阅读说明：本技术 一种叶盘减振的阵列式调谐质量阻尼器 (Array type tuned mass damper for vibration reduction of blade disc ) 是由 王帅 杨庚 纪犁 毕传兴 郑昌军 于 2021-09-28 设计创作，主要内容包括：本发明公开了一种叶盘减振的阵列式调谐质量阻尼器,叶盘是在轮盘的周边设置叶片；阵列式调谐质量阻尼器是在轮盘的内表面呈环状布置调谐质量阻尼器,形成环状调谐质量阻尼器阵列；环状调谐质量阻尼器阵列是在环状支撑结构中沿圆周方向布置各调谐质量阻尼器振子；针对叶盘运行过程中振动幅值超限的被控频率范围,通过模态测试或模态分析获得与被控频率范围相应的叶盘固有频率；调谐质量阻尼器振子具有与叶盘固有频率相接近的振子固有频率；在被控频率范围中,利用调谐质量阻尼器振子吸收叶盘部分振动能量,实现叶盘减振,降低叶盘结构振动幅值,实现减振。(The invention discloses an array type tuned mass damper for vibration reduction of a blade disc, wherein the blade disc is provided with blades at the periphery of a wheel disc; the array tuned mass damper is characterized in that tuned mass dampers are annularly arranged on the inner surface of the wheel disc to form an annular tuned mass damper array; the annular tuned mass damper array is formed by arranging tuned mass damper vibrators in an annular supporting structure along the circumferential direction; aiming at a controlled frequency range with the vibration amplitude exceeding the limit in the operation process of the blade disc, obtaining the inherent frequency of the blade disc corresponding to the controlled frequency range through modal testing or modal analysis; the tuned mass damper oscillator has an oscillator natural frequency close to the leaf disc natural frequency; in the controlled frequency range, the tuning mass damper vibrator is utilized to absorb partial vibration energy of the blade disc, so that vibration reduction of the blade disc is realized, the vibration amplitude of the blade disc structure is reduced, and vibration reduction is realized.)

1. An array type tuned mass damper for vibration reduction of a blade disc, wherein blades (1a) are arranged on the periphery of a wheel disc (1b) of the blade disc (1); the method is characterized in that:

the array tuned mass damper is characterized in that tuned mass dampers are annularly arranged on the inner surface of the wheel disc (1b) to form an annular tuned mass damper array (2); the annular tuned mass damper array (2) is formed by arranging tuned mass damper vibrators (2b) in an annular supporting structure (2a) along the circumferential direction;

aiming at a controlled frequency range with an out-of-limit vibration amplitude in the operation process of the blade disc (1), obtaining the blade disc natural frequency corresponding to the controlled frequency range through modal testing or modal analysis; the tuned mass damper oscillator (2b) has an oscillator natural frequency close to the leaf disc natural frequency; and in the controlled frequency range, the tuning mass damper vibrator (2b) is utilized to absorb partial vibration energy of the blade disc (1) so as to realize vibration reduction of the blade disc.

2. The array tuned mass damper for blisk damping according to claim 1, wherein: the supporting structure (2a) is an annular frame structure, a plurality of circumferentially distributed cavities are formed by an inner ring frame, an outer ring frame and partition plates, and the tuned mass damper vibrators (2b) are arranged in the cavities; the tuned mass damper vibrator (2b) is composed of an elastic beam and a mass block, one end of the elastic beam is fixedly connected to an outer ring frame of the supporting structure, the other end of the elastic beam stretches towards the center of the ring in a hanging mode, and the mass block is fixedly arranged at the end of the stretched beam to form a vibration system; the elastic beam is a beam with equal section or a beam with non-equal section; the equal-section beam is a rectangular equal-section beam.

3. The array tuned mass damper for blisk damping according to claim 1, wherein: recording the number of tuned mass damper vibrators (2b) in the annular tuned mass damper array (2) as A; if the number of blades (1a) in the blade disc (1) is B, the following are provided: 2< A < 3B.

4. The array tuned mass damper for blisk damping according to claim 3, wherein: setting the value of A as: 0.5B < a < 1.5B.

5. The array tuned mass damper for blisk damping according to claim 1, wherein: the relative error between the natural frequency of the vibrator and the natural frequency of the blade disc is not more than 5%.

6. The array tuned mass damper for blisk damping according to claim 1, wherein: the relative error between the natural frequency of the vibrator and the natural frequency of the blade disc is not more than 2%.

7. The array tuned mass damper for blisk damping according to claim 1, wherein: the total mass of all tuned mass damper vibrators (2b) in the annular tuned mass damper array (2) is 1% -12% of the total mass of the bladed disc (1).

8. The array tuned mass damper for blisk damping according to claim 1, wherein: the mode damping of the tuned mass damper vibrator (2b) at the natural frequency of the vibrator is not less than 0.05%.

9. The array tuned mass damper for blisk damping according to claim 1, wherein: the annular tuned mass damper array (2) is arranged on the inner surface of the wheel disc (1b) in an interference fit mode, and the annular tuned mass damper array (2) is attached to the wheel disc (1b) in the operation of the blade disc (1).

Technical Field

The invention relates to the field of structural vibration control, in particular to an array type tuned mass damper for vibration reduction of a blade disc.

Background

The blade disc is a key part of large-scale rotating machinery such as an aircraft engine, a large-scale compressor, a steam turbine and the like, and has the advantages of compact structure, light weight, high thrust-weight ratio and the like. With the improvement of the technology and the improvement of the performance, the blade and the wheel disc are designed into an integrated structure, a tenon, a mortise and a locking device in connection are omitted, the structural weight and the number of parts are reduced, the air flow loss between the tenon and the mortise is eliminated, the fretting wear between the tenon and the mortise is avoided, and the reliability and the durability of the engine are improved. However, due to the lack of a reliable damping source, the blade disc structure often has a low damping characteristic, and can only depend on the weak material damping to dissipate energy, so that the amplitude of the blade disc structure is too large when the blade disc structure passes through a resonance region; in addition, the structure of the blisk is lighter and thinner due to advanced pneumatic design, and the vibration problem of the blisk is easily caused by the fact that the working condition of the aircraft engine is changed, the vibration form is complex, and the excitation frequency band is wide. Meanwhile, random detuning phenomenon can be caused by manufacturing errors of the blade disc and uneven wear in the service process, and the detuning can cause localization of vibration energy and induce high-cycle fatigue damage. With the continuous improvement of the requirements on the performance of the bladed disk, the vibration problem of the bladed disk is increasingly prominent, which becomes a bottleneck problem restricting the further development of the related rotating machinery, the bladed disk structure often works under extreme severe working conditions such as high temperature, high pressure and high rotating speed, the vibration damping device needs to work in a severe environment reliably for a long time, and the bladed disk vibration damping device in the severe working environment is urgently needed in the prior art.

Disclosure of Invention

The invention provides an array type tuned mass damper for vibration reduction of a blade disc, aiming at avoiding the defects in the prior art.

The invention adopts the following technical scheme for solving the technical problems:

the invention relates to an array type tuned mass damper for vibration reduction of a blade disc, wherein blades are arranged on the periphery of a wheel disc;

the invention discloses an array type tuned mass damper for damping vibration of a blade disc, which is characterized in that:

the array tuned mass damper is formed by annularly arranging tuned mass dampers on the inner surface of the wheel disc to form an annular tuned mass damper array; the annular tuned mass damper array is formed by arranging tuned mass damper vibrators in an annular supporting structure along the circumferential direction;

aiming at a controlled frequency range with an out-of-limit vibration amplitude in the operation process of a blade disc, obtaining the inherent frequency of the blade disc corresponding to the controlled frequency range through modal testing or modal analysis; the tuned mass damper oscillator has an oscillator natural frequency close to the leaf disc natural frequency; and in the controlled frequency range, the vibration energy of the blade disc part is absorbed by using the tuned mass damper vibrator to realize the vibration reduction of the blade disc.

The invention also discloses a blade disc vibration reduction array type tuned mass damper, which is characterized in that: the support structure is an annular frame structure and is formed by an inner annular frame, an outer annular frame and partition plates to form a plurality of circumferentially distributed cavities, and the tuned mass damper vibrators are arranged in the cavities; the tuned mass damper oscillator is composed of an elastic beam and a mass block, one end of the elastic beam is fixedly connected to an outer ring frame of the supporting structure, the other end of the elastic beam stretches towards the center of the ring in a hanging mode, and the mass block is fixedly arranged at the end of the stretched beam to form a vibration system; the elastic beam is a beam with equal section or a beam with non-equal section; the equal-section beam is a rectangular equal-section beam.

The invention also discloses a blade disc vibration reduction array type tuned mass damper, which is characterized in that: recording the number of tuned mass damper vibrators in the annular tuned mass damper array as A; if the number of blades in the blade disc is marked as B, the following steps are performed: 2< A < 3B.

The invention also discloses a blade disc vibration reduction array type tuned mass damper, which is characterized in that: setting the value of A as: 0.5B < a < 1.5B.

The invention also discloses a blade disc vibration reduction array type tuned mass damper, which is characterized in that: the relative error between the natural frequency of the vibrator and the natural frequency of the blade disc is not more than 5 percent;

the invention also discloses a blade disc vibration reduction array type tuned mass damper, which is characterized in that: the relative error between the natural frequency of the vibrator and the natural frequency of the blade disc is not more than 2%;

the invention also discloses a blade disc vibration reduction array type tuned mass damper, which is characterized in that: the total mass of all tuned mass damper vibrators in the annular tuned mass damper array is 1% -12% of the total mass of the leaf disc.

The invention also discloses a blade disc vibration reduction array type tuned mass damper, which is characterized in that: the mode damping of the tuning mass damper oscillator at the natural frequency of the oscillator is not less than 0.05%.

The invention also discloses a blade disc vibration reduction array type tuned mass damper, which is characterized in that: the annular tuned mass damper array is arranged on the inner surface of the wheel disc in an interference fit mode, and the annular tuned mass damper array is attached to the wheel disc in the operation of the blade disc.

Compared with the prior art, the invention has the beneficial effects that:

1. the invention adopts the tuned mass damper to form an array structure, has good vibration reduction effect, and basically does not influence the design and manufacture of the blade disc when being arranged on the inner side of the wheel disc;

2. the damper vibrator is fixedly arranged by the high-strength supporting structure, and can reliably operate for a long time in a severe environment.

3. The invention has simple structure and low cost, and is beneficial to practical application.

Drawings

FIG. 1 is a schematic view of a blisk structure with an array of tuned mass dampers according to the present invention;

FIG. 2 is a tuned mass damper array configuration of the present invention;

FIG. 3 is a graph of response amplitude of a blisk as a function of excitation frequency.

Reference numbers in the figures: the vibration damper comprises a blade disc 1, a blade 1a, a wheel disc 1b, an annular tuned mass damper array 2, an annular supporting structure 2a and a tuned mass damper vibrator 2 b.

Detailed Description

Referring to fig. 1 and 2, the vane wheel 1 of the present embodiment is integrally provided with vanes 1a on the periphery of a wheel disc 1 b; the array tuned mass damper is characterized in that tuned mass dampers are annularly arranged on the inner surface of the wheel disc 1b to form an annular tuned mass damper array 2; the annular tuned mass damper array 2 is formed by arranging tuned mass damper vibrators 2b in an annular supporting structure 2a along the circumferential direction, and welding the annular supporting structure 2a and the tuned mass damper vibrators 2b or integrally forming the annular tuned mass damper array by 3D printing; the tuned mass damper array 2 is arranged on the inner circumferential surface of the wheel disc of the blade disc, the pneumatic performance of the blade disc is not affected, the mounting mode is simple, and the implementation is convenient.

The method comprises the steps that a leaf disc is installed on an experiment table to be tested, or a finite element method is used for analysis, a controlled frequency range with an out-of-limit vibration amplitude in the operation process of the leaf disc 1 is determined, and the natural frequency of the leaf disc corresponding to the controlled frequency range is obtained through modal testing or modal analysis aiming at the controlled frequency range with the out-of-limit vibration amplitude in the operation process of the leaf disc 1; the tuned mass damper oscillator 2b has oscillator natural frequency close to the natural frequency of the blade disc, the closer the oscillator natural frequency and the closer the oscillation damping effect, the dynamic vibration absorber matched with the blade disc is formed by the tuned mass damper array, and when the blade disc structure passes through the frequency range of the order natural frequency during operation, the vibration amplitude of the tuned mass damper oscillator 2b is obviously increased, so that partial vibration energy of the blade disc is absorbed, the vibration energy on the blade disc structure is effectively reduced, and further the vibration amplitude is reduced; therefore, in the controlled frequency range, the vibration energy of the blade disc 1 is partially absorbed by the tuned mass damper vibrator 2b, and the blade disc is damped.

In specific implementation, the corresponding technical measures also include:

the supporting structure 2a is an annular frame structure and is a plurality of circumferentially distributed containing cavities formed by an inner annular frame, an outer annular frame and partition plates, and the tuned mass damper vibrators 2b are arranged in the containing cavities; the tuned mass damper oscillator 2b is composed of an elastic beam and a mass block, one end of the elastic beam is fixedly connected to an outer ring frame of the supporting structure, the other end of the elastic beam is suspended towards the center of the ring, the mass block is fixedly arranged at the end of the suspended beam to form a vibration system, and the cantilever beam has high strength and can reliably work for a long time under severe operating environments such as high temperature, high pressure and high rotating speed; in implementation, for the tuned mass damper oscillator, only the natural frequency of the tuned mass damper oscillator needs to be close to the natural frequency to be damped of the blade disc, the shape of the elastic beam is not limited, and the elastic beam can be a beam with a uniform section or a beam with a non-uniform section; for convenience of design and manufacture, the elastic beam with the uniform cross section is preferred, and the beam with the rectangular uniform cross section is a better choice.

The number of tuned mass damper oscillators in the tuned mass damper array structure can obviously influence the vibration damping effect, in order to obtain a better vibration damping effect, a plurality of tuned mass damper oscillators are needed to be adopted, but the difficulty of processing and manufacturing is increased due to too many tuned mass damper oscillators, and in order to effectively arrange the annular tuned mass damper array 2, the number of the tuned mass damper oscillators 2b in the annular tuned mass damper array is marked as A; the number of the blades 1a in the blade disc 1 is recorded as B, the value of B is not less than 20, and the value of A is set as: 2< A < 3B; it is more preferable to set the value of a to: 0.5B < a < 1.5B.

The tuned mass damper array is a dynamic vibration absorber, the working principle of the tuned mass damper array determines that the closer the natural frequency of the tuned mass damper array and the natural frequency of the blade disc to be damped is, the better the damping effect is, and the relative error between the natural frequency of the vibrator and the natural frequency of the blade disc is set to be not more than 5% in the specific embodiment; more preferably: and setting the relative error between the natural frequency of the vibrator and the natural frequency of the blade disc to be not more than 2%.

The total mass of each vibrator in the tuned mass damper array can also influence the vibration damping effect of the vibrator, and the total mass of the vibrator of the tuned mass damper is too small, so that the vibration energy which can be absorbed by the vibrator is limited, and the vibration damping effect is also limited; the total mass of the tuned mass damper vibrators is too large, the total mass of the blade disc can be obviously increased, the thrust-weight ratio of the blade disc is reduced, and in specific implementation, the total mass of all tuned mass damper vibrators 2b in the annular tuned mass damper array 2 is set to be 1% -12% of the total mass of the blade disc 1.

The damping of the tuned mass damper vibrator can affect the vibration reduction effect, the energy of the vibrator can be consumed by the damping of the tuned mass damper vibrator, and therefore the tuned mass damper array can continuously absorb more energy on the blade disc. Therefore, it is necessary to ensure a certain damping of the tuned mass damper oscillator, and in the specific implementation, the modal damping of the tuned mass damper oscillator 2b at the natural frequency of the oscillator is set to be not less than 0.05%.

The tuned mass damper array rotates at a high speed along with the blade disc in work, and is always tightly attached to the inner surface of the blade disc in order to ensure that the tuned mass damper array does not fall off in the operation process, the annular tuned mass damper array 2 is installed on the inner surface of the blade disc 1b in an interference fit mode, interference magnitude in the assembling process is determined according to the structural size and the rotating speed of the blade disc, in particular implementation, in order to achieve assembling, the tuned mass damper array can be immersed in liquid nitrogen in advance to reduce the temperature and shrink, then the annular tuned mass damper array is installed on the inner surface of the blade disc to naturally heat, and in the operation of the blade disc 1, the annular tuned mass damper array 2 is attached to the blade disc 1 b.

The blisk structure shown in fig. 1 has 33 blades, the natural frequency to be damped is 2557Hz, the tuned mass damper array comprises 33 tuned mass damper vibrators which are uniformly distributed along the circumferential direction, the natural frequency design value of the tuned mass damper vibrators is 2557Hz, the modal damping ratio is 0.094%, and the total mass of the tuned mass damper vibrators is 1% of the total mass of the blisk. The harmonic response analysis was performed on the individual blisk structures and the blisk structures with the tuned mass damper arrays installed, the analysis frequency range was 2540Hz-2580Hz, and the variation curves of the maximum response amplitudes of the blades in both cases with the excitation frequency are shown in fig. 3. In FIG. 3, curve F1 is the maximum response amplitude versus frequency for a blade in a single blisk configuration, and curve F2 is the maximum response amplitude versus frequency for a blade in a blisk configuration with an array of tuned mass dampers installed. As can be seen in FIG. 3, the maximum response amplitude of the blisk over the frequency range is 3.2 × 10 when the tuned mass damper array is not installed^-3After the tuned mass damper array is installed, the maximum response amplitude of the blade disc is reduced to 1.9 multiplied by 10^-3The vibration damping effect is obvious.