CN112668123B - Vibration characteristic analysis method, device and equipment for cantilever sensitive type single-shaft rotor - Google Patents
Vibration characteristic analysis method, device and equipment for cantilever sensitive type single-shaft rotor Download PDFInfo
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Abstract
The application discloses a vibration characteristic analysis method, device and equipment of a cantilever sensitive type single-shaft rotor, relates to the technical field of computer software, and can realize effective analysis of vibration characteristics of the cantilever sensitive type single-shaft rotor. The method comprises the following steps: modeling a cantilever rotor mechanism of the unit, and configuring the rotational inertia of an additional part in the model; acquiring the thermal unbalance of the cantilever impeller side according to the attribute parameter information of the model; and calling a Morton effect simulation module to analyze the Morton effect of the model according to the thermal unbalance. The vibration characteristic analysis method is suitable for vibration characteristic analysis of the cantilever sensitive type single-shaft rotor.
Description
Technical Field
The application relates to the technical field of computer software, in particular to a vibration characteristic analysis method, device and equipment of a cantilever sensitive type single-shaft rotor.
Background
Along with the continuous adoption of large-scale air separation equipment, the stability requirement of safety production on a unit shafting is also higher and higher. Rotary machines are often designed with cantilever rotor systems in which the rotor turns at constant speed, the stresses of the system being of the cantilever arm type, with poor anti-jamming capability, which easily cause mechanical vibrations, leading to instability of the operation of the machine set. Among them, the synchronous vibration problem of the cantilever sensitive type single-shaft rotor is particularly remarkable.
However, at present, an effective analysis means for vibration characteristics of the cantilever-sensitive single-shaft rotor is lacking, and an accurate vibration characteristic analysis result cannot be given, so that a corresponding guiding basis cannot be given on solving the synchronous vibration problem of the cantilever-sensitive single-shaft rotor.
Disclosure of Invention
In view of this, the present application provides a vibration characteristic analysis method, device and equipment for a cantilever-sensitive single-shaft rotor, which mainly aims to solve the problem that an effective analysis means for vibration characteristics of a cantilever-sensitive single-shaft rotor is lacking at present, an accurate vibration characteristic analysis result cannot be given out, and further a corresponding instruction basis cannot be given out on the problem of synchronous vibration of the cantilever-sensitive single-shaft rotor.
According to an aspect of the present application, there is provided a vibration characteristic analysis method of a cantilever-sensitive type single-shaft rotor, the method comprising:
modeling a cantilever rotor mechanism of the unit, and configuring the rotational inertia of an additional part in the model;
acquiring the thermal unbalance of the cantilever impeller side according to the attribute parameter information of the model;
and calling a Morton effect simulation module to analyze the Morton effect of the model according to the thermal unbalance.
According to another aspect of the present application, there is provided a vibration characteristic analysis apparatus of a cantilever-sensitive type single-shaft rotor, the apparatus comprising:
the modeling module is used for modeling the unit cantilever rotor mechanism and configuring the rotational inertia of an additional part in the model;
the acquisition module is used for acquiring the thermal unbalance of the cantilever impeller side according to the attribute parameter information of the model;
and the analysis module is used for calling the Morton effect simulation module to analyze the Morton effect of the model according to the thermal unbalance.
According to still another aspect of the present application, there is provided a storage device having stored thereon a computer program which, when executed by a processor, implements the vibration characteristic analysis method of the cantilever-sensitive single-shaft rotor described above.
According to still another aspect of the present application, there is provided a physical device for vibration characteristics analysis of a cantilever-sensitive single-axis rotor, including a storage device, a processor, and a computer program stored on the storage device and executable on the processor, the processor implementing the vibration characteristics analysis method of a cantilever-sensitive single-axis rotor described above when executing the program.
The Morton effect is that when the rotor whirls synchronously, a larger circumferential temperature difference occurs at the journal of the cantilever side due to overlong and overweight cantilever ends, so that thermal unbalance is caused, and the rotor vibrates excessively. The method provides an effective analysis means for the vibration characteristics of the cantilever sensitive type single-shaft rotor, can give accurate vibration characteristic analysis results, and further can accurately give corresponding guiding basis on solving the synchronous vibration problem of the cantilever sensitive type single-shaft rotor so as to find an effective way for solving the synchronous vibration problem.
The foregoing description is only an overview of the technical solutions of the present application, and may be implemented according to the content of the specification in order to make the technical means of the present application more clearly understood, and in order to make the above-mentioned and other objects, features and advantages of the present application more clearly understood, the following detailed description of the present application will be given.
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Various other advantages and benefits will become apparent to those of ordinary skill in the art upon reading the following detailed description of the preferred embodiments. The drawings are only for purposes of illustrating the preferred embodiments and are not to be construed as limiting the application. Also, like reference numerals are used to designate like parts throughout the figures. In the drawings:
fig. 1 is a schematic flow chart of a vibration characteristic analysis method of a cantilever-sensitive single-shaft rotor according to an embodiment of the present application;
FIG. 2 illustrates a vibration spectrum of a typical destabilizing rotor provided by an embodiment of the present application;
FIG. 3 illustrates a Bode diagram with a typical hysteresis loop provided by embodiments of the present application;
FIG. 4 illustrates a cantilever rotor schematic provided by an embodiment of the present application;
FIG. 5 illustrates a rotor thermal bend schematic provided by an embodiment of the present application;
FIG. 6 is a flow chart illustrating a method for analyzing vibration characteristics of another cantilever-sensitive single-shaft rotor according to an embodiment of the present disclosure;
FIG. 7 illustrates three schematic excitation conditions provided by an embodiment of the present application;
FIG. 8 is a graph showing an imbalance response curve at a bearing under condition 3 provided by an embodiment of the present application;
fig. 9 shows a schematic structural diagram of a vibration characteristic analysis apparatus for a cantilever-sensitive single-shaft rotor according to an embodiment of the present application.
Detailed Description
Exemplary embodiments of the present disclosure will be described in more detail below with reference to the accompanying drawings. While exemplary embodiments of the present disclosure are shown in the drawings, it should be understood that the present disclosure may be embodied in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art.
The method aims at solving the problem that the prior art lacks an effective analysis means for vibration characteristics of the cantilever sensitive type single-shaft rotor. The present embodiment provides a vibration characteristic analysis method of a cantilever-sensitive single-shaft rotor, as shown in fig. 1, the method includes:
101. modeling the cantilever rotor mechanism of the unit and configuring the rotational inertia of an additional part in the model.
Wherein the attachment may include a rotor hub, impeller, balance disc, coupling, etc.
The execution body for the present embodiment may be an apparatus or device for vibration characteristic analysis of a cantilever-sensitive single-shaft rotor.
102. And acquiring the thermal unbalance of the cantilever impeller side according to the attribute parameter information of the model.
According to the embodiment, the synchronous vibration problem of the cantilever sensitive type single-shaft rotor is studied in depth, a large number of synchronous vibration cases are summarized, the influence of the Morton effect is found, when the rotor synchronously whirls, the cantilever end is overlong and overweight, so that a larger circumferential temperature difference occurs at the journal of the cantilever side, and further, the thermal unbalance is caused, and the rotor is caused to vibrate too much. Therefore, in order to accurately analyze the vibration characteristics of the cantilever rotor, it is necessary to calculate the amount of thermal unbalance on the cantilever impeller side.
103. And calling a Morton effect simulation module to analyze the Morton effect of the model according to the obtained thermal unbalance.
For example, for large air separation plant rotors. The cantilever rotor has enough isolation margin because of crossing the second-order critical rotating speed, and does not have resonance problem. However, considering the influence of the morton effect, a calculation method of the thermal unbalance is introduced in the rotor dynamics analysis, and the problem of overlarge amplitude at the cantilever side bearing is successfully analyzed.
Compared with the prior art, the vibration characteristic analysis method for the cantilever-sensitive single-shaft rotor provides an effective analysis means for the vibration characteristic of the cantilever-sensitive single-shaft rotor, and can give accurate vibration characteristic analysis results, so that corresponding guidance basis can be accurately given on solving the synchronous vibration problem of the cantilever-sensitive single-shaft rotor, and an effective mode for solving the synchronous vibration problem of the cantilever-sensitive single-shaft rotor can be found.
To better aid in understanding the present embodiment, the following analysis of the vibration mechanism of the cantilever rotor is given:
1. first, for the Morton effect, studies have shown that oil film bearings support the rotor in synchronous whirl conditions, the circumferential surface of the journal will develop a non-uniform temperature field. It has been thought that the temperature of the journal circumferential surface is uniform, but in practice the rotor will whirl synchronously due to the unbalance, and a point at the journal will always be at the outer end of the synchronous track and therefore will be closest to the bearing wall, i.e. at the minimum oil film thickness, and the opposite diameter of that point will be at the maximum oil film thickness. The smaller the oil film thickness, the greater the viscous shear and the higher the temperature and vice versa. This will create an uneven temperature field on the circumferential surface of the journal, the point at the minimum oil film thickness being called the hot spot and the point diametrically opposite the hot spot being called the cold spot. Due to the synchronous whirl, the hot spot will always be at the minimum oil film thickness, i.e. always a hot spot. In fact, this will create a convection current as the oil continues to enter the converging wedge, acting as a cooling, resulting in the hot spot forming a phase difference with the minimum oil film thickness (high spot).
When the whirl track is larger, the larger the circumferential temperature difference of the journal is, the temperature difference can cause the rotor cantilever to generate thermal bending, namely, unbalance is generated. If the rotor system is sensitive to unbalance, excessive vibration of the rotor is caused, and a larger temperature difference is generated, so that larger thermal bending is caused, and the rotor is caused to vibrate more, so that a destabilization system is formed.
2. The rotor thermal instability vibration characteristic is generated based on the Morton effect, and in general, a cantilever rotor or a rotor with a coupler at high rotating speed and high power is easy to generate thermal instability. The main vibration characteristics are as follows:
a) The vibration frequency is the running rotational speed, i.e. synchronous vibration. The frequency spectrum can clearly show that the main vibration frequency is the power frequency, and the typical frequency spectrum is shown in figure 2 because only synchronous vibration has constant hot spots and cold spots.
b) Rotor vibration hysteresis. Since the temperature difference is relatively large after the rotor is accelerated to the thermal instability rotating speed, the temperature difference cannot be timely reduced during the speed reduction, so that the thermal unbalance is still large, and the vibration is still high, as shown in fig. 3. Typically, the rotor is slowed down to a certain rotational speed and after a period of settling, the amplitude is slowly decreased.
c) And (5) spirally vibrating. When the rotor is thermally unstable, the hot spot position is continuously changed, and the temperature difference is continuously increased, so that the thermal unbalance amount is also increased, the vector sum angle of the thermal unbalance amount and the mechanical unbalance amount is continuously changed, and the on-site characterization is that the rotor is in spiral vibration.
3. Finally, through the above analysis process, in order to accurately simulate the morton effect of the rotor, the most important is to obtain the thermal unbalance of the rotor.
As shown in fig. 4, which is a schematic diagram of a typical cantilever rotor, if a temperature difference occurs at the journal circumferential surface, the cantilever rotor will be thermally bent, as shown in fig. 5.
The amount of thermal imbalance created by the morton effect is:
wherein U is T For the amount of thermal unbalance, m o Indicating cantilever mass, L o R is the distance from the center of gravity of the cantilever to the center of the bearing jb For the journal radius, α is the coefficient of thermal expansion of the shaft, the coefficient of thermal expansion of the steel is typically 1.2e-5/°c, Δt is the maximum temperature difference at the journal circumferential surface, L jb Is radial bearing bush width.
Further, based on the above formula, as an extension and refinement of the present embodiment, in order to fully explain the implementation process of the present embodiment, taking a large cantilever rotor as an example, another vibration characteristic analysis method of a cantilever-sensitive single-shaft rotor is provided, as shown in fig. 6, and the method includes:
201. modeling the cantilever rotor mechanism and configuring the moment of inertia of the appendages in the cantilever rotor model.
Wherein, the additional piece includes rotor axle sleeve, impeller, balance disc, shaft coupling etc. at least.
As an alternative, step 201 may specifically include: the cantilever impeller is modeled in an equivalent diameter manner, rather than in a common centralized mass manner, by which a more efficient model can be built based on multiple analytical experiences.
202. The thermal unbalance amount of the cantilever impeller side is calculated using the first preset formula (1-1).
203. And calling a Morton effect simulation module to perform Morton effect analysis on the cantilever rotor model according to the calculated thermal unbalance.
As an alternative, step 203 may specifically include: acquiring a peak value at the maximum continuous rotating speed; using a second preset formula A M&T ＝A M (U M +U T )/U M Calculating a final amplitude value A containing the thermal unbalance amount and the mechanical unbalance amount M&T Wherein A is M U is the amplitude value under the action of mechanical unbalance m Is the mechanical unbalance; formulating a Morton effect analysis specification of the cantilever rotor according to the acquired peak value, the calculated final amplitude value and the thermal unbalance; and then referring to the Morton effect analysis specification, calling a Morton effect simulation module to perform Morton effect analysis on the cantilever rotor model.
The analysis specification of the Morton effect of the cantilever rotor is equivalent to the analysis standard of the rotor dynamics of the cantilever rotor, and aims to realize accurate Morton effect analysis of a cantilever rotor model. In this embodiment, the following cantilever-rotor Morton effect analysis specifications are tailored:
1) The rotor imbalance response analysis modeling needs to consider the rotational inertia of the additional parts such as impellers.
2) Rotor imbalance response analysis was performed under excitation conditions (as shown in FIG. 7), with the mechanical imbalance amount U M An imbalance response curve at the cantilever end bearing is output (as shown in fig. 8).
Wherein U is M ＝4m o *6350/N mc ，m o Is of cantilever mass, N mc Is the maximum continuous rotational speed.
The evaluation criteria are as follows: a) Obtaining N mc Peak-to-peak value a at rotational speed M 。
b) The thermal unbalance amount of the cantilever impeller side was calculated as follows:
wherein: u (U) T -amount of heat imbalance, g-mm; α=1.2e-5—coefficient of thermal expansion, 1/°c;
ΔT＝3+(N mc * Pi D/60-350)/10-journal circumferential temperature difference, DEG C; d, the outer diameter of the cantilever impeller, m; m is m o -cantilever mass, kg; l (L) o -the distance from the center of gravity of the cantilever to the center of the bearing is mm; l (L) jb Bearing bush width, mm; r is R jb Bearing radius, mm.
c) Final amplitude value a containing thermal and mechanical unbalance M&T The calculation formula is as follows, and the value should be less than 25um.
A M&T ＝A M (U M +U T )/U M
Wherein: a is that M&T Represents the final amplitude value, um; a is that M Represents the amplitude value, um, under the effect of the mechanical unbalance.
204. And if the cantilever rotor meets the preset excessive synchronous vibration condition according to the analysis result, readjusting the cantilever rotor model by reducing the diameter size of the journal and/or modifying the bearing structure and/or reducing the moment of the cantilever.
For this embodiment, a numerical analysis method is utilized, and in combination with the morton effect simulation module, a calculation method of the thermal unbalance is introduced. By summarizing a large number of synchronous vibration cases, a method for solving the synchronous vibration is finally successfully found through detailed rotor dynamics analysis and anti-conventional design.
As an alternative, the process of reducing the journal diameter size may specifically include: reducing the journal of the cantilever rotor to enable the bearing specific pressure value to be between 1.5 and 2.0MPa, wherein the calculation formula of the checking method of the bearing specific pressure value is as follows:p is bearing specific pressure, W is bearing static load, D is bearing diameter, and L is bearing bush width.
The process of modifying the bearing structure may specifically include: the radial bearing of the cantilever rotor adopts a four-tile inter-tile supporting mode, the bearing wrap angle is 70-75 degrees, the tile offset ratio is 0.5-0.6, and the included angle between the tile pivot and the vertical direction is 45 degrees.
The processes of reducing the cantilever moment and changing the assembly mode can specifically comprise: the mass of the cantilever impeller is reduced, and the length of the cantilever end is shortened, so that the mass of the cantilever is less than 20% of the total mass of the rotor, and the length of the center of the cantilever from the nearest radial bearing is less than 25% of the total length of the rotor.
205. And calling a Morton effect simulation module to perform Morton effect analysis on the re-adjusted cantilever rotor model until the rotor is determined to be not in accordance with the preset synchronous vibration excessive condition according to the new analysis result.
The problem of overlarge synchronous vibration of the cantilever rotor can be effectively solved through the adjustment mode.
Further, as a specific implementation of the method shown in fig. 1 and fig. 6, the present embodiment provides a vibration characteristic analysis apparatus for a cantilever-sensitive single-shaft rotor, as shown in fig. 9, the apparatus includes: a modeling module 31, an acquisition module 32, an analysis module 33.
The modeling module 31 is used for modeling the unit cantilever rotor mechanism and configuring the rotational inertia of an additional part in the model;
an obtaining module 32, configured to obtain a thermal unbalance amount of the cantilever impeller side according to the attribute parameter information of the model;
and the analysis module 33 is used for calling the Morton effect simulation module to perform Morton effect analysis on the model according to the thermal unbalance.
In a specific application scenario, the obtaining module 32 is specifically configured to use a first preset formulaCalculating the thermal unbalance of the cantilever impeller side; wherein U is T For the amount of thermal unbalance, m o Indicating cantilever mass, L o R is the distance from the center of gravity of the cantilever to the center of the bearing jb Is the journal radius, alpha is the thermal expansion coefficient of the rotating shaft, delta T is the maximum temperature difference at the circumferential surface of the journal, L jb Is radial bearing bush width.
In a specific application scenario, the analysis module 33 is specifically configured to obtain a peak-to-peak value at the maximum continuous rotation speed; using a second preset formula A M&T ＝A M (U M +U T )/U M Calculating a final amplitude value A containing the thermal unbalance amount and the mechanical unbalance amount M&T Wherein A is M U is the amplitude value under the action of mechanical unbalance m Is the mechanical unbalance; according to the instituteFormulating a Morton effect analysis specification for the peak-to-peak value, the final amplitude value, and the thermal imbalance amount; and calling a Morton effect simulation module to perform Morton effect analysis on the model according to the Morton effect analysis specification.
In a specific application scenario, the device further includes: an adjustment module 34;
the adjusting module 34 is configured to readjust the model by reducing the diameter size of the journal, and/or modifying the bearing structure, and/or reducing the moment of the cantilever and changing the assembly mode if the rotor meets the preset excessive synchronous vibration condition according to the analysis result;
the analysis module 33 is specifically configured to call the morton effect simulation module to perform morton effect analysis on the readjusted model until it is determined that the rotor does not meet the preset excessive synchronous vibration condition according to the new analysis result.
In a specific application scenario, the adjusting module 34 is specifically configured to reduce the journal of the cantilever rotor so that the bearing specific pressure value is between 1.5 and 2.0MPa, where the calculation formula of the method for checking the bearing specific pressure value is as follows:p is the bearing specific pressure, W is the bearing static load, D is the bearing diameter, and L is the bearing bush width;
the adjusting module 34 is specifically used for the radial bearing of the cantilever rotor by adopting a four-tile inter-tile supporting mode, the bearing wrap angle is 70-75 degrees, the tile offset ratio is 0.5-0.6, and the included angle between the tile fulcrum and the vertical direction is 45 degrees;
the adjustment module 34 is specifically further configured to reduce the cantilever impeller mass and shorten the cantilever end length such that the cantilever mass is less than 20% of the total rotor mass and the length of the cantilever mass center from the nearest radial bearing is less than 25% of the total rotor length.
In a specific application scenario, the additional piece at least comprises a rotor shaft sleeve, an impeller, a balance disc and a coupler; accordingly, the modeling module 31 is specifically configured to model the cantilever impeller in an equivalent diameter manner.
It should be noted that, other corresponding descriptions of each functional unit related to the vibration characteristic analysis device for a cantilever-sensitive single-shaft rotor provided in the present embodiment may refer to corresponding descriptions in fig. 1 and fig. 6, and are not repeated herein.
Based on the above-described methods shown in fig. 1 and 6, accordingly, the present embodiment also provides a storage device having stored thereon a computer program which, when executed by a processor, implements the vibration characteristic analysis method of the cantilever-sensitive single-shaft rotor shown in fig. 1 and 6.
Based on the above-described methods shown in fig. 1 and 6 and the embodiment of the virtual device shown in fig. 9, the present embodiment further provides a physical apparatus for vibration characteristic analysis of a cantilever-sensitive single-shaft rotor, where the apparatus includes: a processor 41, a storage device 42, and a computer program stored on the storage device 42 and executable on the processor 41, the processor 41 implementing the vibration characteristic analysis method of the cantilever-sensitive single-shaft rotor shown in fig. 1 and 6 when executing the program; the apparatus further comprises: bus 43 is configured to couple processor 41 and memory device 42.
By applying the technical scheme of the embodiment, compared with the prior art, the scheme is used for carrying out deep research on the synchronous vibration problem of the high-speed high-power rotor with the heavy coupler and the cantilever rotor. The project successfully reveals the inherent vibration mechanism of the synchronous vibration problem of the cantilever rotor, and finds out a solution by means of a large amount of rotor dynamics analysis and reference to the design experience of the small cantilever rotor. The specific research and application effects of the project are good, the research targets of the scientific research project are completed, and the main achievements are as follows:
(1) By means of a large number of rotor dynamics calculations and analysis of the vibration data in situ, the coupling weight is reduced or the coupling center of gravity is brought closer to the compressor side.
(2) By introducing a thermal unbalance calculation method, the synchronous vibration problem of the cantilever rotor is successfully simulated.
(3) By referring to the design experience of the small cantilever rotor, a solution is found, namely, the bolt of the cantilever impeller is changed into hydraulic assembly, the diameter of the journal is reduced, the radial bearing is changed from 5 watts to 4 watts, the weight of the cantilever is reduced as much as possible, the gravity center is shortened, and the like.
(4) Through a large number of investigation and summarization of synchronous vibration cases of the same type in the past year, the thermal instability is considered to be easy to occur near the critical rotation speed, and the AF of the critical rotation speed is usually less than 2.5.
(5) The phenomenon of rotor thermal instability is simulated by using a Morton effect simulation module.
(6) The effect of reducing the cantilever length is better than reducing the cantilever weight under the same cantilever moment.
(7) The thermal analysis and the stress deformation analysis are carried out on the journal thermal insulation sleeve, and the simulation result proves that the effect of reducing the circumferential temperature difference of the journal is very obvious, so that the support is provided for the next test verification.
From the above description of the embodiments, it will be apparent to those skilled in the art that the present application may be implemented in hardware, or may be implemented by means of software plus necessary general hardware platforms. Based on such understanding, the technical solution of the present application may be embodied in the form of a software product, which may be stored in a non-volatile storage medium (may be a CD-ROM, a U-disk, a mobile hard disk, etc.), and includes several instructions for causing a computer device (may be a personal computer, a server, or a network device, etc.) to perform the methods described in various implementation scenarios of the present application.
Those skilled in the art will appreciate that the drawings are merely schematic illustrations of one preferred implementation scenario, and that the modules or flows in the drawings are not necessarily required to practice the present application.
Those skilled in the art will appreciate that modules in an apparatus in an implementation scenario may be distributed in an apparatus in an implementation scenario according to an implementation scenario description, or that corresponding changes may be located in one or more apparatuses different from the implementation scenario. The modules of the implementation scenario may be combined into one module, or may be further split into a plurality of sub-modules.
The foregoing application serial numbers are merely for description, and do not represent advantages or disadvantages of the implementation scenario.
The foregoing disclosure is merely a few specific implementations of the present application, but the present application is not limited thereto and any variations that can be considered by a person skilled in the art shall fall within the protection scope of the present application.
Claims (6)
1. A vibration characteristic analysis method of a cantilever-sensitive single-shaft rotor, comprising:
modeling a cantilever rotor mechanism of the unit, and configuring the rotational inertia of an additional part in the model;
acquiring the thermal unbalance of the cantilever impeller side according to the attribute parameter information of the model; the obtaining of the thermal unbalance of the cantilever impeller side according to the attribute parameter information of the model specifically comprises the following steps:
using a first preset formulaCalculating the thermal unbalance of the cantilever impeller side;
wherein U is T For the amount of thermal unbalance, m o Indicating cantilever mass, L o R is the distance from the center of gravity of the cantilever to the center of the bearing jb Is the journal radius, alpha is the thermal expansion coefficient of the rotating shaft, delta T is the maximum temperature difference at the circumferential surface of the journal, L jb Is radial bearing bush width;
according to the thermal unbalance, a Morton effect simulation module is called to analyze Morton effect of the model; and calling a Morton effect simulation module to analyze the Morton effect of the model according to the thermal unbalance, wherein the Morton effect simulation module specifically comprises the following steps:
acquiring a peak value at the maximum continuous rotating speed;
using a second preset formula A M&T ＝A M (U M +U T )/U M Calculating a final amplitude value A containing the thermal unbalance amount and the mechanical unbalance amount M&T Wherein A is M U is the amplitude value under the action of mechanical unbalance m Is the mechanical unbalance;
formulating a cantilever rotor Morton effect analysis specification according to the peak-to-peak value, the final amplitude value and the thermal unbalance;
and calling a Morton effect simulation module to perform Morton effect analysis on the model according to the Morton effect analysis specification.
2. The method of claim 1, wherein if it is determined from the analysis result that the rotor meets a preset synchronous vibration excessive condition, the method further comprises:
readjusting the model by reducing journal diameter size, and/or modifying bearing structure, and/or reducing cantilever moment and altering assembly;
and calling a Morton effect simulation module to perform Morton effect analysis on the readjusted model until the rotor is determined to be not in accordance with the preset excessive synchronous vibration condition according to a new analysis result.
3. The method according to claim 2, characterized in that said reducing journal diameter size comprises in particular:
reducing the journal of the cantilever rotor to enable the bearing specific pressure value to be between 1.5 and 2.0MPa, wherein the calculation formula of the checking method of the bearing specific pressure value is as follows:p is the bearing specific pressure, W is the bearing static load, D is the bearing diameter, and L is the bearing bush width;
the modified bearing structure specifically comprises:
the radial bearing of the cantilever rotor adopts a bearing mode between tiles of four tiles, the bearing wrap angle is 70-75 degrees, the tile offset ratio is 0.5-0.6, and the included angle between the tile fulcrum and the vertical direction is 45 degrees;
the cantilever moment is reduced, and the assembly mode is changed, specifically comprising:
the mass of the cantilever impeller is reduced, and the length of the cantilever end is shortened, so that the mass of the cantilever is less than 20% of the total mass of the rotor, and the length of the center of the cantilever from the nearest radial bearing is less than 25% of the total length of the rotor.
4. The method of claim 1, wherein the attachment comprises at least a rotor hub, an impeller, a balance disc, a coupling;
modeling the unit cantilever rotor mechanism specifically comprises the following steps:
the cantilever impeller is modeled in terms of equivalent diameter.
5. A vibration characteristic analysis apparatus of a cantilever-sensitive single-shaft rotor, comprising:
the modeling module is used for modeling the unit cantilever rotor mechanism and configuring the rotational inertia of an additional part in the model;
the acquisition module is used for acquiring the thermal unbalance of the cantilever impeller side according to the attribute parameter information of the model; the acquisition module is specifically configured to utilize a first preset formulaCalculating the thermal unbalance of the cantilever impeller side;
wherein U is T For the amount of thermal unbalance, m o Indicating cantilever mass, L o R is the distance from the center of gravity of the cantilever to the center of the bearing jb Is the journal radius, alpha is the thermal expansion coefficient of the rotating shaft, delta T is the maximum temperature difference at the circumferential surface of the journal, L jb Is radial bearing bush width;
the analysis module is used for calling a Morton effect simulation module to analyze the Morton effect of the model according to the thermal unbalance;
the analysis module is specifically used for acquiring a peak value at the maximum continuous rotating speed;
using a second preset formula A M&T ＝A M (U M +U T )/U M Calculating a final amplitude value A containing the thermal unbalance amount and the mechanical unbalance amount M&T Wherein A is M U is the amplitude value under the action of mechanical unbalance m Is the mechanical unbalance;
formulating a cantilever rotor Morton effect analysis specification according to the peak-to-peak value, the final amplitude value and the thermal unbalance;
and calling a Morton effect simulation module to perform Morton effect analysis on the model according to the Morton effect analysis specification.
6. A vibration characteristics analysis apparatus of a cantilever-sensitive single-shaft rotor, comprising a storage device, a processor, and a computer program stored on the storage device and executable on the processor, characterized in that the processor implements the vibration characteristics analysis method of a cantilever-sensitive single-shaft rotor according to any one of claims 1 to 4 when executing the program.
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