CN117307529A - Centrifugal fan blade, centrifugal fan and air conditioner - Google Patents
Centrifugal fan blade, centrifugal fan and air conditioner Download PDFInfo
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- CN117307529A CN117307529A CN202311480725.0A CN202311480725A CN117307529A CN 117307529 A CN117307529 A CN 117307529A CN 202311480725 A CN202311480725 A CN 202311480725A CN 117307529 A CN117307529 A CN 117307529A
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- 230000001133 acceleration Effects 0.000 claims abstract description 20
- 230000008859 change Effects 0.000 claims abstract description 14
- 238000009792 diffusion process Methods 0.000 claims description 17
- 230000007704 transition Effects 0.000 claims description 14
- 238000005192 partition Methods 0.000 claims description 10
- 230000002829 reductive effect Effects 0.000 abstract description 22
- 238000005265 energy consumption Methods 0.000 abstract description 13
- 238000000034 method Methods 0.000 abstract description 13
- 238000000926 separation method Methods 0.000 abstract description 13
- 230000008569 process Effects 0.000 abstract description 11
- 230000003068 static effect Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 230000036961 partial effect Effects 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 230000000670 limiting effect Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 229920003023 plastic Polymers 0.000 description 1
- 239000004033 plastic Substances 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000007789 sealing Methods 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
- F04D29/26—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 a centrifugal fan blade, a centrifugal fan and an air conditioner. The centrifugal fan blade comprises a plurality of blades, an airflow channel is formed between two adjacent blades, the airflow channel comprises a deceleration flow channel and an acceleration flow channel which are sequentially communicated along the airflow direction in the airflow channel, and the average flow velocity change ratio Vbb of the deceleration flow channel is [0.95,1]; and/or the average flow rate change ratio Vcc: vbb of the acceleration flow channel is in the numerical range of [1.7,1.9]. According to the centrifugal fan blade, the centrifugal fan and the air conditioner, the size of the gas flow channel and the flow velocity change ratio of the gas flow channel are reasonably set, so that gas is firstly decelerated and then accelerated when flowing through the gas flow channel, the inlet impact loss is reduced, the deceleration process and the flow velocity change of the acceleration process of the gas are reasonably set, the gas separation loss is reduced, the energy consumption of the centrifugal fan is reduced, the noise generated due to the gas separation loss can be reduced, and the comfort of the centrifugal fan is improved.
Description
Technical Field
The invention relates to the technical field of air treatment equipment, in particular to a centrifugal fan blade, a centrifugal fan and an air conditioner.
Background
With the continuous rising of the requirements of users on the performance of the air conditioner, products gradually develop to the trend of miniaturization, large cooling capacity and high static pressure, and under a limited structure, the fan is often accompanied with the increase of the air quantity demand, so that the use experience of the users is seriously influenced.
In the working process of the centrifugal fan, the air flow turning angle is larger, and larger inlet impact loss and blade profile separation loss are generally faced. To reduce inlet impact loss, a smaller blade inlet mounting angle needs to be matched, but a deceleration flow passage area of a blade inlet section and an average flow speed reduction ratio are larger, so that a subsequent acceleration flow passage is shorter, airflow cannot be accelerated greatly at a blade outlet, larger separation loss is generated, energy consumption of a centrifugal fan is increased, and noise is increased due to worsening noise.
Disclosure of Invention
In order to solve the technical problems of high energy consumption and high noise of the centrifugal fan in the prior art, the centrifugal fan blade, the centrifugal fan and the air conditioner are provided, wherein the air flow channel is reasonably designed so that the separation loss of air flow in the air flow channel between the blades is reduced to reduce the energy consumption and the noise.
The centrifugal fan blade comprises a plurality of blades, wherein an airflow channel is formed between two adjacent blades, the airflow channel comprises a deceleration flow passage and an acceleration flow passage which are sequentially communicated along the airflow direction in the airflow channel, the average flow rate change ratio Vbb of the deceleration flow passage is [0.95,1], wherein Vaa is the inlet flow rate of the deceleration flow passage, and Vbb is the outlet flow rate of the deceleration flow passage; and/or the average flow rate change ratio Vcc of the accelerating flow channel is [1.7,1.9], wherein Vcc is the inlet flow rate of the accelerating flow channel, and Vbb is the outlet flow rate of the decelerating flow channel.
The blade has a suction face and a pressure face with an inlet mounting angle beta Pressure inlet An inlet mounting angle beta greater than the suction surface Suction inlet 。
Inlet mounting angle beta of the pressure surface Pressure inlet Inlet mounting angle beta with the suction surface Suction inlet The difference range of (2) and (5)]。
The blade has a suction face and a pressure face with an outlet mounting angle beta Pressure outlet An outlet mounting angle beta greater than the suction surface Suction outlet 。
Outlet mounting angle beta of the pressure surface Pressure outlet An outlet mounting angle beta with the suction surface Suction outlet The difference range of (2) is [5 DEG, 8 DEG ]]。
Along the axial direction of the centrifugal fan blade, the centrifugal fan blade comprises a first fan blade part and a second fan blade part, the blades of the first fan blade part and the blades of the second fan blade part are arranged in a staggered mode, and the ratio range of the central angle delta corresponding to the two mutually staggered blades to the central angle theta corresponding to the airflow channel is [0.25,0.75].
A centrifugal fan comprises the centrifugal fan blade.
The centrifugal fan further comprises a volute, the volute comprises a front cover plate, a coaming and a rear cover plate which are sequentially arranged along the axial direction of the centrifugal fan blade, and a rotary cutting structure is formed at the on-line position of the front cover plate and the coaming and/or at the connection position of the rear cover plate and the coaming.
A chamfer is arranged at the connecting position of the front cover plate and the coaming, and the chamfer forms the rotary cutting structure; and/or the connection position of the rear cover plate and the coaming is provided with a chamfer, and the chamfer forms the rotary cutting structure.
The included angle between the plane of the chamfer and the plane of the front cover plate and/or the included angle between the plane of the chamfer and the plane of the rear cover plate is [45 degrees, 65 degrees ]; and/or the width H of the chamfer ranges from [20mm,40mm ].
The spiral case includes plane section, changeover portion and the diffusion section that connects gradually along the direction of rotation of centrifugal fan blade, rotary-cut structure set up in on the changeover portion.
One end of the rotary cutting structure is positioned at the connection position of the plane section and the transition section, and the other end of the rotary cutting structure is positioned at the connection position of the transition section and the diffusion section.
The centrifugal fan also comprises a partition tongue, and the partition tongue placement angle alpha 1 of the partition tongue is in an angle range of [10 degrees, 20 degrees ]; and/or an air outlet is arranged on the volute, and the angle range of a diffusion angle alpha 2 of the air outlet is [20 degrees, 30 degrees ]; and/or the volute is provided with a diffusion section, one end of the diffusion section forms an air outlet of the volute, and the numerical range of the inclination angle alpha 3 of the plane where the diffusion section is positioned and the horizontal plane is [5 degrees, 15 degrees ].
The minimum radial distance t between the centrifugal fan blade and the volute is in the numerical range of [6mm,12mm ].
An air conditioner comprises the centrifugal fan blade or the centrifugal fan.
According to the centrifugal fan blade, the centrifugal fan and the air conditioner, the size of the gas flow channel and the flow velocity change ratio of the gas flow channel are reasonably set, so that gas is firstly decelerated and then accelerated when flowing through the gas flow channel, the inlet impact loss is reduced, the deceleration process and the flow velocity change of the acceleration process of the gas are reasonably set, the gas separation loss is reduced, the energy consumption of the centrifugal fan is reduced, the noise generated due to the gas separation loss can be reduced, and the comfort of the centrifugal fan is improved.
Drawings
FIG. 1 is a schematic structural view of a centrifugal fan blade according to an embodiment of the present invention;
FIG. 2 is a partial schematic view of FIG. 1 at A;
FIG. 3 is another partial schematic view of FIG. 1 at A;
FIG. 4 is a side view of a centrifugal fan blade provided by an embodiment of the present invention;
FIG. 5 is a top view of a centrifugal fan blade provided by an embodiment of the present invention;
FIG. 6 is a schematic structural diagram of a centrifugal fan according to an embodiment of the present invention;
FIG. 7 is a schematic diagram of another structure of a centrifugal fan according to an embodiment of the present invention;
FIG. 8 is another schematic diagram of a centrifugal fan according to an embodiment of the present invention;
FIG. 9 is another schematic structural view of a centrifugal fan according to an embodiment of the present invention;
FIG. 10 is a graph of power versus a centrifugal fan according to an embodiment of the present invention;
FIG. 11 is a graph of noise curves of a centrifugal fan provided by an embodiment of the present invention versus a centrifugal fan of the prior art;
in the figure:
1. a blade; 11. an air flow channel; 12. a deceleration flow path; 13. acceleration flow path; 14. a suction surface; 15. a pressure surface; 21. a first fan blade section; 22. a second fan blade part; 31. a front cover plate; 32. coaming plate; 33. a back cover plate; 34. a rotary cutting structure; 35. a planar section; 36. a transition section; 37. a diffuser section; 4. the tongue is separated.
Detailed Description
The present invention will be described in further detail with reference to the drawings and examples, in order to make the objects, technical solutions and advantages of the present invention more apparent. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the invention.
In order that those skilled in the art will better understand the present invention, a technical solution in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in which it is apparent that the described embodiments are only some embodiments of the present invention, not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the present invention without making any inventive effort, shall fall within the scope of the present invention.
It should be noted that the terms "first," "second," and the like in the description and the claims of the present invention and the above figures are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order. It is to be understood that the terms so used are interchangeable under appropriate circumstances such that the embodiments of the invention described herein are, for example, capable of operation in other environments. Furthermore, the terms "comprises," "comprising," and "having," and any variations thereof, are intended to cover a non-exclusive inclusion, such that a process, method, system, article, or apparatus that comprises a list of steps or elements is not necessarily limited to those steps or elements expressly listed but may include other steps or elements not expressly listed or inherent to such process, method, article, or apparatus.
It should be noted that, in the description of the present invention, terms such as "upper," "lower," "left," "right," "inner," "outer," and the like indicate directions or positional relationships based on the directions or positional relationships shown in the drawings, which are merely for convenience of description, and do not indicate or imply that the apparatus or elements must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
Furthermore, it should be noted that, in the description of the present invention, unless explicitly specified and limited otherwise, the terms "mounted," "configured," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be directly connected, can be indirectly connected through an intermediate medium, and can also be communicated with the inside of two elements. The specific meaning of the above terms in the present invention can be understood by those skilled in the art according to the specific circumstances.
In the working process of the centrifugal fan, the air flow turning angle is larger, and larger inlet impact loss and blade profile separation loss are generally faced. To reduce inlet impingement losses, it is desirable to match smaller blade inlet mounting angles, but this results in a reduced flow path area for the blade inlet sectionAnd the average flow speed reduction ratio is larger, so that the subsequent acceleration flow channel is shorter, the airflow cannot obtain larger acceleration at the blade outlet, larger separation loss can be generated, the energy consumption of the centrifugal fan is increased, and the problem of noise increase caused by noise deterioration also exists. For this purpose, the present application provides a centrifugal fan blade as shown in fig. 1 to 11, comprising a plurality of blades 1, wherein an airflow channel 11 is formed between two adjacent blades 1, the airflow channel 11 comprises a deceleration flow channel 12 and an acceleration flow channel 13 which are sequentially communicated along the airflow direction in the airflow channel 11, and the average flow velocity variation ratio Vbb of the deceleration flow channel 12 is that the numerical range of Vaa is [0.95,1]]The Vaa is the inlet flow rate of the deceleration flow channel 12, vbb is the outlet flow rate of the deceleration flow channel 12, and the average flow rate change ratio is reasonably defined, so that the gas is reasonably decelerated in the process of entering the gas flow channel, thereby reducing the inlet impact loss, reducing the flow rate loss of the gas, providing guarantee for the accelerated flow of the gas flowing into the acceleration flow rate, and ensuring that the gas finally flowing out of the gas flow channel does not generate separation loss. The average flow rate change ratio Vcc/Vbb of the acceleration flow path 13 is in the range of [1.7,1.9]]The Vcc is the inlet flow rate of the acceleration flow channel 13, vbb is the outlet flow rate of the deceleration flow channel 12, or may be the inlet flow rate of the acceleration flow channel 13, so that the gas can be further accelerated in the acceleration flow channel 13, thereby further reducing the flow rate loss of the gas, avoiding the separation loss of the gas, and reducing the energy consumption requirement and the noise under the same requirement working condition. As shown in fig. 10, under the same demand conditions: static pressure of 50pa, 3200m 3 /h; the power of the prior art (old scheme) is 322W, and the power of the application (new scheme) only needs 286W, which is reduced by 11.2% (36W) compared with the power consumption of the prior art; as shown in fig. 11, under the same demand conditions: static pressure of 50pa, 3200m 3 /h; the noise of the prior art is 51.2dB, and the noise of the centrifugal fan is only 46.2dB, which is reduced by 9.8 percent (5.0 dB) compared with the noise of the prior art, that is, the centrifugal fan can achieve lower energy consumption and noise compared with the prior art, and the comfort of the centrifugal fan is effectively improved. Preferably, along the gas flow direction, the ratio range of the flow path length ab of the deceleration flow path 12 to the flow path length ac of the gas flow path 11 is [0.2,0.3 ], and the reasonable arrangement of the lengths of the deceleration flow path 12 and the acceleration flow path 13 can reduce the gas flow velocity loss, and can also improve the gas flow velocity at the outlet of the gas flow path 11 and improve the working efficiency of the centrifugal fan blade.
Here, aa is the inlet width of the gas flow channel, bb is the maximum width of the gas flow channel, cc is the outlet width of the gas flow channel, at this time, the ratio of the average flow rate variation ratio of the deceleration flow channel 12 is the ratio of aa to bb, and the ratio of the average flow rate variation ratio of the acceleration flow channel 13 is the ratio of cc to bb.
Further, the blade 1 has a suction surface 14 and a pressure surface 15, the inlet mounting angle β of the pressure surface 15 Pressure inlet Greater than the inlet mounting angle beta of the suction surface 14 Suction inlet . When the gas flows into the blade 1, the impact loss of the gas flow at the inlet of the gas flow channel can be reduced, the flow velocity loss of the gas is reduced, the final gas flow velocity can be ensured by the centrifugal fan blade through smaller energy consumption, and the purposes of reducing the energy consumption and noise of the centrifugal fan blade are achieved. Specifically, the inlet mounting angle β of the pressure surface 15 Pressure inlet Inlet mounting angle beta to the suction side 14 Suction inlet The difference range of (2) and (5)]. By constraining the inlet mounting angle beta of the pressure face 15 of the blade 1 Pressure inlet And an inlet mounting angle beta of suction side 14 Suction inlet The area change rule of the gas flow passage inlet can be reasonably controlled, unreasonable setting of the thickness of the blade 1 is prevented, breakage caused by stress concentration is avoided, and the working reliability of the centrifugal fan blade is ensured.
Likewise, the blade 1 has a suction surface 14 and a pressure surface 15, the outlet mounting angle β of the pressure surface 15 Pressure outlet Greater than the outlet mounting angle beta of the suction surface 14 Suction outlet . When the gas flows out of the blade 1, the separation loss of the gas flow can be reduced on the premise of higher gas flow rate, namely the final gas flow rate can be ensured, the noise generated by the separation loss can be reduced, and the energy consumption of the centrifugal blade can be reducedAnd noise. Specifically, the outlet mounting angle β of the pressure surface 15 Pressure outlet Outlet mounting angle beta with said suction surface 14 Suction outlet The difference range of (2) is [5 DEG, 8 DEG ]]. By constraining the outlet mounting angle beta of the pressure face 15 of the blade 1 Pressure outlet And an outlet mounting angle beta of suction side 14 Suction outlet The area change rule at the outlet of the gas flow passage can be reasonably controlled, the unreasonable arrangement of the thickness of the blade 1 is prevented, the breakage caused by stress concentration is avoided, and the working reliability of the centrifugal fan blade is ensured.
The installation angle of the blade 1 refers to an included angle between the tangential direction of the line 1 of the blade at the corresponding position of the gas flow channel and the circumferential rotation reverse direction of the centrifugal blade, and can also be expressed as an included angle between the impeller circle of the centrifugal blade and the tangential line of the line 1 of the blade at the same point. At the inlet mounting angle beta of the pressure surface 15 of the blade 1 Pressure inlet For example, it refers to the angle between the tangential direction of the line of the pressure surface 15 of the blade 1 at the inlet of the gas flow channel (point a) and the direction opposite to the circumferential rotation of the centrifugal blade.
Along the axial direction of the centrifugal fan blade, the centrifugal fan blade comprises a first fan blade part 21 and a second fan blade part 22, the blades 1 of the first fan blade part 21 and the blades 1 of the second fan blade part 22 are arranged in a staggered mode, and the ratio range of the central angle delta corresponding to the two mutually staggered blades 1 to the central angle theta corresponding to the airflow channel 11 is [0.25,0.75]. Through carrying out the dislocation setting with the blade 1 of first fan blade portion 21 and the blade 1 of second fan blade portion 22, can satisfy the drawing of patterns requirement when moulding plastics the centrifugal fan blade, still can stagger the time difference that the air current on two fan blade portions impacted the partition tongue through the dislocation setting, avoid noise peak value to accumulate on single frequency to the tone quality and the noise of effectual reduction centrifugal fan blade.
A centrifugal fan comprises the centrifugal fan blade.
The centrifugal fan further comprises a volute, the volute comprises a front cover plate 31, a coaming 32 and a rear cover plate 33 which are sequentially arranged along the axial direction of the centrifugal fan blade, an air inlet for sucking air of the centrifugal fan is formed in the front cover plate 31, the rear cover plate 33 is of a flat plate structure for sealing, the coaming 32 is bent to form a curved surface shape, two ends of the curved surface are provided with air outlets which are spaced to form the volute, so that after the air enters from the front cover plate 31, the air can flow along the shape enclosed by the coaming 32 under the action of the centrifugal fan blade, and finally is discharged from the air outlets. The joints of the front cover plate 31 and the coaming 32 and the joints of the rear cover plate 33 and the coaming 32 in the prior art are all connected at right angles, when gas flows through the right angle positions, turbulence is generated to cause flow velocity and pressure loss, therefore, the on-line positions of the front cover plate 31 and the coaming 32 and/or the joint positions of the rear cover plate 33 and the coaming 32 are formed with rotary cut structures 34, the right angle structures in the prior art are changed by utilizing the rotary cut structures 34, so that the gas flow can flow along the rotary cut structures 34 when flowing through the rotary cut structures 34 to avoid the problem of turbulence, the flow velocity and pressure loss in the process of flowing in the volute is reduced, and the working efficiency of the centrifugal fan is ensured. As an implementation manner, the connection position of the front cover plate 31 and the coaming 32 is provided with a chamfer, the chamfer forms the rotary cutting structure 34, the connection position of the front cover plate 31 and the coaming 32 is adjusted to be a plane structure by a right-angle structure in the prior art, the included angle of the connection position of the chamfer part and the front cover plate 31 and the included angle of the connection position of the chamfer part and the coaming 32 are obtuse angles, and turbulence of gas can be effectively avoided at the connection position, so that the purposes of reducing the flow speed and the pressure loss of the gas in the spiral case in the flowing process of the gas, reducing the energy consumption of the centrifugal fan and guaranteeing the working efficiency of the centrifugal fan are achieved; likewise, a chamfer is provided at the connection position of the back cover plate 33 and the coaming plate 32, and the chamfer constitutes the rotary cutting structure 34. The connection position of the back cover plate 33 and the coaming 32 is adjusted to be a plane structure by a right-angle structure in the prior art, and the included angle at the connection position of the chamfer part and the back cover plate 33 and the included angle at the connection position of the chamfer part and the coaming 32 are obtuse angles, so that turbulence of gas can be effectively avoided, the loss of flow speed and pressure of the gas in the volute is reduced, the energy consumption of the centrifugal fan is reduced, and the working efficiency of the centrifugal fan is guaranteed. Preferably, the included angle between the plane of the chamfer and the plane of the front cover plate 31 is [45 °,65 ° ], so as to ensure the air guiding effect of the rotary cutting structure 34. Likewise, the included angle between the plane of the chamfer and the plane of the rear cover plate 33 is [45 °,65 ° ], so as to ensure the air guiding effect of the rotary cutting structure 34; in order to avoid the greater influence of the rotary cutting structure 34 on the flow of the gas in the volute, the numerical range of the width H of the chamfer is [20mm,40mm ], and at the moment, the chamfer can only guide the gas flowing through the right-angle structure in the prior art, but can not influence the gas in the central part of the volute, so that the working efficiency of the centrifugal fan is ensured.
Along the rotation direction of the centrifugal fan blade, the volute comprises a plane section 35, a transition section 36 and a diffusion section 37 which are sequentially connected, gas entering the centrifugal fan can rotate and flow under the rotation of the centrifugal fan blade, the flow direction of the gas sequentially passes through the transition section 36 and the diffusion section 37, part of the gas can flow through the plane section 35 and then flow to the transition section 36 in the same way, that is, the gas flowing in the volute can flow through the transition section 36 and needs to flow in a turning way under the diversion effect of the transition section 36, and therefore, the rotary cutting structure 34 is arranged on the transition section 36, the influence of the transition section 36 on the gas flow is reduced as much as possible, and the working reliability of the centrifugal fan is improved. Preferably, one end of the rotary cutting structure 34 is located at the connection position between the plane section 35 and the transition section 36, and the other end is located at the connection position between the transition section 36 and the diffuser section 37, so that the size of the rotary cutting structure 34 is increased as much as possible, and the influence of the right-angle structure on the gas flow is reduced.
The centrifugal fan also comprises a partition tongue 4, wherein the partition tongue placement angle alpha 1 of the partition tongue 4 is in an angle range of [10 degrees, 20 degrees ]; and/or an air outlet is arranged on the volute, and the angle range of a diffusion angle alpha 2 of the air outlet is [20 degrees, 30 degrees ]; and/or the volute is provided with a diffuser section 37, one end of the diffuser section 37 forms an air outlet of the volute, and the numerical range of the inclination angle alpha 3 of the plane where the diffuser section 37 is positioned and the horizontal plane is [5 degrees, 15 degrees ]. The spiral case is used for centralizing and guiding the gas leaving the centrifugal fan blade and converting part of kinetic energy diffusion of the gas flowing through the spiral case into static pressure, wherein the spiral case parameters are as follows: the preferred ranges of the volute tongue position angle alpha 1, the diffusion angle alpha 2 of the air outlet and the inclination angle alpha 3 of the plane where the diffusion section 37 is positioned and the horizontal plane are the optimal parameter designs matched with the centrifugal fan blade, wherein any one of the parameters exceeding the optimal parameter designs can deteriorate the performance parameters such as the power, noise, static pressure capacity and the like of the whole centrifugal fan, so that the working efficiency of the centrifugal fan is reduced.
The minimum radial distance t between the centrifugal fan blade and the volute is in the numerical range of [6mm,12mm ]. The interval can ensure that the centrifugal fan blade can not interfere with the volute, and can also avoid the phenomenon that partial airflow can not flow due to overlarge interval between the centrifugal fan blade and the volute, thereby influencing the working efficiency of the centrifugal fan.
An air conditioner comprises the centrifugal fan blade or the centrifugal fan.
The foregoing examples illustrate only a few embodiments of the invention and are described in detail herein without thereby limiting the scope of the invention. It should be noted that it will be apparent to those skilled in the art that several variations and modifications can be made without departing from the spirit of the invention, which are all within the scope of the invention. Accordingly, the scope of protection of the present invention is to be determined by the appended claims.
Claims (15)
1. The utility model provides a centrifugal fan blade which characterized in that: the device comprises a plurality of blades (1), wherein an airflow channel (11) is formed between two adjacent blades (1), the airflow channel (11) comprises a deceleration flow channel (12) and an acceleration flow channel (13) which are sequentially communicated along the airflow direction in the airflow channel (11), the average flow rate change ratio Vbb of the deceleration flow channel (12) is [0.95,1] in the numerical range of Vaa, wherein Vaa is the inlet flow rate of the deceleration flow channel (12), and Vbb is the outlet flow rate of the deceleration flow channel (12); and/or the average flow rate change ratio Vcc of the acceleration flow channel (13) is [1.7,1.9], wherein Vcc is the inlet flow rate of the acceleration flow channel (13), and Vbb is the outlet flow rate of the deceleration flow channel (12).
2. The centrifugal fan blade according to claim 1, wherein: the blade (1) has a suction surface (14) and a pressure surface (15), the inlet mounting angle beta of the pressure surface (15) Pressure inlet Is greater than the inlet mounting angle beta of the suction surface (14) Suction inlet 。
3. The centrifugal fan blade according to claim 2, wherein: inlet mounting angle beta of the pressure surface (15) Pressure inlet Inlet mounting angle beta to the suction surface (14) Suction inlet The difference range of (2) and (5)]。
4. The centrifugal fan blade according to claim 1, wherein: the blade (1) has a suction surface (14) and a pressure surface (15), the outlet mounting angle beta of the pressure surface (15) Pressure outlet Is greater than the outlet mounting angle beta of the suction surface (14) Suction outlet 。
5. The centrifugal fan blade according to claim 4, wherein: the outlet mounting angle beta of the pressure surface (15) Pressure outlet An outlet mounting angle beta to the suction surface (14) Suction outlet The difference range of (2) is [5 DEG, 8 DEG ]]。
6. The centrifugal fan blade according to claim 1, wherein: along the axis direction of the centrifugal fan blade, the centrifugal fan blade comprises a first fan blade part (21) and a second fan blade part (22), the blades (1) of the first fan blade part (21) and the blades (1) of the second fan blade part (22) are arranged in a staggered mode, and the ratio range of the central angle delta corresponding to the two mutually staggered blades (1) to the central angle theta corresponding to the airflow channel (11) is [0.25,0.75].
7. A centrifugal fan, characterized in that: comprising a centrifugal fan blade according to any of claims 1 to 6.
8. The centrifugal fan according to claim 7, wherein: the centrifugal fan further comprises a volute, the volute comprises a front cover plate (31), a coaming (32) and a rear cover plate (33) which are sequentially arranged along the axial direction of the centrifugal fan blade, and a rotary cutting structure (34) is formed at the online position of the front cover plate (31) and the coaming (32) and/or at the connecting position of the rear cover plate (33) and the coaming (32).
9. The centrifugal fan according to claim 8, wherein: a chamfer is arranged at the connecting position of the front cover plate (31) and the coaming (32), and the chamfer forms the rotary cutting structure (34); and/or, the connection position of the rear cover plate (33) and the coaming plate (32) is provided with a chamfer, and the chamfer forms the rotary cutting structure (34).
10. The centrifugal fan according to claim 9, wherein: the included angle between the plane of the chamfer and the plane of the front cover plate (31) and/or the included angle between the plane of the chamfer and the plane of the rear cover plate (33) is [45 degrees, 65 degrees ]; and/or the width H of the chamfer ranges from [20mm,40mm ].
11. The centrifugal fan according to claim 8, wherein: along the direction of rotation of centrifugal fan blade, the spiral case includes planar segment (35), changeover portion (36) and diffuser (37) that connect gradually, rotary-cut structure (34) set up in on changeover portion (36).
12. The centrifugal fan according to claim 11, wherein: one end of the rotary cutting structure (34) is positioned at the connecting position of the plane section (35) and the transition section (36), and the other end of the rotary cutting structure is positioned at the connecting position of the transition section (36) and the diffusion section (37).
13. The centrifugal fan according to claim 8, wherein: the centrifugal fan also comprises a partition tongue (4), wherein the partition tongue placement angle alpha 1 of the partition tongue (4) is in an angle range of [10 DEG, 20 DEG ]; and/or an air outlet is arranged on the volute, and the angle range of a diffusion angle alpha 2 of the air outlet is [20 degrees, 30 degrees ]; and/or the volute is provided with a diffusion section (37), one end of the diffusion section (37) forms an air outlet of the volute, and the value range of the inclination angle alpha 3 of the plane where the diffusion section (37) is positioned and the horizontal plane is [5 degrees, 15 degrees ].
14. The centrifugal fan according to claim 8, wherein: the minimum radial distance t between the centrifugal fan blade and the volute is in the numerical range of [6mm,12mm ].
15. An air conditioner, characterized in that: comprising a centrifugal fan blade according to any of claims 1 to 7 or a centrifugal fan according to any of claims 8 to 14.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311480725.0A CN117307529A (en) | 2023-11-08 | 2023-11-08 | Centrifugal fan blade, centrifugal fan and air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311480725.0A CN117307529A (en) | 2023-11-08 | 2023-11-08 | Centrifugal fan blade, centrifugal fan and air conditioner |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN117307529A true CN117307529A (en) | 2023-12-29 |
Family
ID=89237519
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202311480725.0A Pending CN117307529A (en) | 2023-11-08 | 2023-11-08 | Centrifugal fan blade, centrifugal fan and air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN117307529A (en) |
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2023
- 2023-11-08 CN CN202311480725.0A patent/CN117307529A/en active Pending
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