CN218563998U - Centrifugal impeller, centrifugal fan and refrigeration equipment - Google Patents
Centrifugal impeller, centrifugal fan and refrigeration equipment Download PDFInfo
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- CN218563998U CN218563998U CN202223196801.9U CN202223196801U CN218563998U CN 218563998 U CN218563998 U CN 218563998U CN 202223196801 U CN202223196801 U CN 202223196801U CN 218563998 U CN218563998 U CN 218563998U
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Abstract
The utility model provides a centrifugal impeller, a centrifugal fan and refrigeration equipment, wherein the centrifugal impeller comprises a front cover, a rear cover and blades, the front cover and the rear cover are arranged at intervals along the axial direction of the centrifugal impeller, the front cover is annular, and the middle part of the front cover forms an air inlet; the blades are in a wing shape and are connected between the front cover and the rear cover, the outer edge of the front cover, the outer connecting edge of the rear cover and the blades enclose an air outlet, and one end of each blade in the height direction is connected with the rear cover; one side of the blade, which is far away from the rear cover, is provided with a blade front edge and a connecting edge which are arranged along the length direction of the blade, the connecting edge is connected with the side wall of the front cover, which faces the rear cover, and the blade front edge is positioned on the radial inner side of the front cover; the distance between the front edge of the blade and the rear cover gradually increases from the front edge end of the blade to the tail edge end of the blade along the length direction of the blade; the camber line of the blade and the chord of the blade do not coincide. The centrifugal impeller can weaken the vortex generated at the front cover, improve the air flow in the centrifugal impeller, reduce the flow loss and improve the working efficiency.
Description
Technical Field
The utility model belongs to the technical field of refrigeration plant and specifically relates to a centrifugal impeller, centrifugal fan and refrigeration plant are related to.
Background
The ceiling machine is also called ceiling machine, ceiling type or embedded type air conditioner. The raise-level air conditioner has the advantages of being long in air supply distance, attractive in appearance and free of occupying space, and is favored by more and more consumers, the centrifugal fan is an important part of the raise-level air conditioner for air supply, the centrifugal fan has the advantages of being large in pressure, small in flow and capable of changing the airflow direction, the fan blades are core parts of the centrifugal fan, and the performance of the fan blades has direct influence on the performance of the whole machine.
Referring to fig. 1 and 2, in a centrifugal impeller 10 of the prior art, the blades 11 have a symmetrical airfoil shape, i.e., the camber line and the chord of the blade 11 coincide. When the airflow passes through the centrifugal impeller 10, the direction is changed from the axial direction to the radial direction, the airflow velocity near the front cover is higher, the airflow velocity near the rear cover 12 is lower, the pressure distribution is uneven in the height direction of the blades, a vortex is formed at the front cover as shown in fig. 2, and the flow loss gradually increases from the rear cover 12 to the front cover as the height of the blades 11 increases. Meanwhile, for the centrifugal impeller with the same inlet angle of the blades, because the airflow speed close to the front cover is higher than the airflow speed close to the rear cover, the airflow attack angle formed by the inlet angle of the blades and the inlet airflow angle is unequal in the height direction of the blades, the impact loss is large at a place with a large attack angle, and the efficiency of the centrifugal fan is lower. The greater the variation in velocity of the airflow along the height of the blade, the greater the effect as the velocity non-uniformity increases as the airflow turns. In addition, the blades of the symmetrical wing shapes are easy to flow and separate at the tail edges of the blades, so that the tail edges of the blades further generate vortex.
SUMMERY OF THE UTILITY MODEL
The utility model discloses a first purpose provides a can weaken the swirl that protecgulum department produced, improves the inside air flow of centrifugal impeller, reduces the loss of flow, improves work efficiency's centrifugal impeller.
The second objective of the present invention is to provide a centrifugal fan with the above centrifugal impeller.
The third objective of the present invention is to provide a refrigeration device with the above centrifugal fan.
In order to achieve the first object, the utility model provides a centrifugal impeller, which comprises a front cover, a rear cover and blades, wherein the front cover and the rear cover are arranged at intervals along the axial direction of the centrifugal impeller, the front cover is annular, and the middle part of the front cover forms an air inlet; the blades are in a wing shape and are connected between the front cover and the rear cover, the outer edge of the front cover, the outer connecting edge of the rear cover and the blades enclose an air outlet, and one end of each blade in the height direction is connected with the rear cover; one side of the blade, which is far away from the rear cover, is provided with a blade front edge and a connecting edge which are arranged along the length direction of the blade, the connecting edge is connected with the side wall of the front cover, which faces the rear cover, and the blade front edge is positioned on the radial inner side of the front cover; the distance between the front edge of the blade and the rear cover gradually increases from the front edge end of the blade to the tail edge end of the blade along the length direction of the blade; the camber line of the blade and the chord of the blade do not coincide.
According to the scheme, the front edge of the blade is gradually increased along the distance between the front edge and the rear cover along the airflow direction, so that the change of the airflow attack angle along the height direction of the blade is small, the impact loss of the blade inlet is reduced, and the efficiency of the centrifugal fan is improved. The structure can make the airflow adapt to the change of the airflow channel in the centrifugal impeller, improve the flow of the airflow in the height direction of the blades in the centrifugal impeller, make the pressure distribution more uniform and reduce the flow loss. Meanwhile, the shape of the blade is designed into an asymmetric wing shape, so that the flow separation of airflow on the suction surface of the blade is greatly reduced, the vortex generated at the front cover can be greatly weakened, the flow of the airflow in the centrifugal impeller is improved, the flow loss is reduced, and the efficiency of the centrifugal impeller is improved. In addition, the front edge of the blade extends into the radial inner side of the front cover, so that the size of an air inlet on the front cover can be increased, and the air inlet efficiency is improved.
Preferably, the blade leading edge comprises a first leading edge section and a second leading edge section, the end of the blade leading edge far away from the connecting edge is provided with a leading edge end, the first leading edge section is arranged close to the leading edge end, and two ends of the second leading edge section are respectively connected to the first leading edge section and the inner peripheral wall of the front cover; establishing a two-dimensional coordinate system by taking the joint of the front edge end of the blade and the rear cover as an origin, taking the chord as an x axis and taking the axis parallel to the centrifugal impeller as a y axis; the projection of the first leading edge segment in the two-dimensional coordinate system is a curve, and the projection of the second leading edge segment in the two-dimensional coordinate system is a straight line.
Further, the first leading edge segment satisfies the following curve equation: y1= a1 x1^ (1/b 1), x1 ∈ [0, L1]; wherein L1 is the projection length of the first leading edge segment on the x-axis, and a1 and b1 are both constants.
Further, a1=30.3294, and b1=2.8001.
Preferably, the second leading edge section satisfies the following equation: y2= a2 x2+ b2, x2 e [ L1, L2], wherein L1 is a projection length of the first leading edge segment on the x-axis, L2 is a projection length of the second leading edge segment on the x-axis, and a2 and b2 are both constant.
Further aspects are, a2=0.4416, and b2=88.0279.
In a preferred embodiment, the ratio of the blades in the radial direction of the centrifugal impeller is a, a = (R2-R)/R2; the proportion of the part of the blade with the blade front edge in the radial direction of the centrifugal impeller is b, b = (R1-R)/R2; the proportion of the part of the blade with the connecting edge in the radial direction of the centrifugal impeller is c, and c = a-b; wherein R is the radius of the circle where the leading edge end of the blade is located, R1 is the radius of the air inlet, R2 is the radius of the circle where the trailing edge end of the blade is located, and a belongs to (0, 0.65), and/or b belongs to (0, 0.3).
Further, a =0.267, b =0.107; and/or R2 ∈ [220, 250] mm.
Preferably, the trailing edge ends of the vanes, the outer peripheral wall of the front cover and the outer peripheral wall of the rear cover are overlapped in the axial direction of the centrifugal impeller.
Preferably, the ratio d of the height of the front cover to the height of the centrifugal impeller is less than 0.5.
Further, d =0.38; and/or the height of the centrifugal impeller is H, H epsilon (135, 155) millimeters.
In a preferred embodiment, the maximum distance Hh between the leading edge of the blade and the rear cover satisfies the following relationship: h2< H-Hh < H1; h is the height of the centrifugal impeller, H1 is the height of the front cover, H2 is the minimum distance between the front edge of the blade and the end wall of the front cover far away from the rear cover, and H2 is larger than 0.
Therefore, a distance H2 needs to be reserved between the front edge of the blade at the upper end of the blade and the flow guide ring, and collision between the front edge of the blade and the flow guide ring is avoided.
In a preferred scheme, the inlet angle at the leading edge end of the blade is rho 1, rho 1 epsilon (10, 20) °, and the inlet angle is an included angle between the tangent of the leading edge end on the profile of the blade and the tangent of the camber line of the blade; and/or an exit angle at the trailing edge end of the blade is ρ 2, ρ 2 ∈ (10, 50) °, the exit angle being the angle between the tangent of the trailing edge end on the profile of the blade and the tangent of the mean camber line of the blade.
Further, ρ 1=12.4 °, ρ 2=13.8 °.
Further, the outlet angle of the blade is kept constant along the height direction of the blade.
One preferred solution is that the chord length of the blade chord is/e (75, 230) mm.
In order to achieve the second objective, the present invention provides a centrifugal fan, which includes the above centrifugal impeller.
One preferred scheme is that the centrifugal fan further comprises a shell, an evaporator and a flow guide ring, wherein the evaporator and the flow guide ring are installed in the shell; the centrifugal impeller is arranged in the shell, a ventilation side wall is arranged on the shell, the ventilation side wall is arranged on one side of the shell, which is far away from the rear cover, a shell air inlet and a shell air outlet are formed in the ventilation side wall, the shell air inlet is positioned in the middle of the ventilation side wall, and the shell air outlet is surrounded outside the shell air inlet; the guide ring is arranged at the air inlet of the shell, and one end of the guide ring extends into the centrifugal impeller; the evaporator is annular and surrounds the centrifugal impeller, and the evaporator is located between the shell air inlet and the shell air outlet in the radial direction.
The centrifugal fan further comprises an electrical box, the guide ring is provided with a mounting groove which is sunken towards one side of the centrifugal impeller, and the electrical box is mounted in the mounting groove.
Therefore, the installation groove is formed, the electric appliance box is embedded in the installation groove, and the overall height of the centrifugal fan can be reduced.
In order to achieve the third objective, the present invention provides a refrigeration device, including the above centrifugal fan.
Drawings
Fig. 1 is a structural diagram of a conventional centrifugal fan.
Fig. 2 is a cloud of air flows through a centrifugal impeller in a conventional centrifugal fan.
Fig. 3 is a sectional view of an embodiment of the centrifugal fan of the present invention.
Fig. 4 is a perspective view of an embodiment of the centrifugal impeller of the present invention.
Fig. 5 is a plan view of an embodiment of the centrifugal impeller of the present invention.
Figure 6 is a radial cross-sectional view of an embodiment of the centrifugal impeller of the present invention.
Fig. 7 is a schematic diagram of a centrifugal impeller embodiment of the present invention establishing a coordinate system at the leading edge end of the blade.
Fig. 8 is a cross-sectional view perpendicular to the radial direction of an embodiment of the centrifugal impeller of the present invention.
Figure 9 is a cloud of the airflow through an embodiment of the centrifugal impeller of the present invention.
The present invention will be further described with reference to the accompanying drawings and examples.
Detailed Description
Referring to fig. 3, the refrigeration apparatus in the present embodiment is a courtyard machine, and the refrigeration apparatus includes a centrifugal fan 2. The centrifugal fan 2 includes a casing 21, and an evaporator 22, a baffle ring 23, a motor 24, an electric appliance box 25, and a centrifugal impeller 26 mounted in the casing 21.
The housing 21 is provided with a ventilation sidewall 211, the ventilation sidewall 211 is disposed on one side of the housing 21 far away from the rear cover 4 of the centrifugal impeller 26, the ventilation sidewall 211 is provided with a housing air inlet 212 and a housing air outlet 213, the housing air inlet 212 is located in the middle of the ventilation sidewall 211, and the housing air outlet 213 surrounds the housing air inlet 212. The guide ring 23 is installed at the housing air inlet 212, and one end of the guide ring 23 extends into the centrifugal impeller 26. The evaporator 22 is annular and surrounds the centrifugal impeller 26, the evaporator 22 being located radially between the housing air inlet 212 and the housing air outlet 213. The guide ring 23 is provided with a mounting groove 231 recessed towards one side of the centrifugal impeller 26, and the electrical box 25 is mounted in the mounting groove 231 to reduce the overall height of the centrifugal fan 2.
Referring to fig. 4 to 6, the centrifugal impeller 26 includes a front cover 3, a rear cover 4 and seven blades 5, the front cover 3 and the rear cover 4 are arranged at intervals along the axial direction of the centrifugal impeller 26, the front cover 3 is located on the upstream side of the rear cover 4 in the airflow direction, the front cover 3 is annular, and the middle part forms an air inlet 31. The blade 5 is connected between the front cover 3 and the rear cover 4, the blade 5 is airfoil-shaped, the camber line 51 of the blade 5 is not overlapped with the chord 52 of the blade 5, the two ends of the blade 5 in the length direction are respectively provided with a leading edge end 55 and a trailing edge end 56, and the leading edge end 55 is located on the upstream side of the trailing edge end 56 along the airflow direction. The trailing edge ends 56 of the vanes 5, the outer peripheral wall of the front cover 3, and the outer peripheral wall of the rear cover 4 are overlapped in ghost in the axial direction of the centrifugal impeller 26. Seven blades 5 are arranged at intervals along the circumferential direction of the centrifugal impeller 26, the leading edge end 55 and the trailing edge end 56 of each blade 5 are arranged at intervals along the circumferential direction of the centrifugal impeller 26, and the outer edge of the front cover 3, the outer connecting edge of the rear cover 4 and the trailing edge ends 56 of two adjacent blades 5 enclose the air outlet 32.
One end of the blade 5 in the height direction is connected with the rear cover 4, one side of the blade 5 away from the rear cover 4 is provided with a blade front edge 53 and a connecting edge 54 which are arranged along the length direction of the blade 5, the connecting edge 54 is connected with the side wall of the front cover 3 facing the rear cover 4, and the blade front edge 53 is positioned on the radial inner side of the front cover 3. The distance between the blade leading edge 53 and the rear cover 4 increases gradually from the leading edge end 55 of the blade 5 to the trailing edge end 56 of the blade 5 along the length direction of the blade 5.
Referring to fig. 5, the proportion of the blade 5 in the radial direction of the centrifugal impeller 26 is a, a = (R2-R)/R2, the proportion of the portion of the blade 5 having the blade leading edge 53 in the radial direction of the centrifugal impeller 26 is b, b = (R1-R)/R2, the proportion of the portion of the blade 5 having the connecting edge 54 in the radial direction of the centrifugal impeller 26 is c, and c = a-b. Wherein, R is the radius of the circle where the leading edge end 55 of the blade 5 is located, R1 is the radius of the air inlet 31, R2 is the radius of the circle where the trailing edge end 56 of the blade 5 is located, a belongs to (0, 0.65), and b belongs to (0, 0.3). Preferably, a =0.267, b =0.107, R2 ∈ [220, 250] millimeter. Preferably, R2=230 mm.
The blade leading edge 53 comprises a first leading edge section 531 and a second leading edge section 532, the first leading edge section 531 being arranged near the leading edge end 55, the second leading edge section 532 being connected between the first leading edge section 531 and the inner circumferential wall of the front cover 3.
As shown in fig. 7, a two-dimensional coordinate system is established with the connecting point of the leading edge 55 of the blade 5 and the rear cover 4 as the origin, the chord 52 of the blade 5 as the x-axis, and the axis parallel to the centrifugal impeller 26 as the y-axis, the projection of the first leading edge segment 531 in the two-dimensional coordinate system is a curve, and the projection of the second leading edge segment 532 in the two-dimensional coordinate system is a straight line.
The first leading edge segment 531 satisfies the following curvilinear equation: y1= a1 x1^ (1/b 1), x1 ∈ [0, L1]; the second leading edge segment 532 satisfies the following straight line equation: y2= a2 x2+ b2, x2 ∈ [ L1, L2]; where L1 is the projection length of the first leading edge segment 531 on the x-axis, L2 is the projection length of the second leading edge segment 532 on the x-axis, and a1, b1, a2, and b2 are all constants, preferably, a1=30.3294, b1=2.8001, a2=0.4416, and b2=88.0279.
As shown in fig. 8, the maximum distance Hh between the blade leading edge 53 and the rear cover 4 satisfies the following relationship: h2< H-Hh < H1. Where H is the height of the centrifugal impeller 26, H e (135, 155) mm, preferably, H =145 mm; h1 is the height of the front cover 3; h2 is the minimum distance between the front edge 53 of the vane and the end wall of the front cover 3 far away from the rear cover 4, H2 is greater than 0, and H2 is greater than the height of the guide ring 23 extending into the front cover 3, so as to avoid interference between the vane 5 and the guide ring 23 and influence on rotation of the vane 5, and preferably, H2=15 mm. The ratio d of the height H1 of the front cover 3 to the height H of the centrifugal impeller 26 is less than 0.5, preferably d =0.38.
As shown in fig. 6, the inlet angle at the leading edge 55 of the blade 5 is ρ 1, ρ 1 ∈ (10, 20) °, the inlet angle being the angle between the tangent of the leading edge 55 on the profile of the blade 5 and the tangent of the camber line 51 of the blade 5. The exit angle at the trailing edge end 56 of the blade 5 is ρ 2, ρ 2 ∈ (10, 50) °, and the exit angle ρ 2 of the blade 5 remains constant along the height direction of the blade 5, the exit angle being the angle between the tangent of the trailing edge end 56 on the profile of the blade 5 and the tangent of the mean camber line 51 of the blade 5. Preferably, ρ 1=12.4 °, ρ 2=13.8 °. The chord 52 of the blade 5 has a chord length l e (75, 230) mm, preferably l =217 mm. Since the distance between the blade leading edge 53 and the rear cover 4 gradually increases in the airflow direction, the chord length l of the chord 52 gradually decreases in the height direction of the blade 5.
Fig. 9 shows a cloud of the airflow passing through the centrifugal impeller in this embodiment, and by designing the shape of the blades to be asymmetric wing-shaped, the flow separation of the airflow at the suction surface of the blades is greatly reduced, and the vortex generated at the front cover can be greatly weakened, so that the flow of the airflow inside the centrifugal impeller is improved.
It is thus clear that through setting the blade leading edge of blade into, along the mode that the distance of airflow flow direction to its and back lid increases gradually to guarantee along the direction of height air current attack angle of blade change little, thereby reduce the impact loss of blade entry, improved centrifugal fan's efficiency. The structure can make the airflow adapt to the change of the airflow channel in the centrifugal impeller, improve the flow of the airflow in the height direction of the blades in the centrifugal impeller, make the pressure distribution more uniform and reduce the flow loss. Meanwhile, the shape of the blade is designed into an asymmetric wing shape, so that the flow separation of airflow on the suction surface of the blade is greatly reduced, the vortex generated at the front cover can be greatly weakened, the flow of the airflow in the centrifugal impeller is improved, the flow loss is reduced, and the efficiency of the centrifugal impeller is improved. In addition, the front edge of the blade extends into the radial inner side of the front cover, so that the size of an air inlet on the front cover can be increased, and the air inlet efficiency is improved.
Furthermore, the utility model discloses a centrifugal fan also can be applied to other air conditioners or refrigeration plant such as refrigerator on. The number of vanes may also be varied as desired. The above changes also enable the object of the present invention to be achieved.
Finally, it should be emphasized that the above-described is merely a preferred embodiment of the present invention, and is not intended to limit the invention, as various changes and modifications may be made by those skilled in the art, and any changes, equivalents, modifications, etc. made within the spirit and scope of the present invention are intended to be included within the scope of the present invention.
Claims (20)
1. The centrifugal impeller comprises a front cover, a rear cover and blades, wherein the front cover and the rear cover are arranged at intervals along the axial direction of the centrifugal impeller, the front cover is annular, and an air inlet is formed in the middle of the front cover;
the blades are in a wing shape, the blades are connected between the front cover and the rear cover, the outer edge of the front cover, the outer connecting edge of the rear cover and the blades form an air outlet, and one end of each blade in the height direction is connected with the rear cover;
the method is characterized in that:
one side of the blade, which is far away from the rear cover, is provided with a blade front edge and a connecting edge, which are arranged along the length direction of the blade, the connecting edge is connected with the side wall of the front cover, which faces the rear cover, and the blade front edge is positioned on the radial inner side of the front cover;
the distance between the front edge of the blade and the rear cover gradually increases from the front edge end of the blade to the tail edge end of the blade along the length direction of the blade;
the camber line of the blade and the chord of the blade are not coincident.
2. The centrifugal impeller of claim 1, wherein:
the blade front edge comprises a first front edge section and a second front edge section, the front edge end is arranged at the end part of the blade front edge far away from the connecting edge, the first front edge section is arranged close to the front edge end, and two ends of the second front edge section are respectively connected to the first front edge section and the inner peripheral wall of the front cover;
establishing a two-dimensional coordinate system by taking the joint of the front edge end of the blade and the rear cover as an origin, the chord as an x-axis and the axis parallel to the centrifugal impeller as a y-axis;
the projection of the first leading edge segment in the two-dimensional coordinate system is a curve, and the projection of the second leading edge segment in the two-dimensional coordinate system is a straight line.
3. The centrifugal impeller of claim 2, wherein:
the first leading edge segment satisfies the following curve equation: y1= a1 x1^ (1/b 1), x1 ∈ [0, L1];
wherein L1 is a projection length of the first leading edge segment on the x-axis, and a1 and b1 are both constant.
4. The centrifugal impeller of claim 3, wherein:
a1=30.3294, and b1=2.8001.
5. The centrifugal impeller of claim 2, wherein:
the second leading edge segment satisfies the following equation: y2= a2 x2+ b2, x2 ∈ [ L1, L2];
wherein L1 is a projection length of the first leading edge segment on the x-axis, L2 is a projection length of the second leading edge segment on the x-axis, and a2 and b2 are both constants.
6. The centrifugal impeller of claim 5, wherein:
a2=0.4416, and b2=88.0279.
7. The centrifugal impeller according to any one of claims 1 to 6, wherein:
the proportion of the blades in the radial direction of the centrifugal impeller is a, a = (R2-R)/R2;
the proportion of the part of the blade having the blade leading edge in the radial direction of the centrifugal impeller is b, b = (R1-R)/R2;
the proportion of the portion of the blade having the connecting edge in the radial direction of the centrifugal impeller is c, c = a-b;
wherein R is the radius of the circle where the leading edge end of the blade is located, R1 is the radius of the air inlet, R2 is the radius of the circle where the trailing edge end of the blade is located, and a belongs to (0, 0.65), and/or b belongs to (0, 0.3).
8. The centrifugal impeller of claim 7, wherein:
a =0.267, b =0.107; and/or
R2 ∈ [220, 250] mm.
9. The centrifugal impeller according to any one of claims 1 to 6, wherein:
the trailing edge end of the blade, the peripheral wall of the front cover and the peripheral wall of the rear cover are overlapped along double images in the axial direction of the centrifugal impeller.
10. The centrifugal impeller according to any one of claims 1 to 6, wherein:
the ratio d of the height of the front cover to the height of the centrifugal impeller is less than 0.5.
11. The centrifugal impeller of claim 10, wherein:
d =0.38; and/or
The height of the centrifugal impeller is H, and H is epsilon (135, 155) millimeter.
12. The centrifugal impeller according to any one of claims 1 to 6, wherein:
the maximum distance Hh between the blade leading edge and the rear cover satisfies the following relationship: h2< H-Hh < H1;
h is the height of the centrifugal impeller, H1 is the height of the front cover, H2 is the minimum distance between the front edge of the blade and the end wall of the front cover far away from the rear cover, and H2 is larger than 0.
13. The centrifugal impeller according to any one of claims 1 to 6, wherein:
an inlet angle at the leading edge end of the blade is rho 1, rho 1 belongs to (10, 20) °, and the inlet angle is an included angle between a tangent of the leading edge end on the profile of the blade and a tangent of a camber line of the blade; and/or
The exit angle at the trailing edge end of the blade is ρ 2, ρ 2 ∈ (10, 50) °, the exit angle being the angle between the tangent of the trailing edge end on the profile of the blade and the tangent of the mean camber line of the blade.
14. The centrifugal impeller of claim 13, wherein:
ρ1＝12.4°，ρ2＝13.8°。
15. the centrifugal impeller of claim 13, wherein:
the exit angle of the blade remains constant along the height of the blade.
16. The centrifugal impeller according to any one of claims 1 to 6, wherein:
the chord of the blade chord is/, l ∈ (75, 230) mm.
17. Centrifugal fan, characterized in that it comprises a centrifugal impeller according to any one of claims 1 to 16.
18. The centrifugal fan of claim 17, wherein:
the centrifugal fan also comprises a shell, an evaporator and a flow guide ring, wherein the evaporator and the flow guide ring are arranged in the shell;
the centrifugal impeller is installed in the shell, a ventilation side wall is arranged on the shell, the ventilation side wall is arranged on one side, away from the rear cover, of the shell, a shell air inlet and a shell air outlet are formed in the ventilation side wall, the shell air inlet is located in the middle of the ventilation side wall, and the shell air outlet is surrounded outside the shell air inlet;
the guide ring is arranged at the air inlet of the shell, and one end of the guide ring extends into the centrifugal impeller;
the evaporator is annular and surrounds the centrifugal impeller, and the evaporator is located between the shell air inlet and the shell air outlet in the radial direction.
19. The centrifugal fan of claim 18, wherein:
the centrifugal fan further comprises an electrical box, the guide ring is provided with an installation groove facing the centrifugal impeller, and the electrical box is installed in the installation groove.
20. Refrigeration appliance, characterized in that it comprises a centrifugal fan according to any one of claims 17 to 19.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202223196801.9U CN218563998U (en) | 2022-11-28 | 2022-11-28 | Centrifugal impeller, centrifugal fan and refrigeration equipment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202223196801.9U CN218563998U (en) | 2022-11-28 | 2022-11-28 | Centrifugal impeller, centrifugal fan and refrigeration equipment |
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| Publication Number | Publication Date |
|---|---|
| CN218563998U true CN218563998U (en) | 2023-03-03 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202223196801.9U Active CN218563998U (en) | 2022-11-28 | 2022-11-28 | Centrifugal impeller, centrifugal fan and refrigeration equipment |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN218563998U (en) |
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- 2022-11-28 CN CN202223196801.9U patent/CN218563998U/en active Active
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