Method, device and equipment for improving shaking of hydraulic mount of power assembly and storage medium

Abstract

The invention discloses a power assembly hydraulic suspension jitter improvement method, device and equipment and a storage medium. The method comprises the steps that power assembly inertial parameters of a power assembly of a current vehicle are obtained; obtaining a hydraulic suspension load of the hydraulic suspension of the current vehicle according to the power assembly inertial parameter; according to the method, the resonance line of the power assembly is obtained, the dynamic stiffness curve of the hydraulic suspension load attached to the resonance line is obtained, and the target hydraulic parameters of the hydraulic suspension are set according to the dynamic stiffness curve, so that the power assembly can be used as a broadband vibration absorber for vehicle driving shaking, the vehicle driving shaking is effectively reduced, and the reliability of the vehicle driving shaking is improved. The later debugging work is avoided, the workload of low-frequency jitter improvement is reduced, and the jitter improvement speed and efficiency of the power assembly hydraulic mount are improved.

Description

Technical Field

[0001] The present invention relates to the field of automobile NVH technology, and in particular to a method, device, equipment and storage medium for improving the vibration of a powertrain hydraulic mount. Background Art

[0002] In recent years, with the intensified competition in the automobile market, automobile noise, vibration and harshness (NVH) issues have received more and more attention, among which the driving jitter problem is a pain point, mainly distributed below 20Hz.

[0003] In the existing technology, various companies mainly solve this type of problem from the excitation source by controlling tire parameters such as tire lateral force variation (LFV), radial force variation (RFV), and tire dynamic balance; some companies also use hydraulic suspension through the powertrain, and later adjust the peak frequency of the hydraulic suspension damping to modulate the amplitude and attenuate the vibration; however, both of the above methods require subsequent debugging, which is labor-intensive and cannot effectively reduce the vibration of the vehicle during driving. Summary of the invention

[0004] The main purpose of the present invention is to provide a method, device, equipment and storage medium for improving the vibration of the powertrain hydraulic suspension, aiming to solve the technical problems in the prior art that post-debugging is required, the workload is large, and the vibration during vehicle driving cannot be effectively reduced.

[0005] In a first aspect, the present invention provides a method for improving the vibration of a powertrain hydraulic mount, the method comprising the following steps:

[0006] Obtain the powertrain inertia parameters of the powertrain of the current vehicle;

[0007] Obtaining a hydraulic mount load of the hydraulic mount of the current vehicle according to the powertrain inertia parameter;

[0008] A resonance line of the powertrain is obtained, and a dynamic stiffness curve of the hydraulic mount load that matches the resonance line is acquired, and a target hydraulic parameter of the hydraulic mount is set according to the dynamic stiffness curve.

[0009] Optionally, the obtaining of the powertrain inertia parameter of the powertrain of the current vehicle includes:

[0010] The powertrain of the current vehicle is tested according to the preset powertrain digital model to obtain the powertrain inertia parameters.

[0011] Optionally, the testing of the powertrain of the current vehicle according to a preset powertrain digital model to obtain the powertrain inertia parameter includes:

[0012] The powertrain of the current vehicle is tested according to a preset powertrain digital model to obtain the mass, center of mass coordinates, moment of inertia in X direction, moment of inertia in Y direction, moment of inertia in Z direction, product of inertia in X direction, product of inertia in Y direction and product of inertia in Z direction of the powertrain, and the mass, the center of mass coordinates, the moment of inertia in X direction, the moment of inertia in Y direction, the moment of inertia in Z direction, the product of inertia in X direction, the product of inertia in Y direction and the product of inertia in Z direction are used as powertrain inertia parameters.

[0013] Optionally, obtaining the hydraulic mount load of the hydraulic mount of the current vehicle according to the powertrain inertia parameter includes:

[0014] Determining hard point coordinates of each suspension of the hydraulic mount of the current vehicle in a center of mass coordinate system of the power assembly according to the power assembly inertia parameter;

[0015] A hydraulic mount load of the hydraulic mount is determined based on the hard point coordinates.

[0016] Optionally, determining the hydraulic mount load of the hydraulic mount according to the hard point coordinates includes:

[0017] The hard point coordinates are input into the NVH installation optimization module to obtain the load borne by each suspension in the Z direction under static conditions, and the load borne is used as the hydraulic suspension load of the hydraulic suspension.

[0018] Optionally, obtaining the resonance line of the powertrain, acquiring a dynamic stiffness curve of the hydraulic mount load that matches the resonance line, and setting a target hydraulic parameter of the hydraulic mount according to the dynamic stiffness curve includes:

[0019] The mass and dynamic stiffness of the hydraulic mount are obtained, and the resonance frequency is calculated according to the mass and the dynamic stiffness by the following formula:

[0020]

[0021] Among them, f is the resonance frequency, K is the dynamic stiffness, and M is the mass;

[0022] When the dynamic stiffness satisfies the following preset design value formula, generating a resonance line of the powertrain according to the preset design value formula;

[0023] K=4π 2 M*f 2

[0024] Where K is the dynamic stiffness, M is the mass, and f is the resonance frequency;

[0025] A dynamic stiffness curve of the hydraulic mount load that matches the resonance line is obtained, and a target hydraulic parameter of the hydraulic mount is set according to the dynamic stiffness curve.

[0026] Optionally, the acquiring a dynamic stiffness curve of the hydraulic mount load that matches the resonance line, and setting a target hydraulic parameter of the hydraulic mount according to the dynamic stiffness curve, comprises:

[0027] Adjusting the initial hydraulic parameters of the hydraulic mount to obtain a dynamic stiffness curve of the hydraulic mount load that fits the resonance line;

[0028] A target hydraulic parameter of the hydraulic mount is set according to the dynamic stiffness curve.

[0029] In a second aspect, in order to achieve the above-mentioned purpose, the present invention further proposes a powertrain hydraulic mount vibration improvement device, the powertrain hydraulic mount vibration improvement device comprising:

[0030] A parameter acquisition module, used to acquire the powertrain inertia parameters of the powertrain of the current vehicle;

[0031] A load acquisition module, configured to obtain a hydraulic suspension load of the hydraulic suspension of the current vehicle according to the powertrain inertia parameter;

[0032] The vibration improvement module is used to obtain the resonance line of the powertrain, obtain the dynamic stiffness curve of the hydraulic mount load that fits the resonance line, and set the target hydraulic parameters of the hydraulic mount according to the dynamic stiffness curve.

[0033] In the third aspect, in order to achieve the above-mentioned purpose, the present invention also proposes a powertrain hydraulic suspension jitter improvement device, which includes: a memory, a processor, and a powertrain hydraulic suspension jitter improvement program stored in the memory and executable on the processor, and the powertrain hydraulic suspension jitter improvement program is configured to implement the steps of the powertrain hydraulic suspension jitter improvement method as described above.

[0034] In a fourth aspect, in order to achieve the above-mentioned purpose, the present invention also proposes a storage medium, on which a powertrain hydraulic suspension jitter improvement program is stored, and when the powertrain hydraulic suspension jitter improvement program is executed by a processor, the steps of the powertrain hydraulic suspension jitter improvement method as described above are implemented.

[0035] The method for improving the powertrain hydraulic mount jitter proposed in the present invention obtains the powertrain inertia parameters of the powertrain of the current vehicle; obtains the hydraulic mount load of the hydraulic mount of the current vehicle according to the powertrain inertia parameters; obtains the resonance line of the powertrain, and obtains the dynamic stiffness curve of the hydraulic mount load that fits the resonance line, and sets the target hydraulic parameters of the hydraulic mount according to the dynamic stiffness curve. This enables the powertrain to serve as a wide-band vibration absorber for vehicle driving jitter, effectively reduces vehicle driving jitter, avoids later debugging work, reduces the workload of low-frequency jitter improvement, and improves the speed and efficiency of powertrain hydraulic mount jitter improvement. BRIEF DESCRIPTION OF THE DRAWINGS

[0036] Figure 1 A schematic diagram of the device structure of the hardware operating environment involved in the embodiment of the present invention;

[0037] Figure 2 It is a schematic flow chart of a first embodiment of a method for improving powertrain hydraulic mount vibration of the present invention;

[0038] Figure 3 It is a schematic diagram of the hydraulic mount dynamic stiffness curve and resonance line in the powertrain hydraulic mount vibration improvement method of the present invention;

[0039] Figure 4 It is a flow chart of a second embodiment of a method for improving the vibration of a powertrain hydraulic mount according to the present invention;

[0040] Figure 5 It is a flow chart of a third embodiment of a method for improving powertrain hydraulic mount vibration of the present invention;

[0041] Figure 6 It is a functional module diagram of the first embodiment of the powertrain hydraulic mount vibration improvement device of the present invention.

[0042] The realization of the purpose, functional features and advantages of the present invention will be further explained in conjunction with embodiments and with reference to the accompanying drawings. DETAILED DESCRIPTION

[0043] It should be understood that the specific embodiments described herein are only used to explain the present invention, and are not used to limit the present invention.

[0044] The solution of the embodiment of the present invention is mainly: by obtaining the powertrain inertia parameters of the powertrain of the current vehicle; obtaining the hydraulic suspension load of the hydraulic suspension of the current vehicle according to the powertrain inertia parameters; obtaining the resonance line of the powertrain, and obtaining the dynamic stiffness curve of the hydraulic suspension load that fits the resonance line, and setting the target hydraulic parameters of the hydraulic suspension according to the dynamic stiffness curve, the powertrain can be used as a wide-band vibration absorber for vehicle driving vibration, effectively reducing vehicle driving vibration, avoiding later debugging work, reducing the workload of improving low-frequency vibration, and improving the speed and efficiency of improving the powertrain hydraulic suspension vibration, solving the technical problems in the prior art that later debugging is required, the workload is large, and the vibration during vehicle driving cannot be effectively reduced.

[0045] Reference Figure 1 , Figure 1 The figure is a schematic diagram of the device structure of the hardware operating environment involved in the embodiment of the present invention.

[0046] like Figure 1 As shown, the device may include: a processor 1001, such as a CPU, a communication bus 1002, a user interface 1003, a network interface 1004, and a memory 1005. Among them, the communication bus 1002 is used to realize the connection and communication between these components. The user interface 1003 may include a display screen (Display), an input unit such as a keyboard (Keyboard), and the optional user interface 1003 may also include a standard wired interface and a wireless interface. The network interface 1004 may optionally include a standard wired interface and a wireless interface (such as a Wi-Fi interface). The memory 1005 may be a high-speed RAM memory, or it may be a stable memory (Non-Volatile Memory), such as a disk memory. The memory 1005 may optionally be a storage device independent of the aforementioned processor 1001.

[0047] Those skilled in the art will understand that Figure 1 The device structure shown in the figure does not constitute a limitation of the device, and may include more or less components than shown in the figure, or combine certain components, or arrange the components differently.

[0048] like Figure 1 As shown, the memory 1005 as a storage medium may include an operating device, a network communication module, a user interface module, and a powertrain hydraulic mount vibration improvement program.

[0049] The device of the present invention calls the powertrain hydraulic mount vibration improvement program stored in the memory 1005 through the processor 1001, and performs the following operations:

[0050] Obtain the powertrain inertia parameters of the powertrain of the current vehicle;

[0051] Obtaining a hydraulic mount load of the hydraulic mount of the current vehicle according to the powertrain inertia parameter;

[0052] A resonance line of the powertrain is obtained, and a dynamic stiffness curve of the hydraulic mount load that matches the resonance line is acquired, and a target hydraulic parameter of the hydraulic mount is set according to the dynamic stiffness curve.

[0053] The device of the present invention calls the powertrain hydraulic mount vibration improvement program stored in the memory 1005 through the processor 1001, and also performs the following operations:

[0054] The powertrain of the current vehicle is tested according to the preset powertrain digital model to obtain the powertrain inertia parameters.

[0055] The device of the present invention calls the powertrain hydraulic mount vibration improvement program stored in the memory 1005 through the processor 1001, and also performs the following operations:

[0056] The powertrain of the current vehicle is tested according to a preset powertrain digital model to obtain the mass, center of mass coordinates, moment of inertia in X direction, moment of inertia in Y direction, moment of inertia in Z direction, product of inertia in X direction, product of inertia in Y direction and product of inertia in Z direction of the powertrain, and the mass, the center of mass coordinates, the moment of inertia in X direction, the moment of inertia in Y direction, the moment of inertia in Z direction, the product of inertia in X direction, the product of inertia in Y direction and the product of inertia in Z direction are used as powertrain inertia parameters.

[0057] The device of the present invention calls the powertrain hydraulic mount vibration improvement program stored in the memory 1005 through the processor 1001, and also performs the following operations:

[0058] Determining hard point coordinates of each suspension of the hydraulic mount of the current vehicle in a center of mass coordinate system of the power assembly according to the power assembly inertia parameter;

[0059] A hydraulic mount load of the hydraulic mount is determined based on the hard point coordinates.

[0060] The device of the present invention calls the powertrain hydraulic mount vibration improvement program stored in the memory 1005 through the processor 1001, and also performs the following operations:

[0061] The hard point coordinates are input into the NVH installation optimization module to obtain the load borne by each suspension in the Z direction under static conditions, and the load borne is used as the hydraulic suspension load of the hydraulic suspension.

[0062] The device of the present invention calls the powertrain hydraulic mount vibration improvement program stored in the memory 1005 through the processor 1001, and also performs the following operations:

[0063] The mass and dynamic stiffness of the hydraulic mount are obtained, and the resonance frequency is calculated according to the mass and the dynamic stiffness by the following formula:

[0064]

[0065] Among them, f is the resonance frequency, K is the dynamic stiffness, and M is the mass;

[0066] When the dynamic stiffness satisfies the following preset design value formula, generating a resonance line of the powertrain according to the preset design value formula;

[0067] K=4π 2 M*f 2

[0068] Where K is the dynamic stiffness, M is the mass, and f is the resonance frequency;

[0069] A dynamic stiffness curve of the hydraulic mount load that matches the resonance line is obtained, and a target hydraulic parameter of the hydraulic mount is set according to the dynamic stiffness curve.

[0070] The device of the present invention calls the powertrain hydraulic mount vibration improvement program stored in the memory 1005 through the processor 1001, and also performs the following operations:

[0071] Adjusting the initial hydraulic parameters of the hydraulic mount to obtain a dynamic stiffness curve of the hydraulic mount load that fits the resonance line;

[0072] A target hydraulic parameter of the hydraulic mount is set according to the dynamic stiffness curve.

[0073] This embodiment adopts the above scheme, by obtaining the powertrain inertia parameters of the powertrain of the current vehicle; obtaining the hydraulic suspension load of the hydraulic suspension of the current vehicle according to the powertrain inertia parameters; obtaining the resonance line of the powertrain, and obtaining the dynamic stiffness curve of the hydraulic suspension load that fits the resonance line, and setting the target hydraulic parameters of the hydraulic suspension according to the dynamic stiffness curve, so that the powertrain can be used as a wide-band vibration absorber for vehicle driving vibration, effectively reducing vehicle driving vibration, avoiding later debugging work, reducing the workload of low-frequency vibration improvement, and improving the speed and efficiency of powertrain hydraulic suspension vibration improvement.

[0074] Based on the above hardware structure, an embodiment of a method for improving the vibration of a powertrain hydraulic mount of the present invention is proposed.

[0075] Reference Figure 2 , Figure 2 It is a flow chart of the first embodiment of the method for improving the vibration of the powertrain hydraulic mount of the present invention.

[0076] In a first embodiment, the powertrain hydraulic mount vibration improvement method comprises the following steps:

[0077] Step S10: Obtain the powertrain inertia parameters of the powertrain of the current vehicle.

[0078] It should be noted that the powertrain inertia parameter is the inertia parameter of the powertrain of the current vehicle, and different powertrains have corresponding different powertrain inertia parameters.

[0079] Step S20: Obtaining a hydraulic mount load of the hydraulic mount of the current vehicle according to the powertrain inertia parameter.

[0080] It should be understood that the hydraulic mount load of the hydraulic mount of the current vehicle, ie, the load carried by the hydraulic mount, can be obtained according to the powertrain inertia parameter.

[0081] Step S30: obtaining a resonance line of the powertrain, acquiring a dynamic stiffness curve of the hydraulic mount load that matches the resonance line, and setting a target hydraulic parameter of the hydraulic mount according to the dynamic stiffness curve.

[0082] It is understandable that after obtaining the resonance line of the powertrain, the dynamic stiffness curve of the hydraulic mount load that matches the resonance line can be obtained, and then the target hydraulic parameters of the hydraulic mount can be set according to the dynamic stiffness curve.

[0083] Furthermore, the step S30 specifically includes the following steps:

[0084] The mass and dynamic stiffness of the hydraulic mount are obtained, and the resonance frequency is calculated according to the mass and the dynamic stiffness by the following formula:

[0085]

[0086] Among them, f is the resonance frequency, K is the dynamic stiffness, and M is the mass;

[0087] When the dynamic stiffness satisfies the following preset design value formula, generating a resonance line of the powertrain according to the preset design value formula;

[0088] K=4π 2 M*f 2

[0089] Where K is the dynamic stiffness, M is the mass, and f is the resonance frequency;

[0090] A dynamic stiffness curve of the hydraulic mount load that matches the resonance line is obtained, and a target hydraulic parameter of the hydraulic mount is set according to the dynamic stiffness curve.

[0091] In a specific implementation, the powertrain suspension is generally symmetrical on the left and right, and the performance parameters are consistent; based on the data in Table 3 below, the average load of the two front suspensions can be calculated as (1482.336+1588.894) / 2=1535.6N, and the mass load M=1535.6 / 9.8=156.7Kg.

[0092] The design concept of this embodiment is to simplify a hydraulic mount and the load it bears into a single degree of freedom system with a mass of M and a dynamic stiffness of K.

[0093] In this embodiment, M=1535.6 kg, which is a constant value.

[0094] K is the preset design value. If the dynamic stiffness K satisfies the above formula in the 5-20Hz frequency band during design, the system will resonate at 5-20Hz and have a vibration absorber effect on vehicle vibration problems; according to the formula K = 4π 2 M*f 2 The plotted curve is defined as the resonance line.

[0095] Furthermore, the step of obtaining a dynamic stiffness curve of the hydraulic mount load that matches the resonance line and setting a target hydraulic parameter of the hydraulic mount according to the dynamic stiffness curve specifically includes the following steps:

[0096] Adjusting the initial hydraulic parameters of the hydraulic mount to obtain a dynamic stiffness curve of the hydraulic mount load that fits the resonance line;

[0097] A target hydraulic parameter of the hydraulic mount is set according to the dynamic stiffness curve.

[0098] In a specific implementation, when designing the 5-20Hz dynamic stiffness of the hydraulic mount, the initial hydraulic parameters of the hydraulic mount, such as the size of the inertial channel and the size of the decoupling disc, can be adjusted to make the 5-20Hz dynamic stiffness curve fit the resonance line as closely as possible, such as Figure 3 As shown, Figure 3 Schematic diagram of hydraulic mount dynamic stiffness curve and resonance line in the powertrain hydraulic mount vibration improvement method of the present invention, see Figure 3 The powertrain uses a hydraulic mount, which simplifies the hydraulic mount and its load into a vibration absorber system for vehicle vibration. The dynamic stiffness of the hydraulic mount at 5-20Hz is designed based on the resonance line, so that it has a vibration absorption effect in this frequency band, improving and avoiding vehicle vibration. This ensures that the powertrain can effectively improve and avoid vehicle vibration problems at 5-20Hz.

[0099] It can be understood that in addition to obtaining the dynamic stiffness curve of the hydraulic suspension load that fits the resonance line by adjusting the initial hydraulic parameters of the hydraulic suspension, i.e., the size of the inertial channel and the size of the decoupling disk, the dynamic stiffness curve of the hydraulic suspension load that fits the resonance line can also be obtained by adjusting the liquid viscosity of the hydraulic suspension, changing the stiffness of the rubber main spring, optimizing the chamber shape and volume of the hydraulic suspension, and adjusting the size of the preload force; this is not limited in this embodiment.

[0100] This embodiment adopts the above scheme, by obtaining the powertrain inertia parameters of the powertrain of the current vehicle; obtaining the hydraulic suspension load of the hydraulic suspension of the current vehicle according to the powertrain inertia parameters; obtaining the resonance line of the powertrain, and obtaining the dynamic stiffness curve of the hydraulic suspension load that fits the resonance line, and setting the target hydraulic parameters of the hydraulic suspension according to the dynamic stiffness curve, so that the powertrain can be used as a wide-band vibration absorber for vehicle driving vibration, effectively reducing vehicle driving vibration, avoiding later debugging work, reducing the workload of low-frequency vibration improvement, and improving the speed and efficiency of powertrain hydraulic suspension vibration improvement.

[0101] Further, Figure 4 FIG. 2 is a flow chart of a second embodiment of a method for improving the vibration of a powertrain hydraulic mount according to the present invention. Figure 4 As shown, based on the first embodiment, a second embodiment of the method for improving the vibration of the powertrain hydraulic mount of the present invention is proposed. In this embodiment, the step S10 specifically includes the following steps:

[0102] Step S11: testing the powertrain of the current vehicle according to a preset powertrain digital model to obtain powertrain inertia parameters.

[0103] It should be noted that the powertrain of the current vehicle can be tested according to the preset powertrain digital model to obtain the powertrain inertia parameters.

[0104] In a specific implementation, the inertia parameters of the powertrain include: powertrain mass, center of gravity coordinates, and three moments of inertia and three products of inertia in the center of gravity coordinate system; generally, they can be measured using a CAD digital model or using a physical object on a rotational inertia test bench, where there may be some differences between the CAD digital model and the actual installed powertrain; for the sake of design rigor, this embodiment uses an experimental method to obtain the powertrain inertia parameters.

[0105] Furthermore, the step S11 specifically includes the following steps:

[0106] The powertrain of the current vehicle is tested according to a preset powertrain digital model to obtain the mass, center of mass coordinates, moment of inertia in X direction, moment of inertia in Y direction, moment of inertia in Z direction, product of inertia in X direction, product of inertia in Y direction and product of inertia in Z direction of the powertrain, and the mass, the center of mass coordinates, the moment of inertia in X direction, the moment of inertia in Y direction, the moment of inertia in Z direction, the product of inertia in X direction, the product of inertia in Y direction and the product of inertia in Z direction are used as powertrain inertia parameters.

[0107] In a specific implementation, the powertrain of the current vehicle can be tested according to the powertrain digital model provided in advance. The origin of the powertrain coordinate system is the intersection of the centerline of the powertrain crankshaft and the front end surface of the cylinder block. The positive direction of the X-axis is along the crankshaft centerline toward the gearbox, the positive direction of the Y-axis is along the crankshaft centerline from the rear end of the powertrain to the right, and the positive direction of the Z-axis is vertically upward, which conforms to the right-hand coordinate system rule.

[0108] In the final test results, the powertrain center of mass coordinates are the results in the powertrain coordinate system, and the moment of inertia and product of inertia are the results in the powertrain coordinate system with the powertrain center of mass coordinates as the origin and the coordinate direction being the same.

[0109] The test results are shown in Table 1 below:

[0110] Table 1 Powertrain inertia parameter test results

[0111] project Test Results Mass(kg) 411.4 Center of mass coordinate (X) (unit: mm) 423.9 Center of mass coordinate (Y) (unit: mm) 8.1 Center of mass coordinate (Z) (unit: mm) 102.3 <![CDATA[Moment of inertia I in the X direction XX (kg·m 2 )]]> 15 <![CDATA[Moment of inertia I in the Y direction YY (kg·m 2 )]]> 56.6 <![CDATA[Z-axis moment of inertia I ZZ (kg·m 2 )]]> 52.2 <![CDATA[Product of inertia I in the X direction XY (kg·m 2 )]]> -1.45 <![CDATA[Product of inertia I in the Y direction YZ (kg·m 2 )]]> 0.16 <![CDATA[Product of inertia I about the Z direction XZ (kg·m 2 )]]> -9.68

[0112] Through the above scheme, this embodiment obtains the powertrain inertia parameters by testing the powertrain of the current vehicle according to the preset powertrain digital model; the powertrain inertia parameters can be obtained quickly, thereby improving the speed and efficiency of improving the powertrain hydraulic suspension vibration.

[0113] Further, Figure 5 FIG. 1 is a flow chart of a third embodiment of a method for improving the vibration of a powertrain hydraulic mount according to the present invention. Figure 5 As shown, based on the first embodiment, a third embodiment of the method for improving the vibration of a powertrain hydraulic mount of the present invention is proposed. In this embodiment, the step S20 specifically includes the following steps:

[0114] Step S21 : determining the hard point coordinates of each mount of the hydraulic mount of the current vehicle in the center of mass coordinate system of the power assembly according to the inertia parameters of the power assembly.

[0115] It should be noted that the hard point coordinates of each suspension of the hydraulic mount of the current vehicle in the center of mass coordinate system of the power assembly can be determined according to the power assembly inertia parameters.

[0116] In a specific implementation, after the inertia parameters of the powertrain are obtained, the hard point coordinates of each suspension in the powertrain mass center coordinate system can be obtained according to the inertia parameters of the powertrain.

[0117] Step S22: determining the hydraulic mount load of the hydraulic mount according to the hard point coordinates.

[0118] It can be understood that the hydraulic mount load of the hydraulic mount, ie the load borne by each mount, can be determined according to the hard point coordinates.

[0119] In the specific implementation, the powertrain is arranged longitudinally and four-point suspension is adopted as an example, wherein the two front suspensions are hydraulic suspensions and the rear suspension is rubber suspension, as shown in the following Table 2:

[0120] Table 2 Coordinates of each suspension hard point

[0121]

[0122] Furthermore, the step S22 specifically includes the following steps:

[0123] The hard point coordinates are input into the NVH installation optimization module to obtain the load borne by each suspension in the Z direction under static conditions, and the load borne is used as the hydraulic suspension load of the hydraulic suspension.

[0124] It should be understood that by inputting the hard point coordinates into the NVH installation optimization module, the load borne by each suspension in the Z direction under static conditions can be obtained, and then the load borne can be used as the hydraulic suspension load of the hydraulic suspension.

[0125] In the specific implementation, the Mount Optimization module of Hypermesh_NVH can be used to output the load borne by each suspension in the Z direction under static conditions, as shown in Table 3 below:

[0126] Table 3 Loads of various suspensions under static conditions

[0127]

[0128] It should be noted that the Mount Optimization module is a practical tool in Altair HyperView. It has the functions of predicting the rigid body modal frequency and kinetic energy distribution of the powertrain and optimizing the suspension system. It can help engineers optimize the suspension stiffness and position layout, reduce vibration and noise transmission, and improve the comfort and reliability of the vehicle.

[0129] Through the above scheme, this embodiment determines the hard point coordinates of each suspension of the hydraulic suspension of the current vehicle in the center of mass coordinate system of the powertrain according to the inertia parameters of the powertrain; determines the hydraulic suspension load of the hydraulic suspension according to the hard point coordinates, thereby effectively reducing the vehicle driving jitter and improving the speed and efficiency of improving the powertrain hydraulic suspension jitter.

[0130] Accordingly, the present invention further provides a powertrain hydraulic suspension vibration improvement device.

[0131] Reference Figure 6 , Figure 6 It is a functional module diagram of the first embodiment of the powertrain hydraulic mount vibration improvement device of the present invention.

[0132] In a first embodiment of the powertrain hydraulic mount vibration improvement device of the present invention, the powertrain hydraulic mount vibration improvement device comprises:

[0133] The parameter acquisition module 10 is used to acquire the powertrain inertia parameters of the powertrain of the current vehicle.

[0134] The load acquisition module 20 is used to obtain the hydraulic mount load of the hydraulic mount of the current vehicle according to the powertrain inertia parameter.

[0135] The vibration improvement module 30 is used to obtain the resonance line of the powertrain, obtain the dynamic stiffness curve of the hydraulic mount load that fits the resonance line, and set the target hydraulic parameters of the hydraulic mount according to the dynamic stiffness curve.

[0136] The parameter acquisition module 10 is also used to test the powertrain of the current vehicle according to a preset powertrain digital model to obtain the powertrain inertia parameters.

[0137] The parameter acquisition module 10 is further used to test the powertrain of the current vehicle according to a preset powertrain digital model, obtain the mass, center of mass coordinates, X-direction moment of inertia, Y-direction moment of inertia, Z-direction moment of inertia, X-direction product of inertia, Y-direction product of inertia and Z-direction product of inertia of the powertrain, and use the mass, the center of mass coordinates, the X-direction moment of inertia, the Y-direction moment of inertia, the Z-direction moment of inertia, the X-direction product of inertia, the Y-direction product of inertia and the Z-direction product of inertia as powertrain inertia parameters.

[0138] The load acquisition module 20 is further used to determine the hard point coordinates of each suspension of the hydraulic suspension of the current vehicle in the center of mass coordinate system of the powertrain according to the inertia parameters of the powertrain; and determine the hydraulic suspension load of the hydraulic suspension according to the hard point coordinates.

[0139] The load acquisition module 20 is also used to input the hard point coordinates into the NVH installation optimization module to obtain the load borne by each suspension in the Z direction under static conditions, and use the load borne as the hydraulic suspension load of the hydraulic suspension.

[0140] The vibration improvement module 30 is further used to obtain the mass and dynamic stiffness of the hydraulic mount, and to obtain the resonance frequency by calculating the mass and the dynamic stiffness through the following formula:

[0141]

[0142] Among them, f is the resonance frequency, K is the dynamic stiffness, and M is the mass;

[0143] When the dynamic stiffness satisfies the following preset design value formula, generating a resonance line of the powertrain according to the preset design value formula;

[0144] K=4π 2 M*f 2

[0145] Where K is the dynamic stiffness, M is the mass, and f is the resonance frequency;

[0146] A dynamic stiffness curve of the hydraulic mount load that matches the resonance line is obtained, and a target hydraulic parameter of the hydraulic mount is set according to the dynamic stiffness curve.

[0147] The jitter improvement module 30 is further used to adjust the initial hydraulic parameters of the hydraulic mount to obtain a dynamic stiffness curve of the hydraulic mount load that fits the resonance line; and to set target hydraulic parameters of the hydraulic mount according to the dynamic stiffness curve.

[0148] Among them, the steps implemented by each functional module of the powertrain hydraulic mount jitter improvement device can refer to the various embodiments of the powertrain hydraulic mount jitter improvement method of the present invention, and will not be repeated here.

[0149] In addition, an embodiment of the present invention further provides a storage medium, on which a powertrain hydraulic mount vibration improvement program is stored. When the powertrain hydraulic mount vibration improvement program is executed by a processor, the following operations are implemented:

[0150] Obtain the powertrain inertia parameters of the powertrain of the current vehicle;

[0151] Obtaining a hydraulic mount load of the hydraulic mount of the current vehicle according to the powertrain inertia parameter;

[0152] A resonance line of the powertrain is obtained, and a dynamic stiffness curve of the hydraulic mount load that matches the resonance line is acquired, and a target hydraulic parameter of the hydraulic mount is set according to the dynamic stiffness curve.

[0153] Furthermore, when the powertrain hydraulic mount vibration improvement program is executed by the processor, the following operations are also implemented:

[0154] The powertrain of the current vehicle is tested according to the preset powertrain digital model to obtain the powertrain inertia parameters.

[0155] Furthermore, when the powertrain hydraulic mount vibration improvement program is executed by the processor, the following operations are also implemented:

[0156] The powertrain of the current vehicle is tested according to a preset powertrain digital model to obtain the mass, center of mass coordinates, moment of inertia in X direction, moment of inertia in Y direction, moment of inertia in Z direction, product of inertia in X direction, product of inertia in Y direction and product of inertia in Z direction of the powertrain, and the mass, the center of mass coordinates, the moment of inertia in X direction, the moment of inertia in Y direction, the moment of inertia in Z direction, the product of inertia in X direction, the product of inertia in Y direction and the product of inertia in Z direction are used as powertrain inertia parameters.

[0157] Furthermore, when the powertrain hydraulic mount vibration improvement program is executed by the processor, the following operations are also implemented:

[0158] Determining hard point coordinates of each suspension of the hydraulic mount of the current vehicle in a center of mass coordinate system of the power assembly according to the power assembly inertia parameter;

[0159] A hydraulic mount load of the hydraulic mount is determined based on the hard point coordinates.

[0160] Furthermore, when the powertrain hydraulic mount vibration improvement program is executed by the processor, the following operations are also implemented:

[0161] The hard point coordinates are input into the NVH installation optimization module to obtain the load borne by each suspension in the Z direction under static conditions, and the load borne is used as the hydraulic suspension load of the hydraulic suspension.

[0162] Furthermore, when the powertrain hydraulic mount vibration improvement program is executed by the processor, the following operations are also implemented:

[0163] The mass and dynamic stiffness of the hydraulic mount are obtained, and the resonance frequency is calculated according to the mass and the dynamic stiffness by the following formula:

[0164]

[0165] Among them, f is the resonance frequency, K is the dynamic stiffness, and M is the mass;

[0166] When the dynamic stiffness satisfies the following preset design value formula, generating a resonance line of the powertrain according to the preset design value formula;

[0167] K=4π 2 M*f 2

[0168] Where K is the dynamic stiffness, M is the mass, and f is the resonance frequency;

[0169] A dynamic stiffness curve of the hydraulic mount load that matches the resonance line is obtained, and a target hydraulic parameter of the hydraulic mount is set according to the dynamic stiffness curve.

[0170] Furthermore, when the powertrain hydraulic mount vibration improvement program is executed by the processor, the following operations are also implemented:

[0171] Adjusting the initial hydraulic parameters of the hydraulic mount to obtain a dynamic stiffness curve of the hydraulic mount load that fits the resonance line;

[0172] A target hydraulic parameter of the hydraulic mount is set according to the dynamic stiffness curve.

[0173] Those skilled in the art will appreciate that all or part of the steps in the above-mentioned implementation method can be accomplished by instructing related hardware through a program, and the program is stored in a storage medium, including a number of instructions for enabling a device (which may be a single-chip microcomputer, chip, etc.) or a processor to execute all or part of the steps of the method described in each implementation method of the present application; and the aforementioned storage medium is a computer-readable storage medium, including: a U disk, a mobile hard disk, a read-only memory (ROM), a random access memory (RAM), a disk or an optical disk, and other media that can store program codes.

[0174] It should be noted that, in this article, the terms "include", "comprises" or any other variations thereof are intended to cover non-exclusive inclusion, so that a process, method, article or device including a series of elements includes not only those elements, but also other elements not explicitly listed, or also includes elements inherent to such process, method, article or device. In the absence of further restrictions, an element defined by the sentence "comprises a ..." does not exclude the existence of other identical elements in the process, method, article or device including the element.

[0175] The serial numbers of the above embodiments of the present invention are only for description and do not represent the advantages or disadvantages of the embodiments.

[0176] The above are only preferred embodiments of the present invention, and are not intended to limit the patent scope of the present invention. Any equivalent structure or equivalent process transformation made using the contents of the present invention specification and drawings, or directly or indirectly applied in other related technical fields, are also included in the patent protection scope of the present invention.

Claims

1. A method for improving the vibration of a powertrain hydraulic mount, characterized in that: The powertrain hydraulic suspension vibration absorption method comprises: Obtain the powertrain inertia parameters of the powertrain of the current vehicle; Obtaining a hydraulic mount load of the hydraulic mount of the current vehicle according to the powertrain inertia parameter; A resonance line of the powertrain is obtained, and a dynamic stiffness curve of the hydraulic mount load that matches the resonance line is acquired, and a target hydraulic parameter of the hydraulic mount is set according to the dynamic stiffness curve.

2. The method for improving the vibration of a powertrain hydraulic mount according to claim 1, characterized in that: The obtaining of the powertrain inertia parameter of the powertrain of the current vehicle includes: The powertrain of the current vehicle is tested according to the preset powertrain digital model to obtain the powertrain inertia parameters.

3. The method for improving the vibration of a powertrain hydraulic mount according to claim 2, characterized in that: The testing of the powertrain of the current vehicle according to the preset powertrain digital model to obtain the powertrain inertia parameters includes: The powertrain of the current vehicle is tested according to a preset powertrain digital model to obtain the mass, center of mass coordinates, moment of inertia in X direction, moment of inertia in Y direction, moment of inertia in Z direction, product of inertia in X direction, product of inertia in Y direction and product of inertia in Z direction of the powertrain, and the mass, the center of mass coordinates, the moment of inertia in X direction, the moment of inertia in Y direction, the moment of inertia in Z direction, the product of inertia in X direction, the product of inertia in Y direction and the product of inertia in Z direction are used as powertrain inertia parameters.

4. The method for improving the vibration of a powertrain hydraulic mount according to claim 1, characterized in that: The step of obtaining the hydraulic mount load of the hydraulic mount of the current vehicle according to the powertrain inertia parameter comprises: Determining hard point coordinates of each suspension of the hydraulic mount of the current vehicle in a center of mass coordinate system of the power assembly according to the power assembly inertia parameter; A hydraulic mount load of the hydraulic mount is determined based on the hard point coordinates.

5. The method for improving the vibration of a powertrain hydraulic mount according to claim 4, characterized in that: Determining the hydraulic mount load of the hydraulic mount according to the hard point coordinates includes: The hard point coordinates are input into the NVH installation optimization module to obtain the load borne by each suspension in the Z direction under static conditions, and the load borne is used as the hydraulic suspension load of the hydraulic suspension.

6. The method for improving the vibration of a powertrain hydraulic mount according to claim 1, characterized in that: The obtaining of the resonance line of the powertrain, acquiring a dynamic stiffness curve of the hydraulic mount load that matches the resonance line, and setting a target hydraulic parameter of the hydraulic mount according to the dynamic stiffness curve includes: The mass and dynamic stiffness of the hydraulic mount are obtained, and the resonance frequency is calculated according to the mass and the dynamic stiffness by the following formula: Among them, f is the resonance frequency, K is the dynamic stiffness, and M is the mass; When the dynamic stiffness satisfies the following preset design value formula, generating a resonance line of the powertrain according to the preset design value formula; K=4π 2 M*f 2 Where K is the dynamic stiffness, M is the mass, and f is the resonance frequency; A dynamic stiffness curve of the hydraulic mount load that matches the resonance line is obtained, and a target hydraulic parameter of the hydraulic mount is set according to the dynamic stiffness curve.

7. The method for improving the vibration of a powertrain hydraulic mount according to claim 1, characterized in that: The step of obtaining a dynamic stiffness curve of the hydraulic mount load that matches the resonance line and setting a target hydraulic parameter of the hydraulic mount according to the dynamic stiffness curve includes: Adjusting the initial hydraulic parameters of the hydraulic mount to obtain a dynamic stiffness curve of the hydraulic mount load that fits the resonance line; A target hydraulic parameter of the hydraulic mount is set according to the dynamic stiffness curve.

8. A powertrain hydraulic mount vibration improvement device, characterized in that: The powertrain hydraulic mount vibration improving device comprises: A parameter acquisition module, used to acquire the powertrain inertia parameters of the powertrain of the current vehicle; A load acquisition module, configured to obtain a hydraulic suspension load of the hydraulic suspension of the current vehicle according to the powertrain inertia parameter; The vibration improvement module is used to obtain the resonance line of the powertrain, obtain the dynamic stiffness curve of the hydraulic mount load that fits the resonance line, and set the target hydraulic parameters of the hydraulic mount according to the dynamic stiffness curve.

9. A powertrain hydraulic mount vibration improvement device, characterized in that: The powertrain hydraulic suspension jitter improvement device includes: a memory, a processor, and a powertrain hydraulic suspension jitter improvement program stored in the memory and executable on the processor, wherein the powertrain hydraulic suspension jitter improvement program is configured to implement the steps of the powertrain hydraulic suspension jitter improvement method as described in any one of claims 1 to 7.

10. A storage medium, characterized in that: The storage medium stores a powertrain hydraulic mount jitter improvement program, which, when executed by the processor, implements the steps of the powertrain hydraulic mount jitter improvement method as claimed in any one of claims 1 to 7.

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