CN114198322A - Centrifugal air compressor based on hydrogen fuel cell engine - Google Patents

Centrifugal air compressor based on hydrogen fuel cell engine Download PDF

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Publication number
CN114198322A
CN114198322A CN202111448658.5A CN202111448658A CN114198322A CN 114198322 A CN114198322 A CN 114198322A CN 202111448658 A CN202111448658 A CN 202111448658A CN 114198322 A CN114198322 A CN 114198322A
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CN
China
Prior art keywords
rotor
stator
air compressor
gas
shell
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Pending
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CN202111448658.5A
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Chinese (zh)
Inventor
殷玉枫
王嘉誉
付良
韩原臻
张锦
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Shanxi Teboyou New Energy Technology Co ltd
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Shanxi Teboyou New Energy Technology Co ltd
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Priority to CN202111448658.5A priority Critical patent/CN114198322A/en
Publication of CN114198322A publication Critical patent/CN114198322A/en
Pending legal-status Critical Current

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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
    • 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
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/057—Bearings hydrostatic; hydrodynamic
    • 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
    • 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
    • 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
    • F04D29/5846—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling by injection
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K3/00—Details of windings
    • H02K3/04—Windings characterised by the conductor shape, form or construction, e.g. with bar conductors
    • H02K3/28—Layout of windings or of connections between windings
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
    • H02K5/161—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields radially supporting the rotary shaft at both ends of the rotor
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/14—Structural association with mechanical loads, e.g. with hand-held machine tools or fans
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02N—ELECTRIC MACHINES NOT OTHERWISE PROVIDED FOR
    • H02N15/00—Holding or levitation devices using magnetic attraction or repulsion, not otherwise provided for

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

The invention discloses a centrifugal air compressor based on a hydrogen fuel cell engine, which comprises a shell, a positioning sleeve, a motor stator, a torque winding and a suspension winding which are arranged on the motor stator, a rotor spindle, a motor rotor and a thrust plate which are fixed with the rotor spindle, a gas bearing part, a volute back plate, a compression volute, an expansion volute, a compression impeller and an expansion impeller. The rotor spindle, the motor rotor and the thrust plate are integrally designed, so that the installation space and the installation process are saved, and a plurality of gas bearing grooves with the outer outlines in the shape of a hummingbird wing are formed in the two end faces of the thrust plate and the rotor spindle. The torque winding and the suspension winding are sequentially sleeved from outside to inside in the radial direction inside the motor stator to provide rotary driving force and controllable radial suspension force for the rotor spindle, so that the rotor spindle can realize suspension work under all working conditions, the service life of the compressor is prolonged, the power consumption is reduced, and the requirements of small size, high speed, large flow and high reliability of the hydrogen fuel cell engine air compressor are met.

Description

Centrifugal air compressor based on hydrogen fuel cell engine
Technical Field
The invention belongs to the technical field of hydrogen fuel cell engines, and particularly relates to a centrifugal air compressor, in particular to a centrifugal air compressor based on a hydrogen fuel cell engine.
Background
With the increasing prominence of environmental and energy problems, new energy engines become research hotspots of various engine manufacturers and research and development institutions in the world, and among them, hydrogen fuel cell engines are generally considered to have wide development prospects with high efficiency and zero pollution emission. The hydrogen fuel cell engine takes hydrogen and oxygen in air as fuel, the hydrogen and the oxygen generate chemical reaction, and chemical energy of the hydrogen and the oxygen is converted into electric energy through electrode chemical reaction, so that the engine is driven to run through a motor. The hydrogen fuel cell engine has the advantages of zero pollution emission, high efficiency, low noise, capability of rapidly supplying fuel and the like, and is widely considered as one of the mainstream development directions of new energy engines in the future.
The most important part of the hydrogen fuel cell engine is a proton exchange membrane reactor, and then an air supply subsystem, namely an air compressor, the proton exchange membrane reactor and the air compressor are equivalent to the heart and the lung of a hydrogen fuel cell power system, and the cardiopulmonary function basically determines the technical level and the performance index of the hydrogen fuel cell system.
Research shows that the oil-free air supply with high pressure ratio and large flow rate has obvious effect on improving the energy conversion efficiency of the pile system. The centrifugal air compressor has the outstanding advantages of no oil, small volume, high rotating speed, large flow, high energy efficiency and the like, and is considered to be the best choice for the air compressor for the proton exchange membrane fuel cell system.
The main structure of the existing centrifugal air compressor comprises a shell, a volute, a motor stator and rotor, a main shaft, a bearing and an impeller from outside to inside, wherein the tail end of the main shaft is connected with the impeller. When the air compressor runs, the motor spindle drives the impeller to rotate at high speed in the volute to supply large-flow and high-pressure air to the hydrogen fuel cell stack. The working impeller of the centrifugal air compressor for rotating and compressing air is generally called as a compression wheel, when a hydrogen fuel cell engine works, hydrogen and air are subjected to chemical reaction in an electric pile to generate water-containing waste gas, and a turbine (called as an expansion wheel) is arranged at the other end of a main shaft of the centrifugal air compressor to recover part of waste gas energy, so that the power consumption of the air compressor is reduced.
The power consumption of the centrifugal air compressor which is practically applied in the current market accounts for 15-20% of the total power output of the hydrogen fuel cell engine, and the centrifugal air compressor is a component with the largest energy consumption of a hydrogen fuel cell system. Mainly the friction-generated losses of the rotor part and the friction losses of the bearing part, making the machine less efficient. In addition, the rotor spindle, the motor rotor and the thrust disc need to be manufactured and installed respectively, parts need to be fixed with the shell, the installation space requirement is large, the process is complex, and the manufacturing and assembling time and the economic cost are high.
Therefore, optimizing the structural design of the centrifugal air compressor and reducing the power consumption thereof is one of the main ways of improving the output power of the hydrogen fuel cell engine at present.
Disclosure of Invention
The invention provides a centrifugal air compressor based on a hydrogen fuel cell engine, which solves the problems of low rotating speed, high power consumption and poor stability of the air compressor of the existing hydrogen fuel cell engine.
In order to solve the technical problems, the technical scheme provided by the invention is as follows: the centrifugal air compressor based on the hydrogen fuel cell engine comprises a shell and an impeller part, wherein the impeller part comprises a first volute back plate and a second volute back plate which are fixed on two sides of the shell; the outer side of the first volute back plate is provided with a compression volute and a compression impeller, the outer side of the second volute back plate is provided with an expansion volute and an expansion impeller, at least one positioning sleeve matched with the inner diameter of the shell is arranged in the shell, and the shell also comprises a rotor part, a stator part and a gas bearing part; the stator part, the rotor part and the gas bearing part are distributed and fixed at intervals through positioning sleeves; the center of the shell is provided with a rotor part which comprises a rotor spindle, a thrust disc and a motor rotor, wherein the thrust disc and the motor rotor are integrally manufactured with the rotor spindle; the compression impeller and the expansion impeller are respectively fixedly connected with two ends of the rotor spindle; the periphery of the rotor part is provided with a stator part, and the stator part comprises a motor stator, a torque winding and a suspension winding which are arranged in the motor stator; the gas bearing portion includes a first gas radial bearing stator and a second gas radial bearing stator; the two gas radial bearing stators are sleeved on the peripheries of rotor main shafts positioned at two ends of the motor rotor, and the diameter of each rotor main shaft is smaller than that of a through hole in the middle of each gas radial bearing stator.
According to the invention, the suspension winding is added in the stator part, so that the motor rotor can avoid friction with the stator part when in work, and the energy loss in the running process is reduced; the rotor spindle, the thrust disc and the motor rotor in the rotor part are integrally manufactured, so that subsequent assembly and fixation of the thrust disc and the motor rotor are reduced, the time and the space for installation are obviously saved, the number of parts for installation and matching is reduced, and the stability of the centrifugal air compressor is improved. In addition, other parts in the shell fix the axial position through a plurality of positioning sleeves, the structure is simple, the manufacturing is easy, the cost is effectively controlled, and the structure of the centrifugal air compressor is simplified.
Furthermore, a torque winding and a suspension winding which are coaxially and radially arranged are arranged inside the motor stator from outside to inside, and an insulating substance is arranged between the torque winding and the suspension winding to separate the torque winding and the suspension winding. The motor stator core is formed by laminating a plurality of annular silicon steel sheets, the suspension winding is added in the motor stator, the permanent magnet is adopted to establish an air gap magnetic field, the torque winding current is not needed to provide excitation, the rotation and self-suspension capacity is realized, and the motor stator core has the advantages of simple internal structure, small size, light weight, small loss and high power density. The insulating substance may be a sheet of insulating paper or a spacer coated with an insulating varnish. Compared with the traditional magnetic suspension bearing motor, the motor rotor can be suspended at the moment of electrifying and starting the motor, and the rotor can rotate in a non-contact manner under the full working condition of the motor; it is simpler in construction and also saves more space in the axial dimension.
Furthermore, a plurality of wedge-shaped grooves are formed in the two end faces of the thrust disc and the circumferential surface of the rotor spindle at the two ends of the motor rotor; the positions of the first gas radial bearing stator and the second gas radial bearing stator correspond to the positions of two grooves formed in the circumferential surface of the rotor spindle, and the two grooves are respectively a first groove and a second groove.
Furthermore, two end faces of the thrust plate are annular grooves which comprise a plurality of wedge-shaped grooves which take the axis as a circular point and are spirally distributed along the central line; the first groove and the second groove are groove groups, each groove group comprises two rows of symmetrically distributed linear grooves, and the symmetric center lines of the linear grooves are perpendicular to the axis of the rotor spindle in space.
Preferably, the shape contour structure of the wedge-shaped groove is consistent with the shape contour of the feather of the hummingbird wing, the wedge-shaped groove is in a strip shape and comprises two arc-shaped edges and two side edges connected with the arc-shaped edges, one side edge is a straight line, the other side edge is a curve, and the transition positions of the two arc-shaped edges and the two side edges are fillets.
Further, the central line of a single wedge-shaped groove in the first groove and the second groove obliquely crosses with the axis of the rotor spindle; the radius of the arc edge close to the center of the circle and the symmetrical center line is smaller than that of the arc edge at the opposite side; in the groove strips and the wedge-shaped grooves, the concave depth of the arc-shaped edge with the larger radius is smaller than that of the arc-shaped edge with the smaller radius.
The flying characteristics of the wings of the hummingbirds are extremely unique, and the lifting force of the wings of the hummingbirds in flying is 75% from a lower wing fan and 25% from an upper wing fan. This characteristic of the hummingbird wings provides the hummingbird with sufficient lift to enable high-speed flight, while also enabling the hummingbird to hover in the air and fly forward, backward, and turn at high-speed maneuvers. The hummingbird wing structure has good aerodynamic performance, and the feather structure forming the hummingbird wing is applied to the groove-shaped gas bearing, namely, the groove formed by two short sides with different radians and arc-shaped long sides connecting the two short sides is designed, and the grooves are regularly arranged, so that the bearing rigidity and stability of the bearing can be effectively improved by analogy with the hummingbird wing feather.
Because the arc edge with larger radius is closer to the outside of the bearing structure, the pumping effect of the gas bearing can be enhanced, the gas flowing efficiency is improved, the groove depth of the arc edge with small radius at the other side is deepened, the pressure change degree of gas can be improved by making the wedge-shaped groove, and the gas film rigidity generated in the area is enhanced.
Furthermore, a gas thrust bearing cover plate and a gas thrust bearing back plate which are coaxial are arranged on the rotor main shaft on two sides of the thrust plate, and round grooves are formed in the end faces, opposite to the gas thrust bearing back plate, of the gas thrust bearing cover plate; the thrust disc is located in the two circular grooves, the thickness of the thrust disc is smaller than the sum of the depths of the two circular grooves, and the diameter of the thrust disc is smaller than the diameters of the two circular grooves. Therefore, the gas thrust bearing cover plate, the gas thrust bearing back plate and the circular groove formed by the gas thrust bearing cover plate and the gas thrust bearing back plate are used as stator parts and provide cavities, so that air at the parts can easily change the flow rate when the thrust disc works; meanwhile, the size of the circular groove is larger than that of the thrust disc, so that the thrust disc is enabled to suspend during working, loss is reduced, and mechanical efficiency is improved.
Furthermore, the positioning sleeves positioned in the inner cavity of the shell comprise a first-stage positioning sleeve, a second-stage positioning sleeve, a third-stage positioning sleeve and a fourth-stage positioning sleeve, the outer circumferential surfaces of the four positioning sleeves are fixed with the inner cavity of the shell, and two end faces of the four positioning sleeves are respectively and tightly connected with the end faces of parts in the inner stator part, the rotor part and the gas bearing part of the shell. The two end faces of each positioning sleeve separate the parts in the housing and fix the axial position of the parts because of the close contact with the end faces of the parts in the housing, namely: the first-stage positioning sleeve is positioned between the volute back plate on one side of the compression impeller and the gas thrust bearing cover plate, the second-stage positioning sleeve is positioned between the gas thrust bearing back plate and the first gas radial bearing stator, the third-stage positioning sleeve is positioned between the first gas radial bearing stator and the motor stator, and the fourth-stage positioning sleeve is positioned between the second gas radial bearing stator and the volute back plate on one side of the expansion impeller. The fixing mode greatly reduces the required auxiliary fixing parts, further lightens the mass and the volume of the integral centrifugal air compressor, simultaneously avoids the damage of internal parts and reduces the times of maintenance.
Furthermore, a cooling system is arranged on the shell and comprises a plurality of spiral water channels surrounding the shell, and a cooling liquid inlet joint and a cooling liquid outlet joint which are arranged in the radial direction and are respectively communicated with the water channels at the two ends. And connecting the cooling liquid inlet joint and the cooling liquid outlet joint with an external cooling system to realize cooling of the centrifugal air compressor.
Compared with the prior art, the invention has the substantial characteristics that:
(1) the spindle rotor, the motor rotor and the thrust disc are integrally designed and integrally manufactured, so that mounting parts and mounting procedures are reduced, the space occupied in the shell is saved, and the size and the quality of the air compressor are reduced.
(2) Carry out axial positioning to the casing inner part through set up a plurality of location sleeve on shell structure, simple structure, convenient manufacturing to it is more nimble during the adjustment, required cooperation installation component is less, has improved the device's stability.
(3) According to the invention, a set of suspension winding is added in the motor stator, and the suspension winding and the torque winding jointly control the motor rotor to realize suspension and rotation, so that the motor is simpler in structure compared with the traditional magnetic suspension bearing motor, and more space can be saved in the axial dimension.
(4) The invention adopts the grooves which are consistent with the feather outline shape of the hummingbird wing and have the wedge-shaped space structure to be arranged on the surfaces of the rotors of the gas bearing part, so that the gas generates the throttling and blocking effect through the grooves with special shapes, the gas flow rate and the gas density at the edges of the grooves are greatly changed, the pressure of a dynamic pressure gas film in an air gap of the gas bearing is increased, and the suspension supporting precision of the gas bearing part is improved.
(5) The invention adopts the mode that the suspension winding in the motor stator provides suspension force to bear main load at low rotating speed and the gas bearing part bears the main load at high rotating speed, so that the air compressor can realize high rotating speed, large flow and high pressure ratio and simultaneously has enlarged application range, obviously reduced energy consumption and obviously improved service life and reliability.
Drawings
The invention is further described with reference to the following figures and detailed description.
Fig. 1 is a schematic view of an external structure of a centrifugal air compressor according to the present invention.
FIG. 2 is a schematic cross-sectional view of the internal structure of the centrifugal air compressor of the present invention
Fig. 3 is a schematic diagram of the groove distribution and structure in the centrifugal air compressor of the present invention.
Fig. 4 is a schematic view of a housing and a positioning sleeve of the centrifugal air compressor of the present invention.
Fig. 5 is a sectional view of a motor stator part of the centrifugal air compressor of the present invention.
Fig. 6 is a schematic diagram of the stator part magnetic field of the permanent magnet synchronous type composite winding magnetic suspension motor.
FIG. 7 is a schematic diagram of the principle of the suspension force when the rotor of the motor is eccentric along the X axis.
FIG. 8 is a schematic diagram of the principle of the levitation force when the motor rotor is eccentric along the Y-axis.
In the figure: 1. the compressor comprises a compression volute, 2 compression impellers, 3 a first volute back plate, 4 a gas thrust bearing cover plate, 5 a gas thrust bearing back plate, 6 a first gas radial bearing stator, 7 a cooling liquid inlet joint, 8 a shell, 9 a motor rotor, 10 a cooling liquid outlet joint, 11 a rotor spindle, 9 a rotor spindle, a stator, a rotor spindle, a stator, a rotor spindle, a stator, a rotor spindle, a stator, a rotor spindle, a rotor spindle, a stator, a rotor spindle, a stator, a,12. The sealing ring gear comprises a sealing ring gear, 13, a stage I positioning sleeve, 14, a thrust plate, 15, a stage II positioning sleeve, 16, a stage III positioning sleeve, 17, a water channel, 18, a motor stator, 19, a torque winding, 20, a suspension winding, 21, a second gas radial bearing stator, 22, a stage IV positioning sleeve, 23, an expansion impeller, 24, an expansion volute, 25, an annular groove, 26, a first groove, 27, a second groove, 28, a second volute back plate, 29 and NxSuspension winding coil, 30.NyA suspension winding coil.
Detailed Description
The technical solutions of the present invention will be described clearly and completely with reference to the accompanying drawings, and it should be understood that the described embodiments are some, but not all embodiments of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
In the description of the present invention, it should be noted that, as the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. appear, their indicated orientations or positional relationships are based on those shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the referred device or element must have a specific orientation, be constructed in a specific orientation, and be operated, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" as appearing herein are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
Examples
A centrifugal air compressor based on a hydrogen fuel cell engine comprises a rotor part, a gas bearing part and a stator part, as shown in the attached drawings: the rotor portion located in the middle of the centrifugal air compressor includes a rotor spindle 11, and a thrust disk 14 and a motor rotor 9 integrally manufactured with the rotor spindle 11.
A gas thrust bearing cover plate 4 and a gas thrust bearing back plate 5 which are coaxial are arranged on the rotor main shaft 11 at two sides of the thrust plate 14, and round grooves are formed in the end faces, opposite to the gas thrust bearing back plate 5, of the gas thrust bearing cover plate 4; the thrust disk 14 is located in two circular grooves, the thickness of the thrust disk 14 is less than the sum of the depths of the two circular grooves, and the diameter of the thrust disk 14 is less than the diameters of the two circular grooves.
The gas bearing portion includes a first gas radial bearing stator 6 and a second gas radial bearing stator 21; the two gas radial bearing stators are sleeved on the peripheries of rotor main shafts 11 positioned at two ends of the motor rotor 9, and the diameter of the rotor main shaft 11 is smaller than that of a through hole in the middle of the two gas radial bearing stators.
A plurality of wedge-shaped grooves are formed in the two end faces of the thrust disc 14 and the circumferential face of the rotor spindle 11 at the two ends of the motor rotor 9; the appearance profile structure of wedge recess is unanimous with the appearance profile of hummingbird wing feather, is rectangular form, including two minor faces and two long limits, including two arc limits and two sides of connecting the arc limit, a side is the straight line, and another side is the curve, and the transition department on two arc limits and two sides is the fillet.
The positions of the first gas radial bearing stator 6 and the second gas radial bearing stator 21 correspond to two grooves formed on the circumferential surface of the rotor spindle 11, and the two grooves are a first groove 26 and a second groove 27 respectively. Specifically, two end faces of the thrust plate 14 are annular grooves 25, and each of the annular grooves comprises a plurality of wedge-shaped grooves which take the axis as a circular point and are spirally distributed on the center line; the first groove 26 and the second groove 27 are groove groups, each of which includes two symmetrically distributed linear grooves, and the symmetric center lines of the linear grooves are perpendicular to the axis of the rotor main shaft 11 in space. The central line of a single wedge-shaped groove in the first groove 26 and the second groove 27 is obliquely crossed with the axis of the rotor spindle 11, so that the original characteristics of the hummingbirds are ensured to a certain extent, and meanwhile, the easiness of gas entering and exiting the wedge-shaped grooves is improved.
The radius of the arc edge close to the center of the circle and the symmetrical center line is smaller than that of the arc edge at the opposite side; in the wedge-shaped groove, the concave depth of the arc-shaped edge with the larger radius is smaller than that of the arc-shaped edge with the smaller radius. The structure and the shape are convenient for air flowing at the position, the pressure change degree of air at the position is improved, the pumping effect of the bearing is improved, and the performance of the air bearing part is obviously improved.
The stator part is sleeved outside the motor rotor 9 and comprises a motor stator 18, a torque winding 19 and a suspension winding 20, wherein the torque winding 19 and the suspension winding 20 are arranged inside the motor stator 18, and the motor stator 18 is formed by laminating a plurality of annular silicon steel sheets. In a plurality of stator teeth of the motor stator 18, a torque winding 19, an insulating sheet, and a levitation winding 20 are coaxially arranged from outside to inside in the radial direction.
And a housing 8 containing the rotor portion, the gas bearing portion, and the stator portion inside.
Further, the centrifugal air compressor includes an impeller portion including the compression impeller 2 and the expansion impeller 23. The compression impeller 2 and the expansion impeller 23 are respectively fixedly connected with two ends of the rotor spindle 11, and one end close to the thrust disc 14 is the compression impeller 2. And comprises a first volute back plate 3 and a second volute back plate 28 which are arranged at two ends of the shell 8, a compression volute 1 with a compression impeller 2 arranged inside is fixed on the first volute back plate 3, an expansion volute 24 with an expansion impeller 23 arranged inside is fixed on the second volute back plate 28,
the shell 8 is provided with a cooling system, the cooling system comprises a plurality of spiral water channels 17 surrounding the shell 8, and a cooling liquid inlet joint 7 and a cooling liquid outlet joint 10 which are radially arranged, and the cooling liquid inlet joint 7 and the cooling liquid outlet joint 10 are respectively communicated with the water channels 17 at the two ends. Annular sealing toothed rings 12 are fixed on the back surfaces of the compression impeller 2 and the expansion impeller 23 and the surfaces of the first volute back plate 3 and the second volute back plate 28, so that the sealing performance of the compression volute 1, the expansion volute 24 and the shell 8 is guaranteed.
Be equipped with in the casing 8 with 8 internal diameter complex four position sleeve of casing: the positioning sleeve comprises a first-stage positioning sleeve 13, a second-stage positioning sleeve 15, a third-stage positioning sleeve 16 and a fourth-stage positioning sleeve 22. The outer circumferential surfaces of the I-stage positioning sleeve 13, the II-stage positioning sleeve 15, the III-stage positioning sleeve 16 and the IV-stage positioning sleeve 22 are fixed with the inner cavity circumferential surface of the shell 8, and two end surfaces of the positioning sleeves are respectively and tightly connected with the end surfaces of parts of the inner stator part, the rotor part and the gas bearing part of the shell 8. The specific arrangement positions are as follows: the I-stage positioning sleeve 13 is positioned between the first volute back plate 3 and the gas thrust bearing cover plate 4 on one side of the compression impeller 2, the II-stage positioning sleeve 15 is positioned between the gas thrust bearing back plate 5 and the first gas radial bearing stator 6, the III-stage positioning sleeve 16 is positioned between the first gas radial bearing stator 6 and the motor stator 18, and the IV-stage positioning sleeve 22 is positioned between the second gas radial bearing stator 21 and the second volute back plate 28 on one side of the expansion impeller 23. This serves to space the components within the housing 8 and fix the axial position of each component.
The spirally arranged annular groove 25, the first groove 26 and the second groove 27 can perform a pumping function during operation and rotation, and high-pressure air films are formed on two end faces of the thrust disk 14 and at corresponding positions of the rotor spindle 11. Meanwhile, when the gas passes through the three wedge-shaped grooves, the speed and the density of the gas at the edge of the wedge-shaped groove are changed due to the throttling and blocking effect of the wedge-shaped groove, so that the gas pressure at the junction of the wedge-shaped groove and the platform is obviously increased, and the rigidity and the bearing capacity of a gas thrust bearing of the device and the dynamic pressure gas film of the bearing gap of the gas radial bearing are improved.
When the bearing works, the air film for supporting is composed of two parts: one part is an aerodynamic pressure film generated in a wedge-shaped space between the inner circumferential surface of a gas bearing stator and a rotor part which eccentrically rotates; the other part is an aerodynamic pressure film generated by a wedge-shaped space formed based on grooves, and a dynamic pressure film generated by an increase in pressure of the film due to a change in velocity and density of gas inside the bearing due to the action of a viscous compressor formed by spirally arranging a plurality of grooves in the annular groove 25. The two dynamic pressure air films are superposed, and the rigidity of the air film in the gap and the bearing capacity of the bearing are obviously improved compared with the prior art, so that the rotor of the bearing can stably work in a suspended mode, and the bearing has high stability and large bearing capacity.
The motor stator 17 is provided with a torque winding 19 and a suspension winding 20 which are coaxially and radially arranged from outside to inside in a winding slot, and the two windings are insulated and separated and are respectively used for providing a rotary driving force and a controllable radial suspension force for the rotor spindle 11.
As shown in fig. 6, the magnetic field generated by the torque winding 19 at a certain instant assuming that the number of pole pairs of the torque winding 19 of the motor stator 18 is 4 is represented by four pairs of magnetic poles, and the form of the motor rotor 9 is set to be a four-stage surface-mount permanent magnet rotor. When the permanent magnet synchronous motor works, three-phase alternating current is introduced into three-phase symmetrical windings of a motor stator 18, an electrified torque winding 19 generates a rotating magnetic field in a motor air gap, and meanwhile, a permanent magnet on a motor rotor 9 generates a static magnetic field with constant polarity. The number of the magnetic pole pairs of the rotor magnetic field is equal to that of the magnetic pole pairs of the stator magnetic field, and the two magnetic fields interact with each other to generate electromagnetic force. When the stator rotating magnetic field rotates clockwise at the synchronous speed, the magnetic poles of the motor rotor 9 are tightly attracted with the rotating magnetic field of the motor stator 18 according to the principle that the N poles and the S poles repel each other at the same level and attract each other, and rotate together at the same speed and direction.
When the suspension winding 20 is electrified, the rotating magnetic field generated by the current breaks the air gap magnetic field balance generated by the permanent magnet, so that the synthesized air gap magnetic field is enhanced in a certain area and weakened in a symmetrical area. The interaction of the two magnetic fields produces a controlled Maxwell force, oriented by the phase of the flux linkage vectors of the two windings, directed to the side of field enhancement, the magnitude of which is related to the air-gap flux linkage of the permanent magnet and levitation winding 20.
Therefore, the essence generated by the radial force is that the current of the levitation winding 20 breaks the balance of the rotating magnetic field generated by the original permanent magnet, and only if the rotating magnetic field is unbalanced, the radial force acts on the motor rotor 9. In practical application, when two sets of windings meet three conditions, namely
a) The number of pole pairs: r is1= r2±1（r1Is the number of pole pairs of the torque winding 19; r is2Number of pole pairs of the levitation winding 20);
b) the electrical angular frequencies of the two sets of windings are equal;
c) the rotating directions of the magnetic fields generated by the two sets of windings are consistent.
By controlling the current of the suspension winding 20, controllable radial suspension force can be generated to counteract Maxwell force generated by the eccentricity of the motor rotor 9, and the motor rotor 9 is pulled back to the center to realize stable suspension.
In fig. 7 and 8, the right and left arrows represent the magnetic fields generated by the permanent magnets on the motor rotor 9, and the oval dotted line boxes represent the magnetic fields generated by the levitation windings. As shown in fig. 7, since the magnetic field generated by the current in the torque winding 19 is small compared with the magnetic field generated by the permanent magnet of the motor rotor 9, the current in the torque winding 19 is negligible when the motor rotor 9 is unloaded, and if the motor rotor 9 is shifted in the negative direction of the X axis, the direction of the eccentric magnetic pull generated by the eccentricity of the motor rotor 9 is in the negative direction of the X axis, and in order to return the motor rotor 9 to the center of the air gap, a force in the positive direction of the X axis must be applied, and when N is given in the direction shown in the figurexWhen the suspension winding coil 29 is energized with corresponding current, the 2-pole magnetic field is superposed with the 4-pole magnetic field, so that the magnetic flux density at the air gap on the right side in fig. 7 is increased, the magnetic flux density at the air gap on the left side in fig. 7 is reduced, and the unbalanced air gap magnetic flux density enables the rotor to bear the magnetic suspension force along the positive direction of the X axis, so that the rotor is forced to move to the right. If the motor rotor 9 deviates in the positive direction along the X axis, NxWhen a current in the opposite direction is applied to the levitation winding coil 29, the magnetic flux density at the air gap on the left side in fig. 7 increases, and the magnetic flux density at the air gap on the right side in fig. 7 decreases, so that a force for moving the motor rotor 9 in the negative X-axis direction is generated.
When the motor rotor 9 is eccentric along the Y axis, N is shown in FIG. 8yThe current in the levitation winding coil 30 will generate a radial levitation force in the Y-direction. Thus, by adjusting Nx Suspension winding coil 29 or NyThe magnitude and direction of the current in the levitation winding coil 30 can adjust the magnitude and direction of the radial levitation force.
In practical implementation, the invention is provided with a whole set of motor control system, and the control system comprises a variable frequency controller, a power amplifier, a sensor for detecting the rotating speed of the motor rotor 9, a sensor for detecting the displacement of the motor rotor 9 and a vibration analyzer for detecting the vibration condition of the central position of the motor rotor 9.
When the motor works, the sensor detects the rotating speed and the displacement of the motor rotor 9, the controller converts the rotating speed and the displacement of the motor rotor 9 into control signals, the power amplifier converts the control signals into control currents, the control currents are introduced into the suspension winding 20 to generate radial suspension force to counteract Maxwell force generated by eccentricity of the motor rotor 9, and the motor rotor 9 is pulled back to the center to keep stable suspension.
The levitation winding 20 is energized to provide levitation force under three conditions,
firstly, when a speed sensor detects the rotating speed V of the motor rotor 9, 0< V < V1 (V1 is 110 percent of the speed value of the air bearing part which can independently suspend the rotor), the suspension winding 20 is electrified to provide suspension force, and when the sensor detects the speed V =0 or V > V1 of the motor rotor 9, the suspension winding 20 is powered off;
when the speed sensor detects that the rotating speed V2 of the motor rotor 9 is less than V < V3, the suspension winding 20 is electrified to work, and when V > V3, the suspension winding 20 is electrified to work (V2 and V3 are respectively 90 percent and 110 percent of the critical rotating speed value when the gas bearing part generates self-excitation vortex);
and thirdly, when the displacement sensor detects that the displacement of the central position of the motor rotor 9 exceeds a preset amplitude range, the suspension winding 20 is electrified to work.
In summary, in the centrifugal air compressor based on the hydrogen fuel cell engine provided by the invention, the suspension winding 20 in the motor stator 18 provides suspension force to bear a main load at a low rotation speed, and the gas bearing part bears the main load at a high rotation speed; meanwhile, when a destabilization working condition caused by overload or stator half-speed whirling of a gas bearing occurs in the high-speed working process of the motor, the suspension winding 20 provides controllable damping for the motor rotor 9. The invention can realize oil-free cleanness, high rotating speed, large flow and high pressure ratio of the air compressor, and has the advantages of high speed, low speed, full working condition, low power consumption, long service life and high reliability.
Finally, it should be noted that: the above examples are only intended to illustrate the technical solution of the present invention, but not to limit it; while the invention has been described in detail and with reference to the foregoing embodiments, it will be understood by those skilled in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; and the modifications or the substitutions do not make the essence of the corresponding technical solutions depart from the scope of the technical solutions of the embodiments of the present invention.

Claims (10)

1. A centrifugal air compressor comprises a shell and an impeller part, wherein the impeller part comprises a first volute back plate and a second volute back plate which are fixed on two sides of the shell; first spiral case backplate outside is equipped with compression spiral case and compression impeller, and the second spiral case backplate outside is equipped with inflation spiral case and inflation impeller, its characterized in that: at least one positioning sleeve matched with the inner diameter of the shell is arranged in the shell, and the shell also comprises a rotor part, a stator part and a gas bearing part; the stator part, the rotor part and the gas bearing part are distributed and fixed at intervals through positioning sleeves;
the center of the shell is provided with a rotor part which comprises a rotor spindle, a thrust disc and a motor rotor, wherein the thrust disc and the motor rotor are integrally manufactured with the rotor spindle;
the compression impeller and the expansion impeller are respectively fixedly connected with two ends of the rotor spindle;
the periphery of the rotor part is provided with a stator part, the stator part comprises a motor stator, a torque winding and a suspension winding which are arranged in the motor stator,
the gas bearing portion includes a first gas radial bearing stator and a second gas radial bearing stator; the two gas radial bearing stators are sleeved on the peripheries of rotor main shafts positioned at two ends of the motor rotor, and the diameter of each rotor main shaft is smaller than that of a through hole in the middle of each gas radial bearing stator.
2. The centrifugal air compressor of claim 1, wherein: the motor stator is internally provided with a torque winding and a suspension winding which are coaxially and radially arranged from outside to inside, and an insulating substance is arranged between the torque winding and the suspension winding to separate the torque winding and the suspension winding.
3. The centrifugal air compressor of claim 1, wherein: a plurality of wedge-shaped grooves are formed in the two end faces of the thrust disc and the circumferential surface of the rotor spindle at the two ends of the motor rotor; the positions of the first gas radial bearing stator and the second gas radial bearing stator correspond to the positions of two grooves formed in the circumferential surface of the rotor spindle, and the two grooves are respectively a first groove and a second groove.
4. The centrifugal air compressor of claim 3, wherein: the two end faces of the thrust plate are annular grooves and comprise a plurality of wedge-shaped grooves which take the axis as a circular point and are spirally distributed along the central line; the first groove and the second groove are groove groups, each groove group comprises two rows of symmetrically distributed linear grooves, and the symmetric center lines of the linear grooves are perpendicular to the axis of the rotor spindle in space.
5. The centrifugal air compressor of claim 3, wherein: the shape contour structure of the wedge-shaped groove is consistent with the shape contour of the feather of the hummingbird wing, is in a long strip shape and comprises two arc-shaped edges and two side edges connected with the arc-shaped edges, one side edge is a straight line, the other side edge is a curve, and the transition positions of the two arc-shaped edges and the two side edges are fillets.
6. The centrifugal air compressor of claim 5, wherein: the central line of a single wedge-shaped groove in the first groove and the second groove obliquely crosses with the axis of the rotor spindle; the radius of the arc edge close to the center of the circle and the symmetrical center line is smaller than that of the arc edge at the opposite side; in the groove strips and the wedge-shaped grooves, the concave depth of the arc-shaped edge with the larger radius is smaller than that of the arc-shaped edge with the smaller radius.
7. The centrifugal air compressor of claim 1, wherein: a gas thrust bearing cover plate and a gas thrust bearing back plate which are coaxial are arranged on the rotor main shaft on two sides of the thrust plate, and round grooves are formed in the end faces, opposite to the gas thrust bearing back plate, of the gas thrust bearing cover plate; the thrust disc is located in the two circular grooves, the thickness of the thrust disc is smaller than the sum of the depths of the two circular grooves, and the diameter of the thrust disc is smaller than the diameters of the two circular grooves.
8. The centrifugal air compressor of claim 1, wherein: the positioning sleeves positioned in the inner cavity of the shell comprise a first-stage positioning sleeve, a second-stage positioning sleeve, a third-stage positioning sleeve and a fourth-stage positioning sleeve, the circumferential surface of the outer side of each positioning sleeve is fixed with the inner cavity of the shell, and two end faces of the four positioning sleeves are respectively and tightly connected with the end faces of parts in the inner stator part, the rotor part and the gas bearing part of the shell.
9. The centrifugal air compressor of claim 1, wherein: the cooling system is arranged on the shell and comprises a plurality of spiral water channels surrounding the shell, and a cooling liquid inlet joint and a cooling liquid outlet joint which are radially arranged and are respectively communicated with the water channels at two ends.
10. Use of the centrifugal air compressor according to claim 1 as a centrifugal air compressor for a hydrogen fuel cell engine.
CN202111448658.5A 2021-11-27 2021-11-27 Centrifugal air compressor based on hydrogen fuel cell engine Pending CN114198322A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202111448658.5A CN114198322A (en) 2021-11-27 2021-11-27 Centrifugal air compressor based on hydrogen fuel cell engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202111448658.5A CN114198322A (en) 2021-11-27 2021-11-27 Centrifugal air compressor based on hydrogen fuel cell engine

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Country Link
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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114508503A (en) * 2022-04-19 2022-05-17 广东美芝制冷设备有限公司 Fan and cleaning equipment
CN114658676A (en) * 2022-04-19 2022-06-24 广东美芝制冷设备有限公司 Fan and cleaning equipment
CN114754015A (en) * 2022-04-19 2022-07-15 广东美芝制冷设备有限公司 Fan and cleaning equipment
CN114876824A (en) * 2022-05-23 2022-08-09 烟台东德实业有限公司 Air cooling structure of high-speed centrifugal air compressor and expander integrated system
CN114876826A (en) * 2022-05-02 2022-08-09 烟台东德实业有限公司 Unilateral two-stage high-speed centrifugal air compressor and expander integrated system

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114508503A (en) * 2022-04-19 2022-05-17 广东美芝制冷设备有限公司 Fan and cleaning equipment
CN114508503B (en) * 2022-04-19 2022-06-21 广东美芝制冷设备有限公司 Fan and cleaning equipment
CN114658676A (en) * 2022-04-19 2022-06-24 广东美芝制冷设备有限公司 Fan and cleaning equipment
CN114754015A (en) * 2022-04-19 2022-07-15 广东美芝制冷设备有限公司 Fan and cleaning equipment
CN114658676B (en) * 2022-04-19 2023-06-23 广东美芝制冷设备有限公司 Fan and cleaning equipment
CN114754015B (en) * 2022-04-19 2023-11-10 广东美芝制冷设备有限公司 Fan and cleaning equipment
CN114876826A (en) * 2022-05-02 2022-08-09 烟台东德实业有限公司 Unilateral two-stage high-speed centrifugal air compressor and expander integrated system
CN114876824A (en) * 2022-05-23 2022-08-09 烟台东德实业有限公司 Air cooling structure of high-speed centrifugal air compressor and expander integrated system
CN114876824B (en) * 2022-05-23 2023-08-29 烟台东德实业有限公司 Air cooling structure of high-speed centrifugal air compressor and expander integrated system

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