CN217129834U - Two-stage centrifugal impeller fan for air pressurization system of breathing machine - Google Patents
Two-stage centrifugal impeller fan for air pressurization system of breathing machine Download PDFInfo
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- CN217129834U CN217129834U CN202123206678.XU CN202123206678U CN217129834U CN 217129834 U CN217129834 U CN 217129834U CN 202123206678 U CN202123206678 U CN 202123206678U CN 217129834 U CN217129834 U CN 217129834U
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Abstract
The utility model relates to a two-stage centrifugal impeller fan for breathing machine air charge system, include: the device comprises a primary air inlet channel, an outer cover, a primary centrifugal impeller, a motor cover, an interstage air guide impeller, a secondary air inlet channel, a secondary centrifugal impeller, an outlet air guide impeller and a tail cover; an inner rotor brushless motor of the integrated double rotor drives two centrifugal impellers, the rotating speed ranges from 0rpm to 36000rpm, inlet air is accelerated to pass through a first-stage air inlet channel through the first-stage centrifugal impeller, the centrifugal impeller sucks the air and applies work to the air, so that the dynamic pressure of the air is increased, the dynamic pressure of the air is reduced in an air storage channel after the air is expanded, the static pressure is increased, the air flows through an air channel and enters an interstage air guide impeller, and the air flows in the axial direction from radial flow; after entering the secondary air inlet channel, the air is sucked by the secondary centrifugal impeller and does work again to increase the dynamic pressure of the air again, and the air is output after being decelerated and pressurized by the outlet air guide impeller.
Description
Technical Field
The utility model relates to a breathing machine technical field especially relates to a two-stage centrifugal impeller fan for breathing machine air supercharging system, is an axial compressor birotor centrifugal impeller fan that produces the strong positive pressure differential of axial.
Background
Modern ventilators were first shown in Mol-gaard and Lund in copenhagen 1915, and Giertz, a surgeon in Stockholm 1916, and their achievements were silent and only reported in scientific communications. In 1934 Frenkner developed a first pneumatic pressure limiting ventilator, named "Spiropulsator", whose air source came from a steel cylinder and when inhaling, the air passed through two pressure reducing valves to generate a pressure of 50cm of water. In 1940, Frenkner and craft collaborated, and improved on the basis of "Spiropulsator" so that it can be used simultaneously with cyclopropane, the first anesthetic respirator was made. In 1942, american engineers Bennett utility model discloses an oxygen supply apparatus using demand valves, which is used for high-altitude flight. After the development of the intermittent positive pressure ventilator TV-2P in 1948, it was used to treat acute and chronic respiratory failure. The breathing machine brands Jefferson, Morch, Stephenson, Bennett and bird brands were the most widely used breathing machines in the US market in 1955. In the 60 s, with the rapid development of electronic products, ventilators also entered the electronic era. The application of the breathing machine is wider, and the control of the breathing machine is more accurate. The postoperative respirator of Emerson in 1964 is an electric control respirator, the breathing time can be adjusted at will, and a compressed air pump is equipped, and various functions can be adjusted electronically, so that the era that the traditional respirator belongs to simple mechanical motion is fundamentally changed, and the precise electronic era is spanned. Until 1970, pneumatic ventilators controlled by the jet principle were developed, which are ventilators controlled by a gas flow, sensors, logic elements, amplifiers and regulation functions, etc., all using the jet principle without any moving parts, but with the same effect as the circuit. In the 70 s of the 20 th century, due to the development of scientific technology, many sophisticated technologies, especially electronic technologies, were introduced into the design of ventilators, and a large group of new ventilators were made available. New ventilation concepts and technologies are developed and applied, positive end expiratory pressure, continuous positive airway pressure, intermittent mandatory ventilation and T-tube technology are applied. With the rapid development of computer technology since the 80 s, a new generation of multifunctional computer type breathing machine has functions such as monitoring, alarming, recording and the like which cannot be realized in the past. In the 90 s, the breathing machine is continuously developing towards intellectualization, the application of computer technology enables the function of the breathing machine to be more perfect, and the performance is greatly improved.
The air pressurization system provides a positive pressure air source for the respirator, and is an important key technology for designing the respirator. Breathing machine manufacturers at home and abroad invest a great deal of manpower and material resources in an air pressurization system for research and development, and try to master key technologies of the breathing machine manufacturers. A typical booster system fan includes two main parts: a rotating part, namely a motor for stirring air and lifting air pressure and a rotating fan blade; the fixing part stores the shell and the guide vanes which limit the direction of the fluid. Most of fan structures are that a motor drives a fan blade wrapped in a wind cabin to rotate at a high speed to do work, and the purpose of increasing the gas pressure and the flow speed is achieved by means of the gap difference between the fan blade and a shell.
The total pressure ratio of the existing air pressurization system is usually 1.025 times, and the isentropic efficiency index is 50%. Most noninvasive ventilators all use the single-impeller air-blower of terminal surface air inlet, side air-out, and the wind that the terminal surface came in is through the high-speed pressurization of impeller circulation strike the blast hood until export through the air outlet, and it is higher to require the motor rotational speed when this in-process total pressure ratio exceeds 1.025 times, and the circulation strikes the blast hood and leads to diversified noise stack. The main technical difficulty of designing the air pressurization system is to enable the shaft power of the air pressurization system and the brushless motor to be matched through the optimization design of parameters such as the geometric shape, the number of blades, the diameter and the rotating speed of the fan blades of the air pressurization system, so as to obtain higher pressure ratio and higher efficiency. Therefore, the optimal design of the pneumatic appearance of the air system of the breathing machine must rely on a large computational fluid dynamics numerical simulation software platform and a high-performance computer to carry out numerical calculation, and the air pressurization system of the breathing machine with excellent performance is obtained by combining the computational fluid dynamics technology, the ground test testing technology, the material technology, the manufacturing technology and the like.
SUMMERY OF THE UTILITY MODEL
The technical solution problem of the utility model is that: the performance of the air pressurization system of the existing respirator is overcome, and the air pressurization system suitable for low rotating speed, high pressure rise and large flow is provided.
To achieve the above object, the present invention provides a two-stage centrifugal impeller fan for a ventilator air supercharging system, comprising two opposed centrifugal impellers 3, 9.
Further, the device comprises a primary air inlet channel 1, an outer cover 2, a primary centrifugal impeller 3, a motor A4, an integrated supporting end cover 5, a motor B6, an interstage air guide impeller 7, a secondary air inlet channel 8, a secondary centrifugal impeller 9, an outlet air guide impeller 10 and a tail cover 11; the tail part of the primary air inlet channel 1 is arranged on the outer cover 2, the primary centrifugal impeller 3 is arranged on a front end shaft of the motor A4, the integrated supporting end cover 5 is arranged on the outer cover 2, and the motor A4 and the motor B6 are respectively arranged at two ends of the integrated supporting end cover 5 and are used for driving the impeller to rotate; the interstage air guide impeller 7 is installed on the motor B6, the secondary air inlet channel 8 is installed on the interstage air guide impeller 7, the secondary centrifugal impeller 9 is installed on a tail section shaft of the motor B6, the outlet air guide impeller 10 is installed on the tail hood 11, and the tail hood 11 is connected with the outer hood 2 and sealed.
The utility model discloses abandon traditional motor structure, adopted unique integrative support end cover 5 structure, this integrative support end cover 5 is the braced system of whole fan, regard integrative support end cover 5 as the center to support, support dustcoat 2, support motor A4 and motor B6, the bearing position of both ends motor casing is coaxial alignment respectively with integrative support end cover 5 bearing position; the two rotors are fixed at the inner ends of the stator coils through the inner rings of the bearings; motor A4 and motor B6 and integrative support end cover 5 enclose rotor and bearing inside the motor, such design safety, the reliability is high, can guarantee that rotor concentricity and bearing grease are difficult to air-dry.
The utility model discloses an inner rotor brushless motor of integrative birotor, birotor and coil can be simultaneously or independent circular telegram work, (general air-blower only single motor), in case one of them a set of coil or a set of rotor break down, can break off the trouble end power supply fast, another group's motor still can continue to rotate in order to provide atmospheric pressure (emergency action) limitedly, and such setting can play the effect of saving nature under the special occasion.
The double rotors are also inner rotors, the centrifugal impeller can be conveniently placed in the structural form of the inner rotors, and the centrifugal impeller is fixed at the extending end of the rotor shaft, so that the installation is convenient. The two rotors are respectively matched with a centrifugal impeller, the two inner rotors work through the operation of a magnetic field generated by the two groups of coils, the rotating speed of the motor of the inner rotors is high, and the centrifugal impeller can obtain stable high rotating speed as far as possible due to the advantage of small rotating inertia, and meanwhile, the centrifugal impeller has better effects on the aspects of motor vibration and noise.
The brushless motor drives the centrifugal impeller to rotate, the rotating speed range is 0-36000 rpm (Revolutions Per Minute), air is accelerated to reach the inlet speed of the first-stage centrifugal impeller 3 through the first-stage air inlet channel 1, the centrifugal impeller sucks the air and applies work to the air, the dynamic pressure of the air is increased, the air is expanded, the dynamic pressure is reduced, the static pressure is increased, the air flows through an air channel between the outer side of the motor cover and the inner side of the outer cover 2 and enters the interstage air guide impeller 7, and the air flows in the radial direction and then flows in the axial direction; after the air enters the secondary air inlet channel 8, the secondary centrifugal impeller 9 sucks the air and applies work to the air again, so that the dynamic pressure of the air is increased again, and the air is output after being accelerated by the outlet air guide impeller 10.
The primary air inlet 1 is mainly used for air inlet and rectification, guiding airflow to accelerate, inhibiting separation and reducing flow loss. The airflow reaches a certain speed after passing through the first-stage air inlet channel 1 and is matched with the rotating speed of the first-stage centrifugal impeller 3, so that the stalling phenomenon of the centrifugal impeller at an inlet is avoided.
Furthermore, the V-shaped first-stage air inlet channel 1 has a throat area to inlet area ratio of 1: 1.1-1: 1.4, a half cone angle of the air inlet channel of 5-15 degrees and an air inlet channel length of 5-10 mm. The primary air inlet channel 1 is directly fixed at the front end of the outer cover 2.
Further, the first-stage centrifugal impeller 3 and the second-stage centrifugal impeller 9 both adopt centrifugal supercharging impellers, the centrifugal impellers are in twisted sweepback pneumatic shapes, and blade installation angles and chord lengths of the centrifugal impellers are gradually reduced along the axial direction of the centrifugal impellers. The distance between the first-stage centrifugal impeller 3 and the front section of the outer cover 2 is 0.1-1 mm.
Furthermore, the number of blades of the first-stage centrifugal impeller 3 is 8-14, the diameter of the impeller is 38-50 mm, the inlet height is 5-10 mm, and the outlet height is 2-4 mm; the relative thickness of the airfoil profile is 10-30% by adopting NACA series airfoil profile developed by the American national aviation council; the radius of the front edge and the rear edge of the blade is 0.25 mm-1 mm. The helix angle of the blade root is 0-50 degrees along the chord length, the preferred value of the airflow angle of the front edge of the blade root is 10-20 degrees, and the airflow angle of the rear edge of the blade root is 0-15 degrees; the helix angle of the blade tip is 10-50 degrees along the chord length, the airflow angle of the front edge of the blade tip is 30-50 degrees, and the airflow angle of the rear edge of the blade tip is 5-20 degrees.
Furthermore, the interstage air guide impeller 7 adopts a 90-degree spiral petal type design, and the number of blades is 4-10; the air guide impeller is a swirler, and changes radial airflow into axial airflow. The area of the channel of the interstage air guide impeller 7 is in a gradually increasing rule and is designed to be a speed reduction channel, and air flow enters the air guide impeller and then enters the secondary air inlet channel 8 after being subjected to speed reduction and diffusion, so that pressure loss caused by flow reversing is reduced. The height of the interstage air guide impeller 7 is 6 mm-16 mm. In order to reduce the airflow separation at the inlet of the air guide impeller, the radiuses of the front edge and the rear edge of the air guide impeller blade are 0.25 mm-0.5 mm, the spiral angles of the blade tip and the blade root are kept consistent with the airflow angle, and the spiral angles are 0. NACA series airfoil profiles are adopted, and the relative thickness is 5% -15%.
Further, the second-stage centrifugal impeller 9 and the first-stage centrifugal impeller 3 are identical in configuration.
Further, the outlet air guide impeller 10 adopts a 125-degree spiral petal type design, and the number of blades is 4-8; the outlet air guide vane 10 is a swirler which changes the radial air flow into axial air flow. The area of the channel of the outlet air guide impeller 10 is gradually reduced, and the channel is designed to be an accelerating channel, and airflow enters the air guide impeller and then is exhausted in an accelerating way. The height of the outlet air guide impeller 10 is 3 mm-8 mm. In order to reduce the airflow separation at the inlet of the air guide impeller, the radius of the front edge and the rear edge of the air guide impeller blade is 0.1 mm-0.5 mm. The helix angle of the blade root of the air guide impeller blade is 0-150 degrees along the chord length, the flow angle of the blade root front edge is 40-75 degrees, and the flow angle of the blade root rear edge is 10-30 degrees. The helix angle and the air flow angle of the blade tip and the blade root are kept consistent. NACA series airfoil profiles are adopted, and the relative thickness is 5% -15%.
Further, the helix angle and the air flow angle of the radial section position of the centrifugal impeller are specifically as follows:
when the distance between the radial section of the centrifugal impeller and the hub is 0, the leading edge helix angle and the airflow angle of the radial section are respectively 0 degree and 20 degrees, the trailing edge helix angle and the airflow angle are respectively 30 degrees and 10 degrees, wherein B is the span length of the centrifugal impeller blade;
when the distance between the radial section of the centrifugal impeller and the hub is 0.5B, the leading edge helix angle and the airflow angle of the radial section are respectively 6 degrees and 24 degrees, the trailing edge helix angle and the airflow angle are respectively 30 degrees and 11 degrees, wherein B is the span length of the centrifugal impeller blade;
when the distance between the radial section of the centrifugal impeller and the hub is 0.75B, the leading edge helix angle and the airflow angle of the radial section are respectively 10 degrees and 29 degrees, the trailing edge helix angle and the airflow angle are respectively 32 degrees and 12 degrees, wherein B is the span length of the centrifugal impeller blade;
when the distance between the radial section of the centrifugal impeller and the hub is 1B, the leading edge helix angle and the airflow angle of the radial section are 14 degrees and 40 degrees respectively, the trailing edge helix angle and the airflow angle are 33 degrees and 14 degrees respectively, and B is the span length of the centrifugal impeller blade.
The utility model discloses to breathing machine air charge system's operating condition, utilize CFD to carry out numerical simulation and geometric parameter optimal design and obtained the centrifugal impeller of high-pressure ratio, high isentropic efficiency, interstage air guide impeller and export air guide impeller's aerodynamic configuration. Adopt unique integrative bearing structure to an organic whole supports the end cover and supports as the center, is equipped with 2 bearing positions respectively, is equipped with two sets of rotors, and a centrifugal impeller is respectively matchd to birotors. The two groups of rotors and the two groups of coils can be electrified and work independently at the same time. The inner rotor has compact structure, better overall layout of the motor, integration of the rotor and the centrifugal impeller and more contribution to air duct design, and the double-rotor structure ensures that the motor has high rotating speed and small rotational inertia, so that a fan with higher air pressure and larger flow can be designed, and the design problem of an air flowing air cavity is better solved.
Drawings
Fig. 1 is a schematic size diagram of an air booster fan according to the present invention;
FIG. 2 is a schematic view of an air booster fan assembly according to the present invention;
FIG. 3 is a schematic view of structural components of a middle booster fan according to the present invention;
fig. 4 is a schematic size diagram of a centrifugal impeller according to an embodiment of the present invention;
FIG. 5 is a schematic size view of an interstage gas guide impeller in an embodiment of the invention;
FIG. 6 is a schematic size view of an outlet air guide impeller according to an embodiment of the present invention;
fig. 7 is a schematic view of an integrated dual-rotor brushless motor assembly according to the present invention;
FIG. 8 is a schematic view of the leading edge and the trailing edge of a blade according to the present invention;
the device comprises a primary air inlet channel 1, an outer cover 2, a primary centrifugal impeller 3, a motor A4, an integrated supporting end cover 5, a motor B6, an interstage air guide impeller 7, a secondary air inlet channel 8, a secondary centrifugal impeller 9, an outlet air guide impeller 10 and a tail cover 11;
12-a gas flow path;
511-motor front end shaft, 512-motor A front end bearing, 513 primary winding-, 514-motor A rotor magnetic steel, 515-motor A stator silicon steel sheet, 516-motor A casing, 517-motor A rear end bearing;
521-secondary winding, 522-motor B rear end bearing, 523-motor B magnetic steel, 524-motor B stator silicon steel sheet, 525-motor B front end bearing, 526-motor B casing, 527-motor rear end shaft
531-integrally supporting the end cap,
Detailed Description
It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.
Referring to fig. 1 and 2, the utility model provides a two-stage centrifugal impeller fan for breathing machine air charge system mainly includes one-level intake duct 1, dustcoat 2, one-level centrifugal impeller 3, motor A4, integrative support end cover 5, motor B6, interstage air guide impeller 7, second grade intake duct 8, second grade centrifugal impeller 9, export air guide impeller 10 and tail cover 11.
The tail of one-level air inlet channel 1 is installed on outer cover 2, one-level centrifugal impeller 3 is installed on the front end shaft of motor A4, integrative support end cover 5 is installed on outer cover 2, and motor A4 and motor B6 are installed respectively at integrative support end cover both ends for the drive impeller rotates.
The interstage air guide impeller 7 is arranged on the motor cover 6, the secondary air inlet channel 8 is arranged on the interstage air guide impeller 7, the secondary centrifugal impeller 9 is arranged on a tail section shaft of the motor 5, the outlet air guide impeller 10 is arranged on the tail cover 11, and the tail cover 11 is connected with the outer cover 2 and sealed.
The utility model abandons the traditional motor structure, adopts a unique integrated supporting end cover structure, the integrated supporting end cover is a supporting system of the whole fan, and is supported by taking the integrated supporting end cover as a center, supporting the outer cover 2 and supporting the motor A4 and the motor B6, and the bearing positions of the motor shells at the two ends and the bearing positions of the integrated supporting end cover are respectively coaxially aligned; the two rotors are fixed at the inner ends of the stator coils through the inner rings of the bearings; motor A4 and motor B6 and integrative support end cover enclose rotor and bearing inside the motor, such design safety, the reliability is high, can guarantee that rotor concentricity and bearing grease are difficult to air-dry.
The utility model discloses an inner rotor brushless motor of integrative birotor, birotor and coil can be simultaneously or independent circular telegram work, (general air-blower only single motor), in case one of them a set of coil or a set of rotor break down, can break off the trouble end power supply fast, another group's motor still can continue to rotate in order to provide atmospheric pressure (emergency action) limitedly, and such setting can play the effect of saving nature under the special occasion.
The double rotors are also inner rotors, the centrifugal impeller can be conveniently placed in the structural form of the inner rotors, and the centrifugal impeller is fixed at the extending end of the rotor shaft, so that the installation is convenient. The two rotors are respectively matched with a centrifugal impeller, the two inner rotors work through the operation of a magnetic field generated by the two groups of coils, the rotating speed of the motor of the inner rotors is high, and the centrifugal impeller can obtain stable high rotating speed as far as possible due to the advantage of small rotating inertia, and meanwhile, the centrifugal impeller has better effects on the aspects of motor vibration and noise.
The gas flow path of the ventilator air plenum system is shown in fig. 3. The brushless motor drives the centrifugal impeller to rotate, the rotating speed range is 0-36000 rpm (Revolutions Per Minute), air is accelerated to reach the inlet speed of the first-stage centrifugal impeller 3 through the first-stage air inlet channel 1, the centrifugal impeller sucks the air and applies work to the air, so that the dynamic pressure of the air is increased, the dynamic pressure is reduced after the air is subjected to diffusion, the static pressure is increased, the air flows through an air channel between the outer side of the shell and the inner side of the outer cover 2 and enters the interstage air guide impeller 7, and the air flows in the radial direction and then flows in the axial direction; after the air enters the secondary air inlet channel 8, the secondary centrifugal impeller 9 sucks the air and applies work to the air again to increase the dynamic pressure of the air again; after the air enters the outlet air guide impeller 10, the dynamic pressure is reduced, the static pressure is increased, the airflow changes from radial to axial flow again, and finally the airflow is ejected through the air outlet of the tail cover 11.
The primary air inlet 1 is mainly used for air inlet and rectification, guiding airflow to accelerate, inhibiting separation and reducing flow loss. The airflow reaches a certain speed after passing through the first-stage air inlet channel 1 and is matched with the rotating speed of the first-stage centrifugal impeller 3, so that the stalling phenomenon of the centrifugal impeller at an inlet is avoided.
Furthermore, the V-shaped first-stage air inlet channel 1 has a throat area to inlet area ratio of 1: 1.1-1: 1.4, a half cone angle of the air inlet channel of 5-15 degrees and an air inlet channel length of 5-10 mm.
Further, the first-stage centrifugal impeller 3 and the second-stage centrifugal impeller 9 both adopt centrifugal supercharging impellers, the centrifugal impellers are in twisted sweepback pneumatic shapes, and blade installation angles and chord lengths of the centrifugal impellers are gradually reduced along the axial direction of the centrifugal impellers. The distance between the first-stage centrifugal impeller 3 and the front section of the outer cover 2 is 0.1-1 mm.
Further, as shown in fig. 4, the number of the blades of the first-stage centrifugal impeller 3 is 8-14, the diameter of the impeller is 38-50 mm, the inlet height is 5-10 mm, and the outlet height is 2-4 mm; NACA series airfoil profiles developed by the American national aviation consultation Commission are adopted, and the relative thickness is 10-30%; the radius of the front edge and the rear edge of the blade is 0.25 mm-1 mm. The helix angle of the blade root is 0-50 degrees along the chord length, the preferred value of the airflow angle of the front edge of the blade root is 10-20 degrees, and the airflow angle of the rear edge of the blade root is 0-15 degrees; the helix angle of the blade tip is 10-50 degrees along the chord length, the airflow angle of the front edge of the blade tip is 30-50 degrees, and the airflow angle of the rear edge of the blade tip is 5-20 degrees.
Furthermore, the interstage air guide impeller 7 adopts a 90-degree spiral petal type design, and the number of blades is 4-10, as shown in fig. 5; the interstage air guide impeller 7 is a swirler, and changes radial airflow into axial airflow. The area of the channel of the interstage air guide impeller 7 is in a gradually increasing rule and is designed to be a speed reduction channel, and air flow enters the air guide impeller and then enters the secondary air inlet channel 8 after being subjected to speed reduction and diffusion, so that pressure loss caused by flow reversing is reduced. The height of the interstage air guide impeller 7 is 6 mm-16 mm. In order to reduce the airflow separation at the inlet of the air guide impeller, the radius of the front edge and the rear edge of each air guide impeller blade is 0.25-0.5 mm, the helix angle of the root part of each blade of the interstage air guide impeller 7 is 0-90 degrees along the chord length, the preferred value is 0-90 degrees, the helix angle of the blade tip and the blade root is consistent with the airflow angle, and the helix angle is 0. NACA series airfoil profiles are adopted, and the relative thickness is 5% -15%.
Further, the secondary centrifugal impeller 9 and the primary centrifugal impeller 3 have the same geometric configuration.
Further, the outlet air guide impeller 10 adopts a 125-degree spiral petal type design, as shown in fig. 6, the number of blades is 4-8; the outlet air guide vane 10 is a swirler which changes the radial air flow into axial air flow. The area of the channel of the outlet air guide impeller 10 is gradually reduced, and the channel is designed to be an accelerating channel, and airflow enters the air guide impeller and then is exhausted in an accelerating way. The height of the outlet air guide impeller 10 is 3 mm-8 mm. In order to reduce the airflow separation at the inlet of the air guide impeller, the radius of the front edge and the rear edge of the air guide impeller blade is 0.1 mm-0.5 mm. The helix angle of the blade root of the air guide impeller blade is 0-150 degrees along the chord length, the flow angle of the blade root front edge is 40-75 degrees, and the flow angle of the blade root rear edge is 10-30 degrees. The helix angle and the air flow angle of the blade tip and the blade root are kept consistent. NACA series airfoil profiles are adopted, and the relative thickness is 5% -15%.
Further, the helix angle and the air flow angle of the radial section position of the centrifugal impeller are specifically as follows:
when the distance between the radial section of the centrifugal impeller and the hub is 0, the leading edge helix angle and the airflow angle of the radial section are respectively 0 degree and 20 degrees, the trailing edge helix angle and the airflow angle are respectively 30 degrees and 10 degrees, wherein B is the span length of the centrifugal impeller blade;
when the distance between the radial section of the centrifugal impeller and the hub is 0.5B, the leading edge helix angle and the airflow angle of the radial section are respectively 6 degrees and 24 degrees, the trailing edge helix angle and the airflow angle are respectively 30 degrees and 11 degrees, wherein B is the span length of the centrifugal impeller blade;
when the distance between the radial section of the centrifugal impeller and the hub is 0.75B, the leading edge helix angle and the airflow angle of the radial section are respectively 10 degrees and 29 degrees, the trailing edge helix angle and the airflow angle are respectively 32 degrees and 12 degrees, wherein B is the span length of the centrifugal impeller blade;
when the distance between the radial section of the centrifugal impeller and the hub is 1B, the leading edge helix angle and the airflow angle of the radial section are 14 degrees and 40 degrees respectively, the trailing edge helix angle and the airflow angle are 33 degrees and 14 degrees respectively, and B is the span length of the centrifugal impeller blade.
Detailed description of the preferred embodiment 1
The utility model discloses to breathing machine air charge system's operating condition, utilize fluid dynamics simulation software CFD to carry out numerical simulation and geometric parameter optimal design and obtained the centrifugal impeller of high-pressure ratio, high isentropic efficiency, interstage air guide impeller 7 and export air guide impeller 10's aerodynamic configuration.
The ratio of the area of the throat to the area of the inlet of the booster fan is preferably 1:1.15, the half cone angle of the inlet is 10 degrees, the length of the inlet is preferably 6mm, and the distance between the first-stage centrifugal impeller 3 and the front section of the outer cover 2 is 0.2 mm.
The booster fan has a length of 91mm and a diameter of 52 mm. The number of blades of the centrifugal impeller is 10, the diameter of the impeller is 41mm, and the height of an inlet of the impeller is 6.8 mm; the number of the blades of the interstage air guide impeller 7 is 6, the diameter of the impeller is 52mm, the inlet height of the impeller is 14mm, the radius of the front edge of the impeller is 0.25mm, and the radius of the rear edge of the impeller is 0.1 mm. The number of the outlet air guide impeller 10 is 6, the diameter of the impeller is 42mm, the inlet height of the impeller is 6mm, the radius of the front edge of the impeller is 0.25mm, and the radius of the rear edge of the impeller is 0.1 mm.
The preferred value of the flow angle of the leading edge of the blade root of the centrifugal impeller is 20 degrees, and the preferred value of the flow angle of the trailing edge of the blade root is 10 degrees; the preferred value of the blade tip leading edge airflow angle is 40 degrees, and the preferred value of the blade root trailing edge airflow angle is 13 degrees
The preferred value of the blade root leading edge airflow angle of the interstage air guide impeller 7 is 78 degrees, and the preferred value of the blade root trailing edge airflow is 0 degree. The helix angle and the air flow angle of the blade tip and the blade root are kept consistent.
The root leading edge flow angle is preferably 69 and the root trailing edge flow is preferably 20. The helix angle and the air flow angle of the blade tip and the blade root are kept consistent.
The relative thicknesses of the centrifugal impeller, the interstage air guide impeller 7 and the outlet air guide impeller 10 are preferably 15%, 10% and 10%.
Under the condition that the rotating speed of the brushless motor is 25000rpm, the total pressure ratio and the isentropic efficiency of the air supercharging system reach the maximum, the total pressure ratio of 1.033 times (the pressure rise is more than or equal to 3300Pa), the air mass flow rate of 2.4g/s, the air volume flow rate of 117L/s and the isentropic efficiency of 55 percent can be obtained, and the air application temperature is-10 ℃ to 50 ℃.
Test results show that under the condition that the rotating speed of the brushless motor is not less than 25000rpm, the total pressure ratio and the isentropic efficiency of the air pressurization system can be higher, the total pressure ratio is not less than 1.033, the isentropic efficiency is not less than 55%, and the technical requirements of the air pressurization system of the breathing machine can be completely met.
Compare current breathing machine air supercharging system the utility model discloses a design has very big promotion. The utility model discloses a booster impeller adopts centrifugal design, adopts space flight aerodynamic technique to establish breathing machine charge-up system flow model, carries out pneumatic numerical simulation and optimal design to centrifugal impeller on high performance large-scale supercomputer platform, confirms the geometric parameters of impeller and blade number, obtains the centrifugal impeller configuration of higher pressure ratio. The utility model discloses a be the one-level intake duct of "√" shape to optimize the inside appearance of intake duct, combine with the centrifugal impeller design, can greatly improve flow efficiency, reduce the noise of centrifugal impeller in the runner, combine axial compressor birotor design to make the system of centrifugal impeller fan always compare greatly, application temperature range is wide, efficient and reliability height.
The above is only the preferred embodiment of the present invention, and not the scope of the present invention, all the equivalent structures or equivalent flow changes made by the contents of the specification and the drawings or the direct or indirect application in other related technical fields are included in the patent protection scope of the present invention.
Claims (3)
1. The utility model provides a two-stage centrifugal impeller fan for breathing machine air charge system which characterized in that: the device comprises a primary air inlet channel (1), an outer cover (2), a primary centrifugal impeller (3), a motor A (4), an integrated supporting end cover (5), a motor B (6), an interstage air guide impeller (7), a secondary air inlet channel (8), a secondary centrifugal impeller (9), an outlet air guide impeller (10) and a tail cover (11); the tail part of the primary air inlet channel (1) is arranged on the outer cover (2), the primary centrifugal impeller (3) is arranged on a front end shaft of the motor A (4), the integral supporting end cover (5) is arranged on the outer cover (2), and the motor A (4) and the motor B (6) are respectively arranged at two ends of the integral supporting end cover (5) and used for driving the impeller to rotate; the interstage air guide impeller (7) is installed on the motor B (6), the secondary air inlet channel (8) is installed on the interstage air guide impeller (7), the secondary centrifugal impeller (9) is installed on a tail section shaft of the motor B (6), the outlet air guide impeller (10) is installed on the tail cover (11), and the tail cover (11) is connected with the outer cover (2) and sealed; wherein the distance between the first-stage centrifugal impeller (3) and the front section of the outer cover (2) is 0.2 mm.
2. The two-stage centrifugal impeller fan for a ventilator air plenum system of claim 1, wherein: the primary air inlet channel (1) is in a V shape, and the area ratio of a throat to an inlet of the air inlet channel is 1.1-1.4; the half cone angle of the air inlet channel is 5-15 degrees, and the length of the air inlet channel is 5-10 mm; the first-stage centrifugal impeller (3) is a centrifugal booster impeller, and the number of blades is 8-14; the diameter of the centrifugal supercharging impeller is 38 mm-50 mm; the height is 5 mm-10 mm, the blade adopts NACA series airfoil profile, and the relative thickness is 10% -30%; the radius of the front edge and the rear edge of the blade is 0.25 mm-1 mm.
3. The two-stage centrifugal impeller fan for a ventilator air plenum system of claim 2, wherein: the interstage air guide impeller (7) adopts a 90-degree spiral petal type design, and the number of blades of the interstage air guide impeller (7) is 6; the interstage air guide impeller (7) is a swirler, radial airflow is changed into axial airflow, the channel area of the interstage air guide impeller (7) is in a gradually increasing rule, so that the airflow enters the air guide impeller and then is subjected to speed reduction and pressure expansion, pressure loss caused by flow reversing is reduced, and the airflow enters the secondary air inlet channel (8); the height of the interstage air guide impeller (7) is 14 mm; the radius of the front edge of a blade of the interstage air guide impeller (7) is 0.25mm, the radius of the rear edge of the blade of the interstage air guide impeller (7) is 0.1mm, the value of the helix angle of the blade root of the blade of the interstage air guide impeller (7) along the chord length is 0-90 degrees, the helix angle and the airflow angle of a blade tip and the blade root are kept consistent, an NACA series airfoil is adopted, and the relative thickness is 10%;
the outlet air guide impeller (10) is designed in a 125-degree spiral petal type mode, the number of blades of the outlet air guide impeller (10) is 6, radial airflow is changed into axial airflow by the outlet air guide impeller (10), the channel area of the outlet air guide impeller (10) is in a gradually decreasing rule, so that the airflow is accelerated and discharged after entering the outlet air guide impeller, the height of the outlet air guide impeller (10) is 5mm, the radius of the front edge of each blade of the outlet air guide impeller (10) is 0.25mm, the radius of the rear edge of each blade of the outlet air guide impeller (10) is 0.1mm, the helix angle of the root of each blade is 0-150 degrees along the chord length, the airflow angle of the front edge of each blade root is 40-75 degrees, the airflow angle of the rear edge of each blade is 10-30 degrees, and the helix angle and the airflow angle of each blade root are consistent with the blade tip.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202123206678.XU CN217129834U (en) | 2021-12-17 | 2021-12-17 | Two-stage centrifugal impeller fan for air pressurization system of breathing machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202123206678.XU CN217129834U (en) | 2021-12-17 | 2021-12-17 | Two-stage centrifugal impeller fan for air pressurization system of breathing machine |
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| Publication Number | Publication Date |
|---|---|
| CN217129834U true CN217129834U (en) | 2022-08-05 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202123206678.XU Active CN217129834U (en) | 2021-12-17 | 2021-12-17 | Two-stage centrifugal impeller fan for air pressurization system of breathing machine |
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| Country | Link |
|---|---|
| CN (1) | CN217129834U (en) |
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2021
- 2021-12-17 CN CN202123206678.XU patent/CN217129834U/en active Active
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