in the case where t and h are determined, α should be as small as possible, and should not be too small to provide the conical disk section 2262 with better flow guiding characteristics.

In a specific embodiment, the diameter D of the motor body 231 is 122mm, and the inner diameter D of the impeller 22 is 212.38 mm.

Claims

1. An impeller, comprising a front ring (221), a rear ring (222), a vane (223) arranged between the front ring (221) and the rear ring (222), and a middle disc (224) arranged between the front ring (221) and the rear ring (222), wherein the vane (223) passes through the middle disc (224), the middle disc (224) is gradually raised towards the direction of the front ring (221) from the position close to the edge to form a profiling (2241) with a certain depth, and the impeller is characterized in that: the air guide sleeve (226) is arranged on one side, facing the rear ring (222), of the middle disc (224), the air guide sleeve (226) comprises a conical disc section (2262) with the outer wall surface used for guiding air, and the size of the conical disc section (2262) is gradually increased from one side, facing the rear ring (222), of the middle disc (224).

2. The impeller of claim 1, wherein: the conical disk section (2262) is frustoconical.

3. The impeller of claim 1, wherein: the air guide sleeve (226) further comprises a flat disc section (2263) arranged on one side, facing the middle disc (224), of the conical disc section (2262), the flat disc section (2263) is annular and is fixedly connected with the middle disc (224), and the conical disc section (2262) is connected to the inner periphery of the flat disc section (2263).

4. The impeller of claim 3, wherein: the flat disc section (2263) is fixed with the part of the middle disc (224) positioned at the periphery of the profiling (2241).

5. A fan system applying an impeller according to any one of claims 1 to 4, comprising a motor (23) for driving the impeller, characterized in that: the motor (23) penetrates through the air guide sleeve (226) and the profiling (2241).

6. The fan system of claim 5, wherein: the motor (23) comprises a motor body (231) and an output shaft (232), the output shaft (232) is fixed with the impeller, and the motor body (231) penetrates through the air guide sleeve (226).

7. The fan system of claim 6, wherein: the air guide sleeve (226) further comprises a cylindrical surface section (2261), one end of the cylindrical surface section (2261) is connected with one end, with the smaller size, of the conical disc section (2262), a certain gap is formed between the cylindrical surface section (2261) and the motor body (231), and a space among the air guide sleeve (226), the middle disc (224) and the outer peripheral wall surface of the motor body (231) forms a sound-absorbing cavity (Q1) serving as a Helmholtz resonator.

8. The fan system of claim 7, wherein: the wall thickness of the air guide sleeve (226) is e, and e is more than or equal to 0.3mm and less than or equal to 1 mm.

9. The fan system of claim 7, wherein: the angle of inclination of the conical disk section (2262) is α and satisfies 0 ° < α <90 °.

10. A range hood, its characterized in that: use of a fan system according to any of claims 5-9.