CN114592925B - Magnetic suspension hydrogen turbine expansion device and method - Google Patents

Magnetic suspension hydrogen turbine expansion device and method Download PDF

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CN114592925B
CN114592925B CN202210335795.6A CN202210335795A CN114592925B CN 114592925 B CN114592925 B CN 114592925B CN 202210335795 A CN202210335795 A CN 202210335795A CN 114592925 B CN114592925 B CN 114592925B
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rotor
bearing
axial
hydrogen
radial bearing
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CN114592925A (en
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孙耕
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Beijing Dazhen Technology Co ltd
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Beijing Dazhen Technology Co ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01D15/10—Adaptations for driving, or combinations with, electric generators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D21/00—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for
    • F01D21/003—Arrangements for testing or measuring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/06—Rotors for more than one axial stage, e.g. of drum or multiple disc type; Details thereof, e.g. shafts, shaft connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/12—Blades
    • F01D5/28—Selecting particular materials; Particular measures relating thereto; Measures against erosion or corrosion
    • F01D5/288—Protective coatings for blades

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Materials Engineering (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)

Abstract

The invention relates to a magnetic suspension hydrogen turbine expansion device and a method, wherein the device comprises a magnetic suspension bearing assembly and a rotor system, and the rotor system is wrapped in the magnetic suspension bearing assembly; the rotor system comprises a rotor spindle, a first driving wheel and a second driving wheel, wherein the first driving wheel and the second driving wheel are respectively arranged at two ends of the rotor spindle; the magnetic bearing assembly comprises a radial bearing and an axial bearing and is used for forming bearing force for suspending and fixing the rotor system after being electrified. The invention reduces friction by adopting the magnetic suspension bearing, avoids polluting hydrogen driving gas, consumes shaft work by adopting the braking electronic rotor and the stator, drives the rotor system by adopting the dual-driving wheel, and has high device operation efficiency and higher energy utilization rate.

Description

Magnetic suspension hydrogen turbine expansion device and method
Technical Field
The invention belongs to the technical field of hydrogen energy application, and particularly relates to a magnetic suspension hydrogen turbine expansion device and a magnetic suspension hydrogen turbine expansion method.
Background
The hydrogen turbo-expansion device is a key part of a hydrogen liquefaction device, energy conversion is carried out by the aid of speed change of flowing working media, the working media expand in a through-flow part of the turbo-expander to obtain kinetic energy, work is output outwards by an expansion wheel, and internal energy and temperature of the working media at an outlet of the expander are reduced. Most of the existing liquid hydrogen production devices in China are based on helium refrigeration cycle, and due to the fact that physical properties of helium and physical properties of hydrogen are greatly different, the helium refrigeration cycle device has large heat exchange loss and low efficiency, and the adoption of a hydrogen turboexpander is the future development direction of the liquid hydrogen production device.
In the process of running the turboexpander, most of the prior art adopts an oil way system to provide lubrication for the bearing so as to ensure the normal operation of the expander. For example, patent document CN108759146A discloses a hydrogen turbo expansion device, which performs refrigeration by hydrogen expansion work, provides a cooling requirement of sufficient depth for hydrogen liquefaction, introduces circulating hydrogen into a turbine from a hydrogen inlet of the turbine, and performs work on an impeller in the turbine by the circulating hydrogen to realize turbo expansion of the circulating hydrogen, wherein a circulating oil path is used to supply lubricating oil to each bearing cycle to reduce friction.
The device can provide the cold volume that hydrogen liquefaction needs better, but the lubricating oil that the bearing lubrication adopted leaks easily and gets into the system, causes the system pollution to be difficult to handle, and lubricating oil system is complicated moreover, is unfavorable for technical development.
There are also related designs in the prior art that use magnetic bearings in hydrogen turboexpanders. For example, patent document CN214501885U discloses an all-low-temperature circulation hydrogen liquefier, which is based on a turbine compression and expansion technology of a magnetic suspension bearing technology, and adopts low-temperature circulation to reduce heat leakage and power consumption, a cold compressor to replace a normal-temperature compressor, and a non-contact magnetic suspension bearing to replace a mechanical bearing and a gas bearing to realize long-time lossless operation of the bearing, thereby improving operation stability.
However, because the material for manufacturing the rotor has high requirements on mechanical strength, the materials suitable for being used as the shaft at present have the problem of hydrogen embrittlement in a hydrogen environment, and most of the materials without the problem of hydrogen embrittlement are not suitable for being used as the material of the shaft, so that the hydrogen embrittlement problem is easily caused when hydrogen driving gas is introduced into the device, and the service durability and the stability of the device are poor. In addition, the braking mode is adopted in the scheme, the shaft work is consumed, the energy utilization rate is low, and meanwhile, the rotor system can only be driven by a single driving wheel, and the working efficiency of the device is not high enough.
Therefore, how to design a magnetic suspension hydrogen turbine expansion device with high working efficiency and high energy utilization rate becomes a problem to be solved urgently by the technical personnel in the field.
Disclosure of Invention
Aiming at the defects in the prior art, the invention aims to provide a magnetic suspension hydrogen turbine expansion device and a magnetic suspension hydrogen turbine expansion method.
In a first aspect, the present invention provides a magnetic suspension hydrogen turbine expansion device, comprising a magnetic suspension bearing assembly and a rotor system, wherein the rotor system is wrapped inside the magnetic suspension bearing assembly;
the rotor system comprises a rotor main shaft, a first driving wheel and a second driving wheel which are respectively arranged at two ends of the rotor main shaft, the rotor main shaft comprises a braking motor rotor, and a matched braking motor stator is arranged on the outer side of the braking motor rotor and is used for transferring shaft work in an electric energy mode;
the magnetic suspension bearing assembly comprises a radial bearing and an axial bearing and is used for forming bearing capacity for suspending and fixing the rotor system after being electrified.
Furthermore, the rotor spindle further comprises a thrust disc coaxially arranged with the rotor spindle, the axial bearings comprise a first axial bearing and a second axial bearing which are respectively arranged on two sides of the thrust disc, a first axial coil and a second axial coil are respectively wrapped in the first axial bearing and the second axial bearing, and the first axial coil and the second axial coil are oppositely arranged;
the radial bearing comprises a first radial bearing and a second radial bearing which are respectively arranged on two sides of a rotor of the brake motor, an even number of magnetic poles which are uniformly distributed along the circumferential direction are arranged in the first radial bearing and the second radial bearing, and every two magnetic poles are used for adjusting the magnetic force of the radial bearing along one direction.
Furthermore, at least one side of the thrust disk is provided with a plurality of first dynamic pressure grooves, the surface of one side of the first radial bearing and/or the second radial bearing close to the rotor spindle is provided with a plurality of groups of second dynamic pressure grooves which are uniformly distributed along the axial direction, and each group comprises a plurality of second dynamic pressure grooves which are uniformly distributed along the circumferential direction; the first dynamic pressure groove is spiral along the axial section structure of the thrust disc, and the second dynamic pressure groove is at least one of herringbone, splay and pi-shaped along the radial expansion structure of the rotor spindle.
Furthermore, the device also comprises at least two protective bearings, wherein the protective bearings are arranged adjacent to the radial bearing, and the gap between the radial bearing and the rotor spindle is larger than the gap between the protective bearing and the rotor spindle.
Furthermore, the rotor spindle further comprises a first journal and a second journal, the first journal is arranged at one end of the rotor spindle close to the first driving wheel and connected with the first driving wheel, and the second journal is arranged at one end of the rotor spindle close to the second driving wheel and connected with the second driving wheel.
Further, the brake motor rotor is located between the first journal and the second journal, one end, away from the first driving wheel, of the first journal is connected with the thrust disk, and the other end of the thrust disk is connected with the brake motor rotor;
the first axial bearing, the thrust disc, the second axial bearing, the first protection bearing, the first radial bearing, the brake motor stator, the second radial bearing and the second protection bearing are sequentially and coaxially arranged between the first journal and the second journal.
Further, the magnetic suspension hydrogen turbine expansion device further comprises a rotating speed monitoring assembly, wherein the rotating speed monitoring assembly comprises an electromagnetic induction tachometer and a boss or a groove arranged on the rotor system.
Furthermore, the first driving wheel and the second driving wheel are in the same mirror image shape, the hydrogen driving gas introduced into the first driving wheel and the second driving wheel has the same flow rate and state, and the first shaft neck and the second shaft neck are both in a hollow structure.
Further, the hydrogen embrittlement-resistant coating is made of a hydrogen embrittlement-resistant ceramic material, the thickness of the hydrogen embrittlement-resistant coating is 10-1000 nanometers, and the hydrogen embrittlement-resistant ceramic material comprises aluminum oxide.
In a second aspect, the present invention further provides a magnetic levitation hydrogen turbine expansion method using the above apparatus, including the following steps:
electrifying the magnetic suspension bearing assembly to form bearing capacity so as to suspend and fix the rotor system;
hydrogen driving gas is introduced into a first driving wheel and a second driving wheel to drive the first driving wheel and the second driving wheel to rotate so as to drive a rotor system to rotate and apply work;
a brake motor rotor on the rotor spindle rotates to generate current in a brake motor stator;
the expanded hydrogen drives the gas exhaust.
Compared with the prior art, the magnetic suspension hydrogen turbine expansion device and the method provided by the invention have the following beneficial effects:
1. the magnetic bearing is adopted to reduce the friction of the hydrogen turbine device, so that the problem that lubricating oil or lubricating gas pollutes a hydrogen system is effectively avoided, the hydrogen embrittlement prevention coating treatment is carried out on the part which is easy to generate the hydrogen embrittlement problem, the hydrogen embrittlement problem generated by the device exposed in the hydrogen working environment is effectively avoided, and the durability of the device is good;
2. the brake motor stator and the rotor are arranged in the middle of the rotor spindle, so that the power generation function is realized while the continuous operation of the device is maintained, the utilization rate of the device energy is higher, the dynamic pressure groove design is adopted on the surfaces of the thrust disc and the radial bearing, and the dynamic pressure effect is utilized to provide extra bearing force for the rotor system, so that the magnetic suspension assembly can maintain the stable and efficient operation of the device under lower power, and the energy is saved;
3. the electromagnetic induction tachometer is adopted to monitor the rotating speed, and the displacement sensor is adopted to assist in adjusting the magnetic pole electromagnetic force of the radial bearing, so that the device is more accurate to adjust, and the working efficiency is higher.
The foregoing describes preferred embodiments of the present invention, and is intended to make the spirit and scope of the present invention clear and understandable, but not to limit the present invention, and modifications, substitutions and improvements made within the spirit and principle of the present invention are included in the scope of the present invention as outlined by the appended claims.
Drawings
The above and other objects, features and advantages of exemplary embodiments of the present disclosure will become readily apparent from the following detailed description read in conjunction with the accompanying drawings. Several embodiments of the present disclosure are illustrated by way of example, and not by way of limitation, in the figures of the accompanying drawings and in which like reference numerals refer to similar or corresponding parts and in which:
FIG. 1 is a schematic diagram showing the construction of a magnetic levitation hydrogen turboexpansion apparatus according to an embodiment of the present invention;
FIG. 2 is a radial cross-sectional view showing a radial bearing of a magnetic levitation hydrogen turbine expansion device according to an embodiment of the present invention;
FIG. 3 illustrates an axial cross-sectional view of a magnetic levitation hydrogen turboexpansion device according to an embodiment of the present invention;
fig. 4 is a flow diagram illustrating a magnetic levitation hydrogen turboexpansion method according to an embodiment of the present invention.
Description of reference numerals: 1-rotor system, 11-first drive wheel, 12-second drive wheel, 13-rotor spindle, 131-thrust disk, 132-first journal, 133-second journal, 134-brake motor rotor, 2-first axial bearing, 21-first axial coil, 3-second axial bearing, 31-second axial coil, 4-first radial bearing, 41-second dynamic pressure groove, 5-second radial bearing, 6-brake motor stator, 7-first protective bearing, 8-second protective bearing.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention clearer, the present invention will be described in further detail with reference to the accompanying drawings, and it is apparent that the described embodiments are only a part of the embodiments of the present invention, not all of the embodiments. All other embodiments, which can be obtained by a person skilled in the art without making any creative effort based on the embodiments in the present invention, belong to the protection scope of the present invention.
The terminology used in the embodiments of the invention is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. As used in the description of the invention and the appended claims, the singular forms "a", "an", and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise, and "the plural" typically includes at least two.
It is also noted that the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that an article or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such article or apparatus. Without further limitation, an element defined by the phrase "comprising one of 8230, and" comprising 8230does not exclude the presence of additional like elements in articles or devices comprising the element.
The present invention will be described in detail with reference to specific examples.
Referring to fig. 1, an embodiment of the present invention provides a magnetic suspension hydrogen turbine expansion device, including a magnetic suspension bearing assembly and a rotor system 1, where the rotor system 1 is wrapped in the bearing assembly, the rotor system 1 includes a rotor spindle 13 and a first driving wheel 11 and a second driving wheel 12 respectively disposed at two ends of the rotor spindle 13, the first driving wheel 11 and the second driving wheel 12 are driven by hydrogen driving gas, and the two driving wheels are connected in series and can bear a larger hydrogen driving gas flow. Rotor spindle 13 includes brake motor rotor 134, and brake motor rotor 134 is provided with a matching brake motor stator 6 on the outside thereof, for generating current in cooperation with brake motor rotor 134, so as to transfer shaft work in the form of electric energy.
The magnetic suspension bearing assembly comprises two radial bearings and two axial bearings and is used for forming bearing capacity of the suspension fixed rotor system 1 after being electrified.
Rotor spindle 13 still includes the thrust disc 131 of coaxial setting, and axial bearing is including establishing first axial bearing 2 and the second axial bearing 3 in thrust disc 131 both sides separately, and the parcel has first axial coil 21 and second axial coil 31 in first axial bearing 2 and the second axial bearing 3 respectively, and specifically, axial bearing includes axial bearing iron core and a plurality of axial bearing groove, and the winding has first axial coil 21 and second axial coil 31 respectively in the axial bearing groove, and first axial coil 21 sets up with second axial coil 31 relatively. A working air gap exists between the thrust disc 131 and the first axial bearing 2 and the second axial bearing 3, and the first axial bearing 2 and the second axial bearing 3 are oppositely arranged relative to the thrust disc 131 to keep an air gap with proper size on two sides. When the device is used, the thrust disc 131 and the rotor spindle 13 are fixed into a whole, the device rotates together when the device works, and the coils arranged in the first axial bearing 2 and the second axial bearing 3 control the electromagnetic force between the first axial bearing 2 and the second axial bearing 3 on both sides of the thrust disc 131 and the rotor spindle 13 so as to keep the balance position of the rotor in the axial direction.
Preferably, the thrust disk 131 is integrally formed with the rotor spindle 13, and the rotor spindle 13 is made of a high-strength and good-magnetism material, such as steel 10 and steel A3.
The radial bearing comprises a first radial bearing 4 and a second radial bearing 5 which are respectively arranged at two sides of the brake motor rotor 134, an even number of magnetic poles which are uniformly distributed along the circumferential direction are arranged in the first radial bearing 4 and the second radial bearing 5, and every two magnetic poles are used for adjusting the magnetic force in one direction.
Preferably, 8 magnetic poles are uniformly distributed in the circumferential direction in the first radial bearing 4 and the second radial bearing 5, wherein two adjacent magnetic poles are in one group and are divided into four groups, and each group is used for adjusting the magnetic force in one direction.
At least one side of the thrust disk 131 is provided with a plurality of first dynamic pressure grooves, and the surface of the first radial bearing 4 and/or the second radial bearing 5 close to the rotor side is provided with a plurality of sets of second dynamic pressure grooves 41 uniformly distributed along the axial direction, so that the rotor system 1 generates a corresponding dynamic pressure effect when rotating, so as to provide a certain bearing force for the rotor system 1. The first dynamic pressure groove has a spiral axial sectional structure. Referring to fig. 2, the second dynamic pressure generating groove 41 has any one of a herringbone type, and a pi type structure on the inner surface of the radial bearing, and each group includes a plurality of second dynamic pressure generating grooves 41 uniformly distributed in the circumferential direction.
When thrust disk 131 is provided with the first dynamic pressure groove, thrust disk 131 has a first predetermined position in the axial direction, which is not generally at the geometric center of the cross section of the two axial bearings, and which is generally shifted toward the direction of the resultant force of rotor main shaft 13, and which keeps the resultant force generated by the first dynamic pressure groove on thrust disk 131 balanced with the resultant force of rotor main shaft 13. When the thrust disc 131 of the rotor spindle 13 is in the first predetermined position, the bearing capacity required to be provided by the magnetic levitation bearing assembly is minimal, the device is relatively safe, and the electric energy resource is saved.
Similarly, when the radial bearing is provided with the second dynamic pressure groove 41, the radial bearing can control the rotor main shaft 13 to an optimal second preset position, i.e., an optimal working position. When the second dynamic pressure groove 41 is not provided, the geometric center of the axial cross section of the rotor spindle 13 coincides with the geometric center of the axial cross section of the bearing assembly, and the second preset position of the rotor spindle 13 after the second dynamic pressure groove 41 is provided is not the geometric center of the axial cross section of the bearing assembly, and is generally a slightly eccentric position. When the rotor spindle 13 works at the second preset position, the bearing capacity required to be provided by the magnetic suspension bearing assembly is minimum, the device is safe, and the electric energy resource is saved.
In particular, for a horizontally placed device, the second preset position is generally a position that is lower and slightly off-set in the direction of rotation, under the action of gravity. Referring to fig. 3, O is the geometric center of the axial section of the radial bearing, O1 is the geometric center of the axial section of the rotor spindle 13, which shows the optimal working position of the rotor spindle 13, x is the horizontal direction, y is the vertical direction, and ω is the rotation direction of the rotor spindle 13.
The position can be obtained in advance by calculation, and parameters required by calculation include: the position and form of the second dynamic pressure groove 41, the gap between the rotor main shaft 13 and the bearing assembly, the rotational speed of the rotor main shaft 13, the weight of the rotor system 1, and the like. The position of the rotor spindle 13 can be controlled to a second preset position by controlling the electromagnetic force of the coils in the radial bearing, and the position can also be corrected by comparing the power consumption required by the coils at each position through experiments.
Therefore, after the second dynamic pressure groove 41 is provided, the optimal working position of the rotor spindle 13 needs to be obtained, and then the magnetic force of the radial bearing needs to be adjusted to ensure that the rotor spindle 13 rotates along the center of the optimal working position in the working operation state. The optimal working position of the rotor main shaft 13 is shifted from the central position of the radial bearing and the rotor main shaft 13 to a downward and eccentric rotation direction, which is the optimal working position of the second dynamic pressure groove 41, and when the rotor main shaft 13 runs at the position, the bearing force required to be provided by the magnetic levitation bearing assembly is the smallest, the safest and the electricity-saving.
Acquiring the optimal working position of the rotor spindle 13 according to the second dynamic pressure groove 41, and adjusting the magnetic force of the radial bearing to make the rotation center of the rotor spindle 13 coincide with the optimal working position, wherein the specific process comprises the following steps:
obtaining the eccentricity ratio lambda corresponding to the second dynamic pressure groove 41;
assuming a first deviation angle
Figure BDA0003574304120000101
Calculating a first load angle according to the eccentricity and the first deviation angle
Figure BDA0003574304120000102
Assuming a second deviation angle
Figure BDA0003574304120000103
Calculating a second load angle according to the eccentricity and the second deviation angle
Figure BDA0003574304120000104
Calculating according to the first load angle, the first deviation angle, the second load angle and the second deviation angle to obtain a third deviation angle
Figure BDA0003574304120000105
The calculation formula is as follows:
Figure BDA0003574304120000106
iterating the deflection angle and the load angle according to a Newton iteration method for a plurality of rounds, and obtaining the deflection angle according to the eccentricity and the round after each round of iteration is completed
Figure BDA0003574304120000107
Calculating to obtain corresponding load angle
Figure BDA0003574304120000108
Entering the next round of iteration until
Figure BDA0003574304120000109
And with
Figure BDA00035743041200001010
Stopping iteration when the difference value of (2) is less than 0.001 to obtain a final deviation angle, wherein a specific calculation formula is as follows:
Figure BDA00035743041200001011
and determining the optimal working position according to the final deviation angle and the eccentricity.
Wherein, calculate according to eccentricity and deflection angle and obtain the load angle, include:
the eccentricity lambda and the offset angle gamma 0 Substituting into Reynolds equation to solve to obtain load force W in x and y directions x And W y ；
According to load force W x And W y Determining the load angle beta 0 Wherein the load angle is calculated by the formula
Figure BDA0003574304120000111
The device also comprises two protective bearings, the protective bearings and the radial bearings are arranged adjacently, and the gap between the radial bearings and the rotor spindle 13 is larger than the gap between the protective bearings and the rotor spindle 13, so that the magnetic suspension bearing assembly is protected from accidental damage. When the rotor is accidentally unstable, the rotor system 1 rotating at high speed falls on the protective bearing first instead of directly falling on the magnetic suspension bearing assembly, so that the protective bearing bears the abrasion from the rotor system 1, and the magnetic suspension bearing assembly is protected from being damaged.
Rotor spindle 13 further includes two journals, a first journal 132 disposed at an end of rotor spindle 13 adjacent to first drive wheel 11 and connected to first drive wheel 11, and a second journal 133 disposed at an end of rotor spindle 13 adjacent to second drive wheel 12 and connected to second drive wheel 12.
Brake motor rotor 134 is located between first journal 132 and second journal 133, one end of first journal 132 remote from first drive wheel 11 is connected to thrust disc 131, and the other end of thrust disc 131 is connected to brake motor rotor 134; the first axial bearing 2, the thrust disk 131, the second axial bearing 3, the first protective bearing 7, the first radial bearing 4, the brake motor stator 6, the second radial bearing 5 and the second protective bearing 8 are coaxially arranged between the first journal 132 and the second journal 133 in sequence.
Preferably, magnetism floats hydrogen turbo expansion device and still includes the rotational speed control subassembly, and the rotational speed control subassembly includes the electromagnetic induction tachometer and sets up boss or recess on rotor system 1, acquires the frequency of change because of the induction magnetic field that boss or recess caused through the electromagnetic induction tachometer to acquire rotor system 1 pivoted angular velocity.
Preferably, displacement sensors are arranged on the first radial bearing 4 and the second radial bearing 5 along the arrangement direction of the magnetic poles, and the displacement sensors are used for detecting the distance between the rotor system 1 and the bearing assembly and feeding back the distance to the control system to be used as reference signals for adjusting the electromagnetic force of the magnetic poles.
Preferably, the first driving wheel 11 and the second driving wheel 12 are in the same mirror image shape, and the hydrogen driving gas introduced into the first driving wheel 11 and the second driving wheel 12 has the same flow rate and state.
Preferably, the first and second journals 132 and 133 are both hollow.
The device adopts a hydrogen-resistant ceramic material to perform hydrogen embrittlement resistant coating treatment, and the thickness of the hydrogen embrittlement resistant coating is 10-1000 nanometers.
Preferably, the hydrogen embrittlement prevention coating treatment employs aluminum oxide.
Preferably, the hydrogen embrittlement prevention coating treatment adopts one or more of thermal spraying, magnetron sputtering and chemical deposition.
Preferably, the parts mentioned in this embodiment are made of a material that does not generate hydrogen embrittlement as much as possible, and if a material that easily generates hydrogen embrittlement needs to be used, for example, there is a certain requirement on the mechanical strength of the material, the corresponding parts are subjected to coating treatment, and the material that does not generate hydrogen embrittlement is one or more of 316L stainless steel, aluminum alloy, and copper alloy.
Preferably, the driving wheel adopts an expansion impeller, and the first expansion impeller and the second expansion impeller adopt the same mirror image blade profile.
When the rotor system works, the first axial coil 21, the second axial coil 31, the first radial bearing 4 and the second radial bearing 5 are energized to form bearing capacity for the rotor system 1 so as to support the rotor system 1 to suspend, so that the friction force is reduced, oil lubrication or gas lubrication is replaced, and pollution to hydrogen driving gas is avoided. When the rotor system 1 is suspended between the magnetic bearing assemblies, two high-pressure hydrogen gas driving gases to be expanded, which are in the same state and flow rate, are respectively led to the first driving wheel 11 and the second driving wheel 12, so that the driving wheels rotate. Because the first driving wheel 11 and the second driving wheel 12 adopt the same mirror image shape, the first driving wheel 11 and the second driving wheel 12 are mirror symmetric, and under the driving of the hydrogen driving gas with the same flow and state, the axial thrust with the same size and the opposite direction is generated in the first driving wheel 11 and the second driving wheel 12, so that the problem of axial unbalance of the whole device is avoided. The hydrogen gas drives the first driving wheel 11 and the second driving wheel 12 to rotate, so that the whole rotor system 1 is driven to rotate, the brake motor rotor 134 rotates to generate current in the brake motor stator 6, shaft work is consumed to maintain the normal operation of the magnetic suspension hydrogen turbine device, energy is recycled, a power generation function is realized, and energy waste in the hydrogen liquefaction process is avoided.
When the rotor system 1 rotates, the rotor system 1 can generate a corresponding dynamic pressure effect by the dynamic pressure groove arranged on the inner surface of the radial bearing so as to provide a certain radial bearing force for the rotor system 1; meanwhile, one side and/or the other side of the thrust disk 131 is/are provided with dynamic pressure grooves, and when the rotor system 1 rotates, the dynamic pressure grooves arranged on one side and/or the other side of the thrust disk 131 can enable the rotor system 1 to generate a corresponding dynamic pressure effect so as to provide a certain axial bearing force for the rotor system 1. With the help of the additional radial bearing force and the axial bearing force, the first axial coil 21, the second axial coil 31, the first radial bearing 4 and the second radial bearing 5 can maintain the stable and efficient operation of the device under smaller power, and energy is saved.
During operation, the whole magnetic suspension hydrogen turbine device is in a hydrogen environment, and hydrogen can be isolated by processing the hydrogen embrittlement prevention coating adopted by the rotor system 1 and the magnetic suspension bearing assembly, so that parts which are easy to generate hydrogen embrittlement problem materials are protected, and the hydrogen embrittlement problem of the parts of the device is avoided.
Referring to fig. 4, an embodiment of the present invention further provides a magnetic levitation hydrogen turbine expansion method, which may include the following steps:
s1, energizing a magnetic suspension bearing assembly to form bearing capacity to suspend and fix the rotor system 1;
s2, introducing hydrogen driving gas into the first driving wheel 11 and the second driving wheel 12, and driving the first driving wheel 11 and the second driving wheel 12 to rotate so as to drive the rotor system 1 to do work in a rotating manner;
s3, the brake motor rotor 134 on the rotor spindle 13 rotates to generate current in the brake motor stator 6;
and S4, driving a gas exhaust device by the expanded hydrogen.
According to the magnetic suspension hydrogen turbine expansion device and the magnetic suspension hydrogen turbine expansion method, the magnetic suspension bearing is adopted to reduce friction of the hydrogen turbine device, the problem that lubricating oil or lubricating gas pollutes a hydrogen system is effectively avoided, the hydrogen embrittlement prevention coating treatment is carried out on parts which are prone to hydrogen embrittlement, the hydrogen embrittlement problem of the device exposed in a hydrogen working environment is effectively avoided, and the durability of the device is good; the brake motor stator and the rotor are arranged in the middle of the rotor spindle, so that the power generation function is realized while the continuous operation of the device is maintained, the utilization rate of the device energy is higher, the dynamic pressure groove design is adopted on the surfaces of the thrust disc and the radial bearing, and the dynamic pressure effect is utilized to provide extra bearing force for the rotor system, so that the magnetic suspension assembly can maintain the stable and efficient operation of the device under lower power, and the energy is saved; the electromagnetic induction tachometer is adopted to monitor the rotating speed, and the displacement sensor is adopted to assist in adjusting the magnetic pole electromagnetic force of the radial bearing, so that the device is more accurate in adjustment and higher in working efficiency.
The foregoing describes preferred embodiments of the present invention, and is intended to make the spirit and scope of the present invention clear and understandable, but not to limit the present invention, and modifications, substitutions and improvements made within the spirit and principle of the present invention are included in the scope of the present invention as outlined by the appended claims.

Claims (10)

1. A magnetic suspension hydrogen turbine expansion device is characterized by comprising a magnetic suspension bearing assembly and a rotor system, wherein the rotor system is wrapped in the magnetic suspension bearing assembly;
the rotor system comprises a rotor main shaft, a first driving wheel and a second driving wheel which are respectively arranged at two ends of the rotor main shaft, the rotor main shaft comprises a braking motor rotor, and a matched braking motor stator is arranged on the outer side of the braking motor rotor and is used for transferring shaft work in an electric energy mode;
the magnetic suspension bearing assembly comprises a radial bearing and an axial bearing and is used for forming bearing capacity for suspending and fixing the rotor system after being electrified;
the radial bearing comprises a first radial bearing and a second radial bearing which are respectively arranged at two sides of a brake motor rotor, an even number of magnetic poles which are uniformly distributed along the circumferential direction are arranged in the first radial bearing and the second radial bearing, and every two magnetic poles are used for adjusting the magnetic force of the radial bearing along one direction;
the surface of one side, close to the rotor spindle, of the first radial bearing and/or the second radial bearing is provided with a plurality of groups of second dynamic pressure grooves which are uniformly distributed along the axial direction, and each group comprises a plurality of second dynamic pressure grooves which are uniformly distributed along the circumferential direction;
the optimal working position of the rotor spindle is obtained according to the second dynamic pressure groove, the magnetic force of the radial bearing is adjusted, the rotation center of the rotor spindle is overlapped with the optimal working position, and the specific process comprises the following steps:
obtaining the eccentricity ratio lambda corresponding to the second dynamic pressure groove;
assuming a first deviation angle
Figure FDA0003943232440000011
Calculating a first load angle according to the eccentricity and the first deviation angle
Figure FDA0003943232440000012
Assuming a second deviation angle
Figure FDA0003943232440000013
Calculating a second load angle according to the eccentricity and the second deviation angle
Figure FDA0003943232440000021
According to the first load angle, the first deviation angle and the second loadCalculating the load angle and the second deviation angle to obtain a third deviation angle
Figure FDA0003943232440000022
The calculation formula is as follows:
Figure FDA0003943232440000023
iterating the deflection angle and the load angle according to a Newton iteration method for a plurality of rounds, and obtaining the deflection angle according to the eccentricity and the round after each round of iteration is completed
Figure FDA0003943232440000024
Calculating to obtain corresponding load angle
Figure FDA0003943232440000025
Entering the next iteration till
Figure FDA0003943232440000026
And with
Figure FDA0003943232440000027
Stopping iteration when the difference value of (2) is less than 0.001 to obtain a final deviation angle, wherein a specific calculation formula is as follows:
Figure FDA0003943232440000028
determining the optimal working position according to the final deviation angle and the eccentricity;
wherein, calculate according to eccentricity and deflection angle and obtain the load angle, include:
the eccentricity lambda and the offset angle gamma 0 Substituting into Reynolds equation to solve to obtain load force W in x and y directions x And W y ；
According to load force W x And W y Determining the load angle beta 0 Wherein the load angle is calculated by the formula
Figure FDA0003943232440000029
2. The apparatus of claim 1, wherein the rotor shaft further comprises a thrust disk coaxially disposed with the rotor shaft, the axial bearings comprise a first axial bearing and a second axial bearing respectively disposed at two sides of the thrust disk, the first axial bearing and the second axial bearing respectively enclose a first axial coil and a second axial coil, and the first axial coil and the second axial coil are disposed opposite to each other.
3. The device of claim 2 wherein said thrust disc is provided on at least one side with a plurality of first dynamic pressure grooves; the first dynamic pressure groove is spiral along the axial section structure of the thrust disc, and the second dynamic pressure groove is at least one of herringbone, splayed and pi-shaped along the radial expansion structure of the rotor spindle.
4. The apparatus of claim 2, further comprising at least two protective bearings disposed adjacent to the radial bearing, the radial bearing having a greater clearance from the rotor shaft than the protective bearings.
5. The apparatus of claim 4, wherein the rotor shaft further comprises a first journal disposed at an end of the rotor shaft proximate the first drive wheel and coupled to the first drive wheel, and a second journal disposed at an end of the rotor shaft proximate the second drive wheel and coupled to the second drive wheel.
6. The apparatus of claim 5, wherein the brake motor rotor is located between the first journal and the second journal, the end of the first journal remote from the first drive wheel being connected to the thrust plate, the other end of the thrust plate being connected to the brake motor rotor;
the first axial bearing, the thrust disc, the second axial bearing, the first protection bearing, the first radial bearing, the brake motor stator, the second radial bearing and the second protection bearing are sequentially and coaxially arranged between the first journal and the second journal.
7. The apparatus of claim 2, wherein the magnetic levitation hydrogen turboexpansion apparatus further comprises a rotation speed monitoring component, wherein the rotation speed monitoring component comprises an electromagnetic induction tachometer and a boss or a groove arranged on a rotor system;
and displacement sensors are arranged on the first radial bearing and the second radial bearing along the arrangement direction of the magnetic poles.
8. The apparatus of claim 5, wherein the first drive wheel and the second drive wheel are identical mirror images, wherein the hydrogen drive gas introduced into the first drive wheel and the second drive wheel has the same flow rate and condition, and wherein the first journal and the second journal are both hollow.
9. The device according to claim 1, wherein the device comprises a hydrogen embrittlement prevention coating formed after coating treatment, the thickness of the hydrogen embrittlement prevention coating is 10-1000 nm, and the material of the hydrogen embrittlement prevention coating is alumina.
10. A magnetic levitation hydrogen turbine expansion method using the apparatus of any of claims 1-9, comprising the steps of:
electrifying the magnetic suspension bearing assembly to form bearing capacity so as to suspend and fix the rotor system;
hydrogen driving gas is introduced into a first driving wheel and a second driving wheel to drive the first driving wheel and the second driving wheel to rotate so as to drive a rotor system to rotate and do work;
a brake motor rotor on the rotor spindle rotates to generate current in a brake motor stator;
the expanded hydrogen drives the gas exhaust.
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