CN116557320B - Active silencing type high-speed centrifugal fan - Google Patents
Active silencing type high-speed centrifugal fan Download PDFInfo
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- CN116557320B CN116557320B CN202310655725.3A CN202310655725A CN116557320B CN 116557320 B CN116557320 B CN 116557320B CN 202310655725 A CN202310655725 A CN 202310655725A CN 116557320 B CN116557320 B CN 116557320B
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- impeller
- inner ring
- pressure
- main shaft
- volute
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- 230000030279 gene silencing Effects 0.000 title description 3
- 230000008030 elimination Effects 0.000 claims abstract description 5
- 238000003379 elimination reaction Methods 0.000 claims abstract description 5
- 230000005540 biological transmission Effects 0.000 claims description 9
- 238000006073 displacement reaction Methods 0.000 claims description 8
- 239000002184 metal Substances 0.000 claims description 3
- 230000004044 response Effects 0.000 claims description 3
- 230000000694 effects Effects 0.000 abstract description 5
- 239000003570 air Substances 0.000 description 38
- 230000008859 change Effects 0.000 description 10
- 238000000034 method Methods 0.000 description 6
- 238000000926 separation method Methods 0.000 description 6
- 230000009471 action Effects 0.000 description 4
- 238000009434 installation Methods 0.000 description 4
- 239000007788 liquid Substances 0.000 description 4
- 230000013011 mating Effects 0.000 description 4
- 239000000126 substance Substances 0.000 description 4
- 230000008569 process Effects 0.000 description 3
- 239000012080 ambient air Substances 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 230000008676 import Effects 0.000 description 2
- 239000000411 inducer Substances 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 230000005012 migration Effects 0.000 description 2
- 238000013508 migration Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 238000009423 ventilation Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 238000004804 winding Methods 0.000 description 2
- 238000010146 3D printing Methods 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000001746 injection moulding Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 210000000697 sensory organ Anatomy 0.000 description 1
- 230000003068 static effect Effects 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
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
- F04D29/444—Bladed diffusers
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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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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Abstract
The invention discloses an active noise elimination type high-speed centrifugal fan, which comprises an inlet section, an impeller, guide vanes, a volute, a machine cover, a main shaft and a main motor, wherein the inlet section and the machine cover are respectively arranged at two sides of the volute; the guide vane comprises an inner ring, a vane body and an outer ring, wherein the inner ring and the outer ring are concentrically arranged, the vane body is distributed around the circumference of the main shaft, two ends of the vane body along the radial direction of the main shaft are respectively fixed with the inner ring and the outer ring, the inner ring is connected with the volute or the cover in a rotating way, and the inlet mounting angle of the vane body is actively adjusted to be tangential according to the airflow direction of the outlet of the impeller. The inner ring is actively controlled to rotate until the blade inlet setting angle is matched with the incoming flow, the impact effect of gas is eliminated, and the noise generating factors are eliminated.
Description
Technical Field
The invention relates to the technical field of centrifugal fans, in particular to an active noise elimination type high-speed centrifugal fan.
Background
Centrifugal fans are often used for medium and large flow gas delivery and have large delivery lifts, and the centrifugal impeller is required to give the gas a large pressure rise. For example, dustproof ventilation of industrial plants, and ventilation of subways, high-rise interiors, gymnasiums and other public places are required by using large fans.
The centrifugal fan has larger noise when running, and the noise needs to be eliminated in time in many occasions.
The noise of the fan generally sources vibration when a structural member moves, dynamic balance is not met, part of noise is generated due to the fact that air tightness of a pipeline is not good, gas leakage generates noise, in addition, the noise also sources impact between the gas and a wall surface when the gas moves nearby the impeller at a high speed, if one of the factors is out of care, the operation noise of the fan is high, sound pollution is caused to the environment, and the sense organs of surrounding people are affected.
In the prior art, noise of a fan is generally reduced by adding a sound-proof cover, arranging a buffer cushion at an installation position and the like, and the noise is passively suppressed, and when the noise is large, the effect of the means is limited. The cost of excessively adding the sound-proof housing is greatly increased and the space is occupied.
Disclosure of Invention
The invention aims to provide an active silencing type high-speed centrifugal fan so as to solve the problems in the background technology.
In order to solve the technical problems, the invention provides the following technical scheme:
the active noise elimination type high-speed centrifugal fan comprises an inlet section, an impeller, a guide vane, a volute, a cover, a main shaft and a main motor, wherein the inlet section and the cover are respectively arranged on two sides of the volute, the main motor is placed on a foundation and is connected with the end part of the cover, the main shaft is rotationally arranged in the cover, one end of the main shaft is in transmission connection with the main motor, the other end of the main shaft is fixedly provided with the impeller, the guide vane is arranged in the volute or on the cover, and the guide vane is positioned at the periphery of the impeller;
the guide vane comprises an inner ring, a vane body and an outer ring, wherein the inner ring and the outer ring are concentrically arranged, the vane body is distributed around the circumference of the main shaft, two ends of the vane body along the radial direction of the main shaft are respectively fixed with the inner ring and the outer ring, the inner ring is connected with the volute or the cover in a rotating way, and the inlet mounting angle of the vane body is actively adjusted to be tangential according to the airflow direction of the outlet of the impeller.
The fan has a basic centrifugal impeller rotating structure, the addition of the guide vane realizes smooth transition of air flow between the impeller and the volute, fluid conveyed by the fan is gas, the gas has compressibility, so when the fan changes pumping air flow through rotating speed change, the relation between flow and rotating speed is different from that of a water pump conveying liquid, the liquid has incompressibility, when the rotating speed change of the impeller causes the change of the flow, the fan basically follows a similar principle, namely the rotating speed is in direct proportion to the flow, the total pressure also changes correspondingly when the rotating speed of the air conveyed by the fan changes, the space volume occupied by air with the quantity of a unit substance changes, so the flow velocity of the gas at the impeller outlet also changes correspondingly with the flow velocity, the direction of the absolute velocity of the gas at the impeller outlet changes to a certain extent, the triangle of the impeller outlet velocity is not in the condition of enlargement and shrinkage, and the gas outflow angle at different rotating speeds is changed because of the gas compressibility, so the gas at the impeller outlet cannot be accepted and summarized out, the important source of noise when the fan deviates from the flow, namely the impinging angle exists between the air flow and the inner wall of the impeller, the air flow and the inner wall of the volute has a corresponding change, the volume of the space volume occupied by the air flow is changed correspondingly, the volume of the air flow is changed, the flow velocity of the gas is changed correspondingly, the flow velocity of the gas at the position of the impeller is changed smoothly, the position of the air outlet is changed at the position of the impeller has no vibration angle, and the air flow has no vibration angle, and the output angle is changed at the position of the scroll, and the scroll has no vibration angle, and has changed when the flow angle, and has changed at the flow angle.
At least one blade body is internally provided with two pressure guiding holes, one ends of the two pressure guiding holes extend to two sides of the inlet position of the blade body respectively, and the other ends of the pressure guiding holes are used as pressure difference signals to be transmitted to a control structure of the inner ring for angle rotation.
The rotation of the inner ring can draw one end of the blade body to deform so as to change the inlet setting angle of the guide vane, the rotation of the inner ring is completed through an active driving structure, the driving mechanism is controlled by referencing the compression condition of the two surfaces of the blade body at the inlet position, under ideal conditions, the air inflow angle of the impeller outlet is along the surface of the inlet position of the blade body, the pressure intensity received by the two surfaces of the inlet position of the blade body is equal, the inner ring does not need to be rotated at the moment, when the air outflow angle of the impeller outlet changes, if the outflow angle is smaller than the inlet setting angle of the blade body, the air can form a low-pressure area at the working surface when passing through the inlet end of the blade body, the back of the blade body is impacted to form a high-pressure area, and the two surfaces of the blade body transmit two pressure intensity information through the pressure guiding holes to serve as control conditions for controlling the rotation of the inner ring, so that the impact action of the air at the blade body position is eliminated, and noise is eliminated.
The centrifugal fan further comprises an indexing motor, the guide vane further comprises a pressure distribution assembly, the indexing motor is arranged on the inner wall of the end face of the volute, the pressure distribution assembly is arranged on the inner ring, air pressure is transmitted between the pressure distribution assembly and the pressure guiding hole through a pressure guiding pipe, the pressure distribution assembly is electrically connected with the indexing motor, the pressure distribution assembly converts pressure difference signals of two sides of the blade body into forward and reverse rotation signals of the indexing motor, the indexing motor is a linear motor, and the output end of the indexing motor is connected with the inner ring through a connecting rod hinged to the two ends of the inner ring.
The stator part of the indexing motor fixed on the volute is static, the extension and retraction of the output end of the stator part corresponds to the clockwise and anticlockwise rotation of the inner ring, the pressure introduced by the pressure guiding hole is converted into a control signal in the pressure distribution assembly, the pressure distribution assembly is fixed on the inner ring and rotates along with the inner ring, the pressure guiding hole can be externally connected from the axial end part of the blade body along the main shaft, the air tightness of the pressure distribution assembly, the pressure guiding pipe and the pressure guiding hole is reduced as much as possible, the problem of air tightness of the relative movement mode occurs, the electric connection of the pressure distribution assembly to the indexing motor only needs to use a deformable wire, and the inner ring rotates only by a small angle even if rotating, so that the problem of wire winding does not occur.
The pressure distribution assembly comprises a shell, a position changing piece, a switch rod and an electrode group, wherein the shell is arranged on the inner ring, the switch rod is arranged in the shell in a sliding mode, the position changing piece is arranged in the middle of the switch rod, the outer edge of the position changing piece is sealed with the inner wall of the shell, the inner cavity of the shell is divided into two areas by the position changing piece, the two areas of the inner cavity of the shell are respectively connected to two side pressure guiding holes of the blade body through pressure guiding pipes, the position changing piece drives the switch rod to move to one end in response to pressure difference of two sides, two ends of the switch rod are respectively provided with two groups of metal sheets, the electrode group at one end of the shell is conducted when the switch rod is positioned at one end of the shell, and the electrode group at two ends of the shell respectively corresponds to two positive and negative electrode wiring modes of the position changing motor.
When the pressure of the left side in the shell is larger than that of the right side, the pressure difference drives the position changing piece to move towards the right side, the switch rod props against the right end of the shell, the electrode group at the right end is communicated, a circuit of a positive electrode wiring and a negative electrode wiring of a direct current power supply of an indexing motor is externally supplied to be conducted, the indexing motor positively rotates to drive the inner ring to rotate until the deformation of the inlet position of the blade body is consistent with the inflow angle of gas, after the pressure difference is not provided in the chambers at the two sides in the shell, the switch rod returns to the middle position and is not contacted with the two ends, the indexing motor is powered off, the inner ring is not rotated any more, and vice versa.
The deflection piece is a diaphragm. The diaphragm only needs a small pressure difference to deform to enable the switch rod to move towards one side, and if the diaphragm is of a sliding block structure, a large initial starting force is needed.
The main shaft and the main motor are connected by an elastic sleeve pin coupler. The elastic sleeve pin coupler reduces the transmission of vibration quantity, only transmits torque, and reduces the transmission of the installation foundation of the vibration main motor at the impeller.
The inlet section comprises a pipe body, a flange and a corrugated pipe, wherein the outer edges of the two ends of the pipe body are respectively provided with the flange which is externally connected through the corrugated pipe, the diameter of the pipe body is equal to the diameter of the inlet of the impeller, and the length of the pipe body is more than three times of the diameter of the pipe body.
The bellows prevents the vibration of fan main part from transmitting to the air inlet, if open and bleed then not influenced, in addition, the pipe length is as long as possible a bit guarantees that the inflow gas in impeller import the place ahead is rectified as far as possible into smooth air current, if direct impeller import is towards ambient air inspiration then the entry condition too disorder and vibration noise greatly increased, the inducer can not be regarded as the standard of this application product, but let the user go to purchase the installation to the suggestion item of use occasion.
The inlet section further comprises a front cover matching plate, the front cover matching plate is installed between the flange and the volute in a butt clamp mode, one side end face of the front cover matching plate, facing the impeller, is provided with a shape matched with the shape of the impeller, and a surface gap between the front cover matching plate and the impeller is smaller than two millimeters.
The gap between the front cover matching plate and the impeller is the position where the leakage from the impeller outlet to the inlet occurs, the gap is as small as possible, and the gap path extends as long as possible, so that the leakage can be reduced, and ineffective work is reduced.
The impeller comprises a front cover plate, a rear cover plate, blades, separation plates and a hub, wherein a plurality of circumferentially distributed blades are fixed between the front cover plate and the rear cover plate, the hub is arranged at the central position of the rear cover plate and connected with a main shaft, a plurality of separation plates are further arranged in flow passages between the blades, and the separation plates axially separate the flow passages along the main shaft.
Because the impeller runner is different in length at the front cover plate and the rear cover plate, the working degree is different, the runner at the rear cover plate is longer, the working is more, the gas is compressed more, the gas molecules with more substances are gathered to the rear cover plate, the uneven distribution of the gas molecules in the runner can lead to the occurrence of internal circulation, the noise and vibration are increased, the current runner is layered, the migration of the gas molecules in the front cover plate and the rear cover plate is physically inhibited, and the uniformity of the gas clusters in the runner is maintained.
Compared with the prior art, the invention has the following beneficial effects: according to the invention, the matching degree of the air flow outflow angle of the impeller outlet and the inlet of the guide vane is identified by detecting the pressure at the two sides of the inlet position of the guide vane, the inner ring is actively controlled to rotate until the inlet setting angle of the vane body is matched with the incoming flow, and the impact effect of gas is eliminated, so that noise is eliminated; the inlet section isolates vibration towards the transmission of the device main suction inlet through a corrugated pipe structure, the main shaft and the main motor isolate vibration towards the transmission of the main motor through an elastic sleeve pin coupler, the impeller runner is layered, the non-uniformity of airflow flowing in the impeller can be reduced, noise generation conditions are also inhibited, noise factors are eliminated from multiple angles, and the centrifugal fan has larger functional force and does not influence the surrounding environment.
Drawings
The accompanying drawings are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate the invention and together with the embodiments of the invention, serve to explain the invention. In the drawings:
FIG. 1 is a schematic view of the overall structure of the present invention;
FIG. 2 is a schematic illustration of the change in impeller speed triangle of the impeller exit velocity as gas passes through the fan;
FIG. 3 is an axial schematic view of an impeller, vane, volute of the present invention;
fig. 4 is view a of fig. 3;
FIG. 5 is a schematic view of the structure of the vane and indexing motor of the present invention;
FIG. 6 is a schematic view of the structure of the pressure distribution assembly of the present invention;
FIG. 7 is a schematic diagram of the forward and reverse wiring of the indexing motor of the present invention;
FIG. 8 is a vane axial schematic of the present invention;
FIG. 9 is a schematic view of the inlet section of the present invention;
FIG. 10 is a schematic view of the construction of the impeller of the present invention;
in the figure: 1-inlet section, 11-pipe body, 12-flange, 13-bellows, 14-front cover matching plate, 2-impeller, 21-front cover plate, 22-back cover plate, 23-blade, 24-division plate, 25-hub, 3-guide vane, 31-inner ring, 32-blade body, 321-leading hole, 33-outer ring, 34-matching pressure component, 341-shell, 342-position changing piece, 343-switch rod, 344-electrode group, 35-leading pipe, 4-volute, 5-cover, 6-main shaft, 7-main motor and 8-position changing motor.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
The active noise elimination type high-speed centrifugal fan comprises an inlet section 1, an impeller 2, a guide vane 3, a volute 4, a cover 5, a main shaft 6 and a main motor 7, wherein the inlet section 1 and the cover 5 are respectively arranged at two sides of the volute 4, the main motor 7 is arranged on a foundation and is connected with the end part of the cover 5, the main shaft 6 is rotationally arranged on the cover 5, one end of the main shaft 6 is in transmission connection with the main motor 7, the other end of the main shaft 6 is fixedly provided with the impeller 2, the guide vane 3 is arranged in the volute 4 or on the cover 5, and the guide vane 3 is positioned at the periphery of the impeller 2;
the guide vane 3 comprises an inner ring 31, a vane body 32 and an outer ring 33, wherein the inner ring 31 and the outer ring 33 are concentrically arranged, the vane body 32 and the vane body 32 are circumferentially distributed around the main shaft 6, the two ends of the vane body 32 along the radial direction of the main shaft 6 are respectively fixed with the inner ring 31 and the outer ring 33, the inner ring 31 is connected with the volute 4 or the cover 5 in a rotating way, and the inlet mounting angle of the vane body 32 is actively adjusted to be tangential according to the outlet airflow direction of the impeller 2.
As shown in fig. 1 to 4, the fan has a basic centrifugal impeller rotating structure, the addition of the guide vane 3 realizes smooth transition of air flow between the impeller 2 and the volute 4, the fluid conveyed by the fan is gas, the gas has compressibility, so when the air flow rate is changed by the fan through the change of the rotating speed, the relation between the flow rate and the rotating speed is different from that of a water pump for conveying liquid, the liquid has incompressibility, when the change of the rotating speed of the impeller causes the change of the flow rate, the rotating speed is in direct proportion to the flow rate, the total pressure is correspondingly changed when the rotating speed of the main shaft of the air conveyed by the fan is changed, the space volume occupied by the air of the unit quantity of substances is changed, the flow rate relative to the flow rate of the air at the outlet of the impeller is correspondingly changed, in fig. 2, β2 is the angle of placement of the impeller 2 blade outlet, U is the peripheral linear velocity of the impeller 2, cr is the radial outflow velocity of air at the impeller outlet, cr is related to the flow rate, C is the absolute velocity of the gas, cu is the projection velocity of the absolute velocity of the gas in the circumferential tangential direction, cu is related to the acting amount, which is not the focus of the subsequent analysis in this application, the present application focuses on the angle θ2 between the absolute velocity C and the circumferential tangential direction, because the compressibility of the gas causes the variation of the gas outflow angle θ2 at different rotational speeds, so the gas at the impeller 2 outlet cannot be smoothly received by the volute 4 and flows together, which is an important source of noise when the fan flow deviates from the rated flow, namely, the impact angle exists between the gas flow and the inner wall of the volute 4, according to the method, the guide vane 3 with the actively adjustable inlet setting angle is added between the impeller 2 and the volute 4, after the outlet angle theta 2 of the impeller 2 is changed, the inlet setting angle of the guide vane 3 is also changed, the outlet angle of the outer ring 33 is unchanged, the guide vane is smoothly transited to the inner wall of the volute 4 to be collected and summarized, and flows out of the outlet of the volute 4, the air flow is at a position in which no impact occurs in the fan, the factors of vibration are actively eliminated, and noise is reduced.
At least one blade body 32 is internally provided with two pressure guiding holes 321, one end of each pressure guiding hole 321 extends to two sides of the inlet position of the blade body 32, and the other end of each pressure guiding hole 321 is used as a pressure difference signal to be transmitted to a control structure of the inner ring 31 for angle rotation.
As shown in fig. 4 and 5, when one end of the vane body 32 is pulled to deform and change the inlet setting angle of the guide vane 3, the rotation of the inner ring 31 is completed through an active driving structure, the control of the driving mechanism refers to the compression condition of two surfaces of the vane body 32 at the inlet position, in an ideal state, the air inflow angle of the outlet of the impeller 2 is along the surface of the inlet position of the vane body 32, the pressure on two surfaces of the inlet position of the vane body 32 is equal, at the moment, the inner ring 31 does not need to be rotated, and when the air outflow angle of the outlet of the impeller 2 changes, if the outflow angle theta 2 is smaller than the inlet setting angle alpha of the vane body 32, a low pressure area is formed at the working surface when air passes through the inlet end of the vane body 32, an impact is formed at the back surface of the vane body 32, a high pressure area is formed, two surfaces of the vane body 32 transmit two pressure value information through the pressure guiding holes 321 as control conditions for controlling the rotation of the inner ring, the inner ring 31 is driven to rotate anticlockwise in the view angle of fig. 4, the inlet setting angle alpha of the vane body 32 is reduced to be matched with the air outflow angle theta 2, and the effect of the air at the position of the vane body 32 is eliminated. The blade body 32 has a plurality of blades uniformly distributed on the periphery of the impeller 2, theoretically, only one blade body with pressure guiding holes 321 is needed to detect the pressure difference, but in practice, a plurality of blade bodies with pressure guiding holes 321 are arranged, and the pressure signals are averaged to achieve the effect of more accurate adjustment, however, the process of processing the pressure guiding holes 321 on the blade body 32 is difficult, and the processing is also cost, so that 10-20% of the blade body processing pressure guiding holes 321 are more suitable, the processing of the pressure guiding holes 321 can be directly performed during the blade body forming, the blade body 32 with the pressure guiding holes 321 is formed by 3D printing, the common blade body 32 is formed by conventional injection molding, and the blade body 32 is made of plastic parts so as to have elasticity to adjust the bending quantity.
The centrifugal fan further comprises an indexing motor 8, the guide vane 3 further comprises a pressure distribution assembly 34, the indexing motor 8 is arranged on the inner wall of the end face of the volute 4, the pressure distribution assembly 34 is arranged on the inner ring 31, air pressure is transmitted between the pressure distribution assembly 34 and the pressure guiding hole 321 through a pressure guiding pipe 35, the pressure distribution assembly 34 is electrically connected with the indexing motor 8, the pressure distribution assembly 34 converts pressure difference signals of the two sides of the blade body 32 into forward and reverse rotation signals of the indexing motor 8, the indexing motor 8 is a linear motor, and the output end of the indexing motor 8 is connected with the inner ring 31 through a connecting rod hinged with two ends.
As shown in fig. 5 and 8, the stator part of the indexing motor 8 fixed to the volute casing 4 is stationary, the extension and retraction of the output end corresponds to the clockwise rotation of the inner ring 31, the pressure induced by the pressure guiding hole 321 is converted into a control signal in the pressure distributing assembly 34, the pressure distributing assembly 34 is fixed to the inner ring 31 and rotates along with the inner ring, the pressure guiding hole 321 can be connected with the outer side of the blade body 32 along the axial end part of the main shaft 6, the air tightness of the pressure distributing assembly 34, the pressure guiding pipe 35 and the pressure guiding hole 321 is reduced as much as possible, and the electric connection of the pressure distributing assembly 34 to the indexing motor 8 only needs to use a deformable wire, and the inner ring 31 rotates only by a small angle even if rotating, so that the problem of wire winding does not occur.
The pressure distribution assembly 34 comprises a shell 341, a displacement piece 342, a switch rod 343 and an electrode group 344, the shell 341 is mounted on the inner ring 31, the switch rod 343 is slidably arranged in the shell 341, the displacement piece 342 is arranged in the middle of the switch rod 343, the outer edge of the displacement piece 342 is also sealed with the inner wall of the shell 341, the inner cavity of the shell 341 is divided into two areas by the displacement piece 342, the two areas of the inner cavity of the shell 341 are respectively connected to the pressure guiding holes 321 on the two sides of the blade body 32 through the pressure guiding pipes 35, the displacement piece 342 drives the switch rod 343 to move to one end in response to pressure difference on the two sides, two ends of the switch rod 343 are respectively provided with two groups of metal sheets, the two ends of the shell 341 are respectively provided with the electrode group 344, when the switch rod 343 is positioned at one end of the shell 341, the electrode group 344 at the two ends of the shell 341 is respectively corresponding to two positive and negative electrode wiring modes of the displacement motor 8.
As shown in fig. 6 and 7, when the pressure difference in the inner left side of the casing 341 is greater than the pressure difference in the right side, the pressure difference drives the position changing member 342 to move towards the right side, the switch rod 343 abuts against the right end of the casing 341, at this time, the electrode group 344 at the right end is communicated, a positive and negative wiring circuit of the direct current power supply externally supplied to the indexing motor 8 is conducted, the indexing motor 8 rotates forward to drive the inner ring 31 to rotate until the deformation of the inlet position of the blade body 32 is consistent with the gas inflow angle, after the pressure difference is no longer provided in the chambers on both sides of the casing 341, the switch rod 343 returns to the middle position and is not contacted with both ends, the indexing motor 8 loses power, the inner ring 31 does not rotate any more, and vice versa. In fig. 7, a wiring manner is shown, corresponding to the switch lever 343 supporting against one end of the housing 341, when the switch lever 343 is in the middle position and is not in contact with two ends of the housing 341, the indexing motor 8 is not powered, when the switch lever 343 is close to the left end, the cross wiring branches in the middle position in fig. 7 are connected, the branches on two sides are disconnected, the indexing motor 8 obtains reverse positive and negative poles, and the output end of the indexing motor 8 drives the inner ring 31 to reversely rotate.
The displacement member 342 is a diaphragm. The diaphragm only requires a small pressure differential to deform to move the switch lever 343 to one side, and in the case of a slider structure, a large initial actuation force is required.
The main shaft 6 and the main motor 7 are connected by using an elastic sleeve pin coupling. The elastic sleeve pin coupling reduces the transmission of vibration quantity, only transmits torque, and reduces the transmission of the installation foundation of the vibration main motor 7 at the impeller 2.
The inlet section 1 comprises a pipe body 11, a flange 12 and a corrugated pipe 13, wherein the outer edges of two ends of the pipe body 11 are respectively provided with the flange 12 which is externally connected through the corrugated pipe 13, the diameter of the pipe body 11 is equal to the inlet diameter of the impeller 2, and the length of the pipe body 11 is more than three times of the diameter of the pipe body 11.
As shown in fig. 1 and 9, the bellows 13 prevents the vibration of the fan main body from being transmitted to the air inlet, if the fan main body is open and air-extracted, the vibration is not affected, in addition, the length of the pipe body 11 is as long as possible, so that the incoming air in front of the inlet of the impeller 2 is rectified into smooth air flow as much as possible, if the inlet of the impeller 2 is directly sucked towards the ambient air, the inlet condition is too disturbed, the vibration noise is greatly increased, and the inlet section 1 can be used not as the standard of the product of the application, but for the recommended item of the application, the user can purchase and install.
The inducer 1 further comprises a front cover mating plate 14, the front cover mating plate 14 is mounted between the flange 12 and the volute 4 in a clamped manner, one side end face of the front cover mating plate 14 facing the impeller 2 is provided with a shape matched with the shape of the impeller 2, and a surface gap between the front cover mating plate 14 and the impeller 2 is smaller than two millimeters.
As shown in fig. 1 and 9, the gap between the front cover matching plate 14 and the impeller 2 is the position where the leakage from the outlet to the inlet of the impeller 2 occurs, the gap is as small as possible, and the gap path extends as long as possible, so that the leakage can be reduced, and ineffective work can be reduced.
The impeller 2 comprises a front cover plate 21, a rear cover plate 22, blades 23, a separation plate 24 and a hub 25, wherein a plurality of circumferentially distributed blades 23 are fixed between the front cover plate 21 and the rear cover plate 22, the hub 25 is arranged at the central position of the rear cover plate 22, the hub 25 is connected with the main shaft 6, a plurality of separation plates 24 are further arranged in flow passages between the blades 23, and the separation plates 24 axially layer the flow passages along the main shaft 6.
As shown in fig. 1 and 10, because the lengths of the flow channels of the impeller 2 at the front cover plate 21 and the rear cover plate 22 are different, the working degrees are different, the flow channels at the rear cover plate 22 are longer, the working is more, the gas is compressed more, the gas molecules with more substances are gathered to the rear cover plate 22, the uneven distribution of the gas molecules in the flow channels can cause the occurrence of internal circulation, the noise and vibration are increased, the current flow channels are layered, the migration of the gas molecules in the directions of the front cover plate and the rear cover plate is physically inhibited, and the uniformity of the gas clusters in the flow channels is maintained.
It is noted that relational terms such as first and second, and the like are used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Moreover, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus.
Finally, it should be noted that: the foregoing description is only a preferred embodiment of the present invention, and the present invention is not limited thereto, but it is to be understood that modifications and equivalents of some of the technical features described in the foregoing embodiments may be made by those skilled in the art, although the present invention has been described in detail with reference to the foregoing embodiments. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (7)
1. An initiative noise elimination formula high-speed centrifugal fan, its characterized in that: the centrifugal fan comprises an inlet section (1), an impeller (2), guide vanes (3), a volute (4), a cover (5), a main shaft (6) and a main motor (7), wherein the inlet section (1) and the cover (5) are respectively arranged on two sides of the volute (4), the main motor (7) is placed on a foundation and is connected with the end part of the cover (5), the main shaft (6) is rotationally arranged in the cover (5), one end of the main shaft (6) is in transmission connection with the main motor (7), the impeller (2) is fixedly arranged at the other end of the main shaft (6), the guide vanes (3) are arranged in the volute (4) or on the cover (5), and the guide vanes (3) are positioned at the periphery of the impeller (2);
the guide vane (3) comprises an inner ring (31), a vane body (32) and an outer ring (33), wherein the inner ring (31) and the outer ring (33) are concentrically arranged, the vane body (32) is circumferentially distributed around a main shaft (6), the vane body (32) is respectively fixed with the inner ring (31) and the outer ring (33) along the radial two ends of the main shaft (6), the inner ring (31) is connected with a volute (4) or a cover (5) in a rotating manner, the inlet mounting angle of the vane body (32) is actively adjusted to be tangential according to the outlet airflow direction of the impeller (2), and the outflow angle of the outer ring (33) is unchanged;
two pressure guiding holes (321) are formed in at least one blade body (32), one ends of the two pressure guiding holes (321) extend to two sides of the inlet position of the blade body (32) respectively, and the other ends of the pressure guiding holes (321) serve as pressure difference signals to be transmitted to a control structure of the inner ring (31) for angular rotation;
the centrifugal fan further comprises an indexing motor (8), the guide vane (3) further comprises a pressure distribution assembly (34), the indexing motor (8) is arranged on the inner wall of the end face of the volute (4), the pressure distribution assembly (34) is arranged on the inner ring (31), air pressure is transmitted between the pressure distribution assembly (34) and the pressure guiding hole (321) through a pressure guiding pipe (35), the pressure distribution assembly (34) is electrically connected with the indexing motor (8), the pressure distribution assembly (34) converts pressure difference signals on two sides of the blade body (32) into positive and negative rotation signals of the indexing motor (8), the indexing motor (8) is a linear motor, and the output end of the indexing motor (8) is connected with the inner ring (31) through a connecting rod hinged at two ends.
2. The active noise-abatement type high-speed centrifugal fan according to claim 1, wherein: the pressure distribution assembly (34) comprises a shell (341), a position changing piece (342), a switch rod (343) and an electrode group (344), wherein the shell (341) is mounted on the inner ring (31), the switch rod (343) is arranged in the shell (341) in a sliding mode, the position changing piece (342) is arranged in the middle of the switch rod (343), the outer edge of the position changing piece (342) is sealed with the inner wall of the shell (341), the inner cavity of the shell (341) is divided into two areas by the position changing piece (342), the two areas of the inner cavity of the shell (341) are respectively connected to two side pressure leading holes (321) of the blade body (32) through pressure leading pipes (35) to the outside, the position changing piece (342) drives the switch rod (343) to move to one end in response to pressure difference of the two sides, two groups of metal sheets are respectively arranged at two ends of the switch rod (343), the two ends of the shell (341) are respectively provided with the electrode group (344), when the switch rod (343) is positioned at one end of the shell (341), the electrode group (344) at the end is conducted, and the electrode group (344) at the two ends of the shell (341) are respectively corresponding to two wiring modes of an index motor (8).
3. The active noise-abatement type high-speed centrifugal fan according to claim 2, wherein: the displacement member (342) is a diaphragm.
4. The active noise-abatement type high-speed centrifugal fan according to claim 1, wherein: the main shaft (6) and the main motor (7) are connected by using an elastic sleeve pin coupler.
5. The active noise-abatement type high-speed centrifugal fan according to claim 1, wherein: the inlet section (1) comprises a pipe body (11), a flange (12) and a corrugated pipe (13), wherein the outer edges of two ends of the pipe body (11) are respectively provided with the flange (12) which is externally connected through the corrugated pipe (13), the diameter of the pipe body (11) is equal to the inlet diameter of the impeller (2), and the length of the pipe body (11) is more than three times the diameter of the pipe body.
6. The active noise-abatement type high-speed centrifugal fan according to claim 5, wherein: the inlet section (1) further comprises a front cover matching plate (14), the front cover matching plate (14) is installed between the flange (12) and the volute (4) in a butt-clamping mode, one side end face of the front cover matching plate (14) facing the impeller (2) is provided with a shape matched with the shape of the impeller (2), and a surface gap between the front cover matching plate (14) and the impeller (2) is smaller than two millimeters.
7. The active noise-abatement type high-speed centrifugal fan according to claim 1, wherein: impeller (2) are including preceding apron (21), back shroud (22), blade (23), division board (24), wheel hub (25), fixed a plurality of circumference distribution's blade (23) between preceding apron (21) and back shroud (22), back shroud (22) central point puts and sets up wheel hub (25), wheel hub (25) are connected with main shaft (6), still set up a plurality of division boards (24) in the runner between blade (23), division board (24) are with runner axial layering along main shaft (6).
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| CN202310655725.3A CN116557320B (en) | 2023-06-05 | 2023-06-05 | Active silencing type high-speed centrifugal fan |
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| CN202310655725.3A CN116557320B (en) | 2023-06-05 | 2023-06-05 | Active silencing type high-speed centrifugal fan |
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| CN116557320B true CN116557320B (en) | 2024-01-02 |
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|---|---|
| CN116557320A (en) | 2023-08-08 |
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