CN110439864B - Air inlet current collector and centrifugal fan with same - Google Patents
Air inlet current collector and centrifugal fan with same Download PDFInfo
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- CN110439864B CN110439864B CN201810419678.1A CN201810419678A CN110439864B CN 110439864 B CN110439864 B CN 110439864B CN 201810419678 A CN201810419678 A CN 201810419678A CN 110439864 B CN110439864 B CN 110439864B
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- 230000015572 biosynthetic process Effects 0.000 abstract description 4
- 238000000034 method Methods 0.000 description 12
- 230000008602 contraction Effects 0.000 description 8
- 238000005452 bending Methods 0.000 description 4
- 230000003116 impacting effect Effects 0.000 description 4
- 230000002411 adverse Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 230000000737 periodic effect Effects 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
- 239000013598 vector Substances 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention relates to an air inlet current collector, which comprises an auxiliary current collector and a main current collector, wherein the main current collector is arranged in the auxiliary current collector and is concentric with the auxiliary current collector, the main current collector encloses a main air inlet area, and an auxiliary air inlet area is enclosed between the main current collector and the auxiliary current collector; and also relates to a centrifugal fan using the air inlet collector. Compared with the prior art, the invention can improve the uniformity of the air flow in the height direction of the impeller inlet, avoid the impact of the air flow thrown out by the impeller on the annular wall of the volute caused by the excessively concentrated and dispersed air flow, improve the opportunity of the impeller tip to do work, and increase the high-pressure area at the outlet side of the impeller tip, thereby better resisting the backflow close to the front cover plate of the volute, reducing the formation of vortex, further optimizing the air flow state in the flow passage of the volute, and achieving the purposes of reducing the noise of the fan and improving the noise quality of the fan.
Description
Technical Field
The invention relates to the field of range hoods, in particular to an air inlet current collector and a centrifugal fan with the current collector.
Background
As shown in fig. 7 to 9, the conventional multi-wing centrifugal fan generally comprises an air inlet collector 4', an impeller 2', a volute 1', a motor 5', and the like, wherein in the working process, gas is guided to the impeller 2 'through the air inlet collector 4', the pressure is increased under the rotation action of the impeller 2', and the gas thrown out from the impeller 2' is collected by the volute 1 'and guided to the outlet of the volute 1', and then is conveyed into a pipeline or discharged into the atmosphere. The main function of the air inlet collector 4 'is to smoothly guide the air flow to the impeller 2', ensure the uniform air flow at the inlet of the impeller 2', and reduce the air leakage of the multi-wing centrifugal fan when the impeller 2' operates.
The structure of the air inlet current collector adopted by the existing multi-wing centrifugal fan is disclosed in China patent application No. 201611168217.9 (publication No. CN 106762837A), china patent application No. ZL201720130595.1 (issued publication No. CN 206723235U) and other patents. For a multi-wing centrifugal fan using the air inlet collector in the conventional structure, when air flows into the impeller, only a small amount of air flows pass through the tip area of the impeller, and less air flows pass through the root area of the impeller, but more air flows are concentrated mainly from the middle area of the impeller and then are thrown into the volute flow channel. This presents some problems: firstly, when the gas flows out of the impeller, the gas flow speed entering the volute flow channel is too high, and the impact of the gas flow on the volute annular wall is more severe, so that the problems of larger noise and vibration are brought; and secondly, after the air flow passes through the impeller and enters the volute flow passage, the pressure can be increased, but as less air flow passes through the tip area of the impeller, a low-pressure area is formed at the outlet side of the tip area of the impeller, and under the action of pressure difference, the back flow and large vortex are generated at the position, close to the front cover plate of the volute, in the volute flow passage, so that the air flow state in the volute flow passage is more turbulent, and the problems of increased fan noise, reduced fan noise quality and the like are presented.
Disclosure of Invention
The invention aims to provide an air inlet collector capable of improving the uniformity of air flow distribution along the height direction of an impeller after entering a fan.
The second technical problem to be solved by the invention is to provide a centrifugal fan with low noise and good noise quality aiming at the prior art.
The technical scheme adopted for solving the technical problems is as follows: an air inlet collector is characterized by comprising an auxiliary collector ring and a main collector ring, wherein the main collector ring is arranged in the auxiliary collector ring and is concentric with the auxiliary collector ring, the main collector ring encloses a main air inlet area, and an auxiliary air inlet area is enclosed between the main collector ring and the auxiliary collector ring.
Preferably, the main collector ring is connected to the auxiliary collector ring through a connection structure provided in the auxiliary air inlet region, and the connection structure is formed with air inlet windows distributed along the circumferential direction. The connection structure can realize the connection of the main current collector and the auxiliary current collector, so that the internal structure of the air inlet current collector is stable, and air flow entering the auxiliary air inlet area is fed through the air inlet window.
Further, preferably, the connection structure includes spokes uniformly distributed along the circumferential direction of the auxiliary air inlet area, two ends of each spoke are respectively fixed with the auxiliary current collector and the main current collector, and adjacent spokes and corresponding positions of the auxiliary current collector and the main current collector enclose the air inlet window. The spoke has a simple structure, can conveniently realize the connection of the main collector ring and the auxiliary collector ring, and can furthest increase the effective air inlet area of the auxiliary air inlet area. Of course, the connecting structure may adopt a mesh structure or the like in addition to the spoke structure described above.
Preferably, the auxiliary current collector comprises a fixed ring used for being fixed with a volute of the fan and an auxiliary air inlet ring positioned on the back side of the fixed ring, and the auxiliary air inlet ring is in a truncated cone shape. The auxiliary air inlet ring with the circular truncated cone shape can prevent air flow entering the auxiliary air inlet area from directly impacting the annular wall of the main collector ring when the air flow is large, so that extra noise can be prevented from being introduced.
Further, preferably, the expansion angle α of the auxiliary air inlet ring is 0 to 15 °, so that the air flow entering the auxiliary air inlet region when the air flow is large can be prevented from directly impacting on the annular wall of the main collector ring, and the air flow can be prevented from excessively impacting on the front end of the impeller, thereby further preventing additional noise from being introduced.
Preferably, the main collector ring comprises a connecting ring used for being connected with the auxiliary collector ring and a main air inlet ring positioned on the back side of the connecting ring, the connecting ring is cylindrical in shape, the main air inlet ring is bell-mouthed in shape, and the connecting ring is outwards flared.
Preferably, the circular arc radius R 1 of the quasi-line of the main air intake ring is as follows: r 1 mm or more and 100mm or less. When the centrifugal fan works, the movement of the air flow along the height direction of the impeller is converted into radial movement along the impeller, so that the more the shape of the main air inlet ring is attached to the movement track of the air flow, the smaller the resistance in the movement process of the air flow is, the larger the R 1 is, the smaller the bending degree (curvature) of the main air inlet ring is, the smaller the R 1 is, and the larger the bending degree (curvature) of the main air inlet ring is, so that the size of the R 1 is limited in the range.
The invention solves the second technical problem by adopting the technical proposal that: the centrifugal fan comprises a volute, an impeller, and an air inlet arranged on the volute, and is characterized by also comprising the air inlet collector, wherein the air inlet collector is arranged in the air inlet.
Further, preferably, the distance between the front end of the impeller and the front cover plate of the volute is S 1, and the conventional distance between the front end of the impeller and the most back end of the air inlet collector is S 2, so that the height H 1 of the auxiliary air inlet ring satisfies the following relation: s 1-S2-5≤H1≤S1-S2, so that the auxiliary air inlet ring is in a flaring shape.
Preferably, the distance between the front end of the impeller and the front cover plate of the volute is S 1, the conventional distance between the front end of the impeller and the most back side end of the air inlet collector is S 2, and the height of the impeller is H 0, so that the height H 2 of the connecting ring satisfies the following relation: s 1-S2≤H2≤S1+0.1H0. When the air flow flows to the inlet of the fan under the action of negative pressure of the fan, the more parts of the total air flow moving along the normal direction of the inlet are far away from the inlet, and the less parts of the total air flow moving along the normal direction of the inlet are arranged, so that the height of the connecting ring is designed as above in order to avoid increasing collision loss in the process of separating the air flow into the main air inlet area and the auxiliary air inlet area.
Preferably, the height H 3 of the main air intake ring satisfies the following relation: 0.15H 0<H3<0.35H0+S2. The main air inlet ring plays a role in guiding air flow to enter the impeller, and meanwhile, the main air inlet ring is used for separating to form a main air inlet area and a secondary air inlet area, so that the height of the main air inlet ring is matched with the height of the tip of the impeller.
Preferably, the diameter D 1 of the connecting ring satisfies the following relationship, assuming that the inner diameter of the impeller is D 3: 0.65D 3-10≤D1≤0.85D3 -10, the connecting ring can keep the external air flow in a moving state after being separated into the main air inlet area, the turbulence intensity of the air flow entering the fan can be properly reduced, the diameter of the connecting ring influences the amount of the air flow entering the main air inlet area and the auxiliary air inlet area respectively, and the air flow entering the auxiliary air inlet area is matched with the amount which can be processed by the tip area of the impeller.
Preferably, the inner diameter of the impeller is D 3, and the diameter D 1 of the connecting ring and the maximum diameter D 2 of the main air intake ring satisfy the following relation: d 1+10≤D2≤D3 -10. The air flows of the main air inlet area and the auxiliary air inlet area are intersected at the tail edge (namely the maximum diameter) of the main air inlet ring, and due to the difference of the channel resistance losses of the two air inlet areas, the two air flows are always in speed difference, vortex generation is easy to induce, the more far away from the inlet of the impeller is easy to generate vortex, the more near to the inlet of the impeller is difficult to generate (the phenomenon that the vortex is taken away by the impeller is not easy to form), but if the intersection is too near to the impeller, extra periodic noise can be brought during the operation of the impeller, so that the diameter of the connecting ring and the maximum diameter of the main air inlet ring are designed as above to avoid the vortex and the noise.
Preferably, the junction of the connecting ring and the main air inlet ring is opposite to the gap between the auxiliary flow collecting ring and the front end of the impeller. In the air inlet channel of the auxiliary air inlet area, the junction of the connecting ring and the main air inlet ring is a turning position for changing the air flow from expansion to contraction, the expansion and contraction process can increase the turbulence degree of the air flow in a local area, and the air flow can be additionally and negatively influenced. During the running process of the impeller, a certain amount of gas leakage exists at the gap between the auxiliary collecting ring and the front disc of the impeller, and the turbulence degree of the increase of the gas flow to the local area exceeds the turbulence caused by the contraction and expansion process, so that the junction between the connecting ring and the main air inlet ring is opposite to the gap between the auxiliary collecting ring and the front end of the impeller, and the adverse effect caused by the contraction and expansion process can be weakened.
Compared with the prior art, the invention has the advantages that: the air inlet collector comprises the auxiliary collector ring and the main collector ring, so that an air inlet area on the air inlet collector is divided into a main air inlet area and an auxiliary air inlet area, and thus, the air flow in the auxiliary air inlet area can enter the tip area of the impeller under the combined guidance of the main collector ring and the auxiliary collector ring, and the air flow in the main air inlet area enters the middle area and the root area of the impeller under the guidance of the main collector ring, so that the uniformity of the air flow in the height direction of the inlet of the impeller can be improved, the air flow thrown out by the impeller is prevented from being too concentrated and dispersed to impact the annular wall of the volute, the chance of the tip of the impeller to do work is improved, the high-pressure area at the outlet side of the tip of the impeller is increased, the backflow at the position close to the front cover plate of the volute can be better resisted, the formation of the vortex is reduced, the air flow state in the runner is optimized, and the purposes of reducing the noise of the fan and improving the noise quality of the fan are achieved.
Drawings
FIG. 1 is a schematic diagram of a centrifugal fan in an embodiment of the invention;
FIG. 2 is a schematic view of the structure of FIG. 1 in another direction;
FIG. 3 is a cross-sectional view taken along line A-A of FIG. 2;
FIG. 4 is an enlarged view of section I of FIG. 3;
fig. 5 is a schematic structural view of an air inlet collector according to an embodiment of the present invention;
FIG. 6 is a schematic view of the structure of FIG. 5 in another direction;
FIG. 7 is a schematic view of a conventional centrifugal fan in the prior art;
FIG. 8 is a cross-sectional view of a conventional centrifugal fan of the prior art;
FIG. 9 is an enlarged view of section II of FIG. 8;
Fig. 10 is a schematic view of a conventional air inlet collector in the prior art;
FIG. 11 is a graph comparing the velocity fields of a conventional centrifugal fan and a centrifugal fan in an embodiment of the invention;
FIG. 12 is a graph comparing velocity vectors of a conventional centrifugal fan with a centrifugal fan in an embodiment of the invention;
Fig. 13 is a graph comparing the pressure field of a conventional centrifugal fan with that of the centrifugal fan in the embodiment of the present invention.
Detailed Description
The invention is described in further detail below with reference to the embodiments of the drawings.
As shown in fig. 1 to 6, a centrifugal fan comprises a volute 1 and an impeller 2, wherein the impeller 2 is arranged in the volute 1, an air inlet is formed in the volute 1, and an air inlet collector 4 is arranged in the air inlet.
The above-described air intake manifold 4 includes a sub-manifold ring 41 and a main manifold ring 42, the main manifold ring 42 being disposed in the sub-manifold ring 41 and being concentric with the sub-manifold ring 41, the main manifold ring 42 enclosing a main air intake area 402, and a sub-air intake area 401 being defined between the main manifold ring 42 and the sub-manifold ring 41. The air inlet area on the air inlet collector 4 is divided into a main air inlet area 402 and a secondary air inlet area 401, so that the air flow in the secondary air inlet area 401 can enter the tip area of the impeller 2 under the combined guidance of the main collector ring 41 and the secondary collector ring 42, and the air flow in the main air inlet area 402 enters the middle area and the root area of the impeller 2 under the guidance of the main collector ring 42, thereby improving the uniformity of the air flow in the height direction of the inlet of the impeller 2, avoiding the air flow thrown out by the impeller 2 from being too concentrated and scattered to impact the annular wall of the volute 1, improving the chance of the tip of the impeller 2 to participate in acting, increasing the high-pressure area at the outlet side of the tip of the impeller 2, better resisting the backflow at the front cover plate 11 close to the volute 1, reducing the formation of vortex, optimizing the air flow state in the runner of the volute 1, and achieving the purposes of reducing the noise of the volute and improving the noise quality of the fan.
Further, the main collector ring 42 and the sub collector ring 41 are connected by a connection structure 43 provided in the sub air intake area 401, and air intake windows 432 distributed in the circumferential direction are formed in the connection structure 43. The connection of the main collector ring 42 and the sub-collector ring 41 can be achieved by the above-mentioned connection structure 43, so that the internal structure of the air inlet collector 4 is stable, and the air flow entering the sub-air inlet area 401 is air-inlet through the air inlet window 432. In this embodiment, the connection structure 43 includes spokes 431 circumferentially spaced apart from the secondary air inlet area 401, two ends of each spoke 431 are respectively fixed with the secondary collector 41 and the primary collector 42, and the adjacent spokes 431 and the corresponding positions of the secondary collector 41 and the primary collector 42 enclose the air inlet window 432. The spoke 431 has a simple structure, can conveniently realize the connection of the main collector ring 42 and the auxiliary collector ring 41, and can furthest increase the effective air inlet area of the auxiliary air inlet area 401. Of course, the connection structure 43 may employ a mesh structure or the like in addition to the spokes 431 described above.
Specifically, the secondary collector 41 includes a fixing ring 411 for fixing to the scroll casing 1, and a secondary air inlet ring 412 located on the back side of the fixing ring 411, and the secondary air inlet ring 412 has a circular truncated cone shape. In this embodiment, the fixing ring 411 has the same structure as the existing fixing ring 411, and the secondary air inlet ring 412 with a circular truncated cone shape can prevent the air flow entering the secondary air inlet area 401 from directly impacting the annular wall of the primary collector ring 42 when the air flow is large, so as to avoid introducing additional noise. The main collector ring 42 includes a connection ring 421 for connecting with the sub collector ring 41, and a main air inlet ring 422 disposed at a back side of the connection ring 421, wherein the connection ring 421 has a cylindrical shape, and the main air inlet ring 422 has a bell mouth shape and is flared outward from the connection ring 421.
As shown in fig. 7 to 10, the conventional centrifugal fan is composed of a volute 1', an impeller 2' and an air inlet collector 4', and the conventional centrifugal fan is similar to the conventional centrifugal fan except for the air inlet collector 4. The conventional inlet air collector 4 'has only one ring body including a fixed fixing ring 411' and an inlet air ring 412 'with its spiral case 1'.
In the present application, keeping the distance between the front end of the impeller 2 and the front cover plate 11 of the volute 1 as S 1 (in this embodiment, the distance between the front end of the impeller 2 'and the front cover plate 11' of the volute 1 'in the conventional centrifugal fan is also S 1), the conventional distance between the front end of the impeller 2 and the most back side end of the air intake collector 4 as S 2 (in this embodiment, the conventional distance S 2 is the distance between the front end of the impeller 2' and the most back side end of the conventional air intake collector 4 'in the conventional centrifugal fan), the height of the impeller 2 is H 0, the inner diameter of the impeller 2 is D 3 (in this embodiment, the inner diameter of the impeller 2' in the conventional centrifugal fan is also D 3), the air intake collector 4 in the present application satisfies the following relation:
(1) S 1-S2-5≤H1≤S1-S2, wherein H 1 is the height of the secondary air inlet ring 412;
(2) S 1-S2≤H2≤S1+0.1H0, wherein H 2 is the height of the connecting ring 421;
(3) 0.15H 0<H3<0.35H0+S2, wherein H 3 is the height of the main air inlet ring 422;
(4) 0.65D 3-10≤D1≤0.85D3 -10, wherein D 1 is the diameter of the connecting ring 421;
(5) D 1+10≤D2≤D3 -10, wherein D 2 is the maximum diameter of the primary air intake 422.
The secondary air inlet ring 412 can be made to have a flaring trend by the above relation (1), and the magnitude of the flaring angle α is 0 to 15 °, so that not only the air flow entering the secondary air inlet area 401 can be prevented from directly striking the annular wall of the primary collector ring 42 when the air flow is large, but also the air flow can be prevented from excessively striking the front end of the impeller 2, thereby further preventing the introduction of additional noise.
When the air flows to the inlet of the fan under the action of the negative pressure of the fan, the more parts of the total air flow moving along the normal direction of the inlet are far away from the inlet, and the less parts of the total air flow moving along the normal direction of the inlet are located, so that the height of the connecting ring 421 is designed to meet the relation (2) in order to avoid collision loss in the process of increasing the separation of the air flow into the main air inlet area 401 and the auxiliary air inlet area 402. The primary air intake ring 422 serves to guide the air flow into the impeller 2, and the primary and secondary air intake areas 401,402 are also formed by the separation of the primary air intake ring 422, so that the height of the primary air intake ring is matched with the tip height of the impeller 2, that is, the relation (3) is satisfied.
The connecting ring 421 can keep the external air flow in the main air inlet area 402 in a moving state after being separated, and can properly reduce the turbulence intensity of the air flow entering the fan, the diameter of the connecting ring 421 influences the amount of the air flow entering the main air inlet area 401 and the auxiliary air inlet area 402, and the air flow entering the auxiliary air inlet area 401 is matched with the amount which can be processed by the tip area of the impeller 2, so that the diameter of the connecting ring 421 is set as shown in the relation (4). In addition, the airflows in the main air intake area 401 and the auxiliary air intake area 402 meet at the trailing edge (i.e. the maximum diameter) of the main air intake ring 422, and due to the difference of the channel resistance losses of the two air intake areas, the two airflows are always different in speed, vortex generation is easy to induce, the vortex is easy to generate when the two airflows meet, the farther the intersection is away from the inlet of the impeller 2, the more difficult to generate (the less so as to be carried away by the impeller 2) when the intersection is closer to the inlet of the impeller 2, but the intersection is possibly brought with additional periodic noise when the impeller 2 runs, so that the diameter of the connecting ring 421 and the maximum diameter of the main air intake ring 422 are designed as in relation (5) to avoid the vortex and noise.
The circular arc radius R 1 of the alignment line of the main intake ring 422 is as follows: r 1 mm or more and 100mm or less. When the centrifugal fan works, the movement of the air flow along the height direction of the impeller 2 is converted into radial movement along the impeller 2, so that the more the shape of the main air inlet ring 422 is fitted with the movement track of the air flow, the smaller the resistance in the movement process of the air flow is, while the shape of the main air inlet ring 422 is determined by the R 1, the larger the R 1 is, the smaller the bending degree (curvature) of the main air inlet ring 422 is, the smaller the R 1 is, and the larger the bending degree (curvature) of the main air inlet ring 422 is, so that the size of the R 1 is limited in the range. The junction of the connecting ring 421 and the main air inlet ring 422 is opposite to the gap between the auxiliary collector 41 and the front end of the impeller 2. In the air inlet channel of the secondary air inlet area 401, the junction between the connecting ring 421 and the main air inlet ring 422 is a turning position where the air flow is changed from expansion to contraction, and the expansion and contraction process can increase the turbulence degree of the air flow in a local area, so that additional adverse effects can be brought to the air flow. During operation of the impeller 2, a certain amount of gas leaks from the gap between the auxiliary collector 41 and the front disc of the impeller 2, and the turbulence degree of the increase of the gas flow to the local area exceeds the turbulence caused by the contraction and expansion process, so that the boundary between the connecting ring 421 and the main air inlet ring 422 is opposite to the gap between the auxiliary collector 41 and the front end of the impeller 2, and the adverse effect caused by the contraction and expansion process can be weakened.
Fig. 11 to 13 are graphs showing comparison between simulation test results of a conventional centrifugal fan and a centrifugal fan according to the present application, wherein the left side in fig. 10 to 12 is the test result of the conventional centrifugal fan, and the right side is the test result of the centrifugal fan according to the present application. As can be seen from fig. 10, the air flow thrown out by the impeller 2 can be prevented from being too concentrated by installing the air inlet collector 4 in the application, and the uniformity of the air flow in the flow channel of the volute 1 along the height direction of the impeller 2 is improved. As can be seen from fig. 11, the intake air collector 4 of the present application can significantly reduce the formation of large eddies compared to the conventional intake air collector 4. As can be seen from fig. 12, the air inlet collector 4 of the present application can reduce the impact of air flow on the disk surface of the impeller 2, thereby significantly reducing noise, as compared with the conventional air inlet collector 4.
Claims (9)
1. The centrifugal fan comprises a volute (1) and an impeller (2), wherein the impeller (2) is arranged in the volute (1), and an air inlet is formed in the volute (1), and the centrifugal fan is characterized by also comprising an air inlet collector (4), wherein the air inlet collector (4) is arranged in the air inlet;
The air inlet current collector comprises a secondary current collector (41) and a primary current collector (42), wherein the primary current collector (42) is arranged in the secondary current collector (41) and is concentric with the secondary current collector (41), the primary current collector (42) encloses a primary air inlet area (402), and a secondary air inlet area (401) is enclosed between the primary current collector (42) and the secondary current collector (41);
The auxiliary flow collecting ring (41) comprises a fixed ring (411) used for being fixed with a volute (1) of the fan and an auxiliary air inlet ring (412) positioned on the back side of the fixed ring (411), and the auxiliary air inlet ring (412) is in a circular truncated cone shape;
The main collector ring (42) comprises a connecting ring (421) used for being connected with the auxiliary collector ring (41) and a main air inlet ring (422) positioned on the back side of the connecting ring (421), the connecting ring (421) is cylindrical, the main air inlet ring (422) is bell-mouthed, and the connecting ring (421) is laterally outwards flared;
Note that the distance between the front end of the impeller (2) and the front cover plate (11) of the volute (1) is S 1, and the conventional distance between the front end of the impeller (2) and the most back side end of the air inlet collector (4) is S 2, the height H 1 of the auxiliary air inlet ring (412) satisfies the following relationship: s 1-S2-5≤H1≤S1-S2;
Note that the distance between the front end of the impeller (2) and the front cover plate (11) of the volute (1) is S 1, the distance between the front end of the impeller (2) and the most back side end of the conventional air inlet collector (4) is S 2, and the height of the impeller (2) is H 0, then the height H 2 of the connecting ring (421) satisfies the following relation: s 1-S2≤H2≤S1+0.1H0.
2. Centrifugal fan according to claim 1, wherein the primary collector ring (42) and the secondary collector ring (41) are connected by a connection structure (43) arranged in the secondary air inlet area (401), and the connection structure (43) is provided with air inlet windows (432) distributed along the circumferential direction.
3. Centrifugal fan according to claim 2, wherein the connecting structure (43) comprises spokes (431) which are uniformly distributed along the circumferential direction of the secondary air inlet area (401), two ends of each spoke (431) are respectively fixed with the secondary collector ring (41) and the primary collector ring (42), and adjacent spokes (431), the secondary collector ring (41) and the primary collector ring (42) are correspondingly surrounded to form the air inlet window (432).
4. Centrifugal fan according to claim 1, wherein the divergence angle α of the secondary inlet ring (412) is of a size of 0-15 °.
5. The centrifugal fan according to claim 1, wherein the radius R 1 of the circular arc of the directrix of the main air intake ring (422) is: r 1 mm or more and 100mm or less.
6. The centrifugal fan according to claim 1, wherein the height H 3 of the main inlet ring (422) satisfies the following relation: 0.15H 0<H3<0.35H0+S2.
7. Centrifugal fan according to claim 1, characterized in that the diameter D 1 of the above-mentioned connecting ring (421) satisfies the following relation, given that the inner diameter D 3 of the impeller (2) is: 0.65D 3-10≤D1≤0.85D3 -10.
8. Centrifugal fan according to claim 1, characterized in that the diameter D 1 of the connection ring (421) and the maximum diameter D 2 of the main air intake ring (422) satisfy the following relation, given that the inner diameter of the impeller (2) is D 3: d 1+10≤D2≤D3 -10.
9. Centrifugal fan according to claim 1, wherein the junction of the connection ring (421) with the primary air intake ring (422) is opposite to the gap between the secondary collector ring (41) and the front end of the impeller (2).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810419678.1A CN110439864B (en) | 2018-05-04 | 2018-05-04 | Air inlet current collector and centrifugal fan with same |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810419678.1A CN110439864B (en) | 2018-05-04 | 2018-05-04 | Air inlet current collector and centrifugal fan with same |
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| CN110439864A CN110439864A (en) | 2019-11-12 |
| CN110439864B true CN110439864B (en) | 2024-08-16 |
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| CN201810419678.1A Active CN110439864B (en) | 2018-05-04 | 2018-05-04 | Air inlet current collector and centrifugal fan with same |
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