A rotor system vibration suppression device and design method

Abstract

The present application relates to the field of vibration reduction, in particular to a rotor system vibration suppression device and design method, comprising two groups of bearing seats forming double-end face support for a rotating shaft and a number of vibration reduction seats corresponding to the bearing seats, the vibration reduction seats are arranged coaxially with the rotating shaft, and the two vibration reduction seats are arranged at equal intervals with the bearing seats; a metal layer and a damping layer are sequentially arranged from inside to outside on the vibration reduction seat coaxially with the rotating shaft, and a gap exists between the damping layer and the rotating shaft. The present application can convert excess energy into heat energy consumption through controllable rub-impact in the window period when the vibration just exceeds the standard but has not yet caused destructive instability, realizes early intervention, and significantly improves the vibration reduction effect.

Description

Technical Field

[0001] This invention relates to the field of vibration reduction, specifically to a vibration suppression device and design method for a rotor system. Background Technology

[0002] As rotating machinery such as aero-engines, gas turbines, and industrial compressors develop towards higher speeds and higher power densities, the dynamic environment of rotor systems is becoming increasingly demanding. During the operation of rotor systems, due to factors such as mass imbalance, thermal bending, or external excitation, rotors often exhibit vibration responses. When the vibration amplitude exceeds the design-allowed safety threshold, it not only affects the operating accuracy and efficiency of the machinery, but in severe cases, it can also cause violent rubbing between the rotor and stator, leading to catastrophic accidents such as blade breakage, shaft bending, or even complete machine failure.

[0003] To control rotor vibration, existing technologies mainly employ passive dampers (such as squeeze film dampers), active control technologies (such as active magnetic bearings), or limit protection devices (such as traditional rolling bearings). However, these technologies suffer from complex structures, high maintenance costs, and sensitive damping characteristics with insufficient reliability. They can only achieve passive response and lack proactive intervention, and these problems urgently need to be solved. Summary of the Invention

[0004] To avoid and overcome the technical problems existing in the prior art, this invention provides a rotor system vibration suppression device and design method. This invention can convert excess energy into heat energy through controlled rubbing during the window period before vibration causes destructive instability, achieving early intervention and significantly improving vibration reduction effect.

[0005] To achieve the above objectives, the present invention provides the following technical solution: A vibration suppression device for a rotor system includes two sets of bearing seats that provide double-end support for a rotating shaft and vibration damping seats corresponding to the number of bearing seats. The vibration damping seats are configured to be arranged coaxially with the rotating shaft, and the two vibration damping seats are arranged at equal intervals with the bearing seats. A metal layer and a damping layer are arranged sequentially from the inside to the outside, coaxially with the rotating shaft, and there is a gap between the damping layer and the rotating shaft.

[0006] As a further embodiment of the present invention: both vibration damping seats are located inside the bearing of the bearing housing or outside the bearing of the bearing housing.

[0007] As a further embodiment of the present invention: the metal layer is made of copper or stainless steel and serves as a bushing protective layer, with a thickness of less than 1 mm; the damping layer is made of rubber and provides system damping when the rotating shaft collides with the vibration damping seat.

[0008] As a further embodiment of the present invention: the vibration damping seat and the bearing seat are both fixed on the same mounting platform, and the position between the vibration damping seat and the bearing seat is adjustable.

[0009] A design method for a rotor system vibration suppression device includes the following steps: S1. Determine the installation position of the vibration damping seat according to the vibration suppression requirements. The installation position may be located inside or outside the bearing housing. S2. Based on the maximum allowable amplitude of the rotor system at the bearing. Determine the gap between the metal layer and the rotating shaft. ; S3, based on the determined Value, calculate the damping coefficient required for the damping layer. ; S4, based on the damping coefficient in S3 Determine the outer diameter of the damping layer.

[0010] As a further aspect of the present invention: when the vibration damping seat is located inside the bearing housing, the gap between the metal layer and the rotating shaft... The following conditions must be met simultaneously: ; ; ; ;

[0011] in, This represents the maximum allowable amplitude of the rotor system at the bearing. This represents the total support stiffness of the bearing housing; The elastic modulus of the shaft material; Let be the moment of inertia of the cross section of the shaft. The diameter of the shaft; This refers to the distance between the bearing housing and the rotating parts on the shaft. This refers to the distance between the vibration damping seat and the rotating parts on the shaft; The viscous damping coefficient of the rotor system before the installation of the vibration damping mount; This is the equivalent stiffness of the rotor system; The equivalent lumped mass of the rotor system; The eccentricity of the rotor system; This is the influence coefficient.

[0012] As a further aspect of the present invention: when the vibration damping seat is located outside the bearing housing, the gap between the metal layer and the rotating shaft... The following conditions must be met simultaneously: ; ; ; ;

[0013] in, This represents the maximum allowable amplitude of the rotor system at the bearing. This represents the total support stiffness of the bearing housing; The elastic modulus of the shaft material; Let be the moment of inertia of the cross section of the shaft. The diameter of the shaft; This refers to the distance between the bearing housing and the rotating parts on the shaft. This refers to the distance between the vibration damping seat and the rotating parts on the shaft; The viscous damping coefficient of the rotor system before the installation of the vibration damping mount; This is the equivalent stiffness of the rotor system; The equivalent lumped mass of the rotor system; The eccentricity of the rotor system; This is the influence coefficient.

[0014] As a further aspect of the present invention: the damping coefficient of the damping layer Conditions to be met: .

[0015] As a further aspect of the present invention: the outer diameter of the damping layer for: ;

[0016] in, The elastic modulus of the damping layer material; The width of the damping layer; This refers to the operating speed of the rotor system.

[0017] As a further aspect of the present invention: when the vibration damping seat is located outside the bearing housing, ;

[0018] When the vibration damping seat is located inside the bearing housing .

[0019] Compared with the prior art, the beneficial effects of the present invention are: 1. In this invention, a gap exists between the metal layer and the rotating shaft of the vibration damping seat, forming a preset contact trigger threshold. When the rotor vibration amplitude exceeds this gap, the rotor first contacts the metal layer, transferring the vibration energy to the outer damping layer. The vibratory energy is then converted into heat energy by utilizing the viscoelastic damping properties of the rubber material. The two work together to proactively intervene before vibration exceeds the limit. Within the window period when the rotor amplitude just exceeds the design threshold but has not yet reached destructive instability, the preset gap triggers controllable contact between the rotor and the metal layer. The damping layer effectively dissipates the vibration energy, suppressing further growth of the rotor amplitude through a pre-dissipation mechanism, preventing the system from entering a nonlinear instability state, and significantly improving the vibration damping effect.

[0020] 2. This invention uses a metal layer as a sacrificial contact surface, which can withstand slight friction without damaging the rotor body; the outer damping layer absorbs impact energy through inelastic deformation and assists the rotor in rebounding and resetting after vibration attenuation; when the rotor may experience excessive amplitude, the contact between the metal layer and the shaft plays a physical limiting role, ensuring the safety and reliability of the system, avoiding rigid direct collision between the rotor and the stator, and significantly reducing the risk of damage to core components from sudden rubbing failures; the whole adopts a pure mechanical structure, does not rely on external power supply, has a simple structure and high reliability, and greatly reduces system complexity and operation and maintenance costs.

[0021] 3. This invention can calculate the optimal clearance range between the metal layer and the shaft, and the damping coefficient range of the damping layer, based on the dynamic parameters of the target rotor system. This ensures that the device possesses optimal vibration reduction performance and self-recovery capability across the entire operating range, enabling the device to achieve optimal energy dissipation efficiency within a specific amplitude range of rotor vibration. Rapid customized design is possible for different rotor systems, adapting to the spatial constraints and vibration modal characteristics of different rotor systems. Attached Figure Description

[0022] Figure 1 This is a schematic diagram of the structure of the first embodiment of the present invention.

[0023] Figure 2 This is a schematic diagram of the structure of the second embodiment of the present invention.

[0024] Figure 3This refers to the horizontal displacement of the rotor at the bearing before the vibration damping seat is installed under the first operating condition.

[0025] Figure 4 This refers to the horizontal displacement of the rotor at the bearing after the vibration damping base is installed under the first operating condition.

[0026] Figure 5 This refers to the horizontal displacement of the rotor at the bearing before the vibration damping seat is installed under the second operating condition.

[0027] Figure 6 This refers to the horizontal displacement of the rotor at the bearing after the vibration damping mount is installed under the second operating condition.

[0028] Figure 7 This refers to the horizontal displacement of the rotor at the bearing before the vibration damping seat is installed under the third operating condition.

[0029] Figure 8 This refers to the horizontal displacement of the rotor at the bearing after the vibration damping seat is installed under the third operating condition.

[0030] In the diagram: 1. Shaft; 2. Bearing housing; 3. Vibration damping seat; 31. Damping layer; 32. Metal layer. Detailed Implementation

[0031] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0032] Please see Figures 1 to 8 In this embodiment of the invention, a rotor system vibration suppression device and design method include two sets of bearing seats 2 that provide double-end surface support for a rotating shaft 1, and vibration damping seats 3 corresponding to the number of bearing seats 2. The two sets of bearing seats 2 are arranged at intervals along the axial direction of the rotating shaft 1, providing double-end surface support for the rotating shaft 1, and are arranged at equal intervals with the rotating components on the rotating shaft 1 to ensure the stable operation of the rotor system.

[0033] The vibration damping seat 3 is configured to be arranged coaxially with the rotating shaft 1. The two sets of vibration damping seats 3 are arranged at equal intervals with the bearing seats 2, and the axial distance between each vibration damping seat 3 and its adjacent bearing seat 2 is equal.

[0034] The vibration damping base 3 is provided with a metal layer 32 and a damping layer 31 arranged coaxially with the rotating shaft 1 from the inside to the outside. The metal layer 32 is the inner layer and is directly opposite to the rotating shaft 1; the damping layer 31 is the outer layer and covers the outside of the metal layer 32. There is a preset radial gap between the damping layer 31 and the rotating shaft 1, which serves as a contact trigger threshold.

[0035] In this embodiment, the metal layer 32 is made of copper or stainless steel, which has wear resistance and thermal conductivity, and can withstand slight friction without damaging the rotating shaft 1. Its thickness is preferably no more than 1 mm. The damping layer 31 is made of rubber, which has elastic damping characteristics and can efficiently convert vibration energy into heat energy. The metal layer 32 provides a rigid contact surface and transmits the load, while the damping layer 31 is dedicated to energy dissipation. The two work together to achieve active intervention before vibration exceeds the standard.

[0036] Both the vibration damping seat 3 and the bearing seat 2 are fixed on the same mounting platform, and the position between the vibration damping seat 3 and the bearing seat 2 is adjustable. By adjusting the installation position of the vibration damping seat 3, different design requirements can be met.

[0037] Both sets of vibration damping seats 3 need to be located either inside the bearing housing 2 or outside the bearing housing 2. Vibration suppression requirements include the following two: When the two sets of damping seats 3 are located inside the bearing (i.e., between the two bearing seats), they mainly suppress the vibration of the rotor span bending mode. When the two sets of damping seats 3 are located outside the bearing (i.e., the overhang end), they mainly suppress the rotational mode vibration of the overhang end.

[0038] The design method for a rotor system vibration suppression device specifically includes the following steps: S1. Determine the installation position of the vibration damping seat 3 according to the vibration suppression requirements. The installation position may be located inside or outside the bearing seat 2. S2. Based on the maximum allowable amplitude of the rotor system at the bearing. Determine the gap between metal layer 32 and rotating shaft 1. ; When the vibration damping seat 3 is located inside the bearing seat 2, the gap between the metal layer 32 and the rotating shaft 1 is... The following conditions must be met simultaneously: ; ;

[0039] When the vibration damping seat 3 is located outside the bearing seat 2, the gap between the metal layer 32 and the rotating shaft 1 is... The following conditions must be met simultaneously: ; ; ; ;

[0040] in, This represents the maximum allowable amplitude of the rotor system at the bearing. This is the total support stiffness of bearing housing 2; this support stiffness is equal to the sum of the support stiffnesses of the two sets of bearing housing 2. The elastic modulus of the shaft material; Let be the moment of inertia of the cross section of the shaft. The diameter of shaft 1; The distance between bearing housing 2 and the rotating component on shaft 1; This refers to the distance between the vibration damping seat 3 and the rotating component on the rotating shaft 1; The viscous damping coefficient of the rotor system before the installation of the vibration damping seat 3; This is the equivalent stiffness of the rotor system; The equivalent lumped mass of the rotor system; The eccentricity of the rotor system; This is the influence coefficient; S3, based on the determined Value, calculate the required damping coefficient for damping layer 31. .

[0041] Damping coefficient of damping layer 31 Conditions to be met: ;

[0042] in, This is the equivalent stiffness of the rotor system; The equivalent lumped mass of the rotor system; The viscous damping coefficient of the rotor system before the installation of the vibration damping seat 3; The eccentricity of the rotor system; This is the influence coefficient; When the vibration damping seat 3 is located outside the bearing seat 2 ;

[0043] When the vibration damping seat 3 is located inside the bearing seat 2 .

[0044] S4, based on the determined Value, calculate the outer diameter of damping layer 31 .

[0045] outer diameter of damping layer 31 for: ;

[0046] in, The elastic modulus of the damping layer material; The width of the damping layer; This refers to the operating speed of the rotor system.

[0047] Under the first operating condition: elastic modulus of shaft material shaft diameter is , , , , The support stiffness of a single bearing housing is The maximum amplitude of the shaft at the bearing is required in the rotor system. ,exist Two sets of vibration damping seats 3 are installed at the location, and the elastic modulus of the damping layer material is... The width of the damping layer is The operating speed of the rotor system for .

[0048] It can be calculated , , According to the calculation based on the conditions, it can be known that ; ,Pick ; Calculations based on preset conditions show that ,Pick The outer diameter of the damping layer can be calculated as follows: The vibration of the shaft at the bearing was compared before and after the installation of the vibration damping seat 3. Figure 3 and Figure 4 As shown, after installing the vibration damping seat 3, the vibration amplitude decreased from... Down to .

[0049] Under the second operating condition: elastic modulus of shaft material shaft diameter is , , , , The support stiffness of a single bearing housing is The maximum amplitude of the shaft at the bearing is required in the rotor system. ,exist Two sets of vibration damping seats 3 are installed at the location, and the elastic modulus of the damping layer material is... The width of the damping layer is The operating speed of the rotor system for .

[0050] It can be calculated , , According to the calculation based on the conditions, it can be known that , ,Pick ; Calculations based on preset conditions show that ,Pick The outer diameter of the damping layer can be calculated as follows: The vibration of the shaft at the bearing was compared before and after the installation of the vibration damping seat 3. Figure 5 and Figure 6 As can be seen, after installing vibration damping seat 3, the vibration amplitude decreased from... Down to .

[0051] Under the third operating condition: elastic modulus of shaft material shaft diameter is , , , , The support stiffness of a single bearing housing is The maximum amplitude of the shaft at the bearing is required in the rotor system. ,exist Two sets of vibration damping seats 3 are installed at the location, and the elastic modulus of the damping layer material is... The width of the damping layer is The operating speed of the rotor system for .

[0052] It can be calculated , , According to the calculation based on the conditions, it can be known that , ,Pick ; Calculations based on preset conditions show that ,Pick The outer diameter of the damping layer can be calculated as follows: The actual outer diameter of the damping layer is set to Actual measurement The vibration of the shaft at the bearing was compared before and after the installation of the vibration damping seat 3. Figure 7 and Figure 8As can be seen, after installing vibration damping seat 3, the vibration amplitude decreased from... Down to .

[0053] The basic principles of this application have been described above with reference to specific embodiments. However, it should be noted that the advantages, benefits, and effects mentioned in this application are merely examples and not limitations, and should not be considered as essential features of each embodiment of this application. Furthermore, the specific details disclosed above are for illustrative and facilitative purposes only, and are not limitations. These details do not limit the application to the necessity of employing the aforementioned specific details for implementation.

[0054] The block diagrams of devices, apparatuses, devices, and systems involved in this application are merely illustrative examples and are not intended to require or imply that they must be connected, arranged, or configured in the manner shown in the block diagrams. As those skilled in the art will recognize, these devices, apparatuses, devices, and systems can be connected, arranged, and configured in any manner. Words such as “comprising,” “including,” “having,” etc., are open-ended terms meaning “including but not limited to,” and are used interchangeably with them. The terms “or” and “and” as used herein refer to the terms “and / or,” and are used interchangeably with them unless the context clearly indicates otherwise. The term “such as” as used herein refers to the phrase “such as but not limited to,” and is used interchangeably with it.

Claims

1. A vibration suppression device for a rotor system, characterized in that, It includes two sets of bearing seats (2) that provide double-end support for the rotating shaft (1) and vibration damping seats (3) corresponding to the number of bearing seats (2). The vibration damping seats (3) are configured to be arranged coaxially with the rotating shaft (1). The two vibration damping seats (3) are arranged at equal intervals with the bearing seats (2). The vibration damping seats (3) are provided with a metal layer (32) and a damping layer (31) arranged coaxially with the rotating shaft (1) from the inside to the outside. There is a gap between the damping layer (31) and the rotating shaft (1).

2. The rotor system vibration suppression device according to claim 1, characterized in that, Both of the vibration damping seats (3) are located inside the bearing of the bearing housing (2) or outside the bearing of the bearing housing (2).

3. The rotor system vibration suppression device according to claim 1, characterized in that, The metal layer (32) is made of copper or stainless steel and serves as a bushing protection layer. The thickness of the metal layer (32) is less than 1 mm. The damping layer (31) is made of rubber and provides system damping when the rotating shaft (1) collides with the damping seat (3).

4. The rotor system vibration suppression device according to claim 1, characterized in that, The vibration damping seat (3) and the bearing seat (2) are both fixed on the same mounting platform, and the position between the vibration damping seat (3) and the bearing seat (2) is adjustable.

5. A design method for a rotor system vibration suppression device according to any one of claims 1 to 4, characterized in that, Includes the following steps: S1. Determine the installation position of the vibration damping seat (3) according to the vibration suppression requirements. The installation position includes the inner or outer side of the bearing seat (2); S2. Based on the maximum allowable amplitude of the rotor system at the bearing. Determine the gap between the metal layer (32) and the rotating shaft (1). ; S3, based on the determined Value, calculate the damping coefficient required for the damping layer (31) ; S4, based on the damping coefficient in S3 Determine the outer diameter of the damping layer (31).

6. The design method of a rotor system vibration suppression device according to claim 5, characterized in that, When the damping seat (3) is located inside the bearing seat (2), the gap between the metal layer (32) and the rotating shaft (1) is... The following conditions must be met simultaneously: in, This represents the maximum allowable amplitude of the rotor system at the bearing. The total support stiffness of the bearing housing (2); The elastic modulus of the shaft material; Let be the moment of inertia of the cross section of the shaft. The diameter of the shaft (1) is the diameter of the rotating shaft; The distance between the bearing housing (2) and the rotating parts on the shaft (1); The distance between the vibration damping seat (3) and the rotating parts on the shaft (1); The viscous damping coefficient of the rotor system before installing the damping seat (3); This is the equivalent stiffness of the rotor system; The equivalent lumped mass of the rotor system; The eccentricity of the rotor system; This is the influence coefficient.

7. The design method of a rotor system vibration suppression device according to claim 5, characterized in that, When the damping seat (3) is located outside the bearing seat (2), the gap between the metal layer (32) and the shaft (1) is... The following conditions must be met simultaneously: in, This represents the maximum allowable amplitude of the rotor system at the bearing. The total support stiffness of the bearing housing (2); The elastic modulus of the shaft material; Let be the moment of inertia of the cross section of the shaft. The diameter of the shaft (1) is the diameter of the rotating shaft; The distance between the bearing housing (2) and the rotating parts on the shaft (1); The distance between the vibration damping seat (3) and the rotating parts on the shaft (1); The viscous damping coefficient of the rotor system before installing the damping seat (3); This is the equivalent stiffness of the rotor system; The equivalent lumped mass of the rotor system; The eccentricity of the rotor system; This is the influence coefficient.

8. A design method for a rotor system vibration suppression device according to claim 6 or 7, characterized in that, Damping coefficient of damping layer (31) Conditions to be met: 。 9. The design method of a rotor system vibration suppression device according to claim 8, characterized in that, outer diameter of damping layer (31) for: in, The elastic modulus of the damping layer material; The width of the damping layer; This refers to the operating speed of the rotor system.

10. The design method of a rotor system vibration suppression device according to claim 8, characterized in that, When the vibration damping seat (3) is located outside the bearing seat (2), When the vibration damping seat (3) is located inside the bearing seat (2), 。

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