Optimization method and optimization system of axial flow expander rotor system and storage medium

Abstract

The invention discloses an optimization method and optimization system of an axial flow expander rotor system and a storage medium. The optimization method comprises the steps that a rotor system model is established, and the critical rotating speed of a rotor system is obtained; based on the critical rotation speed and the operation rotation speed, obtaining an isolation margin; acquiring the amplitude of the rotor based on the running speed; if the isolation margin is not less than the first threshold value and the amplitude is not greater than the second threshold value, entering the next step, otherwise, re-establishing the rotor system model; and mounting and producing according to the rotor system model. The isolation margin of the rotor system is increased, meanwhile, the amplitude of the rotor system is reduced, on one hand, reliable and stable work of the rotor system can be guaranteed, on the other hand, the high-speed and large-scale work requirements of the axial flow expansion machine can be met, and the work reliability of the axial flow expansion machine is guaranteed.

Description

Technical Field

[0001] The invention relates to the technical field of axial flow expander unit design, and in particular to an optimization method, an optimization system and a storage medium for an axial flow expander rotor system. Background Art

[0002] In the traditional design process of the axial flow expander rotor system, a five-pad tilting pad bearing is generally used. The conventional five-pad bearing has a pad wrap angle of 60° and an angle of 30° on both sides of the fulcrum. This type of bearing can be applied to conventional expander rotors. However, as axial flow expander equipment gradually becomes faster and larger, the rotor speed needs to be increased and the impeller mass needs to be increased. This makes the design of the rotor system more difficult, because the increase in speed and the increase in impeller mass increase the risk of rotor resonance on the one hand; on the other hand, the rotor vibrates too much under rated conditions, affecting the stable operation of the rotor system. Summary of the invention

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art or related art.

[0004] In view of this, the present invention provides an optimization method, an optimization system and a storage medium for an axial flow expander rotor system, wherein the optimization method can obtain a better critical speed by limiting the isolation margin and the amplitude, so as to increase the isolation margin of the rotor system and reduce the amplitude of the rotor system. On the one hand, it can ensure the reliable and stable operation of the rotor system, and on the other hand, it can also meet the high-speed and large-scale working requirements of the axial flow expander, thereby ensuring the reliability of the operation of the axial flow expander.

[0005] Specifically, the following technical solutions are included:

[0006] An embodiment of the first aspect of the present invention provides an optimization method for an axial flow expander rotor system, the optimization method comprising:

[0007] Establishing a rotor system model to obtain the critical speed of the rotor system;

[0008] Obtaining an isolation margin based on the critical speed and the operating speed;

[0009] Based on the operating speed, obtaining the amplitude of the rotor;

[0010] If the isolation margin is not less than the first threshold value and the amplitude is not greater than the second threshold value, proceed to the next step, otherwise the rotor system model is re-established;

[0011] Production is installed according to the rotor system model.

[0012] Optionally, establishing the rotor system model includes:

[0013] Build models of the rotor body and bearings;

[0014] By changing the parameters of the bearing, different critical speeds are obtained.

[0015] Optionally, the bearing is a tilting pad bearing, and the parameters of the bearing include: bearing diameter, number of pads, wrap angle, deflection ratio, pad length and bearing installation clearance.

[0016] Optionally, the critical speed of the rotor is adjusted by optimizing the number of bearing pads, the pad wrap angle and the deflection ratio.

[0017] Optionally, the isolation margin is a ratio of a difference between the critical speed and the operating speed to the operating speed.

[0018] Optionally, the amplitude is the vibration amplitude of the rotor in the radial direction of the measuring point at the operating speed.

[0019] Optionally, the first threshold is 30%.

[0020] Optionally, the second threshold is 4.0 μm.

[0021] An embodiment of the second aspect of the present invention provides an optimization system for an axial flow expander rotor system, which is obtained according to the above-mentioned optimization method for an axial flow expander rotor system, and the optimization system comprises:

[0022] A speed module is used to establish a rotor system model and obtain a critical speed of the rotor system;

[0023] An isolation margin module, which obtains an isolation margin based on the critical speed and the operating speed;

[0024] An amplitude module, which obtains the amplitude of the rotor based on the operating speed;

[0025] The judgment module, if the isolation margin is not less than the first threshold value and the amplitude is not greater than the second threshold value, enters the next module, otherwise, re-acquires the speed module;

[0026] Install the production module and install the production according to the rotor system model.

[0027] An embodiment of the third aspect of the present invention provides a computer-readable storage medium having a computer program stored thereon, which implements the steps of the above-mentioned optimization method when executed by a processor.

[0028] The optimization method, optimization system and storage medium of the axial flow expander rotor system provided by the embodiment of the present invention, wherein the operating speed is a parameter that has been determined at the beginning of the rotor system design, and the optimization method includes first establishing a rotor system model, obtaining the critical speed of the rotor system according to the rotor system model, and then obtaining the isolation margin of the rotor system according to the critical speed and the operating speed, and obtaining the amplitude of the rotor system according to the operating speed. When the isolation margin is not less than the first threshold and the amplitude is not greater than the second threshold, the rotor system meets the requirements. When the isolation margin is less than the first threshold and / or the amplitude is greater than the second threshold, it is necessary to adjust the rotor system model until the isolation margin of the rotor system model is not less than the first threshold and the amplitude of the rotor system is not greater than the second threshold. In this way, the rotor system can obtain a better critical speed to increase the isolation margin of the rotor system and reduce the amplitude of the rotor system. On the one hand, it can ensure the reliable and stable operation of the rotor and the stator, and on the other hand, it can also meet the high-speed and large-scale working requirements of the axial flow expander and ensure the reliability of the axial flow expander.

[0029] The above description is only an overview of the technical solution of the present application. In order to more clearly understand the technical means of the present application, it can be implemented in accordance with the contents of the specification. In order to make the above and other purposes, features and advantages of the present application more obvious and easy to understand, the specific implementation methods of the present application are listed below. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the following briefly introduces the drawings required for use in the description of the embodiments. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without creative work.

[0031] Figure 1 A flowchart of the steps of an optimization method for an axial flow expander rotor system according to an embodiment of the present invention;

[0032] Figure 2 A schematic diagram of stiffness characteristics of a four-pad tilting pad bearing and a five-pad tilting pad bearing both having an eccentric ratio of 0.5 according to an embodiment of the present invention;

[0033] Figure 3 A schematic diagram of damping characteristics of a four-pad tilting pad bearing and a five-pad tilting pad bearing both having an eccentric ratio of 0.5 according to an embodiment of the present invention;

[0034] Figure 4 It is a schematic diagram of stiffness comparison of a four-pad tilting pad radial bearing under different eccentric support ratios according to an embodiment of the present invention;

[0035] Figure 5It is a schematic diagram of damping comparison of a four-pad tilting pad radial bearing under different eccentric support ratios according to an embodiment of the present invention;

[0036] Figure 6 is a cross-sectional view of a four-pad tilting pad radial bearing with a pivot offset of 0.533 according to an embodiment of the present invention;

[0037] Figure 7 Schematic diagram of unbalanced response curves of a rotor system under a five-pad tilting pad bearing and a four-pad tilting pad bearing with an eccentric ratio of 0.5 according to an embodiment of the present invention;

[0038] Figure 8 Schematic diagram of unbalanced response curves of a rotor system under a four-pad tilting pad bearing with different eccentric ratios according to an embodiment of the present invention.

[0039] in, Figure 6 The corresponding relationship between the reference numerals and the component names is as follows:

[0040] 100 four-pad tilting pad bearing, 110 pad, 120 fulcrum, α is the wrap angle, β is the oil inlet side angle, γ is the oil inlet angle, and ε is the oil outlet angle. DETAILED DESCRIPTION

[0041] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0042] Before further describing the embodiments of the present invention in detail, the directional nouns involved in the embodiments of the present invention, such as "upper part", "lower part" and "side part", do not have the meaning of limiting the protection scope of the present invention.

[0043] To make the technical solutions and advantages of the present invention more clear, the embodiments of the present invention will be described in further detail below with reference to the accompanying drawings.

[0044] Example 1

[0045] Figure 1 The present invention is a flowchart of the steps of an optimization method for an axial flow expander rotor system according to an embodiment of the present invention.

[0046] like Figure 1 As shown, one embodiment of the present invention provides an optimization method for an axial flow expander rotor system, the optimization method comprising the following steps:

[0047] Step 1, establish a rotor system model and obtain the critical speed of the rotor system;

[0048] Step 2, obtaining the isolation margin based on the critical speed and the operating speed;

[0049] Step 3, obtaining the amplitude of the rotor based on the running speed;

[0050] Step 4: if the isolation margin is not less than the first threshold value and the amplitude is not greater than the second threshold value, proceed to the next step, otherwise the rotor system model is re-established;

[0051] Step 5: Install and produce according to the rotor system model.

[0052] Among them, the operating speed is a parameter that has been determined at the beginning of the rotor system design. The optimization method includes first establishing a rotor system model, obtaining the critical speed of the rotor system according to the rotor system model, and then obtaining the isolation margin of the rotor system according to the critical speed and the operating speed, and obtaining the amplitude of the rotor system according to the operating speed. When the isolation margin is not less than the first threshold and the amplitude is not greater than the second threshold, the rotor system meets the requirements. When the isolation margin is less than the first threshold and / or the amplitude is greater than the second threshold, it is necessary to adjust the rotor system model until the isolation margin of the rotor system model is not less than the first threshold and the amplitude of the rotor system is not greater than the second threshold. In this way, the rotor system can obtain a better critical speed to increase the isolation margin of the rotor system and reduce the amplitude of the rotor system. On the one hand, it can ensure the reliable and stable operation of the rotor and the stator. On the other hand, it can also meet the high-speed and large-scale working requirements of the axial flow expander and ensure the reliability of the axial flow expander.

[0053] It should be noted that there is sufficient isolation margin between the critical speed and the operating speed, that is, the isolation margin cannot be less than the first threshold value, and at the same time, the amplitude of the rotor system is not too large at the operating speed, that is, the amplitude is not greater than the second threshold value. Under such dual conditions, collision and friction between the rotor body and the stator body can be avoided. On the one hand, the reliability of the rotor system can be guaranteed, and on the other hand, the service life of the rotor system and the maintenance cycle of the rotor system can be extended.

[0054] In a feasible implementation manner, establishing a rotor system model includes:

[0055] Step 101, establishing a model of a rotor body and a bearing;

[0056] Step 102, obtaining different critical speeds by changing the parameters of the bearing.

[0057] Among them, in order to make the isolation margin not less than the first threshold and the amplitude not greater than the second threshold, it can be achieved by adjusting the rotor body structure of the axial flow expander, or by increasing the stiffness of the bearings in the rotor system. Since the arrangement of the rotor body structure has been designed and the structure is compact, if the rotor structure is further improved, the improvement design is difficult, which will increase the modification cost and prolong the modification time. Therefore, the present application improves the stiffness of the bearings by changing the parameters of the bearings in the rotor system, thereby achieving the purpose of the isolation margin of the rotor system being not less than the first threshold and the amplitude being not greater than the second threshold.

[0058] In a feasible implementation manner, the bearing is a tilting pad bearing, and the bearing parameters include: bearing diameter, number of pads, wrap angle, deflection ratio, pad length and bearing installation clearance.

[0059] It is understandable that in engineering, numerical methods or finite element methods are generally used to solve the Reynolds equation to obtain the stiffness coefficient and damping coefficient of the bearing fluid film. The above-mentioned bearing parameters (bearing diameter, number of pads, wrap angle, eccentricity ratio, pad length and bearing installation clearance) will affect the stiffness coefficient and damping coefficient of the bearing fluid film.

[0060] Among them, the bearing uses a tilting pad bearing. The elastic pad of the tilting pad bearing has a large contact area with the shaft and the friction force is evenly distributed, which can effectively reduce friction loss and improve the transmission efficiency of the bearing; because the elastic pad of the tilting pad bearing has good deformation ability, it can adapt to larger load deformation, thereby increasing the service life of the bearing; because each elastic pad can swing freely, it can prevent oil film oscillation and maintain good stability under high-speed rotation; because the structure of the tilting pad bearing can disperse the load and thus improve the load-bearing capacity, it is suitable for high-speed and high-load occasions.

[0061] It should be noted that in order to obtain different critical speeds, the relevant parameters of the bearing can be changed. The first is to increase the critical speed by increasing the bearing diameter, which requires the use of larger bearings, which will involve an increase in cost; the second is to adjust the critical speed by adjusting the bearing installation clearance. Based on the requirements of the bearing design manual, the bearing installation clearance range can only be adjusted within a small range. Too large a clearance will increase the vibration of the rotor, and too small a clearance will reduce the damping characteristics of the bearing; the third is to increase the stiffness of the bearing by adjusting the length of the bearing pad. If the pad length is too large, the compactness of the rotor structure will be reduced. If the pad length is too small, the stiffness of the bearing will be reduced. However, some rotors still cannot meet the requirements by adjusting the bearing installation clearance and the pad length within a reasonable range, so other parameters need to be optimized at this time.

[0062] In this embodiment, the number of pads, the wrap angle and the eccentric ratio are selected for optimization, and the optimization of these parameters will not increase the cost in the production, manufacturing, processing and installation of the bearing. In this embodiment, the stiffness of the bearing is changed by further adjusting the number of pads, the wrap angle and the eccentric ratio of the tilting pad bearing, thereby changing the critical speed of the rotor system, ensuring the isolation margin between the critical speed and the operating speed, and avoiding the increase of the rotor amplitude, which can reduce the risk of resonance of the rotor system and ensure the reliability and safety of the axial flow expander.

[0063] In a possible implementation manner, the isolation margin is the ratio of the difference between the critical speed and the operating speed to the operating speed.

[0064] It should be noted that the actual isolation margin calculation method is shown in formula (1):

[0065]

[0066] Among them, N c is the critical speed, N m is the operating speed.

[0067] It can be understood that the isolation margin is a parameter used to indicate the distance between the critical speed and the operating speed. That is, the larger the isolation margin, the safer the rotor system.

[0068] In a feasible implementation, the first threshold is 30%.

[0069] Generally, the API617 standard requires a maximum isolation margin of 27%. For conservative calculation, the first threshold here is taken as 30%.

[0070] In a feasible implementation manner, the amplitude is the vibration amplitude of the rotor in the radial direction of the measuring point at the operating speed.

[0071] Among them, the amplitude can be obtained by performing unbalanced response analysis on the rotor analysis model.

[0072] In a feasible implementation manner, the second threshold is 4.0 μm.

[0073] Among them, in the calculation of conventional axial flow expanders, if the amplitude value is greater than 4.0μm, it is easy to cause unit instability. Based on actual engineering considerations, the amplitude is limited to no more than 4.0μm.

[0074] It should be noted that in this embodiment, the rotor system is analyzed by taking the intermediate support five-pad tilting pad bearing and the fulcrum offset four-pad tilting pad bearing as examples. The three-pad tilting pad bearing has a larger wrap angle and weaker swing flexibility than the four-pad bearing and the five-pad bearing, so it is not considered in the application.

[0075] Among them, the wrap angle of the tilting pad bearing with five pads in the middle support is usually 60°, and the angles on both sides of the fulcrum are 30°. If the five pads are changed to four pads, the wrap angle must be changed. For the tilting pad bearing, the part between the two pads is the oil inlet and outlet area of ​​the lubricating oil, which is generally 10° to 20°. The pad wrap angle of the five-pad bearing is generally 50° to 60°, and the pad wrap angle of the four-pad bearing is generally 70° to 80°.

[0076] In order to further understand the stiffness characteristics of the bearing under different numbers of pads, the rotor system model analysis was carried out for the four-pad tilting pad bearing (with a wrap angle of 75°) and the five-pad tilting pad bearing (with a wrap angle of 60°) with an eccentric ratio of 0.5, as shown in the following figure. Figure 2 and Figure 3 It can be seen that at the same speed, the four-pad tilting pad bearing has higher stiffness and damping, which can increase the critical speed of the rotor system.

[0077] Based on engineering experience, the greater the eccentric support ratio, the greater the critical speed of the rotor system, but it will also lead to a greater amplitude at the critical speed, which makes it more difficult to pass the critical speed during the start-up process, and the stability of the rotor will also decrease. Therefore, the eccentric support ratio of the bearing pad in this embodiment is selected within the range of 0.5 to 0.6. The eccentric support ratio refers to the ratio of the angle from the oil inlet edge to the fulcrum position to the pad wrap angle, that is, Figure 6 Medium β / α.

[0078] It can be understood that for a four-pad tilting pad bearing, if the eccentric support ratio of the pad support point is increased, the rigidity of the bearing fluid film can be increased, and the bearing capacity of the bearing can be increased. Figure 4 and Figure 5 As shown in the figure, the stiffness characteristic curve and damping characteristic curve of the four-pad radial bearing under different eccentric support ratios are shown. From these two figures, it can be seen that the larger the eccentric support ratio, the greater the stiffness and damping of the bearing. However, as the rotor speed increases, the bearing stiffness continues to increase, and the growth is relatively fast, while the bearing damping gradually decreases and tends to be stable.

[0079] Based on the above characteristics and analysis results, the eccentric support ratio of the bearing pad can be reasonably selected. For example, in this embodiment, the eccentric support ratio of the bearing pad is selected within the range of 0.5 to 0.6, so that the rotor system has better dynamic characteristics.

[0080] It should be noted that the four-pad tilting pad radial bearing of this embodiment, such as Figure 6As shown, a four-pad tilting pad bearing 100 includes a pad 110 and a fulcrum 120 arranged on the pad 110. The fulcrum 120 eccentrically supports the housing 110, and the wrap angle α is 75°. The oil inlet side angle β is 40°, then the oil inlet angle γ is 5°, the oil outlet side angle is 35°, and the oil outlet angle ε is 10°. While increasing the critical speed of the rotor system, it is ensured that the rotor system has sufficient damping characteristics. The bearing structure type with an eccentric support ratio of 0.533 (β / α=40 / 75=0.533) can not only increase the critical speed of the axial flow expander, but also reduce the amplitude of the rotor, thereby ensuring that the axial flow expander has sufficient stability.

[0081] Among them, by changing the number of tiles and the eccentric ratio, the rotor unbalance response curve of an axial flow expander is obtained as follows: Figure 7 and Figure 8 As shown, the horizontal axis represents the rotor speed, the vertical axis represents the amplitude, and the rated speed of the rotor (operating speed) is 5300r / min, as shown by the vertical line.

[0082] Among them, through Figure 7 and Figure 8 The obtained rotor critical speed and amplitude are shown in Table 1.

[0083] Table 1 Comparison of lateral vibration analysis results of different types of bearings

[0084]

[0085] It can be seen from Table 1 that after changing to a four-pad bearing, the amplitude of the rotor is significantly reduced, so a four-pad bearing is preferred. When the offset ratio of the four-pad bearing is 0.566 and 0.6, the isolation margin is 29.1% and 28.1% respectively, and the first threshold does not meet the requirement; when the offset ratio of the four-pad bearing is 0.5, its amplitude is greater than 4.0μm, and the second threshold does not meet the requirement; therefore, the four-pad bearing with an offset ratio of 0.533 is the optimal solution.

[0086] Example 2

[0087] An embodiment of the present invention provides an optimization system for an axial flow expander rotor system, which is obtained according to the optimization method for the axial flow expander rotor system of embodiment 1. The optimization system includes:

[0088] Speed ​​module, builds the rotor system model and obtains the critical speed of the rotor system;

[0089] Isolation margin module, which obtains isolation margin based on critical speed and operating speed;

[0090] Amplitude module, which obtains the amplitude of the rotor based on the running speed;

[0091] In the judgment module, if the isolation margin is not less than the first threshold and the amplitude is not greater than the second threshold, the module proceeds to the next module, otherwise the rotation speed module is acquired again;

[0092] Install the production module and install production according to the rotor system model.

[0093] Among them, the optimization system includes a speed module, which first establishes a rotor system model and obtains the critical speed of the rotor system according to the rotor system model; an isolation margin module, which obtains the isolation margin of the rotor system according to the critical speed and the operating speed; an amplitude module, which obtains the amplitude of the rotor system according to the operating speed; a judgment module, when the isolation margin is not less than a first threshold and the amplitude is not greater than a second threshold, the rotor system meets the requirements, and when the isolation margin is less than the first threshold and / or the amplitude is greater than the second threshold, it is necessary to adjust the rotor system model until the isolation margin of the rotor system model is not less than the first threshold and the amplitude of the rotor system is not greater than the second threshold, so that the rotor system can obtain a better critical speed to increase the isolation margin of the rotor system and reduce the amplitude of the rotor system. On the one hand, it can ensure the reliable and stable operation of the rotor and the stator, and on the other hand, it can also meet the high-speed and large-scale working requirements of the axial flow expander and ensure the reliability of the axial flow expander.

[0094] It should be noted that there is sufficient isolation margin between the critical speed and the operating speed, that is, the isolation margin cannot be less than the first threshold value, and at the same time, the amplitude of the rotor system is not too large at the operating speed, that is, the amplitude is not greater than the second threshold value. Under such dual conditions, collision and friction between the rotor body and the stator body can be avoided. On the one hand, the reliability of the rotor system can be guaranteed, and on the other hand, the service life of the rotor system and the maintenance cycle of the rotor system can be extended.

[0095] It can be understood that since this embodiment is obtained according to the optimization method of Example 1, the optimization system of this embodiment has all the advantages of the optimization method and will not be described in detail.

[0096] Example 3

[0097] An embodiment of the present invention provides a computer-readable storage medium on which a computer program is stored. When the computer program is executed by a processor, the steps of the optimization method of embodiment 1 are implemented.

[0098] It should be noted that, since the computer program of this embodiment can implement the steps of the optimization method of Example 1 when executed by the processor, the computer-readable storage medium has all the advantages described in Example 1 and will not be repeated here.

[0099] In the present invention, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance. The term "plurality" refers to two or more than two, unless otherwise clearly defined.

[0100] Those skilled in the art will readily appreciate other embodiments of the present invention after considering the specification and practicing the invention disclosed herein. The present invention is intended to cover any variations, uses or adaptations of the present invention that follow the general principles of the present invention and include common knowledge or customary techniques in the art that are not disclosed by the present invention. The description and examples are to be considered exemplary only.

[0101] The above are only preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present invention should be included in the protection scope of the present invention.

Claims

1. A method for optimizing an axial flow expander rotor system, characterized in that: The optimization method comprises the following steps: Establishing a rotor system model to obtain the critical speed of the rotor system; Obtaining an isolation margin based on the critical speed and the operating speed; Based on the operating speed, obtaining the amplitude of the rotor; If the isolation margin is not less than the first threshold value and the amplitude is not greater than the second threshold value, proceed to the next step, otherwise the rotor system model is re-established; Production is installed according to the rotor system model.

2. The optimization method of the axial flow expander rotor system according to claim 1, characterized in that: The establishing of the rotor system model comprises: Build models of the rotor body and bearings; By changing the parameters of the bearing, different critical speeds are obtained.

3. The optimization method of the axial flow expander rotor system according to claim 2, characterized in that: The bearing is a tilting pad bearing, and the parameters of the bearing include: bearing diameter, number of pads, pad wrap angle, deflection ratio, pad length and bearing installation clearance.

4. The optimization method of the axial flow expander rotor system according to claim 3, characterized in that: The critical speed of the rotor is adjusted by optimizing the number of bearing pads, pad wrap angle and eccentricity ratio.

5. The optimization method of the axial flow expander rotor system according to claim 1, characterized in that: The isolation margin is a ratio of a difference between the critical speed and the operating speed to the operating speed.

6. The optimization method of the axial flow expander rotor system according to claim 1, characterized in that: The amplitude is the vibration amplitude of the rotor in the radial direction of the measuring point at the operating speed.

7. The optimization method of the axial flow expander rotor system according to claim 1, characterized in that: The first threshold is 30%.

8. The method for optimizing the rotor system of an axial flow expander according to claim 1, characterized in that: The second threshold is 4.0 μm.

9. An optimization system for an axial flow expander rotor system, obtained according to the optimization method for an axial flow expander rotor system according to any one of claims 1 to 8, characterized in that: The optimization system comprises: A speed module is used to establish a rotor system model and obtain a critical speed of the rotor system; An isolation margin module, which obtains an isolation margin based on the critical speed and the operating speed; An amplitude module, which obtains the amplitude of the rotor based on the operating speed; The judgment module, if the isolation margin is not less than the first threshold value and the amplitude is not greater than the second threshold value, enters the next module, otherwise, re-acquires the speed module; Install the production module and install the production according to the rotor system model.

10. A computer-readable storage medium having a computer program stored thereon, characterized in that: When the computer program is executed by a processor, the steps of the optimization method according to claim 1 are implemented.

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