CN115289061A - Impeller assembly and centrifugal fan - Google Patents
Impeller assembly and centrifugal fan Download PDFInfo
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- CN115289061A CN115289061A CN202210909165.5A CN202210909165A CN115289061A CN 115289061 A CN115289061 A CN 115289061A CN 202210909165 A CN202210909165 A CN 202210909165A CN 115289061 A CN115289061 A CN 115289061A
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- 238000009792 diffusion process Methods 0.000 abstract description 12
- 238000013461 design Methods 0.000 description 30
- 239000002699 waste material Substances 0.000 description 20
- 230000002349 favourable effect Effects 0.000 description 17
- 230000008859 change Effects 0.000 description 10
- 238000012545 processing Methods 0.000 description 10
- 238000000034 method Methods 0.000 description 7
- 230000003068 static effect Effects 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 238000012423 maintenance Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 230000009286 beneficial effect Effects 0.000 description 3
- 230000003247 decreasing effect Effects 0.000 description 3
- 230000000875 corresponding effect Effects 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 239000000567 combustion gas Substances 0.000 description 1
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- 239000007789 gas Substances 0.000 description 1
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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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
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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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/30—Vanes
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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
- F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
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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 provides an impeller assembly and a centrifugal fan, the impeller assembly comprises: the bottom plate is provided with a shaft hole; the blades are arranged on the bottom plate, are distributed at intervals along the circumferential direction of the shaft hole, and at least part of the blades are reduced in width towards the direction far away from the axis of the shaft hole; wherein, the width direction of blade and the axial syntropy in shaft hole set up. When the distance between two adjacent blades is increased, the width of the blades is reduced, so that the area of the through-flow cross section at different positions can be changed little or kept basically unchanged. Therefore, a diffusion channel is prevented from being formed between two adjacent blades, a vortex area is prevented from being formed between the two adjacent blades, and the backflow phenomenon is reduced.
Description
Technical Field
The invention belongs to the technical field of fan equipment, and particularly relates to an impeller assembly and a centrifugal fan.
Background
The centrifugal fan works air by the rotation of the impeller, and the air is thrown out by the centrifugal action through the rectifying channels of the two blades.
In the direction away from the axis, the distance between two adjacent blades is increased, so that a diffusion channel is formed between the two adjacent blades, a vortex area is easily formed between the two adjacent blades, and the efficiency of the impeller is affected.
Disclosure of Invention
The present invention is directed to solving one of the technical problems of the prior art or the related art.
In view of this, the present invention proposes, in a first aspect, an impeller assembly comprising: the bottom plate is provided with a shaft hole; the blades are arranged on the bottom plate, are distributed at intervals along the circumferential direction of the shaft hole, and at least part of the blades are reduced in width towards the direction far away from the axis of the shaft hole; wherein, the width direction of blade and the axial syntropy in shaft hole set up.
According to the impeller assembly provided by the invention, the plurality of blades are arranged on the bottom plate, the shaft hole is formed in the bottom plate in a machining mode, and the output shaft of the driving part can be assembled with the shaft hole, so that the driving part can drive the bottom plate to rotate, and the bottom plate drives the plurality of blades to rotate. The plurality of blades, when rotated, can drive the airflow to move.
The width of at least one part of the blades is reduced towards the direction far away from the axis of the shaft hole, and the sectional area of a channel between two adjacent blades is changed by changing the width of the blades, so that the vortex problem caused by the diffusion channel is avoided.
Specifically, the plane a is a plane parallel to the axis of the shaft hole, and a plurality of through-flow cross sections can be obtained by cutting the passage between two adjacent blades along the radial direction of the shaft hole through a plurality of planes parallel to the plane a. In the related art, since the distance between two adjacent blades is gradually increased and the width of the blades is usually kept constant, the area of the through-flow section is also gradually increased, so that a diffusion passage is formed between two adjacent blades, and when the diffusion passage generates a vortex, the airflow is disturbed, so that the kinetic energy of partial airflow is mutually offset, and energy waste is caused. In the present invention, however, the flow cross-sectional area is varied by varying the width of the vanes. The area of the through-flow section is equal to the length multiplied by the width, the length is the distance between two adjacent blades, and the width is the width of the blade. Therefore, when the distance between two adjacent blades is increased, the width of the blades is reduced, so that the area of the through-flow cross section at different positions can be changed little or kept basically unchanged. Therefore, a diffusion channel is prevented from being formed between two adjacent blades, a vortex area is prevented from appearing between the two adjacent blades, the backflow phenomenon is reduced, the situation of energy waste caused by airflow disorder is avoided, the work done by the blades on the airflow can be effectively converted into the kinetic energy of the airflow, the impeller efficiency of the impeller assembly can be improved, and the improvement of the air volume of a fan using the impeller assembly is facilitated.
In addition, according to the impeller assembly in the above technical solution provided by the present invention, the following additional technical features may also be provided:
in one possible design, at least a portion of the vanes taper in width radially of the shaft bore and away from the axis.
In this design, the width variation tendency of the blade is defined to be gradually reduced. Specifically, in the direction away from the axis of the shaft hole, the distance between two adjacent blades is gradually increased, and the width of the blades is gradually reduced, so that the change area of the distance between two adjacent blades is basically the same as the change trend of the width of the blades, and further the area of the through-flow cross section between two adjacent blades can be changed slightly or kept unchanged. Further avoid forming diffusion passageway between two adjacent blades, prevent that the vortex region from appearing between two adjacent blades, reduce the emergence of backward flow phenomenon, avoid causing the condition of energy waste to take place because of the air current is disorderly, the work that the blade was done the air current can effectively be the kinetic energy of air current, consequently can further improve the impeller efficiency of impeller subassembly, is favorable to improving the amount of wind of the fan that uses impeller subassembly.
In one possible design, the first end of the blade is spaced from the axis by a distance greater than the second end of the blade; setting the width of each blade as h, setting the distance from any point on each blade except the first end to the axis of the shaft hole as D, and setting the distance from the first end of each blade to the axis as D1; h, D, D1 satisfy h =11.7+0.2 × 2 × (D1-D).
In this design, the first end of the vane is spaced from the axis of the shaft bore by a distance greater than the distance between the second end of the vane and the axis of the shaft bore, so that the first end of the vane is spaced away from the axis of the shaft bore and the second end of the vane is proximate to the axis of the shaft bore. The width of the blade is h, which refers to the direction in which the blade extends in the axial direction of the shaft hole. The distance from the first end of the blade to the axis of the shaft hole is D1, and the distance from the position except the first end of the blade to the axis of the shaft hole is D. The width h of the blade, the distance D1 from the first end of the blade to the axis of the shaft hole, and the distance D from the position except the first end of the blade to the axis of the shaft hole satisfy the following formula: h =11.7+0.2 × 2 × (D1-D). By defining the width h, the distance D1 and the distance D by the above-mentioned publicly known means, the distance from the blade to the axis of the shaft hole is correlated with the width of the blade, so that the width of the blade can be adjusted according to the distance from the blade to the axis of the shaft hole. Further avoid forming the diffusion passageway between two adjacent blades, prevent that the vortex region from appearing between two adjacent blades, reduce the emergence of backward flow phenomenon, avoid causing the condition of energy waste to take place because of the air current is disorderly, the work that the blade was done the air current can effectively be the kinetic energy of air current, consequently can further improve the impeller efficiency of impeller subassembly, is favorable to improving the amount of wind of the fan that uses impeller subassembly.
In one possible design, the inlet angle α 1 of the blade is satisfied, 147 ° < α 1 < 159 °.
In this design, the inlet angle of the blade refers to the angle between the blade and the tangential direction of the shaft hole. Specifically, a connecting line E1 passing through the axis of the shaft hole and the second end of the blade is made, the connecting line E1 and the second end of the blade have an intersection point, and a circle c1 is made with the axis of the shaft hole as a center and the connecting line E1 as a radius. A tangent F1 to the circle c1 is drawn, the tangent F1 passing through the second end of the blade. The inlet angle α 1 of the blade refers to the angle of the blade to the tangent F1. Through the entrance angle that changes the blade, thereby the change gets into the air inlet direction of the air current between two adjacent blades, inject blade and tangent line F1's contained angle between 147 and 159, make the air current that enters into between two adjacent blades more smooth and easy, the velocity of flow of air current everywhere is more balanced in the passageway between two adjacent blades, avoid the air current disorder problem that leads to because of the air current velocity of flow is different, make the air current can flow steadily in the passageway between two adjacent blades, prevent the air current because of the energy waste that the disorder caused, be favorable to impeller assembly's impeller efficiency.
In one possible design, the exit angle α 2 of the blade is satisfied, 100 ° < α 2 < 130 °.
In this design, the exit angle of the blade refers to the angle of the blade from the tangent of the shaft bore. Specifically, a connecting line E2 is drawn between the axis passing through the shaft hole and the first end of the blade, the connecting line E2 has an intersection with the first end of the blade, and a circle c2 is drawn with the axis of the shaft hole as a center and the connecting line E2 as a radius. A tangent F2 to the circle c2 is drawn, the tangent F2 passing through the first end of the blade. The outlet angle α 2 of the blade refers to the angle of the blade to the tangent F2. Through the exit angle that changes the blade, thereby change the direction of airing exhaust by the combustion gas between two adjacent blades, inject blade and tangent line F2's contained angle between 100 and 130, make the air current can discharge the passageway between two adjacent blades more smoothly, avoid the blade to produce the hindrance to the air current discharge process, the velocity of flow of everywhere air current is more balanced in the passageway between two adjacent blades, avoid the air current disorder's that leads to because of the air current velocity of flow difference problem, make the air current can flow in the passageway between two adjacent blades steadily, prevent the air current because of the energy waste that the disorder caused, be favorable to impeller assembly's impeller efficiency.
Combining the inlet angle and the outlet angle can further improve the impeller efficiency of the impeller assembly.
In one possible design, the second end of the blade is spaced from the axis by a distance D2, such that D2/D1 is 0.55 ≦ D2 ≦ 0.65.
In this design, the second ends of the blades are spaced from the axis by a distance D2, the first ends of the blades are spaced from the axis by a distance D1, and the ratio of D2 to D1 is the hub ratio of the impeller assembly. The output wind pressure of the impeller assembly can be changed by changing the hub ratio of the impeller assembly. The hub ratio of the impeller assembly is defined between 0.55 and 0.65 so that the impeller assembly can vary the driving pressure on the airflow.
And, hub through impeller subassembly can also change the smooth and easy nature of the flow of air current between two adjacent blades than, with the hub of fan subassembly than inject in above-mentioned within range, make the air current discharge the passageway between two adjacent blades more smoothly, avoid the blade to produce the hindrance to the air current discharge process, the velocity of flow of air current everywhere in the passageway between two adjacent blades is more balanced, avoid the problem of the air current disorder that leads to because of the air current velocity of flow difference, make the air current can flow steadily in the passageway between two adjacent blades, prevent the air current because of the energy waste that the disorder caused, be favorable to impeller subassembly's impeller efficiency.
Combining the inlet angle, the outlet angle, and the hub ratio can further improve the impeller efficiency of the impeller assembly.
In one possible design, the number n of blades is such that 10. Ltoreq. N.ltoreq.14.
In this design, the number of vanes determines the cross-section of the inter-vane flow passage, and therefore, by changing the number of vanes, the shape of the flow passage between two adjacent vanes can be changed. The number of the blades is limited between 10 and 14, so that the air flow entering between two adjacent blades can flow more smoothly. The flow velocity of the air flow at each position in the channel between every two adjacent blades is more balanced, the problem of air flow disorder caused by different air flow velocity is avoided, energy waste caused by disorder of the air flow is prevented, and the impeller efficiency of the impeller assembly is facilitated.
In one possible design, the blades are arranged at an inclination compared to the radial direction of the shaft bore; the blades are pitched in a direction opposite to the direction of rotation of the impeller assembly.
In this design, the blades are pitched in the opposite direction to the direction of rotation of the impeller assembly, and therefore the impeller assembly takes the form of a rearward facing impeller. The impeller subassembly that adopts the form of backward impeller, the speed of the air current of department at the air outlet is less, and when the velocity of flow of air current was lower, the air current received the frictional force in wind channel just also less, consequently can reduce the air current by the air intake to the energy loss of air outlet's in-process, more the conversion of the shaft work that the drive disk assembly transmitted has been fan static pressure, fan static pressure is big more, the impeller subassembly can be with more energy transfer to air current. Under the same shaft power, the energy loss of the impeller component adopting the backward impeller form is smaller when the impeller component works, and the efficiency of the fan is favorably improved.
In one possible design, the impeller assembly further comprises: the upper cover is connected with the blades, and the bottom plate and the upper cover are positioned on two sides of the width direction of the blades.
In the design, the upper cover is added, so that the air inlet channel and the air outlet channel in the fan can be separated by the upper cover, and the backflow phenomenon of the air inlet and the air outlet can be reduced. Moreover, the upper cover can also form a rectification effect on the channel between two adjacent blades, so that the flow efficiency of the airflow in the channel between the blades is improved, the airflow can stably flow in the channel between the two adjacent blades, the energy waste caused by the turbulence of the airflow is prevented, and the impeller efficiency of the impeller assembly is facilitated.
In one possible design, any point on the first side of the blade is connected to the base plate and any point on the second side of the blade is connected to the cover plate along the width of the blade.
In this design, a first side of the blade is connected to the base plate and a second side of the blade is connected to the cover. Because along the radial in shaft hole, the width dimension of blade changes, consequently need design the shape of bottom plate and upper cover, can be according to the width of blade, the thickness of corresponding adjustment bottom plate and/or upper cover for everywhere homoenergetic of the first side of blade is closely laminated with the bottom plate, and everywhere homoenergetic of the second side of blade is closely laminated with the upper cover, thereby can form passageway between a plurality of relatively independent leaves, be favorable to improving the drive effect of impeller subassembly to the air current.
In one possible design, the impeller assembly further comprises: and the locking piece locks the blade on the bottom plate and the upper cover.
In this design, the blade can be through retaining member locking in bottom plate and upper cover, when the blade takes place to damage, can dismantle the blade to can maintain or change the blade alone, and need not wholly change impeller subassembly, be favorable to improving the maintenance convenience to impeller subassembly, and reduce the maintenance cost to impeller subassembly.
In one possible application, the retaining member may be a bolt or a pin.
In one possible design, the vanes are welded to the base plate and the top cover.
In the design, the blades can be welded on the bottom plate and the upper cover, so that the blades, the bottom plate and the upper cover can be independently processed, and after the blades, the bottom plate and the upper cover are processed and molded, the blades are fixed on the bottom plate and the upper cover in a welding mode. Through the mode of the processing of components of a whole that can function independently, be favorable to reducing the processing degree of difficulty to impeller subassembly.
In one possible design, the blades are integrally formed with the base plate and/or the upper cover.
In the design, the blades, the base plate and the upper cover are limited to be of an integrally formed structure, so that the blades, the base plate and the upper cover do not need to be processed respectively, the processing procedures of the impeller assembly can be reduced, the processing speed of the impeller assembly is improved, and the processing period is shortened.
In a second aspect, the present invention provides a centrifugal fan comprising: such as in any of the possible designs described above. Therefore, the centrifugal fan has the beneficial effects of the impeller assembly in any design, and the description is omitted.
In one possible design, the centrifugal fan further comprises: the impeller assembly is located in the shell.
In the design, the impeller assembly is positioned in the shell, an air inlet and an air outlet are formed in the shell, and the impeller assembly can drive airflow to flow into the shell from the air inlet and be discharged from the air outlet. The impeller assembly may be arranged to be removably attached to the housing, or welded to the housing.
Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.
Drawings
The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:
FIG. 1 shows a schematic structural view of an impeller assembly in an embodiment of the present invention;
FIG. 2 illustrates a structural schematic view from another perspective of an impeller assembly in an embodiment of the present invention;
fig. 3 shows a schematic structural view of a blade in an embodiment of the invention.
Wherein, the correspondence between the reference numbers and the component names in fig. 1 to 3 is:
100 bottom plate, 110 shaft hole, 200 blades and 300 upper cover.
Detailed Description
In order that the above objects, features and advantages of the present invention can be more clearly understood, a more particular description of the invention will be rendered by reference to the appended drawings. It should be noted that the embodiments and features of the embodiments of the present application may be combined with each other without conflict.
In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, however, the present invention may be practiced in other ways than those specifically described herein, and therefore the scope of the present invention is not limited by the specific embodiments disclosed below.
Impeller assemblies provided according to some embodiments of the present invention are described below with reference to fig. 1-3.
In some embodiments of the present invention, as shown in fig. 1, 2 and 3 in combination, there is provided an impeller assembly comprising: a base plate 100 and a plurality of blades 200, the base plate 100 being provided with a shaft hole 110; the plurality of blades 200 are arranged on the base plate 100, the plurality of blades 200 are distributed at intervals along the circumferential direction of the shaft hole 110, and the width of at least one part of the blades 200 is reduced towards the direction far away from the axis of the shaft hole 110; wherein, the width direction of the vane 200 and the axial direction of the shaft hole 110 are arranged in the same direction.
In the impeller assembly provided by this embodiment, the plurality of blades 200 are disposed on the bottom plate 100, the shaft hole 110 is formed on the bottom plate 100 by machining, and the output shaft of the driving part can be assembled with the shaft hole 110, so that the driving part can drive the bottom plate 100 to rotate, and the bottom plate 100 drives the plurality of blades 200 to rotate. The plurality of vanes 200, when rotated, can drive the airflow movement.
The width of at least a portion of the vane 200 is reduced in a direction away from the axis of the shaft hole 110, and the cross-sectional area of the passage between two adjacent vanes 200 is changed by changing the width of the vane 200, thereby preventing the swirl problem caused by the diffuser passage.
Specifically, assuming that the plane a is a plane parallel to the axis of the shaft hole 110, a plurality of flow cross sections can be obtained by cutting the passage between two adjacent blades 200 along the radial direction of the shaft hole 110 by a plurality of planes parallel to the plane a. In the related art, since the distance between two adjacent blades 200 is gradually increased and the width of the blades 200 is generally kept constant, the area of the flow cross section is also gradually increased, so that a diffuser passage is formed between two adjacent blades 200, and when the diffuser passage generates a vortex, the airflow is disturbed, so that the kinetic energy of partial airflows is mutually offset, and energy waste is caused. In the present invention, however, the flow cross-sectional area is varied by varying the width of the vanes 200. The flow cross section has an area equal to the length, which is the distance between two adjacent blades 200, multiplied by the width, which is the width of the blade 200. Therefore, as the spacing between two adjacent blades 200 increases, decreasing the width of the blades 200 can allow the area of the flow cross-section at different locations to vary less or remain substantially constant. Thereby avoid forming the diffusion passageway between two adjacent blades 200, prevent that the vortex region from appearing between two adjacent blades 200, reduce the emergence of backward flow phenomenon, avoid causing the condition of energy waste to take place because of the air current is disorderly, the work that blade 200 was done the air current can effectively be converted into the kinetic energy of air current, consequently can improve the impeller efficiency of impeller subassembly, is favorable to improving the amount of wind of the fan that uses impeller subassembly.
In one possible embodiment, as shown in conjunction with fig. 1, 2 and 3, at least a portion of the vane 200 tapers in width radially of the shaft bore 110 and away from the shaft axis.
In this embodiment, the trend of the width of the blade 200 is limited to be gradually reduced, as shown in fig. 3, and the angle of view in the figure illustrates that the top of the blade 200 is the first end of the blade, the bottom of the blade 200 is the second end of the blade 200, and the width of the blade is reduced from the second end of the blade 200 to the first end of the blade 200, which is only an exemplary illustration, and the specific structure of the blade 200 is not limited thereto. Specifically, in the direction away from the axis of the shaft hole 110, the distance between two adjacent blades 200 is gradually increased, and the width of the blades 200 is gradually decreased, so that the variation region of the distance between two adjacent blades 200 has substantially the same variation trend as the width of the blades 200, and further, the area of the flow cross section between two adjacent blades 200 can be changed slightly or kept substantially unchanged. Further avoid forming the diffusion passageway between two adjacent blades 200, prevent that the vortex region from appearing between two adjacent blades 200, reduce the emergence of backward flow phenomenon, avoid causing the condition of energy waste to take place because of the air current is disorderly, the work that blade 200 was done the air current can effectively be converted into the kinetic energy of air current, consequently can further improve the impeller efficiency of impeller subassembly, is favorable to improving the amount of wind of the fan that uses impeller subassembly.
As shown in connection with fig. 1, 2 and 3, in one possible embodiment, the first end of the blade 200 is spaced from the axis by a distance greater than the second end of the blade 200; let the width of the blade 200 be h, the distance from any point on the blade 200 except the first end to the axis of the shaft hole 110 be D, and the distance from the first end of the blade 200 to the axis be D1; h, D, D1 satisfies h =11.7+0.2 × 2 × (D1-D).
In this embodiment, the first end of the blade 200 is spaced from the axis of the shaft hole 110 by a distance greater than the distance between the second end of the blade 200 and the axis of the shaft hole 110, so that the first end of the blade 200 is spaced away from the axis of the shaft hole 110 and the second end of the blade 200 is proximate to the axis of the shaft hole 110. The width of the vane 200 is h, and the width of the vane 200 refers to a direction in which the vane 200 extends in the axial direction of the shaft hole 110. The distance from the first end of the blade 200 to the axis of the shaft hole 110 is D1, and the distance from the position other than the first end of the blade 200 to the axis of the shaft hole 110 is D. The width h of the vane 200, the distance D1 from the first end of the vane 200 to the axis of the shaft hole 110, and the distance D from the positions other than the first end of the vane 200 to the axis of the shaft hole 110 satisfy the following formula: h =11.7+0.2 × 2 × (D1-D). By defining the width h, the distance D1, and the distance D by the above-mentioned well-known method, the distance from the blade 200 to the axis of the shaft hole 110 is related to the width of the blade 200, so that the width of the blade 200 can be adjusted according to the distance from the blade 200 to the axis of the shaft hole 110. Further avoid forming the diffusion passageway between two adjacent blades 200, prevent that the vortex region from appearing between two adjacent blades 200, reduce the emergence of backward flow phenomenon, avoid causing the condition of energy waste to take place because of the air current is disorderly, the work that blade 200 was done the air current can effectively be converted into the kinetic energy of air current, consequently can further improve the impeller efficiency of impeller subassembly, is favorable to improving the amount of wind of the fan that uses impeller subassembly.
As shown in FIG. 1, in one possible embodiment, the inlet angle α 1 of the blade 200 is satisfied 147 ° < α 1 < 159 °.
In this embodiment, the inlet angle of the vane 200 refers to an angle between the vane 200 and a tangential direction of the shaft hole 110. Specifically, a connection line E1 passing through the axis of the shaft hole 110 and the second end of the vane 200 is made, the connection line E1 has an intersection with the second end of the vane 200, and a circle c1 is made with the axis of the shaft hole 110 as a center and the connection line E1 as a radius. A tangent F1 to the circle c1 is drawn, the tangent F1 passing through the second end of the blade 200. The inlet angle α 1 of the blade 200 refers to the angle of the blade 200 to the tangent F1. Through the entry angle that changes blade 200, thereby the change gets into the air inlet direction of the air current between two adjacent blades 200, inject blade 200 and tangent line F1's contained angle between 147 and 159, make the air current that enters into between two adjacent blades 200 more smooth and easy, the velocity of flow of the air current everywhere is more balanced in the passageway between two adjacent blades 200, avoid the air current disorder problem that leads to because of the air current velocity of flow is different, make the air current can flow steadily in the passageway between two adjacent blades 200, prevent the air current because of the energy waste that the disorder caused, be favorable to impeller assembly's impeller efficiency.
As shown in FIG. 1, in one possible embodiment, the exit angle α 2 of the blade 200 is satisfied with 100 ° < α 2 < 130 °.
In this embodiment, the outlet angle of the blade 200 refers to the angle between the blade 200 and the tangential direction of the shaft hole 110. Specifically, a connection line E2 is drawn through the axis of the shaft hole 110 and the first end of the vane 200, the connection line E2 has an intersection with the first end of the vane 200, and a circle c2 is drawn with the axis of the shaft hole 110 as a center and the connection line E2 as a radius. A tangent F2 to the circle c2 is drawn, the tangent F2 passing through the first end of the blade 200. The exit angle α 2 of the blade 200 refers to the angle of the blade 200 to the tangent F2. Through the exit angle that changes blade 200, thereby change by the direction of airing exhaust of exhaust gas between two adjacent blades 200, inject blade 200 and tangent line F2's contained angle between 100 and 130, make the air current can discharge the passageway between two adjacent blades 200 more smoothly, avoid blade 200 to produce the hindrance to the air current discharge process, the velocity of flow of air everywhere in the passageway between two adjacent blades 200 is more balanced, avoid the problem of the air current disorder because of the air current velocity of flow difference leads to, make the air current can flow in the passageway between two adjacent blades 200 steadily, prevent the air current because of the energy waste that the disorder caused, be favorable to impeller assembly's impeller efficiency.
Combining the inlet angle and the outlet angle can further improve the impeller efficiency of the impeller assembly.
As shown in FIG. 1, in one possible embodiment, the second end of the vane 200 is spaced from the axis by a distance D2, such that 0.55 ≦ D2/D1 ≦ 0.65.
In this embodiment, the second end of the blade 200 is spaced from the axis by a distance D2, the first end of the blade 200 is spaced from the axis by a distance D1, and the ratio of D2 to D1 is the hub ratio of the impeller assembly. The output wind pressure of the impeller assembly can be changed by changing the hub ratio of the impeller assembly. The hub ratio of the impeller assembly is defined between 0.55 and 0.65 so that the impeller assembly can vary the driving pressure on the airflow.
And, the hub ratio through the impeller subassembly can also change the smooth and easy nature of the flow of air current between two adjacent blades 200, the hub ratio with the fan subassembly is injectd in above-mentioned within range, make the air current discharge the passageway between two adjacent blades 200 more smoothly, avoid blade 200 to produce the hindrance to the air current discharge process, the velocity of flow of air current everywhere in the passageway between two adjacent blades 200 is more balanced, avoid the problem of the air current disorder because of the air current velocity of flow difference leads to, make the air current can flow steadily in the passageway between two adjacent blades 200, prevent the air current because of the energy waste that the disorder caused, be favorable to the impeller efficiency of impeller subassembly.
Combining the inlet angle, the outlet angle, and the hub ratio can further improve the impeller efficiency of the impeller assembly.
As shown in FIG. 1, in one possible embodiment, the number n of blades 200 is such that 10 ≦ n ≦ 14.
In this embodiment, the number of the blades 200 determines the cross-section of the inter-blade flow passage, and thus, by changing the number of the blades 200, the shape of the flow passage between two adjacent blades 200 can be changed. The number of the blades 200 is limited between 10 and 14, so that the air flow entering between two adjacent blades 200 can flow more smoothly. The flow velocity of the air flow at each position in the channel between every two adjacent blades 200 is more balanced, the problem of air flow disorder caused by different air flow velocity is avoided, energy waste caused by disorder of the air flow is prevented, and the impeller efficiency of the impeller assembly is facilitated.
As shown in FIG. 1, in one possible embodiment, the vanes 200 are disposed at an inclination with respect to the radial direction of the shaft hole 110; the blades 200 are inclined in a direction opposite to the rotation direction of the impeller assembly.
In this embodiment, the blades 200 are inclined in the opposite direction to the direction of rotation of the impeller assembly, which therefore takes the form of a rearward facing impeller. The impeller component in the form of the backward impeller is adopted, the speed of the air flow at the air outlet is low, when the flow speed of the air flow is low, the friction force of the air flow on the air channel is small, so that the energy loss of the air flow from the air inlet to the air outlet can be reduced, more shaft work transmitted by the driving part is converted into fan static pressure, and the fan static pressure is larger, so that the impeller component can transmit more energy to the air flow. Under the same shaft power, the energy loss of the impeller component adopting the backward impeller form is smaller when the impeller component works, and the efficiency of the fan is favorably improved.
In one possible embodiment, as shown in fig. 1 and 2, the impeller assembly further includes: and an upper cover 300, the upper cover 300 being connected to the plurality of blades 200, the base plate 100 and the upper cover 300 being located at both sides of the blades 200 in a width direction.
In this embodiment, by adding the upper cover 300, the upper cover 300 can separate the air inlet channel and the air outlet channel in the blower, so as to reduce the backflow phenomenon of the air inlet and the air outlet. Moreover, the upper cover 300 can also form a rectification effect on the channel between two adjacent blades 200, and improve the flow efficiency of the airflow in the inter-blade channel, so that the airflow can stably flow in the channel between two adjacent blades 200, thereby preventing the energy waste caused by the turbulence of the airflow and being beneficial to the impeller efficiency of the impeller assembly.
In a possible embodiment, any point of the first side of the blade 200 is connected to the base plate 100 and any point of the second side of the blade 200 is connected to the upper cover 300 along the width direction of the blade 200.
In this embodiment, a first side of the blade 200 is connected to the base plate 100, and a second side of the blade 200 is connected to the upper cover 300. Because along the radial of shaft hole 110, the width dimension of blade 200 changes, consequently need to design the shape of bottom plate 100 and upper cover 300, can be according to the width of blade 200, the thickness of corresponding adjustment bottom plate 100 and/or upper cover 300 for everywhere of the first side of blade 200 all can closely laminate with bottom plate 100, and everywhere of the second side of blade 200 all can closely laminate with upper cover 300, thereby can form a plurality of relatively independent passages between the leaf, be favorable to improving the drive effect of impeller subassembly to the air current.
In one possible embodiment, the impeller assembly further comprises: and a locker for locking the blade 200 to the base plate 100 and the upper cover 300.
In this embodiment, the vane 200 may be locked to the base plate 100 and the upper cover 300 by a locking member, and when the vane 200 is damaged, the vane 200 may be disassembled, so that the vane 200 may be maintained or replaced independently without replacing the entire vane assembly, which is advantageous to improve the convenience of maintenance of the vane assembly and reduce the maintenance cost of the vane assembly.
In one possible application, the retaining member may be a bolt or a pin.
In one possible embodiment, the blade 200 is welded to the base plate 100 and the upper cover 300.
In this embodiment, since the blade 200 can be welded to the base plate 100 and the upper cover 300, the blade 200, the base plate 100 and the upper cover 300 can be separately processed, and after the blade 200, the base plate 100 and the upper cover 300 are formed, the blade 200 is fixed to the base plate 100 and the upper cover 300 by welding. Through the mode of the processing of components of a whole that can function independently, be favorable to reducing the processing degree of difficulty to impeller subassembly.
In one possible embodiment, the blade 200 is integrally formed with the base plate 100 and/or the cover 300.
In this embodiment, the blades 200, the base plate 100 and the upper cover 300 are limited to be integrally formed, so that the blades 200, the base plate 100 and the upper cover 300 do not need to be separately processed, the number of processing steps for the impeller assembly can be reduced, the processing speed for the impeller assembly can be increased, and the processing cycle can be shortened.
In some embodiments of the present invention, a centrifugal fan is provided, comprising: such as the impeller assembly in any of the possible embodiments described above. Therefore, the centrifugal fan has the beneficial effects of the impeller assembly in any one of the above embodiments, which are not described in detail herein.
By adopting the impeller assembly, the static pressure of the fan of the centrifugal fan is improved by 32.23%, and the air quantity of the fan is improved by 47.45%. The impeller assembly in the above embodiments is applicable to all centrifugal fans.
In the centrifugal fan using the impeller assembly, the width of at least a portion of the blades 200 is reduced in a direction away from the axis of the shaft hole 110, and the sectional area of the passage between two adjacent blades 200 is changed by changing the width of the blade 200, thereby preventing the vortex problem caused by the diffuser passage. In the related art, since the distance between two adjacent blades 200 is gradually increased and the width of the blades 200 is generally kept constant, the area of the flow cross section is also gradually increased, so that a diffuser passage is formed between two adjacent blades 200, and when the diffuser passage generates a vortex, the airflow is disturbed, so that the kinetic energy of partial airflows is mutually offset, and energy waste is caused. In the present invention, however, the flow cross-sectional area is varied by varying the width of the vanes 200. The flow cross section has an area equal to the length, which is the distance between two adjacent blades 200, multiplied by the width, which is the width of the blade 200. Therefore, as the spacing between two adjacent blades 200 increases, decreasing the width of the blades 200 can allow the area of the flow cross-section at different locations to vary less or remain substantially constant. Thereby avoid forming the diffusion passageway between two adjacent blades 200, prevent that the vortex region from appearing between two adjacent blades 200, reduce the emergence of backward flow phenomenon, avoid causing the condition of energy waste to take place because of the air current is disorderly, the work that blade 200 was done the air current can effectively be converted into the kinetic energy of air current, consequently can improve the impeller efficiency of impeller subassembly, is favorable to improving the amount of wind of the fan that uses impeller subassembly.
In a possible embodiment, the centrifugal fan further comprises: the impeller assembly is located in the shell.
In this embodiment, the impeller assembly is located in the housing, the housing is provided with an air inlet and an air outlet, and the impeller assembly can drive the airflow to flow into the housing from the air inlet and to be discharged from the air outlet. The impeller assembly may be arranged to be removably attached to the housing, or welded to the housing.
In the present invention, the term "plurality" means two or more unless explicitly defined otherwise. The terms "mounted," "connected," "fixed," and the like are to be construed broadly, and for example, "connected" may be a fixed connection, a removable connection, or an integral connection; "coupled" may be direct or indirect through an intermediary. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
In the description herein, the description of the terms "one embodiment," "some embodiments," "specific embodiments," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (15)
1. An impeller assembly, comprising:
the bottom plate is provided with a shaft hole;
the blades are arranged on the bottom plate, are distributed at intervals along the circumferential direction of the shaft hole, and at least one part of the blades is reduced in width towards the direction far away from the axis of the shaft hole;
the width direction of the blade and the axial direction of the shaft hole are arranged in the same direction.
2. The impeller assembly of claim 1,
at least a portion of the blade tapers in width in a direction radially of the shaft bore and away from the axis.
3. The impeller assembly of claim 2,
the first end of the blade is spaced from the axis by a distance greater than the distance between the second end of the blade and the axis;
the width of the blade is set to be h,
the distance from any point on the blade except the first end to the axis of the shaft hole is D, and the distance from the first end of the blade to the axis is D1;
h, D, D1 satisfies h =11.7+0.2 × 2 × (D1-D).
4. The impeller assembly of claim 1,
the inlet angle alpha 1 of the blade is satisfied, 147 degrees < alpha 1 < 159 degrees.
5. The impeller assembly of claim 1,
the outlet angle alpha 2 of the blade is satisfied, and alpha 2 is more than 100 degrees and less than 130 degrees.
6. The impeller assembly of claim 3,
the distance between the second end of the blade and the axis is D2, and D2/D1 is more than or equal to 0.55 and less than or equal to 0.65.
7. The impeller assembly of claim 1,
the number n of the blades satisfies that n is more than or equal to 10 and less than or equal to 14.
8. The impeller assembly of claim 1,
the blades are arranged in a radial direction inclined relative to the shaft hole;
the blades are inclined in a direction opposite to the direction of rotation of the impeller assembly.
9. The impeller assembly of claim 1, further comprising:
the upper cover is connected with the blades, and the bottom plate and the upper cover are positioned on two sides of the width direction of the blades.
10. The impeller assembly of claim 9,
along the width direction of the blade, any point of the first side of the blade is connected with the bottom plate, and any point of the second side of the blade is connected with the upper cover.
11. The impeller assembly of claim 9, further comprising:
and the locking piece locks the blade to the bottom plate and the upper cover.
12. The impeller assembly of claim 9,
the blade is welded to the base plate and the upper cover.
13. The impeller assembly of claim 9,
the blades are integrally formed on the bottom plate and/or the upper cover.
14. A centrifugal fan, comprising:
an impeller assembly according to any one of claims 1 to 13.
15. The centrifugal fan of claim 14, further comprising:
a housing, the impeller assembly being located within the housing.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210909165.5A CN115289061A (en) | 2022-07-29 | 2022-07-29 | Impeller assembly and centrifugal fan |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210909165.5A CN115289061A (en) | 2022-07-29 | 2022-07-29 | Impeller assembly and centrifugal fan |
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| CN115289061A true CN115289061A (en) | 2022-11-04 |
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| CN202210909165.5A Pending CN115289061A (en) | 2022-07-29 | 2022-07-29 | Impeller assembly and centrifugal fan |
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|---|---|---|---|---|
| CN2718289Y (en) * | 2003-11-04 | 2005-08-17 | 陈阳宝 | Centrifugal fan without tapered vanes |
| CN101787985A (en) * | 2010-01-28 | 2010-07-28 | 北京理工大学 | Negative-pressure adsorption principle-based design method of centrifugal impeller of wall surface-moving robot |
| CN207975029U (en) * | 2018-03-01 | 2018-10-16 | 广东美的白色家电技术创新中心有限公司 | Centrifugal blower and dust catcher with it |
| CN209228698U (en) * | 2018-12-14 | 2019-08-09 | 黄石市粮丰机械有限公司 | A kind of energy-efficient cross-section flow passage impeller |
| CN210565316U (en) * | 2019-09-30 | 2020-05-19 | 广东顺德松达机电设备制造有限公司 | Novel impeller applied to small blower |
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2022
- 2022-07-29 CN CN202210909165.5A patent/CN115289061A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2718289Y (en) * | 2003-11-04 | 2005-08-17 | 陈阳宝 | Centrifugal fan without tapered vanes |
| CN101787985A (en) * | 2010-01-28 | 2010-07-28 | 北京理工大学 | Negative-pressure adsorption principle-based design method of centrifugal impeller of wall surface-moving robot |
| CN207975029U (en) * | 2018-03-01 | 2018-10-16 | 广东美的白色家电技术创新中心有限公司 | Centrifugal blower and dust catcher with it |
| CN209228698U (en) * | 2018-12-14 | 2019-08-09 | 黄石市粮丰机械有限公司 | A kind of energy-efficient cross-section flow passage impeller |
| CN210565316U (en) * | 2019-09-30 | 2020-05-19 | 广东顺德松达机电设备制造有限公司 | Novel impeller applied to small blower |
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