CN114925473A - Modal simulation method and system of suspension support - Google Patents
Modal simulation method and system of suspension support Download PDFInfo
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Abstract
The invention relates to a modal simulation method and a modal simulation system of a suspension bracket, wherein the method comprises the following steps: establishing a CAD model of the suspension bracket; establishing a finite element model; setting constraint conditions of the finite element model; setting the initial dynamic stiffness of a bolt mounting hole of the finite element model; setting an initial additional mass; carrying out modal analysis on the finite element model to obtain a simulation result; carrying out whole vehicle modal test on the suspension bracket to obtain a modal test result; performing benchmarking on the simulation result and the modal test result, judging whether the errors of the modal frequency and the mode shape of the simulation result and the modal test result reach preset precision, and obtaining the optimal dynamic stiffness and the optimal additional mass as modal analysis results; obtaining modal analysis results of other suspension supports; and performing modal benchmarking analysis and solidifying simulation specifications according to modal analysis results of all the suspension supports. The method and the system accurately acquire the state modal level of the whole vehicle of the suspension bracket, and ensure that the development requirement of NVH riding comfort is met.
Description
Technical Field
The invention relates to the field of modal analysis of vehicle parts, in particular to a modal simulation method and a modal simulation system of a suspension bracket.
Background
With the development of scientific technology and the improvement of living standard, consumers pay more attention to riding comfort, and a pure electric vehicle with better comfort becomes the mainstream direction of the future development of the vehicle. The vibration isolation characteristic of the suspension system plays an important role in the riding comfort of the automobile, the vibration isolation design is not good, and the noise vibration of the power source can be transmitted to all parts of the automobile, so that the riding comfort of a driver and passengers is directly influenced. The suspension system with good performance is designed as an important component of the whole vehicle and is a key technology for reducing vibration and noise of the power assembly, and the suspension system with good performance can not only reduce the transmission of vibration to a vehicle body, reduce the noise in the vehicle and improve the riding comfort, but also better protect the power assembly. In order to achieve good vibration isolation, the lowest modal frequency of the suspension mount should be greater than 500 Hz. Through the modal lifting of the suspension system, the vibration transmitted to the vehicle body by the vibration generated by the power assembly can be effectively reduced within the reasonable rotating speed and torque range of power output, and the comfort of the whole vehicle is improved.
Due to the characteristics of few parts, simple assembly of a simulation model and the like of the vehicle suspension system, the type and the size of a grid unit and the model construction can adopt a high-precision simulation scheme, so that boundary conditions and model simplification become the most important factors influencing the modal simulation precision of the vehicle suspension support.
The method comprises the steps that early-stage CAE simulation control is adopted by a plurality of suspension suppliers or host factories, and the traditional suspension support modal analysis comprises a free modal analysis method without any constraint condition, a ground constraint modal analysis method with bolt rigidity fixed constraint and a vehicle constraint modal analysis method with bolt holes and ground elastic connection constraint, wherein the two analysis methods are suspension single body control, and the influence of the constraint condition, additional mass and rigidity under the state of the whole vehicle on the suspension support modal is not fully considered; the method for analyzing the vehicle constraint mode of the bolt hole and ground elastic connection constraint needs to model a power assembly grid and a whole vehicle, the front and back processing cost is long, the cost is high, the design process is not insufficient for error control compared with test data, the simulation difference of later-stage real vehicle test on the standard is larger in the earlier stage, the influence difference reason of the state of the whole vehicle cannot be effectively checked, and early-stage risk assessment and design redundancy reservation cannot be effectively supported.
The improvement of the modal analysis precision of the suspension support in the finished automobile mounting state has an important engineering function, and the accurate calculation of the suspension modal in the finished automobile mounting state is of great significance to NVH (noise, vibration and harshness) real automobile tuning and education and the requirement of ensuring NVH riding comfort development.
Disclosure of Invention
The invention aims to provide a modal simulation method and a modal simulation system for a suspension bracket, which improve simulation precision by optimizing constraint conditions, additional mass, rigidity and other boundaries, accurately acquire the modal level of the suspension bracket in a finished automobile state and ensure that the requirement of developing the riding comfort of NVH is met.
The invention provides a modal simulation method of a suspension bracket on one hand, which comprises the following steps:
s1: acquiring input parameters of a suspension bracket;
s2: establishing a CAD model of the suspension bracket according to the input parameters of the suspension bracket;
s3: establishing a finite element model according to the CAD model of the suspension bracket;
s4: setting constraint conditions of the finite element model;
s5: setting the initial dynamic stiffness of the bolt mounting hole of the finite element model;
s6: setting initial additional mass of the finite element model;
s7: carrying out modal analysis on the finite element model to obtain a simulation result;
s8: carrying out the whole vehicle modal test on the suspension bracket to obtain a modal test result;
s9: performing benchmarking on the simulation result in the step S7 and the modal test result in the step S8, and judging whether the errors of the modal frequency and the mode shape of the simulation result and the modal test result reach preset precision; if so, taking the initial dynamic stiffness and the initial additional mass as the optimal dynamic stiffness and the optimal additional mass; if not, adjusting the initial dynamic stiffness and the initial additional mass of the finite element model and carrying out modal analysis until the errors of the modal frequency and the vibration mode of the obtained simulation result and the modal test result reach the preset precision, so as to obtain the optimal dynamic stiffness and the optimal additional mass; the obtained optimal dynamic stiffness and the optimal additional mass are used as modal analysis results of the suspension bracket;
s10: repeating the steps S1-S9 for other suspension supports of the same platform vehicle type to obtain modal analysis results of the other suspension supports;
s11: and performing modal benchmarking analysis according to modal analysis results of all the suspension supports of the same platform vehicle type, and solidifying simulation specifications according to the modal benchmarking analysis results of all the suspension supports.
Further, the input parameters include a bolt mounting hole position of the power assembly, an aperture, a suspension elastic center point position of the driving end, a bolt mounting hole position of the driven end, elastic bushing design rigidity and surrounding space arrangement envelope information.
Further, step S3 further includes: and importing the CAD model into finite element software, and performing meshing to obtain a finite element model.
Further, the finite element software is NASTRAN, when the finite element model is established, the mesh size of the suspension bracket is set to be 3-4mm, the unit types are set to be second-order tetrahedral units, bolts are set to be Beam units, and Rbe2 units are adopted to connect the suspension bracket.
Further, step S4 includes: and the power assembly is equivalently replaced by the CBUSH unit, one end of the CBUSH unit is connected with a bolt Rbe2 main point of the finite element model, and the other end of the CBUSH unit restrains all directional degrees of freedom.
Further, in step S5, the initial dynamic stiffness includes an initial translational stiffness and an initial rotational stiffness, the initial translational stiffness is set to 200KN/mm, and the initial rotational stiffness is set to 40000 KN/mm.
Further, in step S6, the initial additional mass is a concentrated mass added in the bolt mounting hole, the concentrated mass being half of the total mass of the active end bracket, the rubber, the inner frame, and the main spring frame.
Further, in step S9, the preset accuracy is that the error between the modal frequency and the mode shape of the simulation result and the modal test result is less than 5%.
Further, in step S9, the initial translational stiffness is adjusted at an amplitude of 20KN/mm, the initial rotational stiffness is adjusted at an amplitude of 4000KN/mm, and the initial additional mass is adjusted at an upper and lower deviation of 20%.
Another aspect of the present invention provides a modal simulation system of a suspension mount, including:
the acquisition module is used for acquiring input parameters of the suspension bracket through project product definition;
the modeling module is used for establishing a CAD model of the suspension bracket according to the input parameters;
a finite element module configured to establish a finite element model according to the CAD model of the suspension bracket;
the setting module is used for setting the constraint conditions of the finite element model, the initial dynamic stiffness and the initial additional mass of the bolt mounting hole;
the modal analysis module is configured to perform modal analysis on the finite element model and obtain a simulation result;
the modal testing module is used for carrying out overall vehicle modal testing on the suspension bracket and obtaining a modal testing result;
the optimization module is used for performing benchmarking analysis on the simulation result and the modal test result, adjusting the initial dynamic stiffness and the initial additional mass according to the analysis result, and obtaining the optimal dynamic stiffness and the optimal additional mass as modal analysis results of the suspension bracket;
and the specification establishing module is configured to obtain modal analysis results of all suspension supports of the same platform vehicle type, perform modal benchmarking analysis, and solidify simulation specifications according to the modal benchmarking analysis results of all suspension supports.
According to the modal simulation method and system of the suspension bracket, a CBUSH unit is adopted to equivalently replace a power assembly, one end of the CBUSH unit is connected with a bolt Rbe2 main point of a finite element model, and the other end of the CBUSH unit restrains all directional degrees of freedom, so that the addition of a restraint condition under the state of a whole vehicle is realized; by optimizing the dynamic stiffness and the additional mass, the modal simulation result of the suspension bracket in the whole vehicle state meets the preset precision, and the requirement for developing the riding comfort of NVH is met.
Drawings
FIG. 1 is a flow chart of a method of modal simulation of a suspension mount according to an embodiment of the invention;
FIG. 2 is a schematic diagram of a modal simulation system of a suspension mount according to another embodiment of the present invention.
Detailed Description
The preferred embodiments of the present invention will be described in detail below with reference to the accompanying drawings.
As shown in fig. 1, an embodiment of the present invention provides a modal simulation method of a suspension bracket, including the following steps:
s1: acquiring input parameters of a suspension bracket;
the input parameters comprise the position and the aperture of a bolt mounting hole of the power assembly, the position of a suspended elastic central point of the power assembly, the position of a bolt mounting hole of a passive end of a vehicle body or an auxiliary frame and the like, the design rigidity of an elastic bushing and the arrangement envelope information of peripheral space, and the input parameters can be acquired through the definition of project products.
S2: establishing a CAD model of the suspension bracket according to the input parameters of the suspension bracket;
the suspension bracket comprises an active end bracket, a passive end bracket, an elastic bushing and a limiting block, and the well-established CAD model also comprises information such as the position of a bolt mounting hole, a reinforcing rib, the elastic modulus, the Poisson ratio and the density of materials of each component, the mass (the mass of a single piece, the mass of an assembly and the position of a mass center) of the suspension bracket and the like besides the structure. The reinforcing ribs are arranged in a combining space around the bolt mounting holes and the elastic bushings according to experience, the bolt mounting holes are determined according to matching mounting points of the power assembly, generally three to four bolt mounting holes are formed, the material of each part can be cast aluminum or cast steel, the parts with light weight requirements can be made of plastic materials, and the elastic bushings are made of rubber materials.
S3: establishing a finite element model according to the CAD model of the suspension bracket;
specifically, the CAD model is imported into finite element software, and meshing is carried out in the finite element software to obtain the finite element model.
In the embodiment, the finite element software is NASTRAN, when the grid is divided, the size of the grid is divided according to 3-4mm for the casting suspension bracket, and the type of the unit is a second-order tetrahedral unit; for the split type suspension bracket, bolts are required to build Beam units according to designed diameters, and Rbe2 units are used for connecting the bracket.
S4: setting constraint conditions of the finite element model;
in the embodiment, a CBUSH unit is used for equivalently replacing the power assembly, one end of the CBUSH unit is connected with a main point of a bolt Rbe2 of a finite element model, and the other end of the CBUSH unit restrains all directional freedom degrees, so that the addition of the restraint condition in the state of the whole vehicle is realized.
S5: setting the initial dynamic stiffness of a bolt mounting hole of the finite element model;
specifically, a Beam unit is established in a bolt mounting hole of the finite element model according to a design diameter, a CBUSH unit is established, wherein the Beam unit contributes to the rigidity and the mass of a bolt, the CUBSH unit is used for contributing to the rigidity of the bolt mounting hole of the suspension bracket on the power assembly, the equivalent dynamic rigidity is input as unit rigidity, and the initial dynamic rigidity is set according to the initial translational rigidity of 200KN/mm and the initial rotational rigidity of 40000 KN/mm.
S6: setting initial additional mass of the finite element model;
specifically, the total mass of the active end bracket, the rubber, the inner frame and the main spring frame is weighed, and a concentrated mass which is half of the total mass of the active end bracket, the rubber, the inner frame and the main spring frame is added to the bolt mounting hole, so that the additional mass is set;
s7: carrying out modal analysis on the finite element model to obtain a simulation result;
after the initial dynamic stiffness and the initial additional mass are added, modal analysis can be performed in finite element software, and then a simulation result, namely the mode of the first six-order suspension bracket, is output.
S8: carrying out the whole vehicle modal test on the suspension bracket to obtain a modal test result;
specifically, the test is performed by two states of bolt connection and bolt disconnection at the elastic bushings of the driving end support and the driven end support respectively, so as to obtain modal test results in the two states.
S9: performing benchmarking on the simulation result in the step S7 and the modal test result in the step S8, and judging whether the errors of the modal frequency and the mode shape of the simulation result and the modal test result reach preset precision; if so, taking the initial dynamic stiffness and the initial additional mass as the optimal dynamic stiffness and the optimal additional mass; if not, adjusting the initial dynamic stiffness and the initial additional mass of the finite element model and carrying out modal analysis until the obtained errors of the modal frequency and the vibration mode of the simulation result and the modal test result reach preset precision to obtain the optimal dynamic stiffness and the optimal additional mass; the obtained optimal dynamic stiffness and the optimal additional mass are used as modal analysis results of the suspension bracket;
the preset precision can be set to be less than 5% of the error between the modal frequency and the mode shape of the finite element model, so that the performance NVH development requirement is met, and when the simulation result meets the preset precision, the precision of the finite element model can be guaranteed.
When the error is not less than 5%, the accuracy limited to the model is insufficient, and the accuracy is required to meet the requirement by adjusting the values of the initial dynamic stiffness and the initial additional mass. Specifically, the initial translational stiffness is adjusted by the amplitude of 20KN/mm, the initial rotational stiffness is adjusted by the amplitude of 4000KN/mm, and the initial additional mass is adjusted by the upper and lower deviations of 20%; for example, when the modal frequency and the vibration mode of the simulation result are greater than 5% of the modal test result, the initial translational stiffness is increased by 20KN/mm, the initial rotational stiffness is increased by 4000KN/mm, the modal analysis is performed after the initial additional mass is increased by 20%, the obtained result is compared with the modal test result, otherwise, when the modal frequency and the vibration mode of the simulation result are less than the modal test result, the initial translational stiffness is decreased by 20KN/mm, the initial rotational stiffness is decreased by 4000KN/mm, the modal analysis is performed after the initial additional mass is decreased by 20%, the simulation result meets the preset precision through repeated adjustment, and the dynamic stiffness and the additional mass at the moment are the optimal dynamic stiffness and the optimal additional mass.
S10: repeating the steps S1-S9 for other suspension supports of the same platform vehicle type to obtain the optimal dynamic stiffness and the optimal additional mass of the other suspension supports;
s11: and performing modal benchmarking analysis according to modal analysis results of all suspension supports of the same platform vehicle type, and solidifying simulation specifications according to the modal benchmarking analysis results of all suspension supports.
The optimal dynamic stiffness and the optimal additional mass are obtained by adjusting the dynamic stiffness and the additional mass of different suspension supports and repeatedly aligning and optimizing the dynamic stiffness and the additional mass with a test result, so that a solidified simulation specification is formed, different people can be ensured to make similar or identical results, and the NVH performance development is supported.
According to the modal simulation method of the suspension bracket, a CBUSH unit is adopted to equivalently replace a power assembly, one end of the CBUSH unit is connected with a bolt Rbe2 main point of a finite element model, and the other end of the CBUSH unit restrains all directional degrees of freedom, so that the addition of a restraint condition under the state of a whole vehicle is realized; by optimizing the dynamic stiffness and the additional mass, the modal simulation result of the suspension bracket in the whole vehicle state meets the preset precision, and the requirement for developing the riding comfort of NVH is met.
As shown in fig. 2, another embodiment of the present invention provides a modal simulation system of a suspension bracket, which can implement the modal simulation method of the suspension bracket of the above embodiment, including:
an acquisition module 100 configured to acquire input parameters through project product definitions;
a modeling module 200 configured to establish a CAD model of the suspension bracket according to the input parameters;
a finite element module 300 configured to build a finite element model from the CAD model of the suspension mount;
the setting module 400 is used for setting constraint conditions of the finite element model, initial dynamic stiffness and initial additional mass of the bolt mounting hole and the like;
a modal analysis module 500 configured to perform modal analysis on the finite element model and obtain a simulation result;
the modal testing module 600 is configured to perform a whole vehicle modal test on the suspension bracket and obtain a modal test result;
the optimization module 700 is configured to perform benchmarking analysis on the simulation result and the modal test result, and adjust the initial dynamic stiffness and the initial additional mass according to the analysis result to obtain an optimal dynamic stiffness and an optimal additional mass as modal analysis results of the suspension bracket;
the specification establishing module 800 is configured to obtain modal analysis results of all suspension brackets of the same platform vehicle type, perform modal benchmarking analysis, and solidify simulation specifications according to the modal benchmarking analysis results of all suspension brackets.
The specific implementation method of each module is the same as that in the previous embodiment, and is not described herein again.
The modal simulation system of the suspension bracket provided by the embodiment of the invention can realize the modal simulation method of the suspension bracket of the previous embodiment, a CBUSH unit is adopted to equivalently replace a power assembly, one end of the CBUSH unit is connected with a bolt Rbe2 main point of a finite element model, and the other end of the CBUSH unit restrains all directional freedom degrees, thereby realizing the addition of the restraint condition under the state of the whole vehicle; by optimizing the dynamic stiffness and the additional mass, the modal simulation result of the suspension bracket in the whole vehicle state meets the preset precision, and the requirement for developing the riding comfort of NVH is met.
The foregoing description and description of the embodiments are provided to facilitate understanding and application of the invention by those skilled in the art. It will be readily apparent to those skilled in the art that various modifications can be made to these teachings and the generic principles described herein may be applied to other embodiments without the use of the inventive faculty. Therefore, the present invention is not limited to the above description and the description of the embodiments, and those skilled in the art should make improvements and modifications within the scope of the present invention based on the disclosure of the present invention.
Claims (10)
1. A modal simulation method of a suspension bracket is characterized by comprising the following steps:
s1: acquiring input parameters of a suspension bracket;
s2: establishing a CAD model of the suspension bracket according to the input parameters of the suspension bracket;
s3: establishing a finite element model according to the CAD model of the suspension bracket;
s4: setting constraint conditions of the finite element model;
s5: setting the initial dynamic stiffness of a bolt mounting hole of the finite element model;
s6: setting initial additional mass of the finite element model;
s7: carrying out modal analysis on the finite element model to obtain a simulation result;
s8: carrying out the whole vehicle modal test on the suspension bracket to obtain a modal test result;
s9: performing benchmarking on the simulation result in the step S7 and the modal test result in the step S8, and judging whether the errors of the modal frequency and the mode shape of the simulation result and the modal test result reach preset precision; if so, taking the initial dynamic stiffness and the initial additional mass as the optimal dynamic stiffness and the optimal additional mass; if not, adjusting the initial dynamic stiffness and the initial additional mass of the finite element model and carrying out modal analysis until the obtained errors of the modal frequency and the vibration mode of the simulation result and the modal test result reach preset precision to obtain the optimal dynamic stiffness and the optimal additional mass; the obtained optimal dynamic stiffness and the optimal additional mass are used as a modal analysis result of the suspension bracket;
s10: repeating the steps S1-S9 for other suspension brackets of the same platform vehicle type to obtain modal analysis results of the other suspension brackets;
s11: and performing modal benchmarking analysis according to modal analysis results of all the suspension supports of the same platform vehicle type, and solidifying simulation specifications according to the modal benchmarking analysis results of all the suspension supports.
2. The modal simulation method of a suspension mount of claim 1, wherein the input parameters comprise a bolt mounting hole position of a powertrain, an aperture, a suspended elastic center point position of an active end, a bolt mounting hole position of a passive end, an elastic bushing design stiffness and peripheral space arrangement envelope information.
3. The modal simulation method of a suspension mount of claim 1, wherein step S3 further comprises: and importing the CAD model into finite element software, and performing mesh division to obtain a finite element model.
4. The modal simulation method of the suspension bracket of claim 3, wherein the finite element software is NASTRAN, when the finite element model is established, the mesh size of the suspension bracket is set to be 3-4mm, the element types are set to be second-order tetrahedral elements, bolts are set to be Beam elements, and Rbe2 elements are adopted to connect the suspension bracket.
5. The modal simulation method of a suspension bracket of claim 3, wherein step S4 comprises: and the power assembly is equivalently replaced by the CBUSH unit, one end of the CBUSH unit is connected with a bolt Rbe2 main point of the finite element model, and the other end of the CBUSH unit restrains all directional degrees of freedom.
6. The modal simulation method of a suspension mount of claim 1, wherein the initial dynamic stiffness comprises an initial translational stiffness and an initial rotational stiffness, the initial translational stiffness is set to 200KN/mm, and the initial rotational stiffness is set to 40000KN/mm in step S5.
7. The modal simulation method of a suspension bracket of claim 1, wherein in step S6, the initial additional mass is a concentrated mass added in the bolt mounting hole, the concentrated mass being half of the total mass of the active end bracket, the rubber, the inner frame and the main spring frame.
8. The modal simulation method of a suspension bracket of claim 1, wherein in step S9, the preset precision is that the modal frequency and the mode shape of the simulation result and the modal test result have an error of less than 5%.
9. The modal simulation method of a suspension mount of claim 6, wherein in step S9, the initial translational stiffness is adjusted with an amplitude of 20KN/mm, the initial rotational stiffness is adjusted with an amplitude of 4000KN/mm, and the initial additional mass is adjusted with an upper and lower deviation of 20%.
10. A modal simulation system of a suspension mount, comprising:
the acquisition module is used for acquiring input parameters of the suspension bracket through project product definition;
the modeling module is used for establishing a CAD model of the suspension bracket according to the input parameters;
a finite element module configured to establish a finite element model according to the CAD model of the suspension bracket;
the setting module is used for setting the constraint conditions of the finite element model, the initial dynamic stiffness and the initial additional mass of the bolt mounting hole;
the modal analysis module is configured to perform modal analysis on the finite element model and obtain a simulation result;
the modal testing module is used for carrying out the whole vehicle modal test on the suspension bracket and obtaining a modal test result;
the optimization module is used for performing benchmarking analysis on the simulation result and the modal test result, adjusting the initial dynamic stiffness and the initial additional mass according to the analysis result, and obtaining the optimal dynamic stiffness and the optimal additional mass as modal analysis results of the suspension bracket;
and the specification establishing module is configured to obtain modal analysis results of all suspension supports of the same platform vehicle type, perform modal benchmarking analysis, and solidify simulation specifications according to the modal benchmarking analysis results of all suspension supports.
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103678749A (en) * | 2012-09-24 | 2014-03-26 | 重庆长安汽车股份有限公司 | Finite element analysis method of automobile pull rod type suspension |
| CN111985044A (en) * | 2019-05-23 | 2020-11-24 | 上海汽车集团股份有限公司 | Method and device for analyzing rigidity of transverse stabilizer bar |
| CN112182697A (en) * | 2020-09-15 | 2021-01-05 | 河海大学 | High-precision dynamic measurement method for system tension of damping suspender |
| CN112765724A (en) * | 2020-12-29 | 2021-05-07 | 浙江合众新能源汽车有限公司 | Automobile damping patch position optimization method and system |
| CN113239458A (en) * | 2021-04-26 | 2021-08-10 | 中汽研汽车检验中心（天津）有限公司 | Whole vehicle road noise simulation benchmarking method based on virtual road surface |
-
2022
- 2022-05-30 CN CN202210601540.XA patent/CN114925473B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103678749A (en) * | 2012-09-24 | 2014-03-26 | 重庆长安汽车股份有限公司 | Finite element analysis method of automobile pull rod type suspension |
| CN111985044A (en) * | 2019-05-23 | 2020-11-24 | 上海汽车集团股份有限公司 | Method and device for analyzing rigidity of transverse stabilizer bar |
| CN112182697A (en) * | 2020-09-15 | 2021-01-05 | 河海大学 | High-precision dynamic measurement method for system tension of damping suspender |
| CN112765724A (en) * | 2020-12-29 | 2021-05-07 | 浙江合众新能源汽车有限公司 | Automobile damping patch position optimization method and system |
| CN113239458A (en) * | 2021-04-26 | 2021-08-10 | 中汽研汽车检验中心（天津）有限公司 | Whole vehicle road noise simulation benchmarking method based on virtual road surface |
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