CN117287417A - Fan blade assembly and air conditioning unit - Google Patents
Fan blade assembly and air conditioning unit Download PDFInfo
- Publication number
- CN117287417A CN117287417A CN202311585222.XA CN202311585222A CN117287417A CN 117287417 A CN117287417 A CN 117287417A CN 202311585222 A CN202311585222 A CN 202311585222A CN 117287417 A CN117287417 A CN 117287417A
- Authority
- CN
- China
- Prior art keywords
- fan blade
- guide ring
- section
- straight line
- wheel cover
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000004378 air conditioning Methods 0.000 title claims abstract description 8
- 230000002829 reductive effect Effects 0.000 claims abstract description 67
- 230000007704 transition Effects 0.000 claims description 18
- 230000003014 reinforcing effect Effects 0.000 claims description 13
- 230000004323 axial length Effects 0.000 claims description 12
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 12
- 230000007423 decrease Effects 0.000 claims description 8
- 238000000034 method Methods 0.000 abstract description 9
- 230000008569 process Effects 0.000 abstract description 7
- 230000000694 effects Effects 0.000 description 24
- 230000009471 action Effects 0.000 description 5
- 230000000670 limiting effect Effects 0.000 description 5
- 230000000903 blocking effect Effects 0.000 description 4
- 230000008859 change Effects 0.000 description 4
- 230000036961 partial effect Effects 0.000 description 3
- 230000000630 rising effect Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 239000000243 solution Substances 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 238000009825 accumulation Methods 0.000 description 1
- 230000004888 barrier function Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000003116 impacting effect Effects 0.000 description 1
- 238000001746 injection moulding Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000001151 other effect Effects 0.000 description 1
- 238000002360 preparation method Methods 0.000 description 1
- 238000005728 strengthening Methods 0.000 description 1
- 239000013589 supplement Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
- F04D29/444—Bladed diffusers
-
- 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
-
- 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
-
- 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
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
- F24F1/0047—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in the ceiling or at the ceiling
Abstract
The invention provides a fan blade assembly and an air conditioning unit. The fan blade component comprises fan blades; the guide ring is positioned on the air inlet side of the fan blade, and part of the guide ring extends into the fan blade; the protruding structures are arranged on the outer wall of the guide ring, the protruding structures are located outside the fan blade, a leakage channel is formed between two adjacent protruding structures, and one end of the leakage channel faces the fan blade. According to the fan blade assembly and the air conditioner unit, the protruding structure is arranged on the outer wall of the guide ring, gaps between the outer wall of the guide ring and the wheel cover of the fan blade are filled by the protruding structure, so that leakage loss between the wheel cover and the guide ring is reduced, turbulent flow intensity generated in the process of intersection of leakage air flow and main flow is weakened, impact loss of an inlet of the fan blade is reduced, and the purposes of improving performance and efficiency of a fan system and reducing noise of the fan assembly are achieved.
Description
Technical Field
The invention relates to the technical field of air driving equipment, in particular to a fan blade assembly and an air conditioning unit.
Background
The air conditioner body is arranged between gaps of indoor ceiling plates, and a panel for air inlet and outlet is embedded on the ceiling. The installation of the air conditioner of the courtyard machine can save space and is attractive and popular with consumers. The air conditioner of the courtyard machine adopts a backward centrifugal fan blade, and a guide ring is usually arranged at the inlet of the fan blade so as to improve the flow uniformity of inlet airflow. Because the air flow is changed from axial flow to radial flow, the flow at the tail end of the guide ring and the blade wheel cover is extremely turbulent, on one hand, the gap exists between the guide ring and the blade wheel cover to cause leakage, the air flow flows back to form larger leakage loss, and on the other hand, the leakage air flow is converged into the front edge of the main flow impact blade to cause impact loss, so that the flow resistance is aggravated, and the problems of power consumption rising and noise increasing of the centrifugal blade exist.
Disclosure of Invention
In order to solve the technical problems of power consumption rising and noise increasing of centrifugal fan blades caused by leakage air flow between a guide ring and a wheel cover in the prior art, a fan blade assembly and an air conditioner unit are provided, wherein a protruding structure is arranged on the outer wall of the guide ring so as to reduce leakage loss and impact noise of the leakage air flow to the blades.
A fan blade assembly, comprising:
a fan blade;
the guide ring is positioned on the air inlet side of the fan blade, and part of the guide ring extends into the fan blade;
the protruding structures are arranged on the outer wall of the guide ring, the protruding structures are located outside the fan blade, a leakage channel is formed between two adjacent protruding structures, and one end of the leakage channel faces the fan blade.
And the flow area of the leakage channel is gradually reduced along the direction approaching to the fan blade.
The convex structure is provided with a first end far away from the fan blade and a second end close to the fan blade, and the width of the convex structure is gradually increased along the direction from the first end to the second end; and/or the value range of the width n1 of the first end is t2 to 3t2, and t2 is the wall thickness of the inner part of the fan blade, which extends into the fan blade, of the guide ring; and/or the width n2 of the second end ranges from 1.2n1 to 2n1.
The distance n3 between the end part of the protruding structure, which is close to the fan blade, and the fan blade ranges from 1.2t2 to 2.2t2, and t2 is the wall thickness of the inner part of the guide ring, which extends into the fan blade.
The fan blade assembly further comprises a reinforcing structure, the reinforcing structure is arranged at the end part of the protruding structure, which faces towards the fan blade, the distance n3 is formed between the end part of the protruding structure, which is far away from the protruding structure, and the fan blade, and the thickness n6 of the reinforcing structure is in the numerical range of t2 to 1.5t2.
The height of the protruding structure is increased and then decreased along the direction close to the fan blade, the numerical range of the maximum height n5 of the protruding structure is 2.2t2 to 4.2t2, and t2 is the wall thickness of the guide ring extending into the inner part of the fan blade; and/or the numerical range of the distance n4 between the highest point of the convex structure and the fan blade is 4t2 to 8t2, and t2 is the wall thickness of the guide ring extending into the inner part of the fan blade.
Along the direction that is close to the fan blade, protruding structure includes gradually high section and gradually low section, gradually high section with gradually the junction of low section constitutes protruding structure's highest point, gradually low section keep away from the plane that the side of water conservancy diversion circle is located with gradually high section keep away from the numerical value range of the contained angle θ4 between the plane that the side of water conservancy diversion circle is located is 110 ~ 130.
The side surface of the gradually-increasing section, which is far away from the guide ring, is an arc surface, and an included angle theta 4 is formed between a tangent plane of the arc surface at the highest point of the protruding structure and a plane of the side surface of the gradually-decreasing section, which is far away from the guide ring.
The middle line of the convex structure is an arc line, the radius R of the middle line is in a numerical range of 0.55R3 to 0.75R3, and R3 is the radius of the end part of the guide ring extending into the fan blade; and/or the convex structure is provided with a first end far away from the fan blade and a second end close to the fan blade, and the numerical range of the included angle theta 3 between the connecting line of the end point of the first end and the end point of the second end and the central axis of the guide ring is 10-20 degrees.
The numerical range of an included angle gamma formed by two adjacent protruding structures at the central axis of the guide ring is 3-6 degrees.
The inner wall of the guide ring is provided with guide grooves, and the guide grooves correspond to the protruding structures one by one.
The depth of the diversion groove gradually increases along the gas flow direction; and/or the maximum depth m3 of the guide groove ranges from 0.2t2 to 0.4t2, and t2 is the wall thickness of the guide ring extending into the inner part of the fan blade.
The width of the diversion groove gradually increases along the gas flow direction; and/or the width m1 of the inlet of the diversion groove ranges from 0.8t2 to 2t2; and/or the width m2 of the outlet of the diversion groove ranges from 1.5m1 to 2.5m1.
The middle line of the guide groove is an arc line, the radius R of the middle line is in a numerical range of 0.55R3 to 0.75R3, and R3 is the radius of the guide ring extending into the end part of the fan blade; and/or the diversion groove is provided with a first end far away from the fan blade and a second end close to the fan blade, and the numerical range of the included angle theta 3 between the connecting line of the end point of the first end and the end point of the second end and the central axis of the diversion ring is 10-20 degrees.
Along the gas flow direction, the water conservancy diversion circle is including the first straightway, second changeover portion and the second straightway of intercommunication in proper order, part the second straightway is located the inside of fan blade, just protruding structure set up in the outer wall of second changeover portion with on the outer wall of second straightway.
The numerical range of the length c of the second straight line segment extending into the fan blade is 0.5a to 0.7a, the length c is more than or equal to 2t1, a is the length of the straight line segment of the wheel cover of the fan blade, and t1 is the wall thickness of the wheel cover of the fan blade; and/or the gap w between the second straight line segment and the straight line segment of the wheel cover of the fan blade ranges from 2.5t1 to 3.5t1.
The guide ring further comprises a plane guide section, the plane guide section is arranged at one end of the first straight line section, which is far away from the second transition section, the numerical range of the distance h between the plane guide section and the end part of the second straight line section, which is far away from the second transition section, is 0.37R3-0.45R3, and R3 is the radius of the second straight line section.
The value range of the axial length h1 of the second straight line segment is 0.26h to 0.34h; and/or the axial length h2 of the second transition section ranges from 0.3h to 0.38h; and/or the axial length h3 of the first straight line segment ranges from 0.28h to 0.36h.
Along the gas flow direction, the flow area of the second straight line segment gradually decreases, and the numerical range of an included angle theta 1 between the molded line of the second straight line segment and the outlet end face of the second straight line segment is 90.5-92 degrees; along the gas flow direction, the flow area of the first straight line segment gradually decreases, and the value range of an included angle theta 2 between the molded line of the first straight line segment and the outlet end face of the first straight line segment is 135-145 degrees.
The fan blade comprises a blade and a wheel cover, the wheel cover is arranged at one end of the blade, which faces the guide ring, the wheel cover comprises a wheel cover straight line section and a wheel cover arc section which are sequentially connected, the connection position of the wheel cover straight line section and the wheel cover arc section is positioned between the blade and the guide ring, part of the wheel cover straight line section surrounds the periphery of the end part of the guide ring, the diameter of the wheel cover arc section gradually increases along the direction away from the wheel cover straight line section, and the numerical range of the arc radius R2 of the wheel cover arc section is 0.15R1-0.23R1; and/or the axial length a of the straight wheel cover section is in a numerical range of 0.31R2 to 0.39R2; and/or the distance b between the highest point of the blade and the end face of the straight line section of the wheel cover, which is close to the guide ring, ranges from 0.55R2 to 0.63R2.
An air conditioning unit comprises the fan blade assembly.
According to the fan blade assembly and the air conditioning unit, the protruding structures are arranged on the outer wall of the guide ring, gaps between the outer wall of the guide ring and the wheel cover of the fan blade are filled by the protruding structures, so that leakage loss between the wheel cover and the guide ring is reduced, turbulent flow intensity generated in the process of intersection of leakage air flow and main flow is weakened, impact loss of the fan blade inlet is reduced, leakage channels are formed between the protruding structures, the leakage air flow is forced to flow through the leakage channels, turbulent flow area generated by the leakage air flow is limited, intersection influence of the turbulent flow on the main flow is further limited, impact loss of the fan blade inlet is reduced, meanwhile, due to the limitation of the leakage channels on the leakage air flow, impact range of the leakage air flow on the front edge of the fan blade is reduced, air flow noise is reduced, and the purposes of improving performance and efficiency of a fan system and reducing noise of the fan assembly are achieved.
Drawings
FIG. 1 is a schematic structural diagram of a fan blade assembly according to an embodiment of the present invention;
FIG. 2 is a cross-sectional view of a fan blade assembly according to an embodiment of the present invention;
FIG. 3 is a top view of a fan blade assembly according to an embodiment of the present invention;
FIG. 4 is a schematic view of another structure of a fan blade assembly according to an embodiment of the present invention;
FIG. 5 is a partial schematic view of FIG. 4 at A;
FIG. 6 is a schematic view of another structure of a fan blade assembly according to an embodiment of the present invention;
FIG. 7 is a partial schematic view of FIG. 6 at B;
FIG. 8 is a schematic structural diagram of a deflector ring according to an embodiment of the present invention;
FIG. 9 is a partial schematic view at C of FIG. 8;
FIG. 10 is a schematic view of another structure of a deflector ring according to an embodiment of the present invention;
FIG. 11 is a graph illustrating the power of a fan blade assembly and a centrifugal fan blade according to an embodiment of the present invention;
FIG. 12 is a graph showing the noise between a fan blade assembly and a centrifugal fan blade according to an embodiment of the present invention;
in the figure:
1. a fan blade; 2. a guide ring; 3. a bump structure; 31. a leakage path; 4. a reinforcing structure; 32. a gradually higher section; 33. a lower section; 5. a flow guiding groove; 21. a first straight line segment; 22. a second transition section; 23. a second straight line segment; 24. a planar flow guiding section; 11. a blade; 12. wheel cover; 121. a wheel cover straight line section; 122. arc segments of the wheel cover.
Description of the embodiments
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.
The centrifugal fan blade in the prior art refers to a fan blade which is axially air-in, radially air-out and uses centrifugal force to do work so as to improve the pressure of air. The fan blade rotates anticlockwise under the drive of the motor, negative pressure is generated at the inlet end of the fan blade, and air flow is continuously sucked; an airflow channel is formed between the wheel cover and the wheel disc, and airflow axially enters the channel and is thrown out radially under the action of centrifugal force. An air inlet is formed at the wheel cover of the fan blade in the centrifugal fan blade, when the fan blade rotates, air flow is sucked from the air inlet of the fan blade, meanwhile, the fan blade rotates to exert a power action on the air flow, the pressure and the speed of the air are improved, and the air flow is discharged along the air outlet of the blade flow channel between the fan blades in the fan blade under the action of the centrifugal force. The inlet of the fan blade is usually provided with a guide ring so as to improve the flow uniformity of the inlet airflow. Because the air flow is changed from axial flow to radial flow, the flow at the tail end of the guide ring and the blade cover is extremely turbulent, On the one hand, leakage is caused by the existence of a gap between the guide ring and the wheel cover, and the air flow flows back to form larger leakage loss, and on the other hand, leakage air flow is converged at the front edge of the main flow impact blade to cause impact loss, so that the flow resistance is increased, and the problem of rising power consumption and increasing noise of the centrifugal fan blade is solved. To this end, the present application provides a fan blade assembly as shown in fig. 1 to 12, including: a fan blade 1; the guide ring 2 is positioned on the air inlet side of the fan blade 1, and part of the guide ring 2 extends into the fan blade 1; the protruding structures 3 are arranged on the outer wall of the guide ring 2, the protruding structures 3 are located outside the fan blade 1, a leakage channel 31 is formed between two adjacent protruding structures 3, and one end of the leakage channel 31 faces the fan blade 1. The outer wall of the guide ring 2 is provided with the protruding structure 3, the gap between the outer wall of the guide ring 2 and the wheel cover of the fan blade 1 is filled by the protruding structure 3, so that leakage loss between the wheel cover and the guide ring 2 is reduced, turbulence intensity generated in the process of intersection of leakage air flow and main flow is weakened, so that impact loss of an inlet of the fan blade 1 is reduced, moreover, a leakage channel 31 is formed between the protruding structures 3, the leakage air flow is forced to flow through the leakage channel 31, a turbulent area generated by the leakage air flow is limited, the intersection influence of the turbulence on the main flow is further limited, the impact loss of the inlet of the fan blade 1 is reduced, meanwhile, due to the limitation of the leakage channel 31 on the leakage air flow, the impact range of the leakage air flow on the front edge of the fan blade is reduced, so that air flow noise is reduced, the performance and efficiency of a fan system are improved, and noise of the fan assembly is reduced, as shown in fig. 11 and 12, under the condition of any standard air quantity, the power of the fan blade assembly provided by the application is lower than the prior art, and the noise is 2000m 3 At/h air volume, the power of the embodiment is reduced by about 6W, and the noise is reduced by 0.6dB (A).
Further, the flow area of the leakage channel 31 gradually decreases along the direction approaching the fan blade 1. The flow area of the leakage channel 31 is gradually reduced, so that the resistance to the leakage air flow flowing through the leakage channel 31 is gradually increased, the flow of the leakage air flow can be further restrained by the increase of the resistance, the leakage capacity of the air flow from the guide ring 2 to the wheel cover is weakened, the leakage loss and the flow loss generated by the leakage air flow are reduced, and the impact of the leakage air flow to the fan blade 1 can be reduced, so that the noise is reduced. Moreover, due to the gradual reduction of the flow area of the leakage channel 31, the pressure of the leakage gas finally discharged through the leakage channel 31 is larger than that of the leakage gas without the convex structure 3 in the prior art, and the pressure value of the leakage gas is smaller than that of the main flow gas flowing through the inside of the fan blade 1, so that the turbulence intensity is weaker, and the impact loss of the fan assembly can be further reduced. As an embodiment, in order to gradually decrease the flow area of the leakage path 31, the protrusion 3 has a first end far from the fan blade 1 and a second end near to the fan blade 1, and the width of the protrusion 3 gradually increases in a direction from the first end to the second end. The width of the protruding structure 3 is gradually increased, so that the leakage channel 31 is gradually reduced, the resistance of the leakage channel 31 to leakage gas is gradually increased, the problem that other noises are generated due to fluctuation of the leakage gas caused by abrupt change of the flow area is avoided, and the noises of the fan assembly are effectively improved. The value range of the width n1 of the first end is t2 to 3t2, t2 is the wall thickness of the portion of the guide ring 2 extending into the fan blade 1, if the width n1 of the first end is too large, the flow area of the leakage channel 31 is compressed, a good flow guiding effect cannot be achieved, if the width n1 of the first end is too small, a large amount of leakage gas is led into the leakage channel 31, the flow rate of the leakage gas is increased, the filling effect of the convex structure 3 on the space between the guide ring 2 and the wheel cover is weakened due to too small width n1 of the first end, the problem of increasing the flow rate of the leakage gas is still caused, and only when the width n1 of the first end is in the range of t2 to 3t2, the gap between the guide ring 2 and the wheel cover can be effectively filled, and the flow rate of the leakage gas is reduced; similarly, the value range of the width n2 of the second end is 1.2n1 to 2n1, if the width n2 of the second end is too large, the change of the flow area of the leakage channel 31 narrowing along the air leakage direction is more severe, which can lead to the change of the local flow field of the gap between the guide ring 2 where the convex structure 3 is located and the wheel cover to be more turbulent, and the good flow guiding effect cannot be achieved, while if the width n2 of the second end is too small, the change of the flow area of the leakage channel 31 is smaller, the blocking effect on the leakage gas is reduced, and the problem of increasing the flow of the leakage gas still can be caused. Only the width n2 of the second end is 1.2n1 to 2n1, so that the flow area of the leakage channel 31 can be reduced smoothly, the reasonable distance between the convex structures 3 can be ensured, the flow of leakage gas is reduced, the leakage gas flow between the guide ring 2 and the wheel cover is rectified, the turbulence intensity of the backflow of the leakage gas flow and the main flow mixing in the main air channel of the guide ring 2 is weakened, and the turbulence noise of the inlet of the fan blade 1 is reduced.
The distance n3 between the end of the protruding structure 3 close to the fan blade 1 and the fan blade 1 ranges from 1.2t2 to 2.2t2, and t2 is the wall thickness of the part of the guide ring 2 extending into the fan blade 1. The axial arrangement range of the protruding structure 3 outside the guide ring 2 is limited, the minimum gap between the moving and static parts (the guide ring 2 and the fan blade 1) is ensured, interference with the outer side of the guide ring 2 is avoided when the fan blade 1 rotates, and the reliability of the fan blade assembly is ensured.
The fan blade assembly further comprises a reinforcing structure 4, the reinforcing structure 4 is arranged at the end part of the protruding structure 3, which faces the fan blade 1, the reinforcing structure 4 is far away from the end part of the protruding structure 3, the distance n3 is formed between the end part of the protruding structure 3 and the fan blade 1, and the numerical range of the thickness n6 of the reinforcing structure 4 is t2 to 1.5t2. Through setting up additional strengthening 4, carry out certain supplement to the length of protruding structure 3, improve the length dimension of leakage channel 31 to increase the barrier effect and the rectification effect to the leakage air current, increase the structural strength of water conservancy diversion circle 2, especially to being provided with under the circumstances of water conservancy diversion recess on the inner wall of water conservancy diversion circle 2, guarantee the structural strength and the structural reliability of water conservancy diversion circle 2. Wherein, the extension of protruding structure to the direction of fan blade 1 forms stiffening structure 4.
Along the direction close to the fan blade 1, the height of the protruding structure 3 is increased and then reduced, the numerical range of the maximum height n5 of the protruding structure 3 is 2.2t2 to 4.2t2, t2 is the wall thickness of the part of the guide ring 2 extending into the fan blade 1, the height of the protruding structure 3 is increased and then reduced, the gradually increased height is utilized to further limit the leakage air flow flowing through the leakage channel 31, the flow of the air flow in the leakage channel 31 is guided, the leakage channel 31 is avoided, at the highest point of the protruding structure 3, the blocking effect of the leakage channel 31 on the leakage air is improved, so that the flow rate of the leakage air is reduced, and then the height of the protruding structure 3 is reduced, namely the part of the protruding structure 3 close to the wheel cover is gradually reduced, namely the length of the leakage channel 31 can be extended, and the purpose of avoiding interference between the protruding structure 3 and the wheel cover can be achieved. The distance n4 between the highest point of the protruding structure 3 and the fan blade 1 ranges from 4t2 to 8t2, and t2 is the wall thickness of the part of the guide ring 2 extending into the fan blade 1. Because the gap between the guide ring 2 and the wheel cover still has rotatability along the direction of the fan blade 1, the n4 can disturb local air flow when being too large, so that the leakage air flow is more uneven, the local air flow loss is increased, the fan blade 1 and the guide ring 2 can be interfered at the same time, and the blocking and the guide effect on the leakage air flow can be reduced when the n4 is too small, and the working efficiency of the fan blade assembly can not be ensured. Specifically, along the direction approaching to the fan blade 1, the protruding structure 3 includes a gradually-increasing section 32 and a gradually-decreasing section 33, the connection between the gradually-increasing section 32 and the gradually-decreasing section 33 forms the highest point of the protruding structure 3, and the value range of the included angle θ4 between the plane where the gradually-decreasing section 33 is far away from the side surface of the guide ring 2 and the plane where the gradually-increasing section 32 is far away from the side surface of the guide ring 2 is 110 ° to 130 °. On the premise of ensuring the reliable flow guiding and rectifying of the leaked gas by the protruding structure 3, the length of the gradually-lowered section 33 is reduced as much as possible, so that the interference between the protruding structure 3 and the wheel cover is further avoided.
The side surface of the gradually-rising section 32 away from the guide ring 2 is an arc surface, and the tangent plane of the arc surface at the highest point of the protruding structure 3 and the plane of the side surface of the gradually-falling section 33 away from the guide ring 2 form the included angle theta 4. By setting the side surface of the gradually-raised section 32 to be an arc surface, when leakage gas does not flow into the leakage channel 31 but flows on the surface of the gradually-raised section 32, the leakage gas can be far away from the fan blade 1 under the guiding action of the arc surface of the gradually-raised section 32, so that the impact on the wheel cover and the fan blade 1 is reduced, and the noise of the fan blade assembly is reduced.
The middle line of the convex structure 3 is an arc line, the radius R of the middle line ranges from 0.55R3 to 0.75R3, and R3 is the radius of the end part of the guide ring 2 extending into the fan blade 1. That is, the protruding structure 3 is in a torsion shape relative to the molded line of the guide ring 2, so that the protruding structure 3 forms a leakage channel 31 deflecting towards one side of the protruding structure 3 on the outer wall of the guide ring 2, leakage air flow can perform certain spiral flow, the leakage air flow is prevented from directly impacting the fan blade 1, noise at the inlet of the fan blade 1 is further reduced, the larger the R3 is, the closer the protruding structure 3 is to a straight line, the deflection effect of the protruding structure 3 on the leakage air flow is poor, the smaller the R3 is, the larger the radian of the protruding structure 3 is, the flow of the leakage air flow is blocked, and the flow guiding effect of the leakage channel 31 on the leakage air flow is influenced. Wherein, the protruding structure 3 has a first end far away from the fan blade 1 and a second end close to the fan blade 1, and the value range of the included angle theta 3 between the connecting line of the middle-sized line between the end point of the first end and the end point of the second end and the central axis of the guide ring 2 is 10 DEG to 20 deg. The included angle theta 3 is too small, so that the drainage effect on the leakage air flow can be reduced, the leakage air flow can be severely deflected if too large, the flow field is disordered, the eddy current loss is aggravated, and the impact loss can be reduced by the proper included angle. Preferably, the deflection direction of the protruding structure 3 is consistent with the rotation direction of the fan blade 1, that is, the second end of the protruding structure 3 deflects towards the rotation direction of the fan blade 1 relative to the first end, so that the leakage air flow deflects towards the rotation direction of the fan blade 1, and interference on the main flow air flow is reduced. The middle line refers to a curve that divides the bump structure 3 into two symmetrical parts along the width direction of the bump structure 3, and may be a line passing through the midpoint of the width at any position of the bump structure 3.
The included angle gamma formed by two adjacent protruding structures 3 at the central axis of the guide ring 2 ranges from 3 degrees to 6 degrees. The distribution density of the protruding structures 3 on the outer wall surface of the guide ring 2 is controlled by limiting the included angle gamma, under the density, the protruding structures 3 can reliably block and guide leakage air flow, when the number of the protruding structures 3 is too large, the weight and the structural complexity of the guide ring 2 can be seriously increased, the reliability of the fan blade assembly is affected, and when the protruding structures 3 are too small, the blocking and the guide effect of the protruding structures 3 on the leakage air flow are poor, so that the efficiency of the fan blade assembly is lowered.
Furthermore, a guiding groove 5 is provided on the inner wall of the guiding ring 2, and the guiding groove 5 corresponds to the protruding structures 3 one by one. The air flowing through the inside of the guide ring 2 is guided by the guide grooves 5, the main air flow (the air flow flowing through the inside of the guide ring 2) is better attached to the surfaces of the blades and the wheel cover in the working process of the fan blade 1, the eddy current loss in the flow channel is reduced, the functional capacity of the blades is improved, and the performance of the fan blade assembly is further improved. Preferably, the depth of the diversion trench 5 gradually increases along the gas flow direction. Under the condition that the flow rates of the fan blades 1 are equal, the flow rate of the air flow in the structure of the guide ring 2 provided with the guide grooves 5 is gradually reduced, and the impact on the front edges of the fan blades can be reduced, so that turbulent noise is relieved. Wherein, the maximum depth m3 of the guide groove 5 ranges from 0.2t2 to 0.4t2, and t2 is the wall thickness of the part of the guide ring 2 extending into the fan blade 1. When the value of m3 is bigger, the wall thickness of the guide ring 2 is too thin, the problem that the guide ring 2 is damaged exists, and when the value of m3 is smaller, the guide effect of the guide groove 5 on gas is poor, and only when the value of m3 is in the range of 0.2t2 to 0.4t2, the guide effect of the guide groove 5 can be ensured, and the structural reliability of the guide ring 2 can also be ensured.
Furthermore, the width of the flow guiding groove 5 is gradually increased along the flow direction of the air, and the flow process of the air in the flow guiding groove 5 is gradually decelerated under the same flow, so that the flow guiding effect of the flow guiding groove 5 can be improved, and the impact of the air flow on the fan blade 1 is reduced. Wherein, the value range of the width m1 of the inlet of the diversion trench 5 is 0.8t2 to 2t2, when the width m1 of the inlet of the diversion trench 5 is too large, the flow area of the single diversion trench 5 is too wide, the effect of deflecting and guiding the airflow is weakened, and when the width m1 of the inlet of the diversion trench 5 is too small, the guiding effect of the airflow is poor; likewise, the width m2 of the outlet of the guide groove 5 has a value ranging from 1.5m1 to 2.5m1. When the outlet width m2 of the flow guiding groove 5 is too large, the flow area of the flow guiding groove 5 is too wide, so that the guiding effect of the groove on the air flow is poor, and when the outlet width m2 of the flow guiding groove 5 is too small, the width of the inlet of the flow guiding groove 5 needs to be smaller, the air flow entering the flow guiding groove 5 is reduced, and the guiding effect on the air flow is poor.
The middle line of the guide groove 5 is an arc line, the radius R of the middle line is in a numerical range of 0.55R3 to 0.75R3, R3 is the radius of the end part of the guide ring 2 extending into the fan blade 1, the shape of the guide groove 5 is a torsion shape relative to the line of the guide ring 2, so that the air flowing through the guide groove 5 can be guided towards the rotating direction of the fan blade 1, the aerodynamic resistance of the fan blade 1 during running is reduced, the acting effect of the fan blade 1 is improved, the guide groove 5 and the protruding structure 3 are the same in shape, the protruding structure 3 can structurally reinforce the position of the guide ring 2 where the guide groove 5 is arranged, the structural reliability of the guide ring 2 is ensured, preferably, the reinforcing structure 4 is utilized to compensate the outlet end part of the guide groove 5, the structural reliability of the guide ring 2 is fully ensured, wherein the larger R3 is, the protruding structure 3 is closer to a straight line, the deflecting effect of the air flowing in the guide ring 2 is poor, the smaller is the radian of the guide groove 5, and the air flowing along the flow in the guide groove 5 is influenced, and the uniformity of the air flowing in the guide groove 1 is reduced; wherein, the diversion trench 5 has a first end far away from the fan blade 1 and a second end close to the fan blade 1, and the value range of the included angle theta 3 between the connecting line of the middle-sized line between the end point of the first end and the end point of the second end and the central axis of the diversion ring 2 is 10 DEG to 20 deg. The included angle theta 3 is too small, so that the drainage effect of the airflow flowing in the guide ring 2 to the rotating direction of the wind vane 1 is reduced, the local airflow is deflected violently due to too large included angle, the flow field is disordered, the eddy current loss is aggravated, and the air inlet resistance and the impact loss can be reduced due to the proper included angle. The middle line refers to a curve that divides the guide groove 5 into two symmetrical parts along the width direction of the guide groove 5, and may be a line passing through the middle point of the width of any position of the guide groove 5.
Along the gas flow direction, the water conservancy diversion circle 2 includes first straightway 21, second changeover portion 22 and the second straightway 23 that communicate in proper order, part the second straightway 23 is located the inside of fan blade 1, just protruding structure 3 set up in the outer wall of second changeover portion 22 with on the outer wall of second straightway 23. When the air flow passes through the guide ring 2, the air flow sequentially passes through the first straight line segment 21, the second transition segment 22 and the second straight line segment 23, and as the end part of the second straight line segment 23 is positioned in the fan blade 1, the air flow can directly flow to the fan blade 1, so that leakage air flow between the guide ring 2 and the fan blade 1 is reduced as much as possible, and the working capacity of the fan blade 1 is improved.
The value range of the length c of the second straight line segment 23 extending into the fan blade 1 is 0.5a to 0.7a, the length c is more than or equal to 2t1, a is the length of the straight line segment of the wheel cover of the fan blade 1, and t1 is the wall thickness of the wheel cover of the fan blade 1. The length c is the height of the horizontal overlapping part when the fan blade 1 is matched with the guide ring 2, and when the fan blade 1 rotates, a part of air flow flows back from the gap where the length c is positioned to cause leakage, does not participate in external work, and causes energy loss. When the length c is too large, interference can be generated between the fan blade 1 and the outer side of the guide ring 2 during high-speed operation, and when the length c is too small, the fan blade 1 and the guide ring 2 are not tightly matched, the air flow leaking from the gap can be increased, the performance of the fan blade 1 is reduced, the noise is increased, the size parameter of the second guide section is reasonably controlled, the air inlet capacity of the fan blade 1 is increased, the leakage amount of the matched gap is reduced, the air flow impact loss of the front edge of the fan blade 1 is reduced, and the work efficiency of the fan blade 1 is improved. Preferably, t1 is equal to t 2.
The gap w between the second straight section 23 and the straight section of the shroud of the fan blade 1 ranges from 2.5t1 to 3.5t1. The larger the value of the gap w is, the more leakage airflow between the guide ring 2 and the fan blade 1 is, so that the working efficiency of the fan blade 1 can be affected, and when the smaller the value of the gap w is, the smaller the gap between the guide ring 2 and the fan blade 1 is, the possibility of structural interference between the fan blade 1 and the guide ring 2 exists, so that the reliability of the fan blade assembly is affected. Only when the range of the gap w is 2.5t1 to 3.5t1, the interference between the rotation of the fan blade 1 and the guide ring 2 is avoided, and the leakage loss of the fan system is reduced.
The guide ring 2 further comprises a planar guide section 24, and the planar guide section 24 is disposed at one end of the first straight line section 21 away from the second transition section 22. The plane guide section 24 is used for connecting the guide ring 2 with a preset structure, so that an air inlet on the preset structure is closed, airflow is forced to flow to the fan blade 1 only through the inside of the guide ring 2, the reliable operation of the fan blade assembly is ensured, and the plane guide section 24 can be provided with an electrical box and other structures, so that the installation of other structures of the fan blade assembly is facilitated. The numerical range of the distance h between the plane flow guiding section 24 and the end part of the second straight line section 23 far away from the second transition section 22 is 0.37R3 to 0.45R3, R3 is the radius of the second straight line section 23, the flow guiding distance of the flow guiding ring 2 to the air flow is limited by limiting the distance from the plane flow guiding section 24 to the end part of the second straight line section 23, the axial size and the occupied space of the fan blade component can be increased by excessively large h, the flow guiding effect to the air flow can not be increased, the problem that the flow guiding effect to the air flow is reduced can be caused by excessively small h, and the height of the fan blade component can be reduced on the premise that the reliable flow guiding of the air flow of the flow guiding ring 2 to the air flow can be ensured only if the h is in a reasonable range, so that the air inlet uniformity of the fan blade 1 is ensured. Preferably, the axial length h1 of the second straight line segment 23 ranges from 0.26h to 0.34h; the axial length h2 of the second transition 22 ranges from 0.3h to 0.38h; the axial length h3 of the first straight line segment 21 ranges from 0.28h to 0.36h. When the airflow sequentially flows through the first straight line segment 21, the second transition segment 22 and the second straight line segment 23, the axial size of the guide ring 2 can be reduced as much as possible on the premise of ensuring the reliable guide effect, so that the axial size and the occupied space of the fan blade assembly are reduced.
Along the gas flow direction, the flow area of the second straight line segment 23 is gradually reduced, the numerical range of an included angle theta 1 between the molded line of the second straight line segment 23 and the outlet end face of the second straight line segment 23 is 90.5-92 degrees, the flow area of the second straight line segment 23 is reduced, the flow rate of the gas flowing to the fan blade 1 is increased, and preparation is made for the fan blade 1 to do work on the gas; along the gas flow direction, the flow area of the first straight line segment 21 gradually decreases, the area of one end of the first straight line segment 21 far away from the second straight line segment 23 is larger, more gas can be introduced into the guide ring 2, then under the action of the gradual decrease of the flow area of the first straight line segment 21, the flow speed gradually increases, and further, the fan blade 1 is ready for doing work on the gas; preferably, the value of the angle θ2 between the line of the first line segment 21 and the outlet end face of the first line segment 21 ranges from 135 ° to 145 °. Too large included angle theta 2 can cause the first straight line segment 21 to approach the plane, but can generate an obstruction effect on the air flow, and can also compress the space of the plane diversion segment 24, so that the rationality of the layout of other routing and line fixing structures is affected; the too small included angle θ2 reduces the size of the end of the first straight line segment 21 (the inlet of the guide ring 2), and reduces the airflow entering the guide ring 2, which affects the working efficiency of the fan blade 1.
The second transition section 22 is a cambered surface, and can smoothly transition the first straight line section 21 and the second straight line section 23, so that the problem of reduction of air intake uniformity caused by increase of local flow loss due to non-smooth transition is avoided, attached air flow is smoother, and flow loss is reduced. Similarly, a first transition section is also arranged between the first straight line section 21 and the plane diversion section 24, and the first transition section is an arc surface, so that the air flow entering the first straight line section 21 after flowing through the plane diversion section 24 is smoother, the air flow can be reliably attached to the first straight line section 21 for flowing, the flow loss is reduced, and meanwhile, the first transition section can also prepare for the injection molding part die opening, and the abnormal problems of sharp corner shrinkage, sinking and the like are avoided.
The fan blade 1 comprises a blade 11 and a wheel cover 12, the wheel cover 12 is arranged at one end of the blade 11 facing the guide ring 2, the wheel cover 12 comprises a wheel cover straight line section 121 and a wheel cover arc section 122 which are sequentially connected, the connection position of the wheel cover straight line section 121 and the wheel cover arc section 122 is positioned between the blade 11 and the guide ring 2, part of the wheel cover straight line section 121 surrounds the periphery of the end part of the guide ring 2, and leakage air flow is further limited by the cooperation of the wheel cover straight line section 121 and the end part of the guide ring 2, so that the working efficiency of the fan blade 1 is improved; the diameter of the shroud arc line segment 122 gradually increases along the direction away from the shroud straight line segment 121, the shroud arc line segment 122 is utilized to guide the mixed airflow formed by the leakage airflow and the main flow, meanwhile, the impact and other effects of the leakage airflow on the main airflow of the fan blade 1 are reduced, the numerical range of the arc radius R2 of the shroud arc line segment 122 is 0.15R1 to 0.23R1, when the numerical range of the arc radius R2 is too large, the guiding range of the shroud 12 on the leakage airflow is too large, the outlet height of the fan blade 1 is occupied, the leakage airflow can generate turbulence, accumulation and other problems at the shroud 12, the work of the fan blade 1 is still influenced, and when the R2 is too small, the airflow guiding capability of the too short shroud arc line segment 122 on the main flow edge is insufficient under the condition that the overall axial dimension of the fan blade 1 is unchanged, and the leakage is easy to occur; the axial length a of the wheel cover straight line section 121 ranges from 0.31R2 to 0.39R2, when a is too large, the wheel cover 12 occupies the fan blade 1, the overall axial size of the fan blade 1 is increased, the occupied space is increased, and when a is too small, the size of the guide ring 2 extending into the fan blade 1 is reduced, the leakage air flow is increased, and the working efficiency of the fan is affected; the numerical range of the distance b between the highest point of the blade 11 and the end face of the wheel cover straight line segment 121, which is close to the guide ring 2, is 0.55R2 to 0.63R2, the guide ring 2 can be ensured to reliably extend into the wheel cover 12 through limiting the distance b, meanwhile, the guide ring 2 cannot interfere with the fan blade 1, when b is too large, the wheel cover 12 can be caused to occupy the fan blade 1, the overall axial size of the fan blade 1 is increased, the dynamic and static interference problem can be caused, and when b is too small, the size of the guide ring 2 extending into the fan blade 1 is reduced, the leakage air flow is increased, and the working efficiency of the fan is affected.
An air conditioning unit comprises the fan blade assembly.
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 (21)
1. The utility model provides a fan blade subassembly which characterized in that: comprising the following steps:
a fan blade (1);
the guide ring (2) is positioned on the air inlet side of the fan blade (1), and part of the guide ring (2) extends into the fan blade (1);
protruding structure (3), protruding structure (3) set up in on the outer wall of water conservancy diversion circle (2), just protruding structure (3) are located the outside of fan blade (1), adjacent two form between protruding structure (3) leakage path (31), just leakage path (31) one end orientation fan blade (1).
2. The fan blade assembly of claim 1, wherein: the flow area of the leakage channel (31) gradually decreases along the direction approaching the fan blade (1).
3. The fan blade assembly of claim 2, wherein: the protruding structure (3) is provided with a first end far away from the fan blade (1) and a second end close to the fan blade (1), and the width of the protruding structure (3) is gradually increased along the direction from the first end to the second end; and/or the value range of the width n1 of the first end is t2 to 3t2, and t2 is the wall thickness of the part of the guide ring (2) extending into the fan blade (1); and/or the width n2 of the second end ranges from 1.2n1 to 2n1.
4. The fan blade assembly of claim 1, wherein: the numerical range of the distance n3 between the end part of the protruding structure (3) close to the fan blade (1) and the fan blade (1) is 1.2t2 to 2.2t2, and t2 is the wall thickness of the inner part of the fan blade (1) where the guide ring (2) stretches.
5. The fan blade assembly of claim 4, wherein: the fan blade assembly further comprises a reinforcing structure (4), the reinforcing structure (4) is arranged at the end part of the protruding structure (3) towards the fan blade (1), the reinforcing structure (4) is far away from the end part of the protruding structure (3) and the fan blade (1) to form a distance n3, and the numerical range of the thickness n6 of the reinforcing structure (4) is t2 to 1.5t2.
6. The fan blade assembly of claim 1, wherein: along the direction close to the fan blade (1), the height of the protruding structure (3) is increased and then reduced, the numerical range of the maximum height n5 of the protruding structure (3) is 2.2t2 to 4.2t2, and t2 is the wall thickness of the part of the guide ring (2) extending into the fan blade (1); and/or the numerical range of the distance n4 between the highest point of the protruding structure (3) and the fan blade (1) is 4t2 to 8t2, and t2 is the wall thickness of the part of the guide ring (2) extending into the fan blade (1).
7. The fan blade assembly of claim 6, wherein: along the direction that is close to fan blade (1), protruding structure (3) include gradually high section (32) and gradually low section (33), gradually high section (32) with the junction of gradually low section (33) constitutes protruding structure (3) the highest point, gradually low section (33) keep away from the plane that the side of water conservancy diversion circle (2) is located with gradually high section (32) keep away from the numerical range of angle θ4 between the plane that the side of water conservancy diversion circle (2) is located is 110 to 130.
8. The fan blade assembly of claim 7, wherein: the side surface of the gradually-rising section (32) far away from the guide ring (2) is an arc surface, and an included angle theta 4 is formed between a tangent plane of the arc surface at the highest point of the protruding structure (3) and a plane of the gradually-falling section (33) far away from the side surface of the guide ring (2).
9. The fan blade assembly of claim 1, wherein: the middle line of the convex structure (3) is an arc line, the radius R of the middle line is in a numerical range of 0.55R3-0.75R3, and R3 is the radius of the end part of the guide ring (2) extending into the fan blade (1); and/or the convex structure (3) is provided with a first end far away from the fan blade (1) and a second end close to the fan blade (1), and the included angle theta 3 between the connecting line of the middle-sized line between the end point of the first end and the end point of the second end and the central axis of the guide ring (2) is in the range of 10-20 degrees.
10. The fan blade assembly of claim 1, wherein: the value range of an included angle gamma formed by two adjacent protruding structures (3) at the central axis of the guide ring (2) is 3-6 degrees.
11. The fan blade assembly of claim 1, wherein: the inner wall of the guide ring (2) is provided with guide grooves (5), and the guide grooves (5) are in one-to-one correspondence with the protruding structures (3).
12. The fan blade assembly of claim 11, wherein: the depth of the diversion groove (5) gradually increases along the gas flow direction; and/or the maximum depth m3 of the guide groove (5) is in the range of 0.2t2 to 0.4t2, and t2 is the wall thickness of the part of the guide ring (2) extending into the fan blade (1).
13. The fan blade assembly of claim 11, wherein: the width of the diversion groove (5) gradually increases along the gas flow direction; and/or the width m1 of the inlet of the diversion groove (5) ranges from 0.8t2 to 2t2; and/or the width m2 of the outlet of the flow guiding groove (5) ranges from 1.5m1 to 2.5m1.
14. The fan blade assembly of claim 11, wherein: the middle line of the guide groove (5) is an arc line, the radius R of the middle line is in a numerical range of 0.55R3 to 0.75R3, and R3 is the radius of the end part of the guide ring (2) extending into the fan blade (1); and/or the diversion groove (5) is provided with a first end far away from the fan blade (1) and a second end close to the fan blade (1), and the included angle theta 3 between the connecting line of the middle-sized line between the end point of the first end and the end point of the second end and the central axis of the diversion ring (2) is in the range of 10-20 degrees.
15. The fan blade assembly of claim 1, wherein: along the gas flow direction, water conservancy diversion circle (2) are including first straightway (21), second changeover portion (22) and second straightway (23) that communicate in proper order, and part second straightway (23) are located the inside of fan blade (1), just protruding structure (3) set up in the outer wall of second changeover portion (22) with on the outer wall of second straightway (23).
16. The fan blade assembly of claim 15, wherein: the numerical range of the length c of the second straight line segment (23) extending into the fan blade (1) is 0.5a to 0.7a, the length c is more than or equal to 2t1, a is the length of the wheel cover straight line segment (121) of the fan blade (1), and t1 is the wall thickness of the wheel cover (12) of the fan blade (1); and/or the gap w between the second straight line segment (23) and the straight line segment (121) of the wheel cover of the fan blade (1) ranges from 2.5t1 to 3.5t1.
17. The fan blade assembly of claim 15, wherein: the guide ring (2) further comprises a plane guide section (24), the plane guide section (24) is arranged at one end of the first straight line section (21) far away from the second transition section (22), the distance h between the plane guide section (24) and the end part of the second straight line section (23) far away from the second transition section (22) is in a numerical range of 0.37R3-0.45R3, and R3 is the radius of the second straight line section (23).
18. The fan blade assembly of claim 17, wherein: the axial length h1 of the second straight line segment (23) ranges from 0.26h to 0.34h; and/or the axial length h2 of the second transition section (22) ranges from 0.3h to 0.38h; and/or the axial length h3 of the first straight line segment (21) ranges from 0.28h to 0.36h.
19. The fan blade assembly of claim 15, wherein: along the gas flow direction, the flow area of the second straight line section (23) is gradually reduced, and the value range of an included angle theta 1 between the molded line of the second straight line section (23) and the outlet end face of the second straight line section (23) is 90.5-92 degrees; along the gas flow direction, the flow area of the first straight line section (21) gradually decreases, and the value range of an included angle theta 2 between the line of the first straight line section (21) and the outlet end face of the first straight line section (21) is 135-145 degrees.
20. The fan blade assembly of claim 1, wherein: the fan blade (1) comprises a blade (11) and a wheel cover (12), the wheel cover (12) is arranged at one end of the blade (11) facing the guide ring (2), the wheel cover (12) comprises a wheel cover straight line section (121) and a wheel cover arc line section (122) which are sequentially connected, the connection position of the wheel cover straight line section (121) and the wheel cover arc line section (122) is positioned between the blade (11) and the guide ring (2), part of the wheel cover straight line section (121) surrounds the periphery of the end part of the guide ring (2), the diameter of the wheel cover arc line section (122) gradually increases along the direction away from the wheel cover straight line section (121), and the numerical range of the arc radius R2 of the wheel cover arc line section (122) is 0.15R1-0.23R1; and/or the axial length a of the wheel cover straight line section (121) ranges from 0.31R2 to 0.39R2; and/or the distance b between the highest point of the blade (11) and the end face of the straight wheel cover section (121) close to the guide ring (2) ranges from 0.55R2 to 0.63R2.
21. An air conditioning unit, characterized in that: a wind blade assembly as claimed in any one of claims 1 to 20.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311585222.XA CN117287417A (en) | 2023-11-27 | 2023-11-27 | Fan blade assembly and air conditioning unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311585222.XA CN117287417A (en) | 2023-11-27 | 2023-11-27 | Fan blade assembly and air conditioning unit |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN117287417A true CN117287417A (en) | 2023-12-26 |
Family
ID=89239403
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202311585222.XA Pending CN117287417A (en) | 2023-11-27 | 2023-11-27 | Fan blade assembly and air conditioning unit |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN117287417A (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2013021618A1 (en) * | 2011-08-10 | 2013-02-14 | ダイキン工業株式会社 | Centrifugal blower |
| CN104633886A (en) * | 2013-11-08 | 2015-05-20 | 美的集团股份有限公司 | Air guide ring for air conditioner and air conditioner with air guide ring |
| CN105650033A (en) * | 2014-11-25 | 2016-06-08 | 苏州三星电子有限公司 | Refrigerator and fan assembly thereof |
| CN216897527U (en) * | 2022-01-26 | 2022-07-05 | Tcl空调器(中山)有限公司 | Special-shaped flow guide ring, fresh air module and air conditioner |
| CN217558634U (en) * | 2022-03-30 | 2022-10-11 | 华为技术有限公司 | Wind-guiding circle, fan and electrical equipment |
| CN115899822A (en) * | 2022-11-28 | 2023-04-04 | 珠海格力电器股份有限公司 | Diversion structure and courtyard machine with same |
-
2023
- 2023-11-27 CN CN202311585222.XA patent/CN117287417A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2013021618A1 (en) * | 2011-08-10 | 2013-02-14 | ダイキン工業株式会社 | Centrifugal blower |
| CN104633886A (en) * | 2013-11-08 | 2015-05-20 | 美的集团股份有限公司 | Air guide ring for air conditioner and air conditioner with air guide ring |
| CN105650033A (en) * | 2014-11-25 | 2016-06-08 | 苏州三星电子有限公司 | Refrigerator and fan assembly thereof |
| CN216897527U (en) * | 2022-01-26 | 2022-07-05 | Tcl空调器(中山)有限公司 | Special-shaped flow guide ring, fresh air module and air conditioner |
| CN217558634U (en) * | 2022-03-30 | 2022-10-11 | 华为技术有限公司 | Wind-guiding circle, fan and electrical equipment |
| CN115899822A (en) * | 2022-11-28 | 2023-04-04 | 珠海格力电器股份有限公司 | Diversion structure and courtyard machine with same |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US20210388839A1 (en) | Counter-rotating fan | |
| WO2011043125A1 (en) | Impeller of centrifugal compressor | |
| CN105697394B (en) | The efficient exit flow field of microminiature is undistorted centrifugal blower | |
| CN114233680A (en) | Combined type fan blade and combined air outlet device | |
| CN117287417A (en) | Fan blade assembly and air conditioning unit | |
| CN205371033U (en) | Electric locomotive pulls ventilation blower with centrifugal axial compressor | |
| CN205014559U (en) | Radome fairing, air inlet system and circular cabinet -type air conditioner | |
| CN216812271U (en) | Combined type fan blade and combined air outlet device | |
| CN109424586B (en) | Volute tongue structure for radial flow fan | |
| CN105570991A (en) | Axial flow cabinet air conditioner | |
| JP4665472B2 (en) | Blower | |
| AU2022308067A1 (en) | Fan assembly and air conditioner | |
| CN114962333A (en) | Mixed flow fan and ducted air conditioner | |
| CN111734675B (en) | Backward centrifugal wind wheel and centrifugal fan | |
| CN205316625U (en) | Axial compressor cabinet -type air conditioner | |
| CN114922848A (en) | Mixed flow fan and ducted air conditioner | |
| CN113757166A (en) | Centrifugal fan and range hood | |
| CN217481585U (en) | Mounting structure of through-flow fan blade, wall-mounted indoor unit and air conditioner | |
| CN217421629U (en) | Mixed flow fan and ducted air conditioner | |
| CN110985439A (en) | Forward-bent impeller, centrifugal fan and air conditioner | |
| CN216278647U (en) | Centrifugal fan and range hood | |
| CN214036265U (en) | Volute component and air conditioner | |
| CN219220837U (en) | Volute, fan and air conditioner | |
| CN113202818B (en) | Inlet flow collecting device for centrifugal fan and centrifugal fan | |
| CN218915122U (en) | Raise machine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |