CN107989823B - Impeller, centrifugal compressor, and fuel cell system - Google Patents
Impeller, centrifugal compressor, and fuel cell system Download PDFInfo
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- CN107989823B CN107989823B CN201711436819.2A CN201711436819A CN107989823B CN 107989823 B CN107989823 B CN 107989823B CN 201711436819 A CN201711436819 A CN 201711436819A CN 107989823 B CN107989823 B CN 107989823B
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- impeller
- hub
- centrifugal compressor
- back plate
- motor
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- 239000000446 fuel Substances 0.000 title claims abstract description 27
- 238000007789 sealing Methods 0.000 claims description 14
- 230000002093 peripheral effect Effects 0.000 claims description 6
- 230000000149 penetrating effect Effects 0.000 claims description 3
- 238000003754 machining Methods 0.000 claims description 2
- 239000007789 gas Substances 0.000 description 7
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 description 4
- 239000001257 hydrogen Substances 0.000 description 4
- 229910052739 hydrogen Inorganic materials 0.000 description 4
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 3
- 230000008901 benefit Effects 0.000 description 3
- 239000001301 oxygen Substances 0.000 description 3
- 229910052760 oxygen Inorganic materials 0.000 description 3
- 238000010248 power generation Methods 0.000 description 3
- 230000003068 static effect Effects 0.000 description 3
- 230000007704 transition Effects 0.000 description 3
- 238000001816 cooling Methods 0.000 description 2
- 238000003487 electrochemical reaction Methods 0.000 description 2
- 238000001914 filtration Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 239000007800 oxidant agent Substances 0.000 description 2
- 230000001590 oxidative effect Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000011084 recovery Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000009792 diffusion process Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000003912 environmental pollution Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 230000003746 surface roughness 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
- 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
- F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
-
- 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
- F04D29/08—Sealings
- F04D29/083—Sealings 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
- F04D29/26—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
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
- H01M8/00—Fuel cells; Manufacture thereof
- H01M8/04—Auxiliary arrangements, e.g. for control of pressure or for circulation of fluids
- H01M8/04082—Arrangements for control of reactant parameters, e.g. pressure or concentration
- H01M8/04089—Arrangements for control of reactant parameters, e.g. pressure or concentration of gaseous reactants
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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
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/30—Hydrogen technology
- Y02E60/50—Fuel cells
-
- 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
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P70/00—Climate change mitigation technologies in the production process for final industrial or consumer products
- Y02P70/50—Manufacturing or production processes characterised by the final manufactured product
Abstract
The invention provides an impeller, a centrifugal compressor and a fuel cell system. The impeller includes: a hub having a generally concave frusto-conical shape and having a frusto-conical curved surface defining a hub axis of rotation, the hub having a fine end being an air inlet end and a coarse end being an air outlet end; a plurality of large blades and a plurality of small blades extending from the frustoconical curved surface and spaced about the rotational axis of the hub, wherein, in an axial projection view of the impeller, the outermost edges of the large blades and the small blades relative to the rotational axis form an impeller meridian exit angle between-15 degrees and 15 degrees with the rotational axis. The invention also provides a centrifugal compressor and a fuel cell system with the impeller.
Description
Technical Field
The present invention relates to an impeller, a centrifugal compressor having the impeller, and a fuel cell system having the centrifugal compressor, particularly a fuel cell system for a vehicle.
Background
A fuel cell is a power generation device that directly converts chemical energy of fuel and oxidant into electric energy through an electrochemical reaction. Since fuel cells have many advantages, such as high power generation efficiency, little environmental pollution, low noise, wide fuel range, etc., which are incomparable with conventional batteries, they have been widely used in recent years in industries such as automobile industry, energy power generation, marine industry, aerospace, home power supply, etc.
Electrochemical reactions in fuel cells are a complex process in which the oxidant is typically oxygen or air. Studies have shown that the pressure of oxygen in a fuel cell is directly related to the performance of the fuel cell system, and that increasing the supply pressure of air (i.e., the partial pressure of oxygen) can increase the energy density of the fuel cell system. In addition, increasing the air supply pressure of the fuel cell can also reduce the size of the system, reduce the water content in the air, and maintain the water balance in the fuel cell. Therefore, an air supply subsystem dedicated to supplying high-pressure air to the fuel cell is required in the fuel cell system. Currently, impeller-type centrifugal compressors are commonly used as the air supply subsystem of fuel cell systems.
Impeller centrifugal compressors typically include an impeller, an impeller shroud, and an electric motor. The rotating shaft of the impeller and the rotating shaft of the motor are fixed and rotate along with the rotating shaft of the motor, in the running process of the compressor system, air enters the impeller along the axial direction along with the rotation of the motor, energy is transmitted to the air through the rotation of the impeller, static pressure energy and kinetic energy are obtained by the air, the air leaves the impeller along the radial direction along with the rotation of the impeller and enters a downstream diffuser, the air is subjected to speed reduction and pressure increase in the diffuser, the kinetic energy is converted into the static pressure energy, and the pressure is further increased. The pressurized air exits the compressor, is humidified by a humidifier and ultimately enters the fuel cell channels. Because the impeller is constantly rotating, air can be constantly pressurized and pushed out, thereby maintaining a continuous flow of gas in the compressor.
For the existing centrifugal compressor, the volume is large, the structure is not compact enough, and improvement and promotion are still needed in the aspects of improving full-load efficiency, keeping efficiency stable in a flow range, reducing the size of the whole compressor, reducing the number of parts and the like.
Disclosure of Invention
The present invention is directed to the above problems occurring in the prior art, and provides an impeller, a centrifugal compressor having the impeller, and a fuel cell system using the centrifugal compressor.
According to one embodiment of the invention, an impeller comprises: a hub having a generally concave frusto-conical shape and having a frusto-conical curved surface defining a hub axis of rotation, the hub having a fine end being an air inlet end and a coarse end being an air outlet end; a plurality of large blades and a plurality of small blades extending from the frustoconical curved surface and spaced about the rotational axis of the hub; wherein, on the axial plane projection view of the impeller, the radial outlet angle of the impeller is formed between the outermost edge of the big blade and the small blade relative to the rotation axis of the hub and is between-15 degrees and 15 degrees.
According to one embodiment of the invention, the streamline cross-section of the large blade is S-shaped and the streamline cross-section of the small blade is C-shaped.
According to one embodiment of the invention, the ratio of the radius of curvature of the large and small blades to the diameter of the outlet end of the hub is between 0.5 and 2.
According to one embodiment of the invention, the large and small blades are evenly arranged around the rotational axis of the hub.
According to one embodiment of the invention, the bottom of the hub is provided with a sealing structure, which forms a seal with the back plate in the centrifugal compressor.
According to one embodiment of the invention, the sealing structure of the hub is a circular boss or an annular boss extending downwards from the bottom of the hub, and a plurality of annular sealing teeth protruding outwards in radial direction are arranged on the circumferential surface of the circular boss or the annular boss.
According to one embodiment of the invention, the diameter of the circular boss or annular boss is between 50% and 95% of the diameter of the outlet end of the hub, the axial thickness of the circular boss or annular boss is between 4 and 8 mm, and the number of annular seal teeth is 3 to 6.
According to one embodiment of the invention, the diameter of the circular boss or the annular boss is 75% of the diameter of the outlet end of the hub, the axial thickness of the circular boss or the annular boss is between 5 millimeters, and the number of the annular sealing teeth is 6.
According to one embodiment of the invention, the seal teeth are shaped as saw teeth with a tooth tip angle of between 50 and 75 degrees.
According to one embodiment of the invention, the seal teeth are arcuate in shape.
According to one embodiment of the invention, the machining accuracy Ra of the impeller is less than 1.6 microns.
The present invention also provides a centrifugal compressor comprising: an impeller according to any one of claims 1-10; a motor for powering the rotation of the impeller; a back plate fixed to the motor housing; an impeller rotating shaft penetrating through the back plate and fixed with a motor rotating shaft of the motor, the impeller being fixed on the impeller rotating shaft to rotate with the impeller rotating shaft; an impeller shroud secured to the back plate with the impeller positioned between the impeller shroud and the back plate; wherein, seal is formed between the seal structure of impeller and the backplate to impeller pivot and motor pivot are integrative.
According to one embodiment of the invention, the back plate is integral with the housing of the motor.
According to one embodiment of the invention, the impeller is in interference fit with the impeller shaft.
According to one embodiment of the invention, the end of the impeller shaft has a threaded portion, and the nut is screwed onto the threaded portion to fix the impeller on the impeller shaft, wherein the impeller rotates in a direction opposite to the loosening direction of the nut.
According to one embodiment of the invention, the impeller shroud comprises: an axial air inlet provided at a central position of the impeller shroud; a tangential exhaust pipe provided at a peripheral position of the impeller shroud; a plurality of bolt mounting parts which are arranged at the peripheral position of the impeller shield and correspond to the positions of the bolt mounting parts on the back plate and the motor shell, so that the impeller shield, the back plate and the motor shell can be fixed together by bolts at the same time; wherein the plurality of bolt mounting portions are unevenly distributed at the periphery of the impeller shroud.
According to one embodiment of the present invention, the shape of the exhaust pipe is a combination of a straight line and a conic.
According to one embodiment of the invention, the frustoconical curved surface of the hub is smoothly blended with the surface of the back plate.
The present invention also provides a fuel cell system including the centrifugal compressor and the filtering device according to the above embodiments, a fuel cell stack, a cooling system, a humidifier, a hydrogen supply system, a hydrogen recovery device, a control system, and the like.
The impeller according to the invention has blades arranged in such a way that the relative diffusion speed of the gas discharge is more uniform and has a nominal diameter less than the maximum diameter of the multistage centrifugal compressor blades at the same flow rate and pressure ratio. According to the centrifugal compressor, the impeller rotating shaft and the motor rotating shaft are integrated, and the impeller, the impeller shield and the motor are assembled together, so that the structure is more compact, the size of the centrifugal compressor is smaller, the number of parts is reduced, and the production and maintenance cost is remarkably reduced.
Drawings
For a better understanding of the above and other objects, features, advantages and functions of the present invention, reference should be made to the preferred embodiments illustrated in the accompanying drawings. Like reference numerals refer to like parts throughout the drawings. It will be appreciated by those skilled in the art that the drawings are intended to schematically illustrate preferred embodiments of the present invention, and that the various components in the drawings are not drawn to scale.
FIGS. 1A-1C illustrate an impeller according to a preferred embodiment of the present invention;
2A-2B illustrate exemplary axial projection views of blades of an impeller according to a preferred embodiment of the present invention, wherein FIG. 2A illustrates the case when the impeller meridian outlet angle is positive and FIG. 2B illustrates the case when the impeller meridian outlet angle is negative;
FIG. 3 is an enlarged view of a portion of FIG. 1B showing the sealing structure of the impeller;
FIGS. 4A-4B illustrate a centrifugal compressor according to a preferred embodiment of the present invention;
FIG. 5 is an enlarged view of a portion of FIG. 4B, showing the manner in which the impeller is secured to the shaft of the impeller;
FIGS. 6A-6B illustrate an impeller shroud according to a preferred embodiment of the present invention;
FIG. 7 is another enlarged partial view of FIG. 4B showing a conforming transition between the frustoconical curved surface of the hub and the surface of the backplate.
Detailed Description
Hereinafter, an impeller, a centrifugal compressor having the impeller, and a fuel cell system using the centrifugal compressor of the present invention will be described in detail with reference to the accompanying drawings. What has been described herein is merely a preferred embodiment according to the present invention, and other ways of implementing the invention will occur to those skilled in the art on the basis of the preferred embodiment, and are intended to fall within the scope of the invention as well.
Terms of orientation such as "upper", "lower", "left", "right", and the like appearing in the following detailed description refer to the orientation in the specific figures.
Fig. 1A-1C show a side view, a cross-sectional view and a top view, respectively, of an impeller 10 according to a preferred embodiment of the present invention. As shown, the impeller 10 includes a hub 11 and a plurality of blades extending from the hub 11. Therein, it can be seen from fig. 1B that the hub 11 is generally shaped as a truncated cone with a concave surface and has a truncated cone-shaped curved surface S from which a plurality of large blades 12 and a plurality of small blades 13 protrude and are spaced on said surface about the rotation axis A-A of the impeller or hub, i.e. as shown in fig. 1C, each large blade 12 is located between two adjacent small blades 13 and each small blade 13 is located between two adjacent large blades 12. Referring to FIG. 1B, the hub 11 has an upper, finer end that is the air inlet end and a lower, coarser end that is the outlet end after air pressurization, the radius of the outlet end being r 1 . Wherein the cross section of each large blade 12 and each small blade 13 taken along the respective streamline is a streamline cross section, the shape of each large blade 12 in its streamline cross section is S-shaped, and the shape of each small blade 13 in its streamline cross section is C-shaped.
Fig. 2A-2B show exemplary axial projection views of the blades, by which it can be seen that the impeller meridian exit angle of each blade is α, which refers to the angle formed between the outermost edge of the blade relative to the axis A-A and the axis A-A in the axial projection view of the blade, and in a preferred embodiment according to the present invention, the impeller meridian exit angle α is between-15 degrees and 15 degrees. In fig. 2A, the case where the impeller meridian outlet angle α is a positive value is shown, and when the impeller meridian outlet angle α is a negative value, the angles are in opposite directions, as shown in fig. 2B. Here, it is necessary to describe an axial projection of the impeller, and in the art, since the impeller is a revolution body that rotates around an axis, the shapes of the impeller and the blades are generally described by a cylindrical coordinate system, and the "axial (also referred to as meridian plane)" means a plane passing through the axis of the impeller (in the present invention, the axis A-A), and the axial projection means a figure formed by rotating each point on the blades around the axis A-A onto the axial plane.
In a preferred embodiment according to the invention, the radius of curvature at different points of the large blades 12 and the small blades 13 is equal to the diameter 2r of the outlet end of the hub 11 1 The ratio of (2) is between 0.5 and 2.
In a preferred embodiment according to the present invention, the large blades 12 and the small blades 13 are uniformly arranged around the axis A-A, each in eight pieces in number, of course, the number thereof is not limited thereto, and may be more or less.
Returning to fig. 1A and 1B, in a preferred embodiment according to the invention, the bottom of the hub 11 is provided with a sealing structure 14 which forms a seal with the back plate in the centrifugal compressor, thereby reducing the thrust force experienced by the thrust bearing of the centrifugal compressor. Further, the sealing structure 14 may be a circular boss extending downwards from the bottom of the hub 11, and a plurality of annular sealing teeth 141 protruding radially outwards are disposed on the circumferential surface of the circular boss, where the radius of the circular boss is r 2 Its diameter 2r 2 Diameter 2r at the outlet end of the hub 1 Between 50% and 95%, the axial thickness H of the circular boss is between 4 and 8 mm, and the number of annular seal teeth is 3 to 6.
In a further embodiment according to the invention, the diameter 2r of the circular boss 2 May be the diameter 2r of the outlet end of the hub 1 The axial thickness H of the circular boss may be 5 mm and the number of annular seal teeth 141 may be 6.
In other embodiments according to the present invention, the sealing structure 14 may be not a circular boss but an annular boss, and the plurality of annular sealing teeth 141 protruding radially outward as described above may be provided on an outer circumferential surface of the annular boss.
In a preferred embodiment according to the invention, the sealing teeth 141 are shaped as saw-tooth teeth with a tooth tip angle β between 50 and 75 degrees, as shown in fig. 3. Of course, the shape of the seal teeth may also be other shapes, such as an arc.
In a preferred embodiment according to the invention, the impeller has a surface roughness Ra of less than 1.6 microns.
On the other hand, the invention also provides a centrifugal compressor. As shown in fig. 4A to 4B, the centrifugal compressor according to a preferred embodiment of the present invention includes the impeller 10 according to the above-described embodiment, further includes a motor 20 for powering the rotation of the impeller 10, and further includes: a back plate 30 fixed to or integrally formed with the motor housing 22; an impeller rotating shaft 40 penetrating through the back plate 30 and fixed together with the motor rotating shaft 21 of the motor or integrally formed with the motor rotating shaft 21, the impeller 10 being fixed to the impeller rotating shaft 40 to rotate therewith; and an impeller shroud 50 fixed to the back plate 30 with the impeller 10 located between it and the back plate 30; wherein, as previously described, a seal is formed between the seal structure 14 of the impeller 10 and the back plate 30.
In a preferred embodiment according to the present invention, there is an interference fit between the impeller 10 and the impeller shaft 40. In a further preferred embodiment according to the present invention, as shown in fig. 5, the end of the impeller shaft 40 has a screw portion, on which the nut 41 is screwed to fix the impeller 10 to the impeller shaft 40, and in order to prevent the nut 41 from being loosened during use, it is preferable that the loosening direction of the nut 41 is set opposite to the rotation direction of the impeller 10 so that the nut 41 is not loosened but is tightened with the use of the centrifugal compressor.
In a preferred embodiment according to the present invention, as shown in fig. 6A-6B, the impeller shroud 50 includes an axial air inlet 51 for air inflow at a central portion thereof, and an exhaust pipe 52 disposed substantially tangentially at a peripheral portion thereof to facilitate air outflow after pressurization; and a plurality of bolt mounting portions 53, the bolt mounting portions 53 being provided at peripheral positions of the impeller shroud 50, the positions of the bolt mounting portions 53 being overlapped with positions of the bolt mounting portions on the back plate 30 and the motor housing 22 when the impeller shroud is mounted on the centrifugal compressor, so that the impeller shroud 50, the back plate 30 and the motor housing 22 can be simultaneously fixed together by bolts passing therethrough. Further, as shown in fig. 6B, the plurality of bolt mounting portions 53 are unevenly distributed at the periphery of the impeller shroud 50, so that it is possible to function to position the exhaust pipe 52 with respect to the centrifugal compressor, preventing mounting errors.
In a preferred embodiment according to the present invention, the shape of the exhaust pipe 52 is a combination of straight and conic lines.
As can be seen from fig. 4B, the back plate 30 is vaneless, so that the outer bulge 54 of the impeller shroud 50 and the back plate 30 form a vaneless diffuser portion, and when the gas flows through the passage of the diffuser portion, the flow velocity of the front gas molecules decreases due to the increase of the flow passage section, and the rear gas molecules continuously surge toward the front gas molecules, so that most of the kinetic energy of the gas is converted into static pressure energy, and a further pressurizing effect is achieved. In a further preferred embodiment according to the invention, as shown in fig. 7, the frustoconical curved surface S of the hub transitions smoothly to the surface of the back plate 30, in other words the profile of the hub 11 transitions smoothly to the wall profile of the vaneless diffuser section, both being substantially uniform or aligned, and air is able to pass smoothly from the impeller to the diffuser section, which is able to optimise the diffuser action of the diffuser section.
In still another aspect, the present invention also provides a fuel cell system including the centrifugal compressor and the filtering device according to the above embodiments, a fuel cell stack, a cooling system, a humidifier, a hydrogen supply system, a hydrogen recovery device, a control system, and the like.
The scope of protection of the invention is limited only by the claims. Those skilled in the art, having the benefit of the teachings of this invention, will readily recognize alternative constructions to the disclosed structure as viable alternative embodiments, and the disclosed embodiments may be combined to create new embodiments that fall within the scope of the appended claims.
Claims (18)
1. An impeller, the impeller comprising:
a hub having a generally concave frusto-conical shape and having a frusto-conical curved surface defining an axis of rotation of the hub, the hub having a fine end being an air inlet end and a coarse end being an air outlet end;
a plurality of large blades and a plurality of small blades extending from the frustoconical curved surface and spaced about the rotational axis of the hub;
wherein, on an axial plane projection view of the impeller, an impeller meridian plane outlet angle between-15 degrees and 15 degrees is formed between the outermost edge of the big blade and the small blade relative to the rotation axis and the rotation axis,
wherein the cross section of each big blade and each small blade taken along the respective streamline is a streamline cross section, the shape of each big blade in the streamline cross section is S-shaped, and the shape of each small blade in the streamline cross section is C-shaped.
2. The impeller of claim 1, wherein the ratio of the radius of curvature of the large and small blades to the diameter of the outlet end of the hub is between 0.5 and 2.
3. The impeller of claim 2, wherein the large and small blades are evenly arranged about the rotational axis of the hub.
4. An impeller according to claim 3, wherein the bottom of the hub is provided with a sealing structure, which forms a seal with a back plate in a centrifugal compressor.
5. The impeller of claim 4, wherein the sealing structure of the hub is a circular boss or an annular boss extending downward from a bottom of the hub, and a plurality of annular sealing teeth protruding radially outward are provided on a circumferential surface of the circular boss or the annular boss.
6. The impeller of claim 5, wherein the diameter of the circular boss or annular boss is between 50% and 95% of the diameter of the outlet end of the hub, the axial thickness of the circular boss or annular boss is between 4 and 8 millimeters, and the number of annular seal teeth is 3 to 6.
7. The impeller of claim 6, wherein the diameter of the circular boss or annular boss is 75% of the diameter of the outlet end of the hub, the axial thickness of the circular boss or annular boss is between 5 millimeters, and the number of annular seal teeth is 6.
8. The impeller of claim 7, wherein the seal teeth are saw tooth shaped with a tooth tip angle of between 50 and 75 degrees.
9. The impeller of claim 7, wherein the seal teeth are arcuate in shape.
10. The impeller of claim 8, wherein the impeller has a machining accuracy Ra of less than 1.6 microns.
11. A centrifugal compressor, the centrifugal compressor comprising:
an impeller according to any one of claims 1-10;
a motor for powering the rotation of the impeller;
a back plate fixed to the motor housing;
an impeller rotating shaft penetrating through the back plate and fixed with a motor rotating shaft of the motor, the impeller being fixed on the impeller rotating shaft to rotate with the impeller rotating shaft;
an impeller shroud secured to the back plate with the impeller positioned between the impeller shroud and the back plate;
wherein, seal is formed between the seal structure of impeller and the backplate to impeller pivot and motor pivot are integrative.
12. The centrifugal compressor of claim 11, wherein the back plate is integral with a housing of the motor.
13. The centrifugal compressor of claim 11, wherein the impeller is an interference fit with the impeller shaft.
14. The centrifugal compressor according to claim 13, wherein the impeller shaft has a threaded portion at an end thereof, and a nut is screwed onto the threaded portion to fix the impeller to the impeller shaft, wherein a rotation direction of the impeller is opposite to a loosening direction of the nut.
15. The centrifugal compressor of claim 11, wherein the impeller shroud comprises:
an axial air inlet provided at a central position of the impeller shroud;
a tangential exhaust pipe provided at a peripheral position of the impeller shroud;
a plurality of bolt mounting parts which are arranged at the peripheral position of the impeller shield and correspond to the positions of the bolt mounting parts on the back plate and the motor shell, so that the impeller shield, the back plate and the motor shell can be fixed together by bolts at the same time;
wherein the plurality of bolt mounting portions are unevenly distributed at the periphery of the impeller shroud.
16. The centrifugal compressor according to claim 15, wherein said discharge pipe has a shape of a combination of a straight line and a conic line.
17. The centrifugal compressor of claim 16, wherein the frustoconical curved surface of the hub is smoothly transitioned with the surface of the backplate.
18. A fuel cell system comprising a centrifugal compressor according to any one of claims 11-17.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711436819.2A CN107989823B (en) | 2017-12-26 | 2017-12-26 | Impeller, centrifugal compressor, and fuel cell system |
| PCT/CN2018/076402 WO2019127870A1 (en) | 2017-12-26 | 2018-02-12 | Impeller, centrifugal compressor and fuel cell system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711436819.2A CN107989823B (en) | 2017-12-26 | 2017-12-26 | Impeller, centrifugal compressor, and fuel cell system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107989823A CN107989823A (en) | 2018-05-04 |
| CN107989823B true CN107989823B (en) | 2023-12-01 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201711436819.2A Active CN107989823B (en) | 2017-12-26 | 2017-12-26 | Impeller, centrifugal compressor, and fuel cell system |
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| Country | Link |
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| CN (1) | CN107989823B (en) |
| WO (1) | WO2019127870A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11421702B2 (en) | 2019-08-21 | 2022-08-23 | Pratt & Whitney Canada Corp. | Impeller with chordwise vane thickness variation |
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Also Published As
| Publication number | Publication date |
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| WO2019127870A1 (en) | 2019-07-04 |
| CN107989823A (en) | 2018-05-04 |
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