CN218293945U - Impeller of multi-wing centrifugal fan, multi-wing centrifugal fan and range hood - Google Patents
Impeller of multi-wing centrifugal fan, multi-wing centrifugal fan and range hood Download PDFInfo
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- CN218293945U CN218293945U CN202222331303.4U CN202222331303U CN218293945U CN 218293945 U CN218293945 U CN 218293945U CN 202222331303 U CN202222331303 U CN 202222331303U CN 218293945 U CN218293945 U CN 218293945U
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Abstract
An impeller for a multi-bladed centrifugal fan comprising: a front plate; the rear disc is arranged opposite to the front disc; the two longitudinal ends of the at least three blades are respectively arranged on the front disc and the rear disc and are distributed at intervals along the circumferential direction; the method is characterized in that: at least one slot extending substantially in the transverse direction is provided in each of at least two of the blades, which improves the overall aerodynamic efficiency and reduces noise. The multi-wing centrifugal fan with the impeller of the multi-wing centrifugal fan and the range hood with the multi-wing centrifugal fan are further related.
Description
Technical Field
The utility model relates to a power device, concretely relates to be an impeller of multi-wing centrifugal fan, still relate to the multi-wing centrifugal fan that uses the impeller that has aforementioned multi-wing centrifugal fan, also relate to an impeller that uses and has aforementioned multi-wing centrifugal fan.
Background
The range hood has become one of the indispensable kitchen household electrical appliances in modern families. The range hood works by utilizing the fluid dynamics principle, sucks and exhausts oil smoke through a centrifugal fan arranged in the range hood, and filters partial grease particles by using a filter screen. The centrifugal fan comprises a volute, an impeller arranged in the volute and a motor driving the impeller to rotate. When the impeller rotates, negative pressure suction is generated in the center of the fan, oil smoke below the range hood is sucked into the fan, accelerated by the fan and then collected and guided by the volute to be discharged out of a room. The blade of the centrifugal fan is provided with a pressure surface and a suction surface, wherein the pressure surface of the blade is a working surface, namely the windward surface of the blade; the suction surface of the blade is a non-working surface, namely the leeward surface of the blade.
The power device of the existing range hood generally adopts a multi-wing centrifugal fan. The blade of the impeller of the multi-wing centrifugal fan mainly adopts a single circular arc line structure, if the impeller for the multi-wing centrifugal fan is disclosed by the Chinese utility model patent with the application number of ZL201621179780.1, the impeller consists of blades along the circumferential uniform distribution, the outer diameter of the impeller is 180-240 mm, the inner diameter is 150-180 mm, the blade is arc-shaped, the curvature radius is 18-25 mm, the blades are 36-45 pieces along the circumferential uniform distribution, the projection radian theta is 8-10 degrees, and the thickness of the blade is 0.8-1.2 mm.
The multi-wing centrifugal fan has the advantages that the axial width (namely the longitudinal direction of the blades) is large, air flow is easy to be uneven in the axial direction of the multi-wing centrifugal fan to generate pressure difference, the pressure difference easily enables vortex flow of a suction surface of the blades and air flow flowing out of the impeller to flow transversely, and the transverse flow easily forms large secondary flow vortex in the volute, so that the overall aerodynamic efficiency is reduced, and the noise is increased.
Disclosure of Invention
The utility model aims to solve the first technical problem that provides a promote whole aerodynamic efficiency and reduce the impeller of multi-wing centrifugal fan of noise to foretell technical situation.
The utility model discloses the second technical problem that will solve provides an use multi-wing centrifugal fan who has above-mentioned multi-wing centrifugal fan's impeller to foretell technical situation.
The utility model aims to solve the third technical problem that to foretell technical current situation and provide a range hood that uses above-mentioned multiple-wing centrifugal fan.
The utility model provides a technical scheme that above-mentioned first technical problem adopted is: an impeller for a multi-bladed centrifugal fan comprising:
a front plate;
the rear disc is arranged opposite to the front disc;
at least three blades, the longitudinal two ends of which are respectively arranged on the front disk and the rear disk and are distributed at intervals along the circumferential direction;
the method is characterized in that:
of the at least two vanes, each vane is provided with at least one slot extending substantially in the transverse direction.
By "substantially transverse" it is meant that the slot may extend in the transverse direction or may deviate from the transverse direction by a small angle, such as within 5 °.
In order to avoid the mutual influence between different along-hole gap flows, the blade with the slotted holes is provided with at least two slotted holes which are basically parallel to each other at intervals along the longitudinal direction of the blade.
The impeller can be a single-air-inlet impeller or a double-air-inlet impeller, in order to increase the air inlet amount, a middle disc is further arranged between the front disc and the rear disc, each blade penetrates through the middle disc, the middle disc is used for being connected with a motor of a centrifugal fan, and the front disc and the rear disc are used as air inlets.
In a further design, the cross section of the blade is arc-shaped. In the impeller, the closer to the front and rear disks, the more chaotic the flow, the stronger the suction surface vortex develops along the blade, and the larger the gap flow is needed to limit the cross flow; the closer to the middle disc is the main airflow, the airflow outflow is stable, the gap flow is too large, and the main blades are influenced to do work, so that the flow area of each slot hole is gradually increased along the direction from the middle disc to the front disc and/or the rear disc.
Further, the arc length of each slot hole is gradually increased along the direction from the middle disc to the front disc and/or the rear disc.
Further, one end parts of all the long holes are flush along the direction from the middle disc to the front disc and/or the rear disc, the included angle between the connecting line between the other end parts of the two adjacent long holes and the longitudinal direction of the corresponding blade is theta, and theta epsilon is [1 DEG, 10 DEG ].
In order to avoid influencing the working of the blades, the arc length of the cross section of each blade is L, the slot hole between the middle disc and the front disc and closest to the middle disc is made to be a slot hole A, and the arc length of the slot hole A is L 1A And is and
and/or the slot hole between the middle disc and the rear disc and closest to the middle disc is a slot hole B, and the arc length of the slot hole B is L 1B And is made of
Similarly, in the impeller, the closer to the front and rear disk positions, the more turbulent the flow, the stronger the suction surface vortex develops along the blade, and the larger the gap flow is required to restrict the cross flow; and the closer to the middle disc is the main airflow, the airflow outflow is stable, the gap flow is too large, the main blade is influenced to do work, and therefore, the distance d between every two adjacent long and narrow holes is gradually reduced along the direction from the middle disc to the front disc and/or the rear disc.
Further, the adjacent distance d satisfies:
wherein i ∈ N + 。
The main working area is near the middle disc, so that the working condition is good, more narrow and long holes are not needed to assist in restraining secondary flow, and the overlarge size of the narrow and long holes close to the middle disc can influence the working of the blades, so that the distance between the middle disc and the front disc is H 1 The slot hole between the middle disc and the front disc closest to the middle disc is a slot hole A, and the distance between the slot hole A and the middle disc is d A Satisfy the following requirements
And/or the presence of a gas in the atmosphere,the distance between the middle disc and the rear disc is H 2 The slot hole between the middle disc and the back disc closest to the middle disc is a slot hole B, and the distance between the slot hole B and the middle disc is d B Satisfy the following requirements
The slots between the middle disk and the front disk and the slots between the middle disk and the rear disk are independent from each other, and may or may not correspond to each other, as long as the slots satisfy the parameter setting conditions.
In order to reasonably set the width of the long and narrow hole, the width of the long and narrow hole is w, the thickness of the blade is t, and the requirement of satisfying
For the blade with larger t, the proportion value is smaller, and the gap flow is prevented from being too wide and dispersed to influence other flows.
The utility model provides a technical scheme that above-mentioned second technical problem adopted does: the utility model provides a multi-wing centrifugal fan which characterized in that: the impeller of the multi-blade centrifugal fan as described above is applied.
The utility model provides a technical scheme that above-mentioned third technical problem adopted does: a range hood, its characterized in that: a multi-wing centrifugal fan as described above is applied.
Compared with the prior art, the utility model has the advantages of: through in two at least blades among them, every blade is equipped with a slot hole that basically extends along transversely at least, make the pressure differential between pressure surface and the suction surface in the slot hole form stronger along hole gap flow, this gap flow not only can prevent the swirl lateral flow near the blade suction surface, can also strike the secondary flow in the spiral case after the impeller of efflux gets into the spiral case, reduce the big secondary flow from the back dish to front disk department, especially the backward flow is serious when high resistance high rotational speed operating mode, this kind of gap flow can be fine with its scattering, and then promote holistic aerodynamic efficiency, reduce the noise.
Drawings
Fig. 1 is a perspective structural view of an impeller of a multi-blade centrifugal fan according to an embodiment of the present invention;
fig. 2 is a first schematic structural diagram of a blade according to an embodiment of the present invention;
fig. 3 is a schematic structural diagram ii of a blade according to an embodiment of the present invention.
Detailed Description
The invention is described in further detail below with reference to the accompanying examples.
Example 1
As shown in fig. 1 to 3, the preferred embodiment of the present invention is shown.
As shown in fig. 1, the impeller of the multi-blade centrifugal fan in this embodiment includes a front disk 1, a rear disk 2, a plurality of blades 3, and a middle disk 4. This front tray 1 sets up with back plate 2 is relative, and well dish 4 is located between front tray 1 and the back plate 2, and this well dish 4 is used for connecting centrifugal fan's motor, and front tray 1 department and back plate 2 department all regard as the air intake. Each blade 3 passes through the middle disc 4, the two longitudinal ends of each blade are respectively arranged on the front disc 1 and the rear disc 2, and all the blades 3 are uniformly distributed at intervals along the circumferential direction. The cross section of each blade 3 is arc-shaped.
As shown in fig. 3, each blade 3 is provided with a plurality of parallel slots 30 at intervals along the longitudinal direction thereof, and each slot 30 is transversely arranged, so that a pressure difference between a pressure surface and a suction surface in each slot 30 forms a strong along-hole slot flow, which not only can prevent vortex transverse flow near the suction surface of the blade 3, but also can impact secondary flow in the volute after the outflow impeller enters the volute, thereby reducing large secondary flow from the middle disc 4 to the front disc 1 and/or the rear disc 2, or from the middle disc 4 to the current collector, particularly serious backflow under high-resistance high-rotating-speed working conditions, such slot flows can well disperse the secondary flow, further improving the overall pneumatic efficiency, and reducing noise.
As shown in FIGS. 2 and 3, each slot 30 has a width w and the blade 3 has a thickness wt, satisfies
The arc length of each slot hole 30 is gradually increased in a direction from the middle disc 4 to the front disc 1 and in a direction from the middle disc 4 to the rear disc 2. One end parts of all the long and narrow holes 30 are flush, the connecting line between the other end parts of two adjacent long and narrow holes 30 and the longitudinal direction of the corresponding blade 3 form an included angle theta, and theta is belonged to [1 DEG ], and is 10 DEG]. The arc length of the cross section of the blade 3 is L, the slot hole 30 between the middle disc 4 and the front disc L and closest to the middle disc 4 is a slot hole A, and the arc length of the slot hole A is L 1A And is and
the slot hole 30 between the middle disc 4 and the back disc 2, which is closest to the middle disc 4, is a slot hole B, and the arc length of the slot hole B is L 1B And is made of
As shown in fig. 3, the interval d between adjacent two slit holes 30 is gradually reduced in the direction from the middle disc 4 to the front disc 1 and in the direction from the middle disc 4 to the rear disc 2. The adjacent spacing d satisfies:
wherein i ∈ N + . The distance between the middle disc 4 and the front disc 1 is H 1 The distance between the slot A and the middle disc 4 is d A To satisfy
The distance between the middle disc 4 and the rear disc 2 is H 2 The distance between the slot B and the central disk 4 is d B To satisfy
The multi-blade centrifugal fan in this embodiment is an impeller of the multi-blade centrifugal fan.
The range hood in the embodiment is provided with the multi-wing centrifugal fan.
Claims (14)
1. An impeller for a multi-bladed centrifugal fan comprising:
a front plate (1);
the rear disc (2) is arranged opposite to the front disc (1);
the two longitudinal ends of the at least three blades (3) are respectively arranged on the front disc (1) and the rear disc (2) and are distributed at intervals along the circumferential direction;
the method is characterized in that:
of the at least two blades (3), each blade (3) is provided with at least one slot (30) extending substantially in the transverse direction.
2. The impeller of claim 1, wherein: the blade (3) with the long and narrow holes (30) is provided with at least two long and narrow holes (30) which are basically parallel to each other at intervals along the longitudinal direction of the blade (3).
3. The impeller of claim 2, wherein: a middle disc (4) is further arranged between the front disc (1) and the rear disc (2), and each blade (3) penetrates through the middle disc (4).
4. The impeller of claim 3, wherein: the cross section of the blade (3) is arc-shaped.
5. The impeller of claim 4, wherein: the flow area of each slot (30) is gradually increased along the direction from the middle disc (4) to the front disc (1) and/or the rear disc (2).
6. The impeller of claim 5, wherein: the arc length of each slot hole (30) is gradually increased along the direction from the middle disc (4) to the front disc (1) and/or the rear disc (2).
7. The impeller of claim 6, wherein: in the direction from the middle disc (4) to the front disc (1) and/or the rear disc (2), one end parts of all the long holes (30) are flush, the included angle between the connecting line between the other end parts of two adjacent long holes (30) and the longitudinal direction of the corresponding blade (3) is theta, and theta epsilon [1 DEG, 10 DEG ].
8. The impeller of claim 4, wherein: the arc length of the cross section of the blade (3) is L, the slot hole (30) between the middle disc (4) and the front disc (1) and closest to the middle disc (4) is a slot hole A, and the arc length of the slot hole A is L 1A And is and
and/or the slot hole (30) between the middle disc (4) and the rear disc (2) and closest to the middle disc (4) is a slot hole B, and the arc length of the slot hole B is L 1B And is and
9. the impeller according to claim 3, characterized in that: the distance d between two adjacent slotted holes (30) is gradually reduced along the direction from the middle disc (4) to the front disc (1) and/or the rear disc (2).
10. The impeller of a centrifugal fan with multiple blades as claimed in claim 9, wherein: the adjacent distance d satisfies the following conditions:
11. The impeller of claim 3, wherein: the distance between the middle disc (4) and the front disc (1) is H 1 The slot hole (30) between the middle disc (4) and the front disc (1) which is closest to the middle disc (4) is a slot hole A, and the distance between the slot hole A and the middle disc (4) is d A To satisfy
And/or the distance between the middle disc (4) and the rear disc (2) is H 2 The slot hole (30) between the middle disc (4) and the rear disc (2) which is closest to the middle disc (4) is a slot hole B, and the distance between the slot hole B and the middle disc (4) is d B To satisfy
12. The impeller according to any one of claims 1 to 10, characterized in that: the width of the slot hole (30) is w, the thickness of the blade (3) is t, and the requirement of
13. The utility model provides a multiple-wing centrifugal fan which characterized in that: impeller for a centrifugal fan with multiple blades as defined in any one of the preceding claims 1 to 12.
14. A range hood, its characterized in that: a multi-bladed centrifugal fan according to any of the preceding claims 1 to 13 is used.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202222331303.4U CN218293945U (en) | 2022-08-31 | 2022-08-31 | Impeller of multi-wing centrifugal fan, multi-wing centrifugal fan and range hood |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202222331303.4U CN218293945U (en) | 2022-08-31 | 2022-08-31 | Impeller of multi-wing centrifugal fan, multi-wing centrifugal fan and range hood |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN218293945U true CN218293945U (en) | 2023-01-13 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202222331303.4U Active CN218293945U (en) | 2022-08-31 | 2022-08-31 | Impeller of multi-wing centrifugal fan, multi-wing centrifugal fan and range hood |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN218293945U (en) |
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2022
- 2022-08-31 CN CN202222331303.4U patent/CN218293945U/en active Active
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