Oil seepage hole angle combination optimization design method of elastic ring type squeeze film damper

Abstract

The invention relates to an angle combination optimization design method for oil seepage holes of an elastic ring type squeeze film damper, and the oil seepage holes of the damper are in one of the following two combination modes: the punching angles of all the oil seepage holes in each group of oil seepage holes are the same, and the angle range of the oil seepage holes is 0-80 degrees; the punching angles of the two oil seepage holes of the first pair of oil seepage holes in each group are opposite, the punching angles of the two oil seepage holes of the second pair of oil seepage holes are also opposite, and the angle range of the oil seepage holes is-45 degrees to 45 degrees. The punching angles of the oil seepage holes are set, the internal flowing structure of an oil film can be actively regulated and controlled, vortexes and unstable flowing can be effectively restrained, the pressure distribution uniformity and the energy dissipation efficiency of the oil film are remarkably improved, and therefore the better damping performance and the better vibration reduction effect are obtained. The damper is especially suitable for rotating machines such as aero-engines with harsh requirements for vibration control, and excellent and stable damping performance can be achieved within the wide working condition range (including the high eccentricity ratio).

Description

TECHNICAL FIELD

[0001] The embodiment of the application relates to the technical field of vibration control of rotating machinery, and particularly relates to a method for optimizing the angle combination of oil infiltration holes of an elastic ring type squeeze oil film damper. BACKGROUND

[0002] The method for controlling the vibration of an aero-engine rotor system mainly includes performing rotor dynamics design, arranging dampers at support points, and performing dynamic balancing. The elastic ring type squeeze oil film damper (ERSFD) not only has a series of advantages of the squeeze oil film damper, but also improves the high nonlinearity of oil film stiffness, has the frequency modulation function of the elastic support, and has broad application prospects.

[0003] The elastic ring type squeeze oil film damper is composed of an inner bushing, an elastic ring and an outer bushing, and the inner bushing and the outer bushing form a plurality of cavities with the elastic ring. A plurality of bosses are included on the outer surface and the inner surface of the elastic ring, and the bosses are uniformly distributed on the inner and outer surfaces of the elastic ring and are in contact with the inner bushing and the outer bushing, respectively. The lubricating oil film in the cavity between the inner bushing and the inner ring is defined as an inner oil film, and the lubricating oil film between the outer ring and the outer bushing is defined as an outer oil film. The outer oil cavity and the inner oil cavity are connected to each other through the oil holes on the elastic ring. The elastic ring type squeeze oil film damper is supplied with oil, and the lubricating oil fills the entire elastic ring assembly. When the rotor rotates, the journal deviates from the center and whirls due to unbalance and other effects, and the elastic ring is deformed by being squeezed, and then the inner and outer oil films are squeezed, the flow and pressure distribution of each oil film are changed, the oil film reaction force acts on the elastic ring and the journal, and the oil film stiffness and the oil film damping are provided, wherein the oil film damping can play a damping effect.

[0004] Zhao Lu, Liao Mingfu, et al. pointed out in "Experimental Study on Vibration Reduction of Elastic Ring Type Squeeze Oil Film Damper" [J]. Propulsion Technology, 2021, 42(05): 1129-1137. that the ERSFD has a relatively obvious damping effect on the rotor, and the relative change of each order critical speed of the rotor system before and after oil supply is not more than 4.63%, which indicates that the oil film of the ERSFD does not significantly change the modal of the rotor system, and there are many parameters that affect the damping effect of the ERSFD, and the parameter optimization design of the ERSFD and the rotor system needs to be performed.

[0005] Y. Xu, X. Chen, J. Zou, et al. in "Influence of orifice distribution on the characteristics of Elastic Ring Squeeze Film Dampers for Flywheel Energy Storage System," 2012 16th International Symposium on Electromagnetic Launch Technology, Beijing, China, 2012, pp. 1-6. plotted the relationship between oil film force and orifice position in axial and circumferential directions, summarized the principle of optimal orifice position, and verified it by changing orifice radius. It is pointed out that orifice with optimal distribution can play the greatest role in adjusting damping coefficient, providing guidance for the design and application of ERSFD.

[0006] ERSFD itself produces damping effect through the fluid-structure coupling of oil film and elastic ring. The above research shows that the oil film stiffness of ERSFD is small, and the modal characteristics of the rotor system changes little; changing the position of the oil permeation orifice can adjust the oil film pressure distribution and thus adjust the damping coefficient, maximizing the vibration reduction effect of ERSFD. However, the existing technology mainly focuses on the optimal design of the position (axial / circumferential) and diameter of the oil permeation orifice. For the punching angle of the oil permeation orifice, especially the systematic influence law of the specific angle combination mode between multiple orifices on the internal flow field structure (such as secondary flow, vortex) of the oil film, pressure distribution uniformity and final damping performance, there is no in-depth research and effective optimization design method. Single angle or disordered angle combination is easy to induce complex secondary flow, vortex and even flow separation in the oil film, resulting in uneven pressure distribution and reduced energy dissipation efficiency, and the performance deteriorates significantly under high eccentricity ratio and large load conditions.

[0007] The existing elastic ring squeeze film damper is prone to problems such as vortex and uneven pressure distribution under high eccentricity ratio and wide speed conditions, which limits the energy dissipation efficiency. Therefore, there is an urgent need for a structure and design method that can improve the uniformity of oil film pressure and enhance the equivalent damping of the system without significantly increasing the structural complexity.

[0008] It should be noted that this section is intended to provide background or context to the technical solution of the invention stated in the claims. The description herein is not admitted to be prior art merely because it is included in this section. SUMMARY

[0009] The present application aims to provide a kind of elastic ring type extrusion oil film damper oil hole angle combination optimization design method, and then at least in some extent, one or more problems caused by the limitation and defects of related technology are solved.

[0010] The present application first provides an elastic ring type extrusion oil film damper, which comprises a damper outer bushing, an elastic ring and a damper inner bushing, the elastic ring is located between the damper inner bushing and the damper outer bushing, a plurality of groups of oil holes are provided on the elastic ring, each group of oil holes comprises a first pair of oil holes and a second pair of oil holes, the distance between the first pair of oil holes is greater than the distance of the second pair of oil holes, and the connecting line of the first pair of oil holes is parallel to the connecting line of the second pair of oil holes, the punching angle of each group of oil holes is one of the following two combination modes: The first combination mode: the punching angle of all oil holes in each group of oil holes is the same, and the angle range of the oil holes is 0°-80°. The second combination mode: the punching angle of the two oil holes of the first pair of oil holes in each group is opposite, and the punching angle of the two oil holes of the second pair of oil holes is also opposite, and the angle range of the oil holes is -45°-45°.

[0011] Supplement In the present application, the inner and outer sides of the elastic ring are respectively provided with inner and outer bosses.

[0012] In the present application, the height of the inner and outer bosses is 0.30mm, and the width is 5mm.

[0013] In the present application, the width of the inner / outer boss is not greater than 30% of the arc length of the elastic ring on which the adjacent two inner / outer bosses are located.

[0014] In the present application, the width of the elastic ring is 20.8mm.

[0015] In the first combination mode, the punching angle of the oil holes in each group of oil holes is 0°, 30°, 45° or 60°.

[0016] In the second combination mode, the angle of the oil holes is -30°, 30°, -45°, 45°.

[0017] The present application further provides an elastic ring type extrusion oil film damper oil hole angle combination optimization design method, which is used for punching the oil holes of the damper according to the first combination mode or the second combination mode.

[0018] In the present application, a three-dimensional finite element model of the damper is established, and the elastic deformation of the damper under various bearing loads is calculated by using finite element analysis method.

[0019] In the present application, the elastic deformation result is used to calculate the vibration response of the rotor system of the oil infiltration hole damper at different angles in the running speed range.

[0020] The technical solution provided by the present application can include the following beneficial effects: The present application sets the punching angle of the oil infiltration hole, actively regulates the internal flow structure of the oil film, effectively suppresses vortex and unstable flow, significantly improves the uniformity of the oil film pressure distribution and the energy dissipation efficiency, thereby obtaining better damping performance and vibration reduction effect. It is especially suitable for rotary machines such as aircraft engines which have strict requirements for vibration control, and can achieve excellent and stable damping performance in a wide operating condition range (including high eccentricity ratio). BRIEF DESCRIPTION OF DRAWINGS

[0021] The accompanying drawings, which are incorporated into and form part of the specification, illustrate embodiments consistent with the present disclosure and, together with the specification, serve to explain the principles of the disclosure. Obviously, the drawings in the following description are only some embodiments of the present disclosure, and other drawings can be obtained from these drawings without creative labor for those skilled in the art.

[0022] Figure 1 A structure schematic diagram of an elastic ring type extruded oil film damper in an exemplary embodiment of the present application is shown. Figure 2 A structure schematic diagram of an elastic ring in an exemplary embodiment of the present application is shown. Figure 3 An enlarged structure schematic diagram of an outer boss in an exemplary embodiment of the present application is shown. Figure 4 A three-dimensional model of an elastic ring outer bushing, an elastic ring and an elastic ring inner bushing in an exemplary embodiment of the present application is shown. Figure 5 An oil infiltration hole schematic diagram with a punching angle of 0°, 0°, 0° and 0° in an exemplary embodiment of the present application is shown. Figure 6 An oil infiltration hole schematic diagram with a punching angle of 30°, 30°, 30° and 30° in an exemplary embodiment of the present application is shown. Figure 7 An oil infiltration hole schematic diagram with a punching angle of 45°, 45°, 45° and 45° in an exemplary embodiment of the present application is shown. Figure 8 An oil infiltration hole schematic diagram with a punching angle of 30°, -30°, 30° and -30° in an exemplary embodiment of the present application is shown. Figure 9 An oil infiltration hole schematic diagram with a punching angle of 45°, -45°, 45° and -45° in an exemplary embodiment of the present application is shown. Figure 10Fig. 2 shows a schematic diagram of the oil permeating holes with a punching angle of 60°, 60°, 60°, 60° in the exemplary embodiment of the present application; Fig. 11 shows the oil film pressure distribution diagrams of the elastic ring type squeeze film damper with different combinations of the oil permeating hole punching angle in the exemplary embodiment of the present application, wherein (a) represents the punching angle of 0°, 0°, 0°, 0°; (b) represents the punching angle of 30°, 30°, 30°, 30°; (c) represents the punching angle of 45°, 45°, 45°, 45°; (d) represents the punching angle of 30°, -30°, 30°, -30°; (e) represents the punching angle of 45°, -45°, 45°, -45°; (f) represents the punching angle of 60°, 60°, 60°, 60° Figure 12 Fig. 12 shows the equivalent oil film damping of the elastic ring type squeeze film damper with different combinations of the oil permeating hole punching angle in the exemplary embodiment of the present application, wherein (a) represents the equivalent oil film damping of the elastic ring type squeeze film damper with different combinations of the oil permeating hole punching angle under small eccentricity ratio; (b) represents the equivalent oil film damping of the elastic ring type squeeze film damper with different combinations of the oil permeating hole punching angle under large eccentricity ratio; Figure 13 Fig. 13 shows the rotor vibration response of the elastic ring type squeeze film damper with different combinations of the oil permeating hole punching angle in the exemplary embodiment of the present application.

[0023] Reference Signs: 1, damper outer bushing; 2, elastic ring; 3, damper inner bushing; 4, bearing; 5, oil permeating hole; 6, inner boss; 7, outer boss. DETAILED DESCRIPTION

[0024] Example implementations will now be described more fully with reference to the accompanying drawings. Example implementations may, however, be implemented in many different forms and should not be construed as limited to the examples set forth herein; rather, these implementations are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the example implementations to those skilled in the art. Features, structures or characteristics described in connection with one example implementation can be combined in any suitable manner with features, structures or characteristics of another example implementation.

[0025] In addition, the drawings are only schematic and are non-limiting. Like references signs denote like features in the drawings and a repeated description is omitted. Some of the blocks in the drawings are functional blocks, which can not necessarily correspond to physical or logical entities.

[0026] In the present example implementation, an elastic ring type squeeze film damper is first provided, which is described with reference to Fig. 1. Figures 1-4As shown, the damper comprises a damper outer bushing 1, an elastic ring 2 and a damper inner bushing 3. The elastic ring 2 is located between the damper inner bushing 3 and the damper outer bushing 1, and a plurality of groups of oil infiltration holes 5 are arranged on the elastic ring 2, for example, at least 4 groups of oil infiltration holes 5 can be arranged, and there can also be 16 groups, 20 groups, 24 groups, etc., and 20 groups are preferred.

[0027] Each group of oil infiltration holes 5 comprises a first pair of oil infiltration holes and a second pair of oil infiltration holes, the distance between the first pair of oil infiltration holes is greater than the distance between the second pair of oil infiltration holes, and the connecting line of the first pair of oil infiltration holes is parallel to the connecting line of the second pair of oil infiltration holes.

[0028] The punching angle of each group of oil infiltration holes 5 is one of the following two combination modes: The first combination mode (i.e. the same angle mode): the punching angles of all oil infiltration holes 5 in each group of oil infiltration holes 5 are the same, and the angle range of the oil infiltration holes 5 is 0°-80°. In this mode, the four oil infiltration holes in the group form a trapezoidal arrangement, the center distance of the first pair of oil infiltration holes along the circumference is d1, the center distance of the second pair of oil infiltration holes is d2, and d1>d2; the connecting lines of the first pair and the second pair of oil infiltration holes are parallel to each other. Define the punching angle θ as the angle between the oil infiltration hole axis and the radial line at the position of the oil infiltration hole (positive in the forward direction and negative in the reverse direction), the punching angles of the four oil infiltration holes in the group are the same, θ is 30° or 45°. The eccentricity ratio ε: the ratio of the rotor eccentricity to the radial gap, which is consistent with the boss height value here.

[0029] The second combination mode (i.e. the anti-symmetry mode): the punching angles of the two oil infiltration holes 5 in the first pair of oil infiltration holes in each group are opposite, and the punching angles of the two oil infiltration holes 5 in the second pair of oil infiltration holes are also opposite, and the angle range of the oil infiltration holes 5 is -45°-45°. The punching angles of the four oil infiltration holes in the group satisfy θ1=-θ2, θ3=-θ4, and |θ| is 30° or 45°.

[0030] It should be noted that the ball bearing 4 is arranged at a certain fulcrum of the rotor system, and the elastic ring type extruded oil film damper is arranged at the fulcrum.

[0031] The present application optimizes the structure of the oil infiltration hole 5 by setting the punching angle of the oil infiltration hole 5, thereby obtaining a new type of elastic ring type extruded oil film damper (ERSFD), which can actively control the internal flow structure of the oil film, effectively suppress vortex and unstable flow, significantly improve the uniformity of oil film pressure distribution and energy dissipation efficiency, thereby obtaining better damping performance and vibration reduction effect. Especially suitable for aviation engines and other rotating machinery with strict requirements for vibration control, which can achieve excellent and stable damping performance in a wide range of working conditions (including high eccentricity ratio).

[0032] The structure of the damper of the present application will be described below.

[0033] The elastic ring 2 of the damper of the present application can be provided with multiple groups of oil infiltration holes 5, for example, 20 groups of oil infiltration holes 5, and each group of oil infiltration holes 5 includes 4 oil infiltration holes 5 with specific spatial distribution, and the four oil infiltration holes 5 are distributed in a trapezoidal shape. The angle tolerance of the oil infiltration holes 5 is ±1°, and the orifice surface roughness Ra is ≤0.8 μm.

[0034] Optionally, in some embodiments, the inner diameter of the elastic ring 2 is 241.8 mm, the outer diameter is 243.84 mm, and the axial width b is about 0.5-1 times the width of the corresponding fulcrum bearing 4, preferably 20.8 mm.

[0035] The inner side of the elastic ring 2 is provided with multiple inner bosses 6, and the outer side is provided with multiple outer bosses 7. The height h of the inner boss 6 and the outer boss 7 is 0.20-0.40 mm, preferably 0.30 mm, which is about 2-3‰ of the average radius of the elastic ring 2, and the width w of the inner boss 6 and the outer boss 7 is 3-7 mm, preferably 5 mm. w is not greater than 30% of the arc length of the elastic ring between adjacent two bosses. The shape of the inner boss 6 and the outer boss is a sector shape.

[0036] The width w of the boss of the elastic ring 2 accounts for no more than 30% of the arc length of the substructure (the arc length of the elastic ring 2 on which the adjacent two inner bosses / outer bosses are located) of the elastic ring 2.

[0037] The outer boss 7 of the elastic ring 2 is in interference fit with the outer bushing 1 of the damper, and the inner boss 6 of the elastic ring 2 is in clearance fit with the inner bushing 3 of the damper, where the inner bushing 3 of the damper serves as the role of the outer ring of the bearing 4, and the inner boss 6 is in fit with the outer ring of the bearing. This structural feature determines that the adjustment space of the radius of the elastic ring 2 is limited by the size of the bearing, and at the same time, the axial width is generally 0.5-1 times the width of the corresponding fulcrum bearing.

[0038] The specific parameters of the oil infiltration hole 5 are described below.

[0039] In some embodiments, the hole diameter of the oil infiltration hole 5 is 0.6-1.2 mm, preferably 0.8 mm. The punching angle of the oil infiltration hole 5 is set as follows: First combined mode: the punching angles of all the oil infiltration holes 5 in each group of oil infiltration holes 5 are the same, for example, the punching angles of each group of oil infiltration holes 5 can be 0°, 0°, 0°, 0°; 30°, 30°, 30°, 30°; 45°, 45°, 45°, 45° or 60°, 60°, 60°, 60°, but are not limited thereto.

[0040] Second combined mode: the punching angles of the two oil infiltration holes 5 of the first pair of oil infiltration holes in each group are opposite, and the punching angles of the two oil infiltration holes 5 of the second pair of oil infiltration holes are also opposite, and the punching angles of each group of oil infiltration holes 5 can be 30°, -30°, 30°, -30° or 45°, -45°, 45°, -45°.

[0041] It should be noted that in the present application, the punching angle is defined as the included angle between the center line of the oil seepage hole and the radial direction (i.e. the direction of the vertical line of the tangent plane) of the position of the oil seepage hole on the elastic ring.

[0042] The present application also provides a method for optimizing the angle combination of the oil seepage hole 5 of the elastic ring type squeeze oil film damper, and the oil seepage hole 5 of the damper according to any one of the above embodiments is punched according to the first combination mode or the second combination mode.

[0043] Simulation analysis is carried out on the rotor vibration response of the elastic ring type squeeze oil film damper with different combination modes of the punching angle of the oil seepage hole 5.

[0044] Step 1: Establish accurate three-dimensional finite element models of the elastic ring outer bushing 1, the elastic ring 2 and the elastic ring inner bushing 3. Calculate the elastic deformation of each component under typical bearing load by using finite element analysis software (such as ANSYS Workbench).

[0045] Step 2: Extract the calculation results of Step 1, including the displacement of the inner surface of the elastic ring outer bushing 1, the displacement of the outer surface of the elastic ring inner bushing 3, the displacement of the inner surface of the elastic ring 2, the displacement of the outer surface of the elastic ring 2 and the solid deformation data at the oil seepage hole 5. The total of the deformation of the inner surface of the elastic ring outer bushing 1 and the solid deformation data at the oil seepage hole 5 is the outer oil film deformation of the elastic ring type squeeze oil film damper, and the total of the deformation of the outer surface of the elastic ring inner bushing 3 and the solid deformation data at the oil seepage hole 5 is the inner oil film deformation of the elastic ring type squeeze oil film damper. The inner surface displacement of the elastic ring 2 includes the solid deformation data at the oil seepage hole 5, and the outer surface displacement of the elastic ring 2 includes the solid deformation data at the oil seepage hole 5. The difference between the inner surface displacement of the elastic ring outer bushing 1 and the outer surface deformation of the elastic ring 2 is the outer oil film gap function of the elastic ring deformation, and the difference between the inner surface of the elastic ring 2 and the outer surface deformation of the elastic ring inner bushing 3 is the inner oil film gap function.

[0046] Step 3: Take the inner and outer oil film gap functions obtained in Step 2, as well as the position and geometric information of the oil seepage hole as input, and use a fluid dynamics calculation model based on the Reynolds equation or the Navier-Stokes equation (such as finite difference method, finite volume method) to solve the pressure field distribution of the inner and outer oil films of the damper considering the effect of the oil seepage hole. When the finite difference or finite volume is discretized by using the Reynolds equation or the Navier-Stokes equation, the convergence criterion is that the relative residual is ≤1×10 -6 .

[0047] Step 4: The oil film pressure field calculated in step 3 is integrated along the axial and circumferential surface area covered by the oil film to obtain the total oil film force acting on the elastic ring by the inner and outer oil films, including the radial and tangential force components, using Simpson integration method. By calculating the oil film force variation curve under different load / eccentricity ratios, the equivalent oil film damping coefficient under the angle combination mode can be further linearized.

[0048] Step 5: Substitute the equivalent oil film damping coefficient obtained in step 4 into the rotor-bearing system dynamics model, and calculate and compare the vibration response of the rotor system with different oil hole angle combination ERSFD installed within the operating speed range.

[0049] wherein the numerical integration of the oil film pressure field uses Simpson method; the eccentricity ratio ε (the ratio of the rotor eccentricity to the radial gap) is segmented within the range of 0.1-0.8 to form an evaluation working condition set, and the vibration amplitude of each θ angle combination is compared under the working condition set to select the θ angle combination with the smallest vibration amplitude.

[0050] Figures 5-10 Corresponding to the punching angle of the elastic ring 2 in the combinations of 0°, 0°, 0°, 0° (Example One), 30°, 30°, 30°, 30° (Example Two), 45°, 45°, 45°, 45° (Example Three), 30°, -30°, 30°, -30° (Example Four), 45°, -45°, 45°, -45° (Example Five), and 60°, 60°, 60°, 60° (Example Six), respectively.

[0051] Figure 11 is a three-dimensional diagram of the inner and outer oil film pressure of the elastic ring type squeeze oil film damper when the eccentricity ratio is 0.6 under different oil hole angle combination modes. It can be seen that the inner and outer oil film pressure values of the elastic ring type squeeze oil film damper of Example Five are greater than those of other examples, and the peak value of the outer oil film pressure reaches 1.2 MPa, and the peak value of the inner oil film reaches 0.4 MPa, so the equivalent oil film damping that the damper can provide is increased. The outer oil film main peak (1.2 MPa) is prominent, which can suppress large amplitude vibration of the rotor under critical speed working condition; the inner film double peak is separated, which can provide additional damping to avoid instability of the inner cavity oil film; the inner and outer pressure difference is significant, the lubricating oil is locked in the outer cavity, the leakage is reduced, and the stability of the oil film carrying capacity is maintained.

[0052] From Figure 12 It can be seen that the equivalent oil film damping coefficients of each example under different eccentricity ratios are compared: At small eccentricity ratio (ε<0.4), the damping coefficient of each embodiment is linear, but the damping value of embodiment five has been significantly ahead. For example, at the eccentricity ratio of ε=0.3, the equivalent oil film damping coefficient of embodiment five reaches 3750 N·s / m, which is much higher than that of embodiment three (3500 N·s / m) and embodiment four (3300 N·s / m); At large eccentricity ratio (ε>0.4), the damping nonlinearity is enhanced, and the advantage of embodiment five is more prominent. For example, at the eccentricity ratio of ε=0.7, the equivalent oil film damping coefficient of embodiment five reaches about 9300 N·s / m, which is much higher than that of embodiment three (8500 N·s / m) and embodiment four (7500 N·s / m). The equivalent oil film damping coefficient of the damper in embodiment six decreases sharply, which is about one fourth of that of embodiment three, indicating that too large an angle leads to performance deterioration.

[0053] From Figure 13 It can be seen that the vibration response amplitude of the rotor system installed with the ERSFD adopting the angle combination mode of embodiment five (45°, -45°, 45°, -45°) is significantly lower than that of the ERSFD adopting other angle combination modes in a wide speed range, especially near the critical speed and in the high-speed area, and the vibration reduction effect is most obviously improved. This directly verifies the superiority of the anti-symmetric 45° angle combination mode in improving the overall vibration reduction performance of the system.

[0054] Compared with the comparative structure (θ=0° same angle), the embodiment in which the oil infiltration hole has an angle of -45° and 45° in the present application reduces the vibration amplitude by 27.2% at 6557 rpm and by 30.77% at 6785 rpm. The above results show that the angle combination described in the present application can improve the pressure distribution and improve the energy dissipation efficiency.

[0055] In summary, through systematic simulation and experimental verification, it is found that the use of the anti-symmetric angle combination mode, especially the mode in which the angles of adjacent holes in the group are opposite and have the same absolute value, can significantly optimize the internal flow field of the oil film: In the oil film extrusion area, the oil infiltration holes with opposite angles have a complementary guiding effect on the oil flow, effectively inhibiting or eliminating large-scale vortex and unstable flow that is easily generated by single-direction punching; This flow field regulation promotes more orderly and sufficient radial exchange and pressure transmission between the inner and outer oil chambers, significantly improving the uniformity of the circumferential distribution of the oil film pressure; Finally, under a specific angle combination (especially the anti-symmetric mode in which the absolute values of the angles of adjacent holes are both 45°), the highest energy dissipation efficiency (equivalent oil film damping) and the best vibration reduction effect (lowest rotor vibration response amplitude) are achieved, and the angle combination reaches the best balance point of fluid guiding efficiency, vortex suppression effect, and flow resistance under typical structural dimensions and working condition parameters.

[0056] The application obtains oil film force and equivalent oil film damping under different eccentricity ratios through finite element / fluid dynamic coupling calculation, and selects an optimal angle combination accordingly. The application can actively regulate oil film flow field, suppress vortex and unstable flow, improve pressure distribution uniformity and energy dissipation efficiency, realize stable and excellent damping performance in a wide operating condition range, and is suitable for high requirement rotor systems such as aero-engines.

[0057] It should be understood that the orientations or positional relationships indicated by the terms 'center', 'longitudinal', 'transverse', 'length', 'width', 'thickness', 'upper', 'lower', 'front','rear', 'left', 'right','vertical', 'horizontal', 'top', 'bottom', 'inner', 'outer', 'clockwise', 'counterclockwise' and the like appearing in the above description are based on the orientations or positional relationships shown in the drawings, and are only for the convenience of describing the embodiments of the application and simplifying the description, and therefore cannot be understood as indicating or implying that the devices or elements indicated must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the embodiments of the application.

[0058] In addition, the terms 'first' and'second' are only for descriptive purposes, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the technical features indicated. Therefore, the features defined with 'first' and'second' can explicitly or implicitly include one or more of the features. In the description of the embodiments of the application, the meaning of 'plurality' is two or more, unless otherwise explicitly specified and limited.

[0059] In the embodiments of the application, unless otherwise explicitly specified and limited, the terms'mounting', 'connection', 'connecting', 'fixing' and the like should be understood in a broad sense, for example, can be fixed connection, can also be detachable connection or integral; can be mechanical connection, can also be electrical connection; can be directly connected, can also be indirectly connected through an intermediate medium; can be the internal communication of two elements or the interaction relationship between two elements. For those skilled in the art, the specific meanings of the above terms in the application can be understood according to the specific circumstances.

[0060] In the embodiments of the present application, unless specifically defined and limited otherwise, the first feature "on" or "under" the second feature can include that the first and second features are in direct contact, or that the first and second features are not in direct contact but are in contact through another feature between them. Moreover, the first feature "on", "above" and "over" the second feature includes that the first feature is directly above and obliquely above the second feature, or only means that the first feature is higher than the second feature in horizontal height. The first feature "under", "below" and "underneath" the second feature includes that the first feature is directly below and obliquely below the second feature, or only means that the first feature is lower than the second feature in horizontal height.

[0061] In the description of the specification, the description of the terms "one embodiment", "some embodiments", "an example", "a specific example" or "some examples" and the like means that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present application. In the specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art can combine and combine different embodiments or examples described in the specification.

[0062] Other embodiments of the present application will be apparent to those skilled in the art from consideration of the specification and practice of the application disclosed herein. This application is intended to cover any variations, uses or adaptations of the application following the general principles thereof and including such departures from the present disclosure as come within known use or custom in the art. The specification and examples are to be regarded as illustrative only, and the true scope and spirit of the application is indicated by the appended claims.

Claims

1. A resilient ring type squeeze film damper, the damper comprising: The damping device outer sleeve, the elastic ring and the damping device inner sleeve, the elastic ring is located between the damping device inner sleeve and the damping device outer sleeve, a plurality of groups of oil seepage holes are arranged on the elastic ring, characterized in that each group of oil seepage holes comprises a first pair of oil seepage holes and a second pair of oil seepage holes, the distance between the first pair of oil seepage holes is greater than the distance between the second pair of oil seepage holes, and the connecting line of the first pair of oil seepage holes is parallel to the connecting line of the second pair of oil seepage holes, and the punching angle of each group of oil seepage holes is one of the following two combination modes: The first combination mode: the punching angles of all oil seepage holes in each group of oil seepage holes are the same, and the angle range of the oil seepage holes is 0°-80°. The second combination mode: the punching angles of the two oil seepage holes of the first pair of oil seepage holes in each group are opposite, and the punching angles of the two oil seepage holes of the second pair of oil seepage holes are also opposite, and the angle range of the oil seepage holes is -45°-45°.

2. The elastic ring type squeeze film damper according to claim 1, wherein The inner and outer sides of the elastic ring are respectively provided with inner and outer bosses.

3. The elastic ring type squeeze film damper according to claim 2, wherein The height of the inner and outer bosses is 0.30 mm, and the width is 5 mm.

4. The elastic ring type squeeze film damper according to claim 3, wherein The width of the inner and outer bosses is not greater than 30% of the arc length of the elastic ring on which the adjacent two inner and outer bosses are located.

5. The elastic ring type squeeze film damper according to claim 1, wherein The width of the elastic ring is 20.8 mm.

6. The elastic ring type squeeze film damper according to claim 1, wherein In the first combination mode, the punching angles of the oil seepage holes in each group of oil seepage holes are 0°, 30°, 45° or 60°.

7. The elastic ring type squeeze film damper according to claim 1, wherein In the second combination mode, the angles of the oil seepage holes are -30°, 30°, -45°, 45°.

8. The method for optimization design of the oil leakage hole angle combination of the elastic ring type squeeze oil film damper, characterized in that, The oil seepage holes of the damping device according to any one of claims 1-7 are punched according to the first combination mode or the second combination mode.

9. The method of claim 8, wherein the angle of the oil passage is optimized by the following equation: ###0001### where, θ is the angle of the oil passage, L is the length of the oil passage, R is the radius of the elastic ring, and h is the thickness of the elastic ring. A three-dimensional finite element model of the damping device is established, and a finite element analysis method is used to calculate the elastic deformation of the damping device under various bearing loads.

10. The oil passage hole angle combination optimization design method of the elastic ring type squeeze oil film damper according to claim 9, characterized by, The elastic deformation results are used to calculate the vibration response of the rotor system of the oil seepage hole damping device with different angles in the operating speed range.

Images