Method, device and computer readable storage medium for controlling operation of dual-rotor system

Abstract

The present application relates to the field of intermediate bearings, and in particular to a method, device, and computer-readable storage medium for controlling the operation of a dual-rotor system. The method comprises: obtaining the inner ring radius, outer ring radius, and number of rolling elements of the intermediate bearing; calculating the rotation frequency relationship between the high-pressure rotor and the low-pressure rotor when the dual-rotor system has intermittent impact vibration under the condition of local fault of the inner ring of the intermediate bearing according to the inner ring radius, outer ring radius, and number of rolling elements of the intermediate bearing; and controlling the rotation frequencies of the high-pressure rotor and the low-pressure rotor during the operation of the dual-rotor system so that they do not satisfy the rotation frequency relationship. The present invention can reduce or avoid the risk of intermittent impact vibration of the dual-rotor system under the condition of local fault of the inner ring of the intermediate bearing, and ensure the stable operation of the dual-rotor system.

Description

Technical Field

[0001] The present application generally relates to the field of intermediate bearing technology, and more particularly to a method, device and computer-readable storage medium for controlling the operation of a dual-rotor system. Background Art

[0002] The rotor is the most common structure in rotating machinery, and is often used to generate mechanical power or electricity, such as gas turbines, aircraft engines, generators, etc. Most rotors adopt a single rotor structure and are supported by bearings. The inner ring of the bearing is directly connected to the rotor journal and rotates with the rotor, while the outer ring of the bearing is fixed to the ground foundation structure and does not rotate.

[0003] In order to improve the thrust-to-weight ratio, some rotating machinery adopts a set double rotor structure, such as aircraft engines and marine gas turbines. The inner cavity of the high-pressure rotor of the aircraft engine is a hollow rotor structure, which is mounted on the outside of the low-pressure rotor. The high-pressure rotor and the low-pressure rotor are coupled through an intermediate bearing. When the double rotors are working, the inner and outer rings of the intermediate bearing will rotate due to the rotation of the high / low-pressure rotors.

[0004] During operation, the intermediate bearing has the characteristics of high speed, double speed, large dynamic load, and difficult lubrication due to the external excitation of the high / low pressure rotor and its special installation position. Therefore, the intermediate bearing is prone to local faults such as pitting, pitting, and peeling of the inner / outer raceway or rolling element.

[0005] In addition, as the core component of the high- and low-pressure rotor coupling, the intermediate bearing has the biggest feature of having two speeds of simultaneous rotation of the inner and outer rings compared to the rolling bearings in general positions. This determines that the local failure of the intermediate bearing will cause more complex dynamic behavior of the dual-rotor system. Paroxysmal impact vibration is a dynamic phenomenon unique to the intermediate bearing-dual-rotor system.

[0006] Paroxysmal impact vibration is manifested as the alternation of large-amplitude impact vibration and small-amplitude impact vibration. Its corresponding envelope spectrum contains only the bearing fault frequency and its fractional or integer multiples of the fault frequency, but no side frequencies. Paroxysmal impact vibration caused by local faults of the intermediate bearings is a potential threat to the safe operation of rotating machinery systems.

[0007] In the current existing technology, Cui Jiang established a mathematical model of the intermediate bearing in the "Study on the Dynamic Characteristics of the Dual Rotor-Rolling Bearing System", combined the nonlinear intermediate bearing model with the dual rotors, and established the nonlinear dynamic equation of the dual rotor-rolling bearing system, but did not propose a relevant model for the intermittent impact vibration phenomenon of the dual rotor system.

[0008] Therefore, there is an urgent need in the art for a method for predicting and controlling the paroxysmal impact vibration of a dual-rotor system under a local fault condition of the inner ring of the intermediate bearing. Summary of the invention

[0009] The present application provides a method, device and non-volatile computer-readable storage medium for controlling the operation of a dual-rotor system, so as to reduce or avoid the risk of paroxysmal impact vibration of the dual-rotor system when a local fault occurs in the inner ring of an intermediate bearing, thereby ensuring the stable operation of the dual-rotor system.

[0010] According to the first aspect of the present application, a method for controlling the operation of a dual-rotor system is provided, wherein the dual-rotor system comprises a high-pressure rotor, a low-pressure rotor and an intermediate bearing, wherein the intermediate bearing comprises an outer ring, a rolling element and an inner ring from the outside to the inside, wherein the high-pressure rotor is coupled to the outer ring, and wherein the low-pressure rotor is coupled to the inner ring. The method comprises: obtaining the inner ring radius, the outer ring radius and the number of rolling elements of the intermediate bearing; calculating the rotation frequency relationship between the high-pressure rotor and the low-pressure rotor when the dual-rotor system is in a state of a local fault in the inner ring of the intermediate bearing and undergoing paroxysmal impact vibration according to the inner ring radius, the outer ring radius and the number of rolling elements of the intermediate bearing, wherein the rotation frequency relationship is a relationship when the high-pressure rotor rotation frequency is equal to a fractional or integer multiple of the intermediate bearing inner ring fault frequency and the low-pressure rotor rotation frequency is equal to a fractional or integer multiple of the intermediate bearing inner ring fault frequency; and controlling the rotation frequencies of the high-pressure rotor and the low-pressure rotor during the operation of the dual-rotor system so that they do not satisfy the rotation frequency relationship.

[0011] In one embodiment, the rotation frequency relationship includes: Wherein, λ is the ratio of the rotation frequency of the high-pressure rotor to the rotation frequency of the low-pressure rotor, m l is the ratio of the rotation frequency of the low-pressure rotor to the inner ring fault frequency of the intermediate bearing, R o is the outer ring radius of the intermediate bearing, R i is the inner ring radius of the intermediate bearing, N b is the number of rolling elements of the intermediate bearing.

[0012] In one embodiment, the ratio m of the rotation frequency of the low-pressure rotor to the inner ring fault frequency of the intermediate bearing is l Determined according to the minimum multiple frequency of the inner ring fault frequency of the intermediate bearing, m l = k·m base , Among them, m base is the base of the minimum multiple frequency of the inner ring fault frequency of the intermediate bearing, and k is a positive integer.

[0013] In one embodiment, the rotation frequency relationship includes: Wherein, λ is the ratio of the rotation frequency of the high-pressure rotor to the rotation frequency of the low-pressure rotor, m his the ratio of the rotation frequency of the high-pressure rotor to the inner ring fault frequency of the intermediate bearing, R o is the outer ring radius of the intermediate bearing, R i is the inner ring radius of the intermediate bearing, N b is the number of rolling elements of the intermediate bearing.

[0014] In one embodiment, the ratio m of the rotation frequency of the high-pressure rotor to the inner ring fault frequency of the intermediate bearing is h Determined according to the minimum multiple frequency of the inner ring fault frequency of the intermediate bearing, m h =j·m base , Among them, m base is the base of the minimum multiple frequency of the inner ring fault frequency of the intermediate bearing, and j is a positive integer.

[0015] In one embodiment, controlling the rotation frequencies of the high-pressure rotor and the low-pressure rotor during the operation of the dual-rotor system so that they do not satisfy the rotation frequency relationship includes: controlling the rotation frequencies of the high-pressure rotor and the low-pressure rotor so that their ratio is greater than λ and less than or equal to the maximum rotation frequency ratio of the high-pressure rotor to the low-pressure rotor; or controlling the rotation frequencies of the high-pressure rotor and the low-pressure rotor so that their ratio is less than λ and greater than or equal to the minimum rotation frequency ratio of the high-pressure rotor to the low-pressure rotor.

[0016] In one embodiment, the maximum rotation frequency ratio of the high-pressure rotor to the low-pressure rotor is set according to the rated parameters, operating conditions and operating requirements of the dual-rotor system; or the minimum rotation frequency ratio of the high-pressure rotor to the low-pressure rotor is set according to the rated parameters, operating conditions and operating requirements of the dual-rotor system.

[0017] In one embodiment, the ratio of the rotational frequencies of the high-pressure rotor to the low-pressure rotor is the ratio of the rotational frequencies of the high-pressure rotor to the low-pressure rotor when the dual-rotor system is in a steady state of operation.

[0018] According to the second aspect of the present application, the present application provides a device for controlling the operation of a dual-rotor system, wherein the dual-rotor system includes a high-pressure rotor, a low-pressure rotor and an intermediate bearing, wherein the intermediate bearing includes an outer ring, a rolling element and an inner ring from the outside to the inside, the high-pressure rotor is coupled to the outer ring, and the low-pressure rotor is coupled to the inner ring; the device includes a processor and a memory, wherein the memory stores computer program instructions, and when the processor executes the computer program instructions, it implements the method for controlling the operation of the dual-rotor system according to any one of the first aspects of the present application.

[0019] According to a third aspect of the present application, a computer-readable storage medium is provided, on which computer program instructions are stored. When the computer program instructions are executed, the method for controlling the operation of a dual-rotor system according to any one of the first aspects of the present application is implemented.

[0020] According to the method and device for controlling the operation of the dual-rotor system of the present invention, by calculating the rotation frequency relationship between the high-pressure rotor and the low-pressure rotor when the dual-rotor system has paroxysmal impact vibration under the condition of local fault of the inner ring of the intermediate bearing, and controlling the rotation frequency ratio of the high-pressure rotor and the low-pressure rotor during the operation of the dual-rotor system so that it does not satisfy the rotation frequency relationship, the risk of paroxysmal impact vibration of the dual-rotor system under the condition of local fault of the inner ring of the intermediate bearing is reduced or avoided. That is to say, the inventor found through research that when the rotation frequency ratio of the high-pressure rotor and the low-pressure rotor satisfies a specific relationship, the dual-rotor system will have paroxysmal impact vibration. Based on this, the inventor controls the rotation frequency of the high-pressure rotor and the low-pressure rotor according to the method of the present application during the operation of the dual-rotor so that the ratio does not satisfy the specific relationship, so that the dual-rotor system is not in a specific working condition that causes paroxysmal impact vibration during steady-state operation, thereby ensuring the stable operation of the dual-rotor system. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] By reading the detailed description below with reference to the accompanying drawings, the above and other purposes, features and advantages of the exemplary embodiments of the present application will become easy to understand. In the accompanying drawings, several embodiments of the present application are shown in an exemplary and non-limiting manner, and the same or corresponding reference numerals represent the same or corresponding parts, wherein:

[0022] Figure 1 is a schematic structural diagram of an example dual-rotor system in the prior art;

[0023] Figure 2 is a flow chart of a method for controlling the operation of a dual-rotor system according to an embodiment of the present application;

[0024] Figure 3 It is the time history and envelope spectrum of the vibration acceleration signal obtained under the test condition according to the method for controlling the operation of the dual-rotor system in the embodiment of the present application;

[0025] Figure 4 It is the time history and envelope spectrum of the vibration acceleration signal obtained under the control working condition according to the method for controlling the operation of the dual-rotor system in the embodiment of the present application;

[0026] Figure 5 is a block diagram of a device for controlling the operation of a dual-rotor system according to an embodiment of the present application. DETAILED DESCRIPTION

[0027] The following will be combined with the drawings in the embodiments of the present application to clearly and completely describe the technical solutions in the embodiments of the present application. Obviously, the described embodiments are part of the embodiments of the present application, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative work are within the scope of protection of the present application.

[0028] It should be understood that when the terms "first", "second", etc. are used in the claims, specification and drawings of the present application, they are only used to distinguish different objects, rather than to describe a specific order. The terms "include" and "comprise" used in the specification and claims of the present application indicate the presence of the described features, wholes, steps, operations, elements and / or components, but do not exclude the presence or addition of one or more other features, wholes, steps, operations, elements, components and / or their collections.

[0029] According to a first aspect of the present application, the present application provides a method for controlling the operation of a dual-rotor system. The dual-rotor system may be a dual-rotor system used in an aircraft engine, or may be a dual-rotor system in other equipment such as a marine gas turbine, and the present application does not impose any particular limitation on this.

[0030] Figure 1 FIG. 2 shows a schematic diagram of the structure of an example dual-rotor system in the prior art. Figure 1 As shown, the dual rotor system includes a high-pressure rotor and a low-pressure rotor and an intermediate bearing 10. The high-pressure rotor includes a high-pressure rotor support 7, a high-pressure rotor disk 8 and a high-pressure rotor hollow shaft 9. The low-pressure rotor includes low-pressure rotor supports 1, 3, 5; low-pressure rotor disks 2, 4; and a low-pressure rotor solid shaft 6. The intermediate bearing 10 includes an outer ring, a rolling element and an inner ring from the outside to the inside. The outer ring of the intermediate bearing 10 is coupled to the high-pressure rotor hollow shaft 9, and the inner ring of the intermediate support 10 is coupled to the low-pressure rotor solid shaft 6, that is, the high-pressure rotor and the low-pressure rotor are coupled through the intermediate bearing 10. When the high-pressure rotor and the low-pressure rotor rotate, the inner ring and the outer ring of the intermediate bearing 10 will rotate. The coupling can adopt the connection methods commonly used in the art, including welding, meshing, etc., and the present application does not impose any special restrictions on this.

[0031] Figure 2 A flow chart of a method for controlling the operation of a dual-rotor system according to an embodiment of the present invention is shown. The method for controlling the operation of a dual-rotor system includes steps S201 to S203. The following is a detailed description.

[0032] S201, obtaining the inner ring radius, outer ring radius and number of rolling elements of the intermediate bearing.

[0033] Specifically, the inner ring radius, outer ring radius and number of rolling elements of the intermediate bearing can be queried from an established bearing specification database, or determined by looking up a bearing manual, or by direct measurement or manual input. This application does not impose any particular restrictions on the method of obtaining these parameters.

[0034] S202, based on the inner ring radius, outer ring radius and number of rolling elements of the intermediate bearing, calculate the rotation frequency relationship between the high-pressure rotor and the low-pressure rotor when the dual-rotor system undergoes intermittent impact vibration due to a local fault in the inner ring of the intermediate bearing, wherein the rotation frequency relationship is a relationship when the high-pressure rotor rotation frequency is equal to a fractional or integer multiple of the intermediate bearing inner ring fault frequency, and the low-pressure rotor rotation frequency is equal to a fractional or integer multiple of the intermediate bearing inner ring fault frequency.

[0035] In this application, the terms "frequency" and "rotation speed" are used interchangeably, and "frequency ratio" and "rotation speed ratio" are used interchangeably.

[0036] The inventor has found through research that the conditions for the occurrence of paroxysmal impact vibration in the state of local fault of the inner ring of the intermediate bearing are: ① the rotation frequency of the high-pressure rotor is equal to a fractional or integer multiple of the fault frequency of the inner ring of the intermediate bearing; ② the rotation frequency of the low-pressure rotor is equal to a fractional or integer multiple of the fault frequency of the inner ring of the intermediate bearing. When the dual-rotor system has paroxysmal impact vibration, both conditions ① and ② will be met at the same time.

[0037] The failure frequency of the inner ring of the intermediate bearing is a known formula, which can be directly obtained

[0038]

[0039] Where f l and f h are the low-pressure rotor rotation frequency and the high-pressure rotor rotation frequency, respectively, N b is the number of rolling elements, R i and R o are the inner and outer ring radii of the intermediate bearing respectively.

[0040] According to condition ①, the prediction formula of paroxysmal impact vibration can be derived as follows:

[0041] f h =m h f bpi (2)

[0042] Substituting formula (1) into formula (2), we can get the prediction formula A for paroxysmal impact vibration:

[0043]

[0044] Where λ = f h / f lis the ratio of the high-pressure rotor speed to the low-pressure rotor speed, m h It is a multiple of the intermediate bearing inner ring failure frequency.

[0045] According to condition ②, the prediction formula of paroxysmal impact vibration can be derived as follows:

[0046] f l =m l f bpi (4)

[0047] Substituting formula (1) into formula (4), we can get the prediction formula B for paroxysmal impact vibration:

[0048]

[0049] Where m l It is a multiple of the intermediate bearing inner ring failure frequency.

[0050] If ① and ② are satisfied at the same time, the minimum multiple frequency of the fault frequency is the difference between the high-pressure rotor rotation frequency and the low-pressure rotor rotation frequency. The minimum multiple frequency of the fault frequency of the inner ring of the intermediate bearing is defined as m. base f bpi , we can get

[0051] m base f bpi =f h -f l (6)

[0052] Substituting formula (1) into formula (6), we can get the prediction formula C for paroxysmal impact vibration:

[0053]

[0054] Where m l and m h Both are m base An integer multiple of .

[0055] Formulas (3), (5) and (7) form a complete set of paroxysmal impact vibration prediction formulas. Two of the three formulas are independent. Formulas (3) and (7) can be used to predict the working conditions of paroxysmal impact vibration phenomena, and formulas (5) and (7) can also be used to predict the working conditions of paroxysmal impact vibration phenomena.

[0056] According to the above principle, the rotation frequency relationship between the high-pressure rotor and the low-pressure rotor can be determined when the dual-rotor system has intermittent impact vibrations in the state of a local fault in the inner ring of the intermediate bearing.

[0057] That is, in one embodiment, the rotation frequency relationship includes:

[0058] Wherein, λ is the ratio of the rotation frequency of the high-pressure rotor to the rotation frequency of the low-pressure rotor, m l is the ratio of the rotation frequency of the low-pressure rotor to the inner ring fault frequency of the intermediate bearing, R o is the outer ring radius of the intermediate bearing, R i is the inner ring radius of the intermediate bearing, N b is the number of rolling elements of the intermediate bearing. The ratio of the rotation frequency of the low-pressure rotor to the inner ring fault frequency of the intermediate bearing is m l Determined according to the minimum multiple frequency of the inner ring fault frequency of the intermediate bearing, m l = k·m base , Among them, m base is the base of the minimum multiple frequency of the inner ring fault frequency of the intermediate bearing, and k is a positive integer.

[0059] Alternatively, in another embodiment, the rotation frequency relationship includes:

[0060] Wherein, λ is the ratio of the rotation frequency of the high-pressure rotor to the rotation frequency of the low-pressure rotor, m h is the ratio of the rotation frequency of the high-pressure rotor to the inner ring fault frequency of the intermediate bearing, R o is the outer ring radius of the intermediate bearing, R i is the inner ring radius of the intermediate bearing, N b is the number of rolling elements of the intermediate bearing. The ratio of the rotation frequency of the high-pressure rotor to the inner ring fault frequency of the intermediate bearing is m h Determined according to the minimum multiple frequency of the inner ring fault frequency of the intermediate bearing, m h =j·m base , Among them, m base is the base of the minimum multiple frequency of the inner ring fault frequency of the intermediate bearing, and j is a positive integer.

[0061] S203, controlling the rotation frequencies of the high-pressure rotor and the low-pressure rotor during the operation of the dual-rotor system so that they do not satisfy the rotation frequency relationship.

[0062] Specifically, controlling the rotational frequencies of the high-pressure rotor and the low-pressure rotor during the operation of the dual-rotor system can be achieved in different ways. As an example, the rotational frequency of the low-pressure rotor can be fixed and the rotational frequency of the high-pressure rotor can be adjusted, or the rotational frequency of the high-pressure rotor can be fixed and the rotational frequency of the low-pressure rotor can be adjusted, or the rotational frequency of the low-pressure rotor and the rotational frequency of the high-pressure rotor can be adjusted at the same time, as long as the rotational frequencies of the high-pressure rotor and the low-pressure rotor after adjustment do not satisfy the rotational frequency relationship calculated in the above step S202, and this application does not impose any special restrictions on this.

[0063] As an example, in one embodiment, the rotation frequencies of the high-pressure rotor and the low-pressure rotor can be adjusted so that their ratio is greater than the λ. In addition, other parameters can be considered in the adjustment process. For example, a threshold value, i.e., a maximum rotation frequency ratio, can be set, which is used to characterize the upper limit of the rotation frequency ratio of the high-pressure rotor and the low-pressure rotor in the dual-rotor system. Therefore, when controlling the rotation frequencies of the high-pressure rotor and the low-pressure rotor during the operation of the dual-rotor system, the rotation frequencies of the high-pressure rotor and the low-pressure rotor can be controlled so that their ratio is greater than the λ and less than or equal to the maximum rotation frequency ratio of the high-pressure rotor and the low-pressure rotor.

[0064] In another embodiment, the rotation frequencies of the high-pressure rotor and the low-pressure rotor can be adjusted so that their ratio is less than the λ. In addition, other parameters can be considered in the adjustment process. For example, a threshold value, i.e., a minimum rotation frequency ratio, can be set, which is used to characterize the lower limit of the rotation frequency ratio of the high-pressure rotor and the low-pressure rotor in the dual-rotor system. Therefore, when controlling the rotation frequencies of the high-pressure rotor and the low-pressure rotor during the operation of the dual-rotor system, the rotation frequencies of the high-pressure rotor and the low-pressure rotor can be controlled so that their ratio is less than the λ and greater than or equal to the minimum rotation frequency ratio of the high-pressure rotor and the low-pressure rotor.

[0065] Specifically, the maximum rotation frequency ratio and the minimum rotation frequency ratio of the high-pressure rotor to the low-pressure rotor can be set according to the rated parameters, operating conditions, and operating requirements of the dual-rotor system, and can also be appropriately set according to other conditions to ensure the long-term stable operation of the dual-rotor system.

[0066] In addition, since the intermittent impact vibration phenomenon usually only occurs when the high-pressure rotor and the low-pressure rotor are in steady-state operation under the condition of local fault of the inner ring of the intermediate bearing, instantaneous satisfaction of the rotation frequency relationship during the process of adjusting the rotation frequency ratio will not cause intermittent impact vibration and thus affect the stable operation of the dual-rotor system.

[0067] According to the method for controlling the operation of a dual-rotor system of the present application, by calculating the rotational frequency relationship between the high-pressure rotor and the low-pressure rotor when the dual-rotor system undergoes intermittent impact vibration due to a local fault in the inner ring of the intermediate bearing, and controlling the rotational frequency ratio of the high-pressure rotor to the low-pressure rotor during the operation of the dual-rotor system so that it does not satisfy the rotational frequency relationship, the risk of intermittent impact vibration in the dual-rotor system due to a local fault in the inner ring of the intermediate bearing is reduced or avoided, thereby ensuring the stable operation of the dual-rotor system.

[0068] In order to make it easier to understand the technical solution of the present application, the specific process of the method for controlling the operation of the dual-rotor system of the present application is described in detail below through an example.

[0069] The method example is implemented on an intermediate bearing-dual rotor test bench. The structure of the intermediate bearing-dual rotor test bench can be adopted Figure 1 The structure shown in the figure, in which the high-pressure rotor and the low-pressure rotor are driven by two independent motors, each with a maximum speed of 7,500 rpm. In the experiment, a tachometer is used to measure the rotation frequency of the high- and low-pressure rotor system under steady-state rotation, and two acceleration sensors are used to detect the vibration of the high-pressure rotor bearing seat in the horizontal and vertical directions. The sampling frequency of the acceleration sensor is set to 50,000 Hz.

[0070] Regarding the detection of paroxysmal impact vibration, since the acceleration signal of paroxysmal impact vibration is manifested as alternating large-amplitude impact vibration and small-amplitude impact vibration, and the corresponding envelope spectrum only contains the bearing fault frequency and its fractional or integer multiples of the fault frequency, and no sideband, the presence or absence of paroxysmal impact vibration can be determined by detecting the acceleration signal and the envelope spectrum.

[0071] This example uses the above formulas A and C in the method according to the first aspect of the present application as an example to illustrate the process of the method for controlling the operation of the dual-rotor system, as follows:

[0072] (a) Measure and input the inner ring radius R of the intermediate bearing used in the experiment i =13mm, outer circle radius R o =23mm, number of rolling elements N b =11.

[0073] (b) The inner ring radius R of the intermediate bearing i , outer radius R o , number of rolling elements N b Substituting into formula C, we can find the minimum multiple frequency base of the fault frequency that satisfies 1 / m base =7.028.

[0074] (c) Take k = 2 and 3 respectively to verify the working conditions.h =2m base or m h =3m base and the inner ring radius R of the intermediate bearing i =13mm, outer circle radius R o =23mm, number of rolling elements N b Substituting 11 into formula (3), we can obtain the rotational speed ratios of the two groups that experience paroxysmal impact vibrations, λ=2.00 and λ=1.50.

[0075] (d) Arbitrarily select the high-pressure rotor rotation frequency f h =82.83Hz, according to the speed ratio of the high-pressure rotor and the low-pressure rotor, the low-pressure rotor rotation frequency can be further obtained. Due to certain operating errors in the experiment, the two groups of paroxysmal impact vibration experimental conditions finally adopted are: If h =82.83Hz, f l =41.82Hz,λ=1.98;II.f h =82.83Hz, f l =55.31Hz, λ=1.50. The time history and envelope spectrum of the vibration acceleration signal of the rotor test bench under the two test conditions are shown as follows: Figure 3 (a) and 3(b) and Figure 3 (c) and 3(d).

[0076] (e) Adjust the speed ratio of the high-pressure rotor and the low-pressure rotor so that the dual-rotor system is in an experimental condition different from that in step (d). Specifically, make λ slightly higher and lower than the two sets of λ in step (d), select three sets of general speed ratios λ = 1.30, λ = 1.70 and λ = 2.20, and the corresponding three sets of experimental conditions are: III.f h =82.83Hz, f l =63.71Hz,λ=1.30;IV.f h =82.83Hz, f l =48.72Hz,λ=1.70;Vf h =82.83Hz, f l =37.65Hz, λ=2.20. The time history and envelope spectrum of the vibration acceleration signal of the rotor test bench under the three control working conditions are as follows: Figure 4 (e) and 4(f), Figure 4 (g) and 4(h) and Figure 4 (i) and 4(j).

[0077] according to Figure 3 and Figure 4It can be seen from the measured results that, under the state of local fault of the inner ring of the intermediate bearing, when the experimental working conditions meet the conditions for the occurrence of paroxysmal impact vibration, that is, when in working conditions I and II, the vibration acceleration signal of the dual-rotor test bench shows the phenomenon of alternating large-amplitude impact vibration and small-amplitude impact vibration, that is, the phenomenon of paroxysmal impact vibration, and the corresponding envelope spectrum only contains the bearing fault frequency and its multiple fault frequencies, without side frequencies; after adjusting the speed ratio, when the experimental working conditions do not meet the conditions for the occurrence of paroxysmal impact vibration, that is, when in working conditions III, IV and V, the vibration acceleration signal of the dual-rotor test bench will not show the phenomenon of alternating large-amplitude impact vibration and small-amplitude impact vibration, but will show continuous large-amplitude impact vibration. The envelope spectrum corresponding to the impact vibration response contains the bearing fault frequency, the rotation frequency of the high / low pressure rotor, and the side frequencies around the fault frequency, thereby verifying the effectiveness of the method of the present application in suppressing paroxysmal impact vibration.

[0078] A second aspect of the present application provides a device for controlling the operation of a dual-rotor system. Figure 5 4 is a block diagram of a device 50 for controlling the operation of a dual-rotor system according to an embodiment of the present application.

[0079] The dual-rotor system includes a high-pressure rotor, a low-pressure rotor and an intermediate bearing, wherein the intermediate bearing includes an outer ring, a rolling element and an inner ring from the outside to the inside, the high-pressure rotor is coupled to the outer ring, and the low-pressure rotor is coupled to the inner ring. The device includes a processor and a memory, wherein the memory stores computer program instructions, and when the processor executes the computer program instructions, the method for controlling the operation of the dual-rotor system according to the first aspect of the present application is implemented.

[0080] The principle of the device 50 for controlling the operation of the dual-rotor system of the present application is the same as the method for controlling the operation of the dual-rotor system in the first aspect. The corresponding technical details are not repeated here, and reference is made to the description of the corresponding parts in the first aspect.

[0081] The device may be implemented in the form of software, or in the form of hardware, or in the form of a combination of software and hardware, and this application does not impose any particular limitation on this.

[0082] The third aspect of the present application provides a computer-readable storage medium having computer program instructions stored thereon, characterized in that when the computer program instructions are executed, the method for controlling the operation of a dual-rotor system according to the first aspect of the present application is implemented.

[0083] In the present application, the aforementioned readable storage medium may be any tangible medium containing or storing a program, which may be used by or in combination with an instruction execution system, apparatus or device. For example, a computer-readable storage medium may be any suitable magnetic storage medium or magneto-optical storage medium, such as a resistive random access memory RRAM (Resistive Random Access Memory), a dynamic random access memory DRAM (Dynamic Random Access Memory), a static random access memory SRAM (Static Random-Access Memory), an enhanced dynamic random access memory EDRAM (Enhanced Dynamic Random Access Memory), a high-bandwidth memory HBM (High-Bandwidth Memory), a hybrid memory cube HMC (Hybrid Memory Cube), etc., or any other medium that can be used to store the required information and can be accessed by an application, a module, or both. Any such computer storage medium may be part of a device or accessible or connectable to a device. Any application or module described in this application may be implemented using computer-readable / executable instructions that may be stored or otherwise maintained by such a computer-readable medium.

[0084] According to the above description of this specification, those skilled in the art may also understand that the terms used below, such as "upper", "lower" and other terms indicating orientation or positional relationship, are based on the orientation or positional relationship shown in the drawings of this specification, and are only for the purpose of facilitating the explanation of the scheme of the present application and simplifying the description, rather than explicitly or implicitly indicating that the device or element involved must have the specific orientation, be constructed and operated in a specific orientation. Therefore, the above-mentioned orientation or positional relationship terms cannot be understood or interpreted as limitations on the scheme of the present application.

[0085] The technical features of the above-described embodiments may be arbitrarily combined. To make the description concise, not all possible combinations of the technical features in the above-described embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0086] The above-described embodiments only express several implementation methods of the present application, and the descriptions thereof are relatively specific and detailed, but they cannot be construed as limiting the scope of the patent application. It should be pointed out that, for a person of ordinary skill in the art, several variations and improvements can be made without departing from the concept of the present application, and these all belong to the protection scope of the present application. Therefore, the protection scope of the patent application shall be subject to the attached claims.

Claims

1. A method for controlling the operation of a dual-rotor system, wherein the dual-rotor system comprises a high-pressure rotor, a low-pressure rotor and an intermediate bearing, wherein the intermediate bearing comprises an outer ring, a rolling element and an inner ring in sequence from the outside to the inside, wherein the high-pressure rotor is coupled to the outer ring, and the low-pressure rotor is coupled to the inner ring, wherein: The method comprises: Obtaining the inner ring radius, outer ring radius and number of rolling elements of the intermediate bearing; According to the inner ring radius, outer ring radius and number of rolling elements of the intermediate bearing, calculate the rotation frequency relationship between the high-pressure rotor and the low-pressure rotor when the dual-rotor system has intermittent impact vibration under the condition of local fault of the inner ring of the intermediate bearing, wherein the rotation frequency relationship is the relationship when the rotation frequency of the high-pressure rotor is equal to a fractional or integer multiple of the fault frequency of the inner ring of the intermediate bearing, and the rotation frequency of the low-pressure rotor is equal to a fractional or integer multiple of the fault frequency of the inner ring of the intermediate bearing. Controlling the rotational frequencies of the high-pressure rotor and the low-pressure rotor during the operation of the dual-rotor system so that they do not satisfy the rotational frequency relationship; Wherein, the rotation frequency relationship includes: ; is the ratio of the rotation frequency of the high-pressure rotor to the low-pressure rotor, is the ratio of the rotation frequency of the low-pressure rotor to the inner ring fault frequency of the intermediate bearing, is the outer ring radius of the intermediate bearing, is the inner ring radius of the intermediate bearing, is the number of rolling elements of the intermediate bearing; the ratio of the rotation frequency of the low-pressure rotor to the inner ring fault frequency of the intermediate bearing Determined according to the minimum multiple frequency of the inner ring fault frequency of the intermediate bearing, , , is the base number of the minimum multiple frequency of the inner ring fault frequency of the intermediate bearing, k is a positive integer; Alternatively, the rotation frequency relationship includes: ; is the ratio of the rotation frequency of the high-pressure rotor to the low-pressure rotor, is the ratio of the rotation frequency of the high-pressure rotor to the inner ring fault frequency of the intermediate bearing, is the outer ring radius of the intermediate bearing, is the inner ring radius of the intermediate bearing, is the number of rolling elements of the intermediate bearing; the ratio of the rotation frequency of the high-pressure rotor to the inner ring fault frequency of the intermediate bearing Determined according to the minimum multiple frequency of the inner ring fault frequency of the intermediate bearing, , , is the base number of the minimum multiple frequency of the inner ring fault frequency of the intermediate bearing, j Is a positive integer.

2. The method for controlling the operation of a dual-rotor system according to claim 1, characterized in that: The controlling the rotational frequencies of the high-pressure rotor and the low-pressure rotor during the operation of the dual-rotor system so that they do not satisfy the rotational frequency relationship comprises: Control the rotation frequency of the high-pressure rotor and the low-pressure rotor so that the ratio is greater than the and is less than or equal to the maximum rotation frequency ratio of the high-pressure rotor to the low-pressure rotor; or Control the rotation frequency of the high-pressure rotor and the low-pressure rotor so that the ratio is smaller than the And is greater than or equal to the minimum rotation frequency ratio of the high-pressure rotor to the low-pressure rotor.

3. The method for controlling the operation of a dual-rotor system according to claim 2, characterized in that The maximum rotation frequency ratio of the high-pressure rotor to the low-pressure rotor is set according to the rated parameters, operating conditions and operating requirements of the dual-rotor system; or The minimum rotation frequency ratio of the high-pressure rotor to the low-pressure rotor is set according to the rated parameters, operating conditions and operating requirements of the dual-rotor system.

4. The method for controlling the operation of a dual-rotor system according to claim 1, characterized in that: The ratio of the rotation frequency of the high-pressure rotor to the low-pressure rotor is the ratio of the rotation frequency of the high-pressure rotor to the low-pressure rotor when the dual-rotor system is in a steady state of operation.

5. A device for controlling the operation of a dual-rotor system, the dual-rotor system comprising a high-pressure rotor, a low-pressure rotor and an intermediate bearing, the intermediate bearing comprising an outer ring, a rolling element and an inner ring from the outside to the inside, the high-pressure rotor coupled to the outer ring, and the low-pressure rotor coupled to the inner ring; the device comprises a processor and a memory, characterized in that: The memory stores computer program instructions, which implement the method according to any one of claims 1 to 4 when executed by the processor.

6. A computer-readable storage medium having computer program instructions stored thereon, characterized in that: The computer program instructions implement the method according to any one of claims 1 to 4 when executed.

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