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CN111486115A - Direct-drive high-speed permanent magnet centrifugal blower and blower unit - Google Patents

Direct-drive high-speed permanent magnet centrifugal blower and blower unit Download PDF

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Publication number
CN111486115A
CN111486115A CN202010293875.0A CN202010293875A CN111486115A CN 111486115 A CN111486115 A CN 111486115A CN 202010293875 A CN202010293875 A CN 202010293875A CN 111486115 A CN111486115 A CN 111486115A
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China
Prior art keywords
volute
blower
motor
impeller
inlet
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Pending
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CN202010293875.0A
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Chinese (zh)
Inventor
邵准远
徐建锋
刘燕潇
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Zhejiang Shangfeng Hi Tech Specialized Wind Industrial Co ltd
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Zhejiang Shangfeng Hi Tech Specialized Wind Industrial Co ltd
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Priority to CN202010293875.0A priority Critical patent/CN111486115A/en
Publication of CN111486115A publication Critical patent/CN111486115A/en
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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/001—Testing thereof; Determination or simulation of flow characteristics; Stall or surge detection, e.g. condition monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/008—Stop safety or alarm devices, e.g. stop-and-go control; Disposition of check-valves
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • 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
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/462—Fluid-guiding means, e.g. diffusers adjustable 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially 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
    • F04D29/663—Sound attenuation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

The invention discloses a direct-drive high-speed permanent magnet centrifugal blower and a blower unit, wherein the blower comprises: the volute comprises a front cover plate, a volute, a motor, an impeller and a diffuser and is characterized in that the front cover plate is connected with the volute, the diffuser is arranged at the inlet of a rotating channel of the volute, and the volute is connected with the motor through a flange; a matching surface is arranged between the volute and the motor, so that the center of the volute is aligned with the center of the motor; the impeller is directly hung on the motor shaft and is connected with the motor shaft in a double-key mode, and the air blower further comprises a motor water inlet and a motor water outlet. The direct-drive high-speed permanent magnet centrifugal blower and the blower unit can effectively solve the problems of low efficiency, high noise, large volume, low intellectualization, high failure rate and the like of the conventional blower, and provide the direct-drive high-speed permanent magnet centrifugal blower and the blower unit with high efficiency, low noise and intellectualization integration for various industries.

Description

Direct-drive high-speed permanent magnet centrifugal blower and blower unit
Technical Field
The invention relates to the technical field of air blowers, in particular to a direct-drive high-speed permanent magnet centrifugal air blower and an air blower unit.
Background
The fluid machinery is a mechanical device which takes fluid as a working medium to convert energy, converts different energy sources into pressure energy and kinetic energy, and is a core driving device in many fields, wherein a blower is one of high-energy-consumption power devices in the fluid machinery. The blowers widely used in the industry comprise a Roots blower, a multi-stage blower, a single-machine high-speed blower and the like, the devices have low efficiency, high noise, large volume, high failure rate and low intellectualization, for example, the Roots blower has the operation polytropic efficiency of mostly between 30 and 50 percent and the operation noise of mostly between 115 and 120db (A), which provides great challenge for the energy conservation and emission reduction industry of China. The existing magnetic suspension air blower and air suspension air blower have certain advantages in the aspects of efficiency, noise, intellectualization and the like, but the production cost of equipment is higher and the cost performance is lower. In particular, when the air suspension blower is started, the shaft and the air bearing have friction, so that the failure rate is generally high; the pneumatic system is greatly influenced by the environment, the rigidity is small, and the stability is tested.
Therefore, how to realize an air blower with high efficiency, low noise, good stability, high intellectualization and high cost performance is a problem to be solved urgently in the field.
Disclosure of Invention
The invention aims to provide a direct-drive high-speed permanent magnet centrifugal blower and a blower unit aiming at the defects of the prior art. The direct-drive high-speed permanent magnet centrifugal blower and the blower unit can effectively solve the problems of low efficiency, high noise, large volume, low intellectualization, high failure rate and the like of the conventional blower, and provide the direct-drive high-speed permanent magnet centrifugal blower and the blower unit with high efficiency, low noise and intellectualization integration for various industries.
In order to achieve the purpose, the invention adopts the following technical scheme:
a direct drive high speed permanent magnet centrifugal blower comprising: the volute comprises a front cover plate, a volute, a motor, an impeller and a diffuser, wherein the front cover plate is connected with the volute, the diffuser is arranged at the inlet of a rotating channel of the volute, and the volute is connected with the motor through a flange; a matching surface is arranged between the volute and the motor, so that the center of the volute is aligned with the center of the motor; the impeller is directly hung on the motor shaft and is connected with the motor shaft in a double-key mode, and the air blower further comprises a motor water inlet and a motor water outlet.
Further, the diffuser is a widening vaneless diffuser, and specifically meets the following requirements:
rCθ≈cons tan t
ρCm2πb＝m
Figure BDA0002451459660000021
Figure BDA0002451459660000022
Figure BDA0002451459660000023
Figure BDA0002451459660000024
Figure BDA0002451459660000025
Figure BDA0002451459660000026
wherein C is the absolute velocity, CmIs the linear tangential velocity, CθAt streamline normal velocity, α is CmAngle of inclination with respect to C, r2Is the vaneless diffuser inlet radius or impeller outlet radius, r5Is the exit radius of the vaneless diffuser or the inlet radius of the volute, R is the radius from the center of the impeller, b is the diffuser width, ρ is the density, p is the pressure, T is the absolute temperature, R is the gas atmosphereNumber, CfIs coefficient of frictional resistance, CpSpecific heat capacity at constant pressure
Further, the volute is a pear-shaped symmetrical volute, and specifically meets the following requirements:
the flow in the volute satisfies the law of momentum distance:
Cθr＝cons tan t
the volute molded line satisfies the following formula:
Figure BDA0002451459660000031
Figure BDA0002451459660000032
Figure BDA0002451459660000033
Figure BDA0002451459660000034
Figure BDA0002451459660000035
the pear-shaped symmetrical volute is designed as follows:
Figure BDA0002451459660000036
Figure BDA0002451459660000037
Figure BDA0002451459660000038
Figure BDA0002451459660000039
let h be rs-r5
Figure BDA00024514596600000310
Figure BDA0002451459660000041
Substitution of △ A, △ h for dA, dh
Figure BDA0002451459660000042
According to the requirement of trimming sharp corner, △ A is 2S, and S is (0.03-0.07) A
Figure BDA0002451459660000043
Figure BDA0002451459660000044
Wherein, CmIs the linear tangential velocity, CθIs the streamline normal velocity, r is the radius from the center of the impeller, b is the width of any radial position, b5Is the width of the radial position of the diffuser outlet or volute inlet, C5θIs the streamline normal velocity, C, of the diffuser outlet or volute inlet5mIs the streamline tangential velocity, C, of the diffuser outlet or the volute inlet5Absolute speed at diffuser outlet or volute inlet, α5Is C5mAnd C5Angle of (d) rsVolute profile radius, r5Is the vaneless diffuser outlet radius or the volute inlet radius,
Figure BDA0002451459660000045
is any one of
Figure BDA0002451459660000046
Volume flow, Q, at the flow cross-section of the angular position spiral casingV5Is the volume flow at the inlet of the volute,
Figure BDA0002451459660000047
is the position angle in the volute; r is5Is the volute inlet radius; r issIs the volute profile radius; final volute line radius rs', R is the radius at the cusp of the volute shape, where C is the absolute velocity and C ismIs the linear tangential velocity, CθThe streamline normal speed is adopted, and theta s is a volute expansion angle which is 30-50 degrees.
Furthermore, a guide cap is arranged at the front part of the impeller, the lower part of the molded line of the guide cap is tangent to the line of the hub, and the angle of the center position of the guide cap is 70-90 degrees.
Further, the air blower further comprises a base, the motor is connected with the base through bolts, and jackscrews connected with the base are arranged under the volute.
Further, the impeller is a three-dimensional flow controllable vortex impeller which is five-axis fine-machining high-strength aluminum alloy and is a semi-open type three-dimensional flow impeller, the attack angle of an inlet wing tip is 0-1 degree, and the attack angle of an inlet wing root is 2-4 degrees; the outlet angle of the blade is-30 degrees to-40 degrees; the hub ratio is 0.4-0.5; the thickness of the blade is that the tail edge of the front edge is small, the middle is large, the wing root is large, and the wing tip is small.
Furthermore, the front cover plate is a gap-controllable cover plate, so that the installation height of the front cover plate and the volute can be adjusted.
The invention also provides a direct-drive high-speed permanent magnet centrifugal blower unit, which comprises the direct-drive high-speed permanent magnet centrifugal blower, and is characterized by further comprising: and the water cooling system is connected with a water inlet of a motor of the air blower and provides corresponding water cooling capacity for the air blower.
Further, the centrifugal blower unit further comprises a controller, the controller is connected with the blower and comprises a sensor unit and a control unit, and the control unit analyzes information collected by the sensor unit and judges the running state of the blower.
Furthermore, the centrifugal blower unit further comprises a noise elimination through-flow box body, the blower, the water cooling system and the controller are arranged in the noise elimination through-flow box body, and the noise elimination through-flow box body contains wavy noise elimination cotton and a filtering system and has a self-absorption cooling function.
Compared with the prior art, the direct-drive high-speed permanent magnet centrifugal blower and the blower unit provided by the invention have the following advantages:
(1) the direct-drive high-speed permanent magnet centrifugal blower and the blower unit can effectively solve the problems of low efficiency, high noise, large volume, low intellectualization, high failure rate and the like of the existing blower, and provide high-efficiency, low-noise and intellectualized integrated direct-drive high-speed permanent magnet centrifugal blower and blower unit for various industries;
(2) the invention adopts a variable-width vaneless diffuser. The flow state of an outlet of the impeller is controlled by slightly reducing the pressure in a diffusion section, so that dynamic pressure is converted into static pressure, the working condition range of equipment is widened, surging is controlled, and the efficiency of the fan is improved; performing adaptive calculation and design on each parameter of the variable-width vaneless diffuser according to required parameters of the blower;
(3) the invention adopts the pear-shaped symmetrical volute, so that the air flow from the diffuser is fully and smoothly guided and diffused, and the adaptability calculation and design of each parameter of the pear-shaped symmetrical volute are carried out according to the required parameters of the blower;
(4) the matching surface is arranged between the volute and the motor, so that the center of the volute is ensured to be aligned with the center of the motor, and a rotating part and a static part are prevented from colliding with the housing due to the fact that the volute and the motor are not aligned;
(5) the impeller and the motor shaft are directly connected in a double-key mode, and the impeller is directly hung on the motor shaft and is in a direct-drive mode without intermediate process loss due to the fact that the rotating speed of the motor is high and has better stability compared with a single-key structure;
(6) the guide cap is connected with the impeller through a key or a pin, the lower part of the molded line of the guide cap is tangent to the hub line, the angle of the central position of the guide cap is 70-90 degrees, and the guide effect is good;
(7) the jackscrew connected with the base is arranged right below the volute, so that the stability of a product can be improved, the vibration can be reduced, the screw can be unscrewed, water can be discharged, and the fan can be cleaned;
(8) the three-dimensional flow controllable vortex impeller has the advantages of wide high-efficiency area, high impeller efficiency, wide high-efficiency area, good strength performance and capability of controlling the stall and surge of the impeller;
(9) the cover plate is a controllable gap cover plate, the installation height can be adjusted according to the impeller, and the safety reliability and the pneumatic performance of the fan are improved;
(10) the invention adopts a water cooling mode to forcibly cool the gas, thereby avoiding the overhigh exhaust temperature of the blower and improving the running safety of the blower; the water cooling system has small operation power and is energy-saving and efficient;
(11) the blower unit comprises the noise elimination through-flow box body, so that the noise of the blower is greatly reduced, and the noise elimination through-flow box body also has a self-absorption cooling function, so that electric components in the box body are cooled without additional cooling of a fan, and the service life of the electric components is prolonged;
(12) the blower unit comprises a controller for collecting information such as air volume, air pressure, temperature, vibration and the like of the blower in real time. The control unit integrates an intelligent control function, analyzes information collected by the sensor, judges the running state of the air blower, prevents surging, faults and the like, and enables the equipment to run in a safe and efficient area all the time. Meanwhile, when the conditions such as air blower faults occur, early warning is carried out in real time, loss caused by the air blower faults is reduced to the maximum extent, and the intelligence of the air blower is improved.
Drawings
FIG. 1 is a schematic structural diagram of a direct-drive high-speed permanent magnet centrifugal blower;
FIG. 2 is a schematic of a velocity triangle in a diffuser;
FIG. 3 is a schematic view of a pear-shaped volute design calculation;
FIG. 4 is a schematic structural diagram of a direct-drive high-speed permanent magnet centrifugal blower unit;
in the figure, 1-a front cover plate, 2-a cover plate and volute bolt, 3-a blade, 4-a hub, 5-a volute and motor connecting bolt, 6-a motor water inlet, 7-a motor water outlet, 8-a high-speed permanent magnet motor, 9-a motor and base connecting bolt, 10-a base, 11-a base connecting jackscrew below the volute, 12-a guide cap and impeller connecting bolt, 13-a guide cap, 14-a cooling system, 15-a direct-drive high-speed permanent magnet centrifugal blower, 16-a controller, 17-a silencing guide box body and 18-the volute.
Detailed Description
The embodiments of the present invention are described below with reference to specific embodiments, and other advantages and effects of the present invention will be easily understood by those skilled in the art from the disclosure of the present specification. The invention is capable of other and different embodiments and of being practiced or of being carried out in various ways, and its several details are capable of modification in various respects, all without departing from the spirit and scope of the present invention. It is to be noted that the features in the following embodiments and examples may be combined with each other without conflict.
It should be noted that the drawings provided in the following embodiments are only for illustrating the basic idea of the present invention, and the drawings only show the components related to the present invention rather than being drawn according to the number, shape and size of the components in actual implementation, and the form, quantity and proportion of each component in actual implementation can be changed freely.
The invention is further described with reference to the following drawings and specific examples, which are not intended to be limiting.
Example one
As shown in fig. 1, the present embodiment provides a direct-drive high-speed permanent magnet centrifugal blower, including: front shroud 1, spiral case 18, motor 8, impeller, diffuser.
A diffuser is arranged at the inlet of a rotating channel of the volute, the volute is connected with the motor through a flange and is further connected and fixed with a motor connecting bolt 5 through the volute. The matching surface is arranged between the volute and the motor, so that the center of the volute and the center of the motor are ensured to be aligned, and the rotating part and the static part are prevented from colliding with the housing due to the fact that the volute and the motor are not aligned. The impeller includes blade 3, wheel hub 4 etc. and the impeller is direct with the double bond form with the motor shaft to be connected, because motor speed is high, compares in single bond structure, possesses better stability, and the impeller is directly hung on the motor shaft, is the direct drive formula, does not have the intermediate process loss. The front cover plate is connected with the volute, and specifically, the front cover plate is connected with the volute through the front cover plate and the volute bolt 2.
In addition, the front part of the impeller of the blower is provided with a flow guide cap 13, the flow guide cap is connected with the impeller through a key or a pin, the lower part of the molded line of the flow guide cap is tangent to the line of the hub, the angle of the central position of the flow guide cap is 70-90 degrees, and the flow guide effect is good. As shown in fig. 1, the connecting bolt of the deflector cap and the impeller is 12. The blower is also provided with a matched base 10, and the motor and the base are connected through a motor and a base connecting bolt 9. A jackscrew 11 connected with the base is arranged right below the volute, so that the stability of a product can be improved, vibration is reduced, a screw can be unscrewed, water is discharged, and a fan is cleaned.
Specifically, the motor is a high-speed permanent magnet stepless speed regulating motor, and the impeller can be a three-dimensional controllable vortex impeller. The three-dimensional flow controllable vortex impeller is a five-axis finish machining high-strength aluminum alloy, the impeller is a semi-open type three-dimensional flow impeller, the attack angle of an inlet wing tip is 0-1 degree, and the attack angle of an inlet wing root is 2-4 degrees; the outlet angle of the blade is-30 degrees to-40 degrees; the hub ratio is 0.4-0.5; the thickness of the blade is that the tail edge of the front edge is small, the middle is large, the wing root is large, and the wing tip is small. Therefore, the three-dimensional flow controllable vortex impeller has the advantages of wide high-efficiency area, high impeller efficiency, wide high-efficiency area, control of stall and surge of the impeller and good strength performance.
Because the impeller is a semi-open impeller, and the gap between the impeller and the cover plate has great influence on the safety reliability and the pneumatic performance of the fan, the installation height of the front cover plate and the volute is adjustable, namely the cover plate is a controllable gap cover plate. Specifically, the controllable gap cover plate has a certain gap with the wing tip of the impeller. The clearance is determined according to the dependent variable of the impeller, and the clearance between the impeller and the cover plate has great influence on the overall performance of the blower, so that the designed cover plate clearance is adjustable, and the height can be adjusted at the cover plate and the volute flange through gaskets in the actual process.
The air flow velocity is quite large due to the outlet of the impeller of the blower, and when the high-velocity air flows into the casing from the outlet of the impeller, large sudden expansion loss is generated due to the sudden expansion of the cross-sectional area of the flow passage. Meanwhile, kinetic energy cannot be sufficiently converted into static pressure energy in the volute, so that the dynamic pressure of the blower is relatively high. For reducing sudden expansion loss and increasing static pressure of blower and its methodEfficiency, the diffuser of the present invention is a vaneless diffuser. The vaneless diffusers vary in width and blower efficiency. Therefore, the present invention further employs a widening vaneless diffuser. The flow state of the outlet of the impeller is controlled by slightly reducing the pressure in the diffusion section, so that the dynamic pressure is converted into static pressure, the working condition range of equipment is widened, surging is controlled, and the efficiency of the fan is improved. FIG. 2 is a triangular diagram of velocity in a diffuser, where C is the absolute velocity and C ismIs the linear tangential velocity, CθAt streamline normal velocity, α is CmAngle of inclination with respect to C, r2Is the vaneless diffuser inlet radius (or impeller exit radius), r5The radius of the outlet of the vaneless diffuser (or the radius of the inlet of the volute) specifically meets the following requirements:
rCθ≈cons tan t
ρCm2πb＝m
Figure BDA0002451459660000081
Figure BDA0002451459660000082
Figure BDA0002451459660000083
Figure BDA0002451459660000091
Figure BDA0002451459660000092
Figure BDA0002451459660000093
where R is the radius from the center of the impeller, b is the diffuser width, ρ is the density, p is the pressure, T is the absolute temperature, R is the gas constant, C is the pressurefIs coefficient of frictional resistance, CpThe specific heat capacity is constant pressure.
And for the inlet and the outlet of the vaneless diffuser, the corresponding radius, width, speed and the like meet the design formula. For example, the design air volume for the blower is 33m3Min, pressure of 60kPa, design rotating speed of 22000rpm, motor power of 39kW, direct-drive impeller hanging on motor shaft without intermediate process loss, and calculating
Figure BDA0002451459660000094
The root part of the variable-width vaneless diffuser is straight, the top part begins to reduce at the outlet of the impeller, and the root part of the variable-width vaneless diffuser starts to reduce at rp＝(0.3～0.5)(r5-r2)+r2Stopping shrinkage, the shrinkage process being linear shrinkage, rp-r5A straight section is arranged between the two sections.
Common volutes include symmetrical volutes and asymmetrical volutes, and symmetrical volutes further include circular volutes, rectangular volutes, pear-shaped symmetrical volutes. Compared with a conventional circular volute, a rectangular volute and an asymmetric volute, the pear-shaped symmetric volute is higher in efficiency, and the air flow coming out of the diffuser can be guided and diffused smoothly and fully. Therefore, the volute is a pear-shaped symmetrical volute.
Flow rate in volute casing following circumferential angle
Figure BDA0002451459660000095
Satisfies the following formula:
Figure BDA0002451459660000096
Figure BDA0002451459660000098
is any one of
Figure BDA0002451459660000097
Volume flow on the flow-through cross section of the angular position volute; qV5Is the volume flow at the inlet of the volute.
The flow in the volute satisfies the law of momentum distance:
Cθr＝cons tan t
fig. 3 shows a schematic diagram of a pear-shaped volute design calculation, and the volute profile satisfies the following formula:
Figure BDA0002451459660000101
Figure BDA0002451459660000102
Figure BDA0002451459660000103
Figure BDA0002451459660000104
Figure BDA0002451459660000105
Cmis the linear tangential velocity, CθIs the streamline normal velocity, r is the radius from the center of the impeller, b is the width of any radial position, C5θIs the streamline normal velocity, C, of the diffuser outlet or volute inlet5mIs the streamline tangential velocity, C, of the diffuser outlet or the volute inlet5Absolute speed at diffuser outlet or volute inlet, α5Is C5mAnd C5Angle of (d) rsVolute profile radius, r5Is the vaneless diffuser exit radius (or volute inlet radius),
Figure BDA0002451459660000106
is any one of
Figure BDA0002451459660000107
The volume flow on the flow-through cross-section of the angular position volute,
Figure BDA0002451459660000108
is the position angle in the volute.
Specifically, the pear-shaped symmetrical volute is designed as follows:
Figure BDA0002451459660000109
Figure BDA00024514596600001010
Figure BDA00024514596600001011
Figure BDA00024514596600001012
let h be rs-r5
Figure BDA0002451459660000111
Figure BDA0002451459660000112
Substitution of △ A, △ h for dA, dh
Figure BDA0002451459660000113
According to the requirement of trimming sharp corner, △ A is 2S, and S is (0.03-0.07) A
Figure BDA0002451459660000114
Figure BDA0002451459660000115
Wherein the circumferential angle
Figure BDA0002451459660000116
The unit is radian; r is5Is the volute inlet radius; r issIs the volute profile radius; byTwo sharp corners of the trapezoidal volute are not beneficial to gas flow, the final volute shape is a pear-shaped symmetrical volute, and the final volute line radius rs', R is the radius at the cusp of the volute shape, where C is the absolute velocity and C ismIs the linear tangential velocity, CθThe streamline normal speed is adopted, and theta s is a volute expansion angle which is 30-50 degrees.
When the exhaust temperature of the blower is high, thermal state gaps among the impellers and between the impellers and the casing become small, and the impellers and the casing are mutually clamped seriously. In addition, the blower bearings are typically located close to the air cavity and are sensitive to the heat transfer of the air, so that the discharge temperature of the blower should not be too high. The high-speed permanent magnet centrifugal blower adopts a water cooling mode to forcibly cool gas. Therefore, the blower of the invention further comprises a motor water inlet 6 and a motor water outlet 7. In order to improve the sealing performance of the blower, the rotating part and the static part of the direct-drive high-speed permanent magnet centrifugal blower are not provided with other sealing rings, are absolutely sealed and have no leakage loss.
Example two
As shown in fig. 4, the present embodiment provides a direct-drive high-speed permanent magnet centrifugal blower unit, including: a direct-drive high-speed permanent magnet centrifugal blower 15, a water cooling system 14, a controller 16 and a silencing through-flow box 17.
As mentioned above, the present invention uses water cooling to forcibly cool the gas. Therefore, in order to ensure that the high-speed permanent magnet centrifugal blower operates normally, the blower needs to be matched with a water cooling system, and the water cooling system is connected with a motor water inlet of the blower. The matched water cooling system provides corresponding water cooling capacity for the blower, and meanwhile, the system is guaranteed to have low running power, energy conservation and high efficiency under the condition of ensuring the cooling capacity. The direct-drive high-speed permanent magnet centrifugal blower unit is as described in the first embodiment, and the water cooling system may be any existing high-efficiency and energy-saving cooling system, which is not described herein again.
In addition, the direct-drive high-speed permanent magnet centrifugal blower unit also comprises a noise elimination through-flow box body so as to realize a low-noise blower. Specifically, the blower, the water cooling system and the controller are arranged in the silencing through-flow box body, and the silencing through-flow box body contains wavy silencing cotton and a filtering system to reduce the noise of the blower unit. The silencing through-flow box body also has a self-absorption cooling function, electric components in the box body are cooled, extra fans are not needed for cooling, and the service life of the electric components is prolonged.
In order to improve the intelligence of the blower, the direct-drive high-speed permanent magnet centrifugal blower unit further comprises a controller, and the controller is connected with the blower. Specifically, the controller comprises a sensor unit and a control unit, wherein the sensor unit comprises sensors of air volume, air pressure, temperature, vibration and the like, so as to collect information of the air volume, the air pressure, the temperature, the vibration and the like of the air blower in real time. The control unit integrates an intelligent control function, analyzes information collected by the sensor, judges the running state of the air blower, prevents surging, faults and the like, and enables the equipment to run in a safe and efficient area all the time. Meanwhile, when the conditions such as air blower faults occur, early warning is carried out in real time, and loss caused by the air blower faults is reduced to the maximum extent.
Therefore, the direct-drive high-speed permanent magnet centrifugal blower and the blower unit can effectively solve the problems of low efficiency, high noise, large volume, low intellectualization, high failure rate and the like of the conventional blower, and provide the direct-drive high-speed permanent magnet centrifugal blower and the blower unit which are efficient, low noise and intellectualized for various industries; a wide-width vaneless diffuser is used. The flow state of an outlet of the impeller is controlled by slightly reducing the pressure in a diffusion section, so that dynamic pressure is converted into static pressure, the working condition range of equipment is widened, surging is controlled, and the efficiency of the fan is improved; performing adaptive calculation and design on each parameter of the variable-width vaneless diffuser according to required parameters of the blower; the pear-shaped symmetrical volute is adopted, so that the air flow from the diffuser is fully and smoothly guided and diffused, and the adaptability calculation and design of each parameter of the pear-shaped symmetrical volute are carried out according to the required parameters of the air blower; a matching surface is arranged between the volute and the motor, so that the center of the volute and the center of the motor are ensured to be aligned, and a rotating part and a static part are prevented from colliding with the housing due to the fact that the volute and the motor are not aligned; the impeller is directly connected with the motor shaft in a double-key mode, and compared with a single-key structure, the impeller has better stability due to high rotating speed of the motor, is directly hung on the motor shaft and is in a direct-drive mode, and no intermediate process loss exists; the guide cap is connected with the impeller through a key or a pin, the lower part of the molded line of the guide cap is tangent to the hub line, the angle of the central position of the guide cap is 70-90 degrees, and the guide effect is good; a jackscrew connected with the base is arranged right below the volute, so that the stability of a product can be improved, the vibration can be reduced, a screw can be unscrewed, water can be discharged, and a fan can be cleaned; the three-dimensional flow controllable vortex impeller has wide high-efficiency area, high impeller efficiency and wide high-efficiency area, controls the stall and surge of the impeller and has good strength performance; the cover plate is a controllable gap cover plate, the installation height can be adjusted according to the impeller, and the safety reliability and the pneumatic performance of the fan are improved; the water cooling mode is adopted to cool the gas forcibly, so that the overhigh exhaust temperature of the blower is avoided, and the running safety of the blower is improved; the water cooling system has small operation power and is energy-saving and efficient; the blower unit comprises a noise elimination through-flow box body, so that the noise of the blower is greatly reduced, the noise elimination through-flow box body also has a self-absorption cooling function, electric components in the box body are cooled, an additional fan is not needed for cooling, and the service life of the electric components is prolonged; the blower unit comprises a controller, and the blower unit collects information such as air volume, air pressure, temperature, vibration and the like of the blower in real time. The control unit integrates an intelligent control function, analyzes information collected by the sensor, judges the running state of the air blower, prevents surging, faults and the like, and enables the equipment to run in a safe and efficient area all the time. Meanwhile, when the conditions such as air blower faults occur, early warning is carried out in real time, loss caused by the air blower faults is reduced to the maximum extent, and the intelligence of the air blower is improved.
It is to be noted that the foregoing is only illustrative of the preferred embodiments of the present invention and the technical principles employed. It will be understood by those skilled in the art that the present invention is not limited to the particular embodiments described herein, but is capable of various obvious changes, rearrangements and substitutions as will now become apparent to those skilled in the art without departing from the scope of the invention. Therefore, although the present invention has been described in greater detail by the above embodiments, the present invention is not limited to the above embodiments, and may include other equivalent embodiments without departing from the spirit of the present invention, and the scope of the present invention is determined by the scope of the appended claims.

Claims (10)

1. A direct drive high speed permanent magnet centrifugal blower comprising: the volute comprises a front cover plate, a volute, a motor, an impeller and a diffuser and is characterized in that the front cover plate is connected with the volute, the diffuser is arranged at the inlet of a rotating channel of the volute, and the volute is connected with the motor through a flange; a matching surface is arranged between the volute and the motor, so that the center of the volute is aligned with the center of the motor; the impeller is directly hung on the motor shaft and is connected with the motor shaft in a double-key mode, and the air blower further comprises a motor water inlet and a motor water outlet.
2. The centrifugal blower according to claim 1, wherein the diffuser is a wide-width vaneless diffuser, specifically satisfying:
rCθ≈constant
ρCm2πb＝m
Figure FDA0002451459650000011
Figure FDA0002451459650000012
Figure FDA0002451459650000013
Figure FDA0002451459650000014
Figure FDA0002451459650000015
Figure FDA0002451459650000016
wherein C is the absolute velocity, CmIs the linear tangential velocity, CθAt streamline normal velocity, α is CmAngle of inclination with respect to C, r2Is the vaneless diffuser inlet radius or impeller outlet radius, r5Is the vaneless diffuser exit radius or volute inlet radius, R is the radius from the impeller center, b is the diffuser width, ρ is the density, p is the pressure, T is the absolute temperature, R is the gas constant, CfIs coefficient of frictional resistance, CpThe specific heat capacity is constant pressure.
3. The centrifugal blower according to claim 2, wherein the volute is a pear-shaped symmetrical volute that specifically satisfies:
the flow in the volute satisfies the law of momentum distance:
Cθr＝cons tan t
the volute molded line satisfies the following formula:
Figure FDA0002451459650000021
Figure FDA0002451459650000022
Figure FDA0002451459650000023
Figure FDA0002451459650000024
Figure FDA0002451459650000025
the pear-shaped symmetrical volute is designed as follows:
Figure FDA0002451459650000026
Figure FDA0002451459650000027
Figure FDA0002451459650000028
Figure FDA0002451459650000029
let h be rs-r5
Figure FDA00024514596500000210
Figure FDA0002451459650000031
Substitution of △ A, △ h for dA, dh
Figure FDA0002451459650000032
According to the requirement of trimming sharp corner, △ A is 2S, and S is (0.03-0.07) A
Figure FDA0002451459650000033
Figure FDA0002451459650000034
Wherein, CmIs the linear tangential velocity, CθIs the streamline normal velocity, r is the radius from the center of the impeller, b is the width of any radial position, b5Is the width of the radial position of the diffuser outlet or volute inlet, C5θIs the streamline normal velocity, C, of the diffuser outlet or volute inlet5mIs the streamline tangential velocity, C, of the diffuser outlet or the volute inlet5Absolute speed at diffuser outlet or volute inlet, α5Is C5mAnd C5Angle of (d) rsVolute profile radius, r5Is the vaneless diffuser outlet radius or the volute inlet radius,
Figure FDA0002451459650000035
is any one of
Figure FDA0002451459650000036
Volume flow, Q, at the flow cross-section of the angular position spiral casingV5Is the volume flow at the inlet of the volute,
Figure FDA0002451459650000037
is the position angle in the volute; r is5Is the volute inlet radius; r issIs the volute profile radius; final volute line radius rs', R is the radius at the cusp of the volute shape, where C is the absolute velocity and C ismIs the linear tangential velocity, CθThe streamline normal speed is adopted, and theta s is a volute expansion angle which is 30-50 degrees.
4. The centrifugal blower according to claim 1, wherein a guide cap is provided at a front portion of the impeller, a line of the guide cap is tangent to a line of the hub below a molded line of the guide cap, and an angle of a center position of the guide cap is 70 ° to 90 °.
5. The centrifugal blower according to claim 1, further comprising a base, wherein the motor is bolted to the base, and a jackscrew is connected to the base directly below the volute.
6. The centrifugal blower according to claim 1, wherein the impeller is a three-dimensional flow controllable vortex impeller which is a five-axis fine-finished high-strength aluminum alloy, and is a semi-open three-dimensional flow impeller, and the inlet wing tip attack angle is 0 ° to 1 °, and the inlet wing root attack angle is 2 ° to 4 °; the outlet angle of the blade is-30 degrees to-40 degrees; the hub ratio is 0.4-0.5; the thickness of the blade is that the tail edge of the front edge is small, the middle is large, the wing root is large, and the wing tip is small.
7. The centrifugal blower of claim 1, wherein the front cover plate is a controlled clearance cover plate, such that a mounting height of the front cover plate to the volute is adjustable.
8. A direct drive high speed permanent magnet centrifugal blower unit comprising a direct drive high speed permanent magnet centrifugal blower according to any one of claims 1 to 7, further comprising: and the water cooling system is connected with a water inlet of a motor of the air blower and provides corresponding water cooling capacity for the air blower.
9. The centrifugal blower of claim 8, wherein the centrifugal blower unit further comprises a controller, the controller is connected with the blower and comprises a sensor unit and a control unit, and the control unit analyzes information collected by the sensor unit and judges the running state of the blower.
10. The centrifugal blower according to claim 9, further comprising a noise elimination flow box, wherein the blower, the water cooling system and the controller are disposed in the noise elimination flow box, and the noise elimination flow box contains wave-shaped noise elimination cotton and a filtering system and has a self-absorption cooling function.
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