CN114608840A - Decoupling whole vehicle state power assembly rigid body modal anti-drag test bench - Google Patents
Decoupling whole vehicle state power assembly rigid body modal anti-drag test bench Download PDFInfo
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- CN114608840A CN114608840A CN202210272086.8A CN202210272086A CN114608840A CN 114608840 A CN114608840 A CN 114608840A CN 202210272086 A CN202210272086 A CN 202210272086A CN 114608840 A CN114608840 A CN 114608840A
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- 239000000725 suspension Substances 0.000 claims abstract description 42
- 230000003068 static effect Effects 0.000 claims abstract description 19
- 230000005540 biological transmission Effects 0.000 claims description 18
- 230000005284 excitation Effects 0.000 abstract description 9
- 238000000034 method Methods 0.000 abstract description 4
- 238000010586 diagram Methods 0.000 description 3
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- 238000005259 measurement Methods 0.000 description 2
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M17/00—Testing of vehicles
- G01M17/007—Wheeled or endless-tracked vehicles
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M7/00—Vibration-testing of structures; Shock-testing of structures
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- G01M7/06—Multidirectional test stands
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Abstract
The invention discloses a reverse-dragging test bed for decoupling rigid body mode of a power assembly in a whole vehicle state, which comprises a bracket, three bed suspensions, a motor, a power supply module and a rotating speed control module, wherein the three bed suspensions are arranged on the bracket; the rack suspensions are respectively fixed on the upper end surfaces of the brackets; the motor is fixed on the upper end face of the bracket; the power supply module is electrically connected with the motor through a lead; the rotating speed control module is electrically connected with the motor through a lead; the three racks are suspended, and the static rigidity of the three racks is in the X direction: 340N/mm-460N/mm, static stiffness Y direction: 340N/mm-460N/mm, static stiffness Z direction: 1700N/mm-2300N/mm; the rigid body mode of the power assembly is improved to be above the first-order excitation range of the idle speed of the engine, resonance of the power assembly can be avoided under the idle speed, the accuracy of the vibration test result of the power assembly is ensured, meanwhile, the time for replacing the power assembly parts on the rack is short, and compared with the method for replacing the power assembly parts in the state of a whole vehicle, the replacement time is greatly saved.
Description
Technical Field
The invention relates to an automobile power assembly testing device, in particular to a reverse-dragging test bed frame for decoupling a rigid body mode of a whole automobile state power assembly.
Background
The idling working condition of the engine is an important working condition of the vehicle, and the seat vibration under the idling working condition is an important NVH performance index of the whole vehicle; the main frequency components of the seat vibration are engine speed second order vibration and first order vibration. The reason that the first-order vibration of the engine of the power assembly is large is complex, and the first-order vibration of the power assembly is influenced mainly by the dynamic balance of rotating parts, the axis alignment and combination process of the engine and a transmission and the like.
When studying the main influencing factors of the first-order vibration of different assemblies, the problem exists if the power assembly is arranged on the whole vehicle for vibration testing. Most vehicles have the idle speed of 650-750 r/min, so the first-order vibration frequency component of the engine speed is 10.8-12.5 Hz, which is just the same as the rigid body mode range of the power assembly. Therefore, the first-order excitation of the power assembly in the state of the whole vehicle can cause the resonance of the whole power assembly, and when the influence factors of the power assembly on the first-order vibration are researched, the deviation can be generated on the vibration measuring point result of the power assembly.
The NVH performance of the whole automobile is seriously influenced by the first-order vibration of the rotating speed of the idling engine, and the idling engine is more and more concerned by various automobile manufacturers; however, most manufacturers still research the problems based on the state of the whole vehicle, which can not only ensure the accuracy of the vibration test of the power assembly but also waste time; therefore, the vibration test of the idle speed and the rotation speed is required to be carried out on the power assembly rack, and meanwhile, the rack suspension reasonably matched with the power assembly is required to decouple the rigid body mode of the power assembly from the rigid body mode of the whole vehicle state power assembly.
Most of the current power assembly back-dragging test bed has the functions of checking whether the state of a part is normal or not and not matching a power assembly suspension system, so that the back-dragging test bed with decoupling vehicle state power assembly rigid body mode does not exist.
Disclosure of Invention
In order to solve the problems, the invention provides a reverse-dragging test bench for decoupling the rigid body mode of a power assembly in the whole vehicle state, which improves the rigid body mode of the power assembly to be above the first-order excitation range of the idle speed of an engine, namely 10.8Hz-12.5Hz, can avoid the power assembly from generating resonance at the idle speed, ensures the accuracy of the vibration test result of the power assembly, achieves the aim of decoupling the rigid body mode of the power assembly in the whole vehicle state, has short time for replacing components of the power assembly on the bench, and greatly saves the replacement time compared with the replacement of components of the power assembly in the whole vehicle state.
The invention relates to a reverse-dragging test bed for decoupling rigid body mode of a power assembly in a whole vehicle state, which comprises a bracket, three bed suspensions, a motor, a power supply module and a rotating speed control module, wherein the three bed suspensions are arranged on the bracket;
the bracket is composed of a first bracket, a second bracket, a third bracket and a motor bracket, and the bracket is used for supporting the motor and suspending the rack so as to fix the motor and the power assembly;
the platform suspension is respectively fixed on the upper end surfaces of the first support, the second support and the third support, and the rigid body mode of the power assembly in the platform state is higher than 10.8Hz-12.5Hz of a first-order excitation range of idle speed rotation speed through suspension matching, so that the purpose of decoupling the rigid body mode of the power assembly in the whole vehicle state is achieved;
the motor is fixed on the upper end face of the motor support and used as a power source of the whole test bench, and power is transmitted to the belt through the motor belt pulley to achieve the anti-dragging rotating speed required by the test;
the power supply module is electrically connected with the motor through a lead and provides power for the motor;
the rotating speed control module is electrically connected with the motor through a lead and controls the rotating speed and the forward rotation and the reverse rotation of the motor through a controller;
the three rack suspensions have the same parameters, and the static rigidity of each rack suspension is in the X direction: 340N/mm-460N/mm, static stiffness Y direction: 340N/mm-460N/mm, static stiffness Z direction: 1700N/mm-2300N/mm, when the static stiffness values of the three rubber blocks in the X direction, the Y direction and the Z direction are in the value ranges, the rigid body mode of the power assembly is improved to be above the first-order excitation range of the idle speed of the engine, namely 10.8Hz-12.5Hz, resonance of the power assembly can be avoided under the idle speed, the accuracy of the vibration test result of the power assembly is ensured, and the purpose of decoupling the rigid body mode of the power assembly in the whole vehicle state is achieved.
Each rack is suspended into a rubber block, and the dynamic and static rigidity ratio of the rubber block is 1.5.
The rack suspension is fixed with the first support, the second support and the third support in a screwing mode through bolts.
The first support, the second support, the third support and the motor support are all T-shaped structures, and each T-shaped structure is composed of a horizontal supporting surface and a supporting rod vertically arranged in the middle of the lower end face of the horizontal supporting surface.
The vertical height of the first support is higher than that of the second support, and the vertical height of the second support is higher than that of the third support.
The utility model provides a decoupling zero puts in order car state power assembly rigid body modal anti-dragging test bench, still includes power assembly and belt, power assembly respectively with rack suspension fixed connection on first support, second support and the third support, the belt pulley of power assembly passes through the belt and is connected with the drive wheel transmission of motor, the belt transmits the belt pulley of power assembly to the power of the drive wheel of motor, reaches the anti-rotational speed that holds in the palm of experimental demand.
The power assembly comprises an engine and a transmission, a front connecting arm is arranged on the rear side wall of the front part of the engine in a protruding mode, and the front end of the front connecting arm is screwed and fixed with the upper end face of the rack suspension at the upper end of the first support; the lower side wall of the middle part of the engine is provided with an engine supporting part which is screwed and fixed with the upper end surface of the rack suspension at the upper end of the third bracket; the transmission supporting part is arranged on the lower side wall of the rear part of the transmission and is screwed and fixed with the upper end face of the rack suspension at the upper end of the second support, and the engine and the transmission are respectively screwed and fixed with the three rack suspensions, so that the time for replacing the power assembly part on the rack is short.
Advantageous effects
The rigid body mode of the power assembly is improved to be above the first-order excitation range of 10.8Hz-12.5Hz of the idle speed of the engine, resonance of the power assembly can be avoided under the idle speed, the accuracy of the vibration test result of the power assembly is ensured, the purpose of decoupling the rigid body mode of the power assembly in the whole vehicle state is achieved, meanwhile, the time for replacing parts of the power assembly on the rack is short, and compared with the method for replacing parts of the power assembly in the whole vehicle state, the method greatly saves the replacing time.
Drawings
FIG. 1 is a schematic structural diagram of an embodiment of the present invention.
Fig. 2 is a schematic structural diagram of a second embodiment of the present invention.
FIG. 3 is a diagram of the calculation result distribution of the rigid body modal back-dragging test bed of the power assembly of the present invention.
In the figure:
1. a support;
11. a first bracket;
12. a second bracket;
13. a third support;
14. a motor bracket;
2. suspending a rack;
3. a motor;
31. a driving wheel;
4. a power supply module;
5. a rotation speed control module;
6. a power assembly;
61. an engine;
611. a belt pulley;
612. a front linkage arm;
613. an engine support portion;
62. a transmission;
621. a transmission support portion;
7. a belt.
Detailed Description
In order to make the technical problems solved, the technical solutions adopted and the technical effects achieved by the present invention clearer, the technical solutions of the present invention are further described below by way of specific embodiments with reference to the accompanying drawings. It is to be understood that the specific embodiments described herein are merely illustrative of the invention and are not limiting of the invention. It should be further noted that, for the convenience of description, only some but not all of the elements associated with the present invention are shown in the drawings.
In the description of the present invention, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplification of description, but do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance. Wherein the terms "first position" and "second position" are two different positions.
In the description of the present invention, it should be noted that unless otherwise explicitly stated or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection or a removable connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
Example 1
Referring to fig. 1, the back-dragging test bench for decoupling the rigid body mode of the complete vehicle state power assembly comprises a support 1, three bench suspensions 2, a motor 3, a power supply module 4 and a rotating speed control module 5;
the bracket 1 consists of a first bracket 11, a second bracket 12, a third bracket 13 and a motor bracket 14;
the rack suspension 2 is respectively fixed at the upper end faces of the first support 11, the second support 12 and the third support 13;
the motor 3 is fixed on the upper end face of the motor bracket 14;
the power supply module 4 is electrically connected with the motor 3 through a lead;
the rotating speed control module 5 is electrically connected with the motor 3 through a lead;
the three gantry suspensions 2 have the same parameters, and the static stiffness thereof in the X direction: 400N/mm, static stiffness Y direction: 400N/mm, static stiffness Z direction: 2000N/mm.
Each rack suspension 2 is a rubber block, and the dynamic-static rigidity ratio of the rubber block is 1.5.
The gantry suspension 2 is screwed and fixed to the first bracket 11, the second bracket 12, and the third bracket 13 by bolts, respectively.
The first support 11, the second support 12, the third support 13 and the motor support 14 are all T-shaped structures, and each T-shaped structure is composed of a horizontal supporting surface and a supporting rod vertically arranged in the middle of the lower end face of the horizontal supporting surface.
The vertical height of the first bracket 11 is higher than that of the second bracket 12, and the vertical height of the second bracket 12 is higher than that of the third bracket 13.
Referring to fig. 3, the modes corresponding to 6 degrees of freedom of the powertrain are calculated according to parameters such as suspension stiffness, arrangement position, arrangement angle, powertrain mass, inertia distribution, center of mass position and the like; ensuring that 6 rigid body modal frequencies of the power assembly in the rack state are higher than 12.5Hz, thereby avoiding the resonance of the power assembly; as can be seen from the above table, for a certain longitudinally-arranged powertrain, when 3 suspensions with the same parameters are matched, the static stiffness in the X direction is as follows: 400N/mm, static stiffness Y direction: 400N/mm, static stiffness Z direction: 2000N/mm, the ratio of dynamic stiffness to static stiffness is 1.5, the rigid body modal calculation results matched with the parameter suspension are that the rigid body modal frequencies of the power assembly are 13.12Hz, 13.79Hz, 22.05Hz, 25.48Hz, 31.51Hz and 40.49Hz, the numerical values corresponding to the abscissa in the table are the calculated rigid body modal of the power assembly, and the rigid body modal of the power assembly in the rack state can be higher than the first-order excitation range of the idle speed through reasonable suspension matching.
After the calculated rigid body mode of the power assembly meets the first-order excitation higher than the idle speed, a calculation result verification test is required; mounting the power assembly on the rack through a suspension satisfying the calculation result, performing a rigid body modal test on the power assembly, and testing the rigid body modal result of the power assembly in the rack state; the measured rigid body mode result of the power assembly also meets the first-order excitation higher than the idle speed, and the result proves that the rigid body mode of the rack meets the use requirement; and if the actual measurement result of the rigid body mode of the power assembly does not meet the requirement, adjusting the rigidity of the suspension, and then performing the rigid body mode test of the power assembly again until the actual measurement result of the rigid body mode of the power assembly meets the requirement.
Example 2
Referring to fig. 2, a back-dragging test bed for decoupling rigid body mode of a vehicle state power assembly is different from that in embodiment 1,
the utility model provides a decoupling zero puts up anti-test bench that drags of car state power assembly rigid body mode, still includes power assembly 6 and belt 7, power assembly 6 respectively with first support 11, second support 12 and the rack suspension 2 fixed connection on the third support 13, power assembly 6's belt pulley 611 is connected with the drive wheel 31 transmission of motor 3 through belt 7.
The power assembly 6 comprises an engine 61 and a transmission 62, a front connecting arm 612 is arranged on the rear side wall of the front part of the engine 61 in a protruding mode, and the front end of the front connecting arm 612 is screwed and fixed with the upper end face of the rack suspension 2 at the upper end of the first support 11; an engine support part 613 is arranged on the lower side wall of the middle part of the engine 61, and the engine support part 613 is screwed and fixed with the upper end surface of the stand suspension 2 at the upper end of the third bracket 13; the lower side wall of the rear part of the transmission 62 is provided with a transmission support 621, and the transmission support 621 is screwed and fixed with the upper end surface of the stand suspension 2 at the upper end of the second bracket 12.
While the invention has been particularly shown and described with reference to a preferred embodiment, it will be understood by those skilled in the art that various changes in form and detail may be made therein without departing from the spirit and scope of the invention as defined by the appended claims.
Claims (7)
1. The utility model provides a decoupling zero puts in order car state power assembly rigid body modal anti-dragging test bench which characterized in that: the device comprises a bracket (1), three platform suspension devices (2), a motor (3), a power supply module (4) and a rotating speed control module (5);
the bracket (1) is composed of a first bracket (11), a second bracket (12), a third bracket (13) and a motor bracket (14);
the rack suspension (2) is respectively fixed on the upper end surfaces of the first bracket (11), the second bracket (12) and the third bracket (13);
the motor (3) is fixed on the upper end face of the motor bracket (14);
the power supply module (4) is electrically connected with the motor (3) through a lead;
the rotating speed control module (5) is electrically connected with the motor (3) through a lead;
the parameters of the three gantry suspensions (2) are completely the same, and the static rigidity of each gantry suspension is in the X direction: 340N/mm-460N/mm, static stiffness Y direction: 340N/mm-460N/mm, static stiffness Z direction: 1700N/mm-2300N/mm.
2. The reverse-dragging test bed for decoupling rigid body modes of the complete vehicle state power assembly according to claim 1, characterized in that: each rack suspension (2) is a rubber block, and the dynamic and static rigidity ratio of the rubber block is 1.5.
3. The reverse-dragging test bed for decoupling rigid body modes of the complete vehicle state power assembly according to claim 2, characterized in that: the rack suspension (2) is fixed with the first support (11), the second support (12) and the third support (13) through bolts in a screwed mode.
4. The reverse-dragging test bed for decoupling rigid body modes of the complete vehicle state power assembly according to claim 2, characterized in that: the first support (11), the second support (12), the third support (13) and the motor support (14) are all T-shaped structures, and each T-shaped structure is composed of a horizontal supporting surface and a supporting rod vertically arranged in the middle of the lower end face of the horizontal supporting surface.
5. The reverse-dragging test bed for decoupling rigid body modes of the complete vehicle state power assembly according to claim 2, characterized in that: the vertical height of the first support (11) is higher than that of the second support (12), and the vertical height of the second support (12) is higher than that of the third support (13).
6. The reverse-dragging test bed for decoupling rigid body modes of the complete vehicle state power assembly according to claim 2, characterized in that: the utility model provides a decoupling complete car state power assembly rigid body modal anti-drag test bench, still includes power assembly (6) and belt (7), power assembly (6) respectively with rack suspension (2) fixed connection on first support (11), second support (12) and third support (13), belt pulley (611) of power assembly (6) are connected through belt (7) and drive wheel (31) transmission of motor (3).
7. The reverse-dragging test bed for decoupling rigid body modes of the complete vehicle state power assembly according to claim 6, characterized in that: the power assembly (6) comprises an engine (61) and a transmission (62), a front connecting arm (612) is arranged on the rear side wall of the front part of the engine (61) in a protruding mode, and the front end of the front connecting arm (612) is fixedly screwed with the upper end face of a rack suspension (2) at the upper end of the first support (11); an engine supporting part (613) is arranged on the lower side wall of the middle part of the engine (61), and the engine supporting part (613) is screwed and fixed with the upper end surface of the rack suspension (2) at the upper end of the third bracket (13); and a transmission supporting part (621) is arranged on the lower side wall of the rear part of the transmission (62), and the transmission supporting part (621) is screwed and fixed with the upper end surface of the rack suspension (2) at the upper end of the second bracket (12).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210272086.8A CN114608840B (en) | 2022-03-18 | Anti-test bench that drags of decoupling zero car state power assembly rigid body mode |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210272086.8A CN114608840B (en) | 2022-03-18 | Anti-test bench that drags of decoupling zero car state power assembly rigid body mode |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114608840A true CN114608840A (en) | 2022-06-10 |
| CN114608840B CN114608840B (en) | 2024-05-10 |
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Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201041529Y (en) * | 2006-12-31 | 2008-03-26 | 奇瑞汽车有限公司 | Drive assembly testing frame |
| CN201955234U (en) * | 2010-12-28 | 2011-08-31 | 中国第一汽车集团公司 | Centering adjustment device for engine bench |
| CN102323036A (en) * | 2011-08-31 | 2012-01-18 | 长城汽车股份有限公司 | Device for testing static torsional strength and vibration strength of transmission assembly |
| CN203519346U (en) * | 2013-11-06 | 2014-04-02 | 张金磊 | Blade electric vehicle power assembly test bench |
| CN104063549A (en) * | 2014-07-02 | 2014-09-24 | 湖南大学 | Method for matching power system and drive system based on vibration performance |
| CN104515661A (en) * | 2014-12-29 | 2015-04-15 | 安徽江淮汽车股份有限公司 | Method for measuring vibration contribution of suspension point |
| WO2015180476A1 (en) * | 2014-05-30 | 2015-12-03 | 长春轨道客车股份有限公司 | Device and method for testing vibration characteristics of railway vehicle |
| CN106033027A (en) * | 2015-03-09 | 2016-10-19 | 陕西重型汽车有限公司 | Rigid modal testing device and rigid modal testing method of heavy type automotive power assembly suspension system |
| DE102018010252A1 (en) * | 2018-02-14 | 2019-08-14 | Gesellschaft zur Förderung angewandter Informatik eV | Method and system for dynamic structural analysis |
| CN112362364A (en) * | 2020-11-27 | 2021-02-12 | 上海柴油机股份有限公司 | Dynamometer-based anti-dragging starting device and anti-dragging control method thereof |
| CN112697448A (en) * | 2020-08-24 | 2021-04-23 | 中国汽车技术研究中心有限公司 | Method for identifying driving side exciting force of power assembly suspension under vehicle idling working condition |
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201041529Y (en) * | 2006-12-31 | 2008-03-26 | 奇瑞汽车有限公司 | Drive assembly testing frame |
| CN201955234U (en) * | 2010-12-28 | 2011-08-31 | 中国第一汽车集团公司 | Centering adjustment device for engine bench |
| CN102323036A (en) * | 2011-08-31 | 2012-01-18 | 长城汽车股份有限公司 | Device for testing static torsional strength and vibration strength of transmission assembly |
| CN203519346U (en) * | 2013-11-06 | 2014-04-02 | 张金磊 | Blade electric vehicle power assembly test bench |
| WO2015180476A1 (en) * | 2014-05-30 | 2015-12-03 | 长春轨道客车股份有限公司 | Device and method for testing vibration characteristics of railway vehicle |
| CN104063549A (en) * | 2014-07-02 | 2014-09-24 | 湖南大学 | Method for matching power system and drive system based on vibration performance |
| CN104515661A (en) * | 2014-12-29 | 2015-04-15 | 安徽江淮汽车股份有限公司 | Method for measuring vibration contribution of suspension point |
| CN106033027A (en) * | 2015-03-09 | 2016-10-19 | 陕西重型汽车有限公司 | Rigid modal testing device and rigid modal testing method of heavy type automotive power assembly suspension system |
| DE102018010252A1 (en) * | 2018-02-14 | 2019-08-14 | Gesellschaft zur Förderung angewandter Informatik eV | Method and system for dynamic structural analysis |
| CN112697448A (en) * | 2020-08-24 | 2021-04-23 | 中国汽车技术研究中心有限公司 | Method for identifying driving side exciting force of power assembly suspension under vehicle idling working condition |
| CN112362364A (en) * | 2020-11-27 | 2021-02-12 | 上海柴油机股份有限公司 | Dynamometer-based anti-dragging starting device and anti-dragging control method thereof |
Non-Patent Citations (4)
| Title |
|---|
| 刘金琪: "动力总成悬置系统的性能优化与试验研究", 中国优秀硕士学位论文全文数据库 (工程科技Ⅱ辑), no. 2, 15 February 2020 (2020-02-15) * |
| 张燕;秦永舜;杨景玲;赵飞;李明建;翟若愚;: "动力总成异常振动测试与研究", 噪声与振动控制, no. 06, 18 December 2015 (2015-12-18) * |
| 张跃;崔根群;王海霞;: "农用柴油机动力总成刚体模态参数识别", 农机化研究, no. 08 * |
| 赵文杰;刘涛;唐培;: "基于悬置匹配的整车怠速抖动问题研究", 上海汽车, no. 10, 10 October 2020 (2020-10-10) * |
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