Active hydraulic mount parameter identification method based on significant characteristics of dynamic characteristics

Abstract

The present invention discloses a method for identifying the parameters of an active hydraulic mount based on significant dynamic characteristics, which relates to the technical field of active hydraulic mounts. The method includes the following steps: identifying the storage dynamic stiffness and viscous damping of the rubber main spring; identifying the natural frequency of the inertia passage, the volume stiffness of the upper liquid chamber, and the area of the main spring pump liquid piston; identifying the decoupling membrane coupling parameters, the dynamic sub-damping ratio, and the natural frequency of the dynamic sub; identifying the net mass of the dynamic sub in the liquid-free state, the line stiffness of the decoupling membrane, the viscous damping of the decoupling membrane, the natural frequency of the dynamic sub, and the dynamic sub-damping ratio; based on the identified parameters, identifying the area of the decoupling membrane pump liquid piston, the volume stiffness of the decoupling membrane, the volume stiffness of the rubber main spring, the total mass of the dynamic sub with attached liquid in the liquid-filled state, and the total viscous damping of the dynamic sub system including fluid damping and decoupling membrane damping. The technical solution of the present invention can achieve the full parameter identification of the active hydraulic mount.

Description

Technical Field

[0001] The present invention relates to the technical field of active hydraulic mounts, and particularly relates to a method for identifying parameters of an active hydraulic mount based on significant dynamic characteristics, especially a method for identifying parameters of an inertia passage-decoupling membrane-oscillating coil actuator type active hydraulic mount, and particularly a method for identifying parameters of passive and active characteristics of an inertia passage-decoupling membrane-oscillating coil actuator type active hydraulic mount. Background Technique

[0002] The powertrain is the main vibration source of an automobile. As an elastic connection system between the powertrain and the body / frame, the mount not only fixes and supports the powertrain, but also is a key system for isolating and attenuating the vibration of the powertrain and reducing the transmission of structural noise.

[0003] The vibration isolation of the automotive powertrain has gone through many stages such as rigid connection, soft pads (leather or cloth pads), rubber mounts, three generations of hydraulic mounts, semi-active mounts, and active mounts with the development of dynamics and vibration theory.

[0004] The active hydraulic mount is an effective solution to further improve the dynamic comfort of vehicle vibration and noise. It is applicable to both traditional fuel powertrains and new energy electric drive powertrains, and is also commonly used in scenarios such as high-speed rails, buildings, bridges, and stay cables of bridges. The active hydraulic mount with an inertia passage-decoupling membrane type hydraulic mount as the carrier has been widely used due to its compact structure and good basic performance of large damping at low frequencies. By fixedly connecting an electromagnetic actuator to the decoupling membrane, the active force and the force transmitted to the vehicle body end via the primary passage are equal in magnitude and opposite in direction, thus canceling each other out and further reducing the vibration and noise of the whole vehicle.

[0005] The active hydraulic mount belongs to a complex system of mechanical-electromagnetic-fluid coupling / integration, and its research involves three aspects: model, parameters, and control algorithms. The model and parameters are the basis of the control algorithm. The active hydraulic mount generally adopts a lumped parameter model; accurately identifying its model parameters is a prerequisite for vibration isolation performance analysis, design, and active control. The methods for obtaining parameters mainly include numerical calculation based on virtual prototypes (virtual experiments), direct testing methods based on specific components of physical prototypes, and parameter identification based on the external dynamic characteristics of the mount assembly. The first one is applicable to the forward development stage. Due to limitations of the constitutive model of rubber materials, simplification of the virtual prototype model, and numerical calculation errors, etc., its parameters are not applicable to active control. The second one is applicable to the physical prototype stage, but the direct testing based on component levels has a large workload, high cost, long cycle, and it is difficult to accurately reproduce the non-linear working state of the assembly. The third parameter identification method based on the external dynamic characteristics of the mount assembly is applicable to the physical prototype stage. The physical meaning of the identified parameters is clear, and the identification results have a good characteristic of natural coincidence with the external dynamic characteristics of the assembly, which is a parameter identification method applicable to active control and urgently needs to be solved. Summary of the Invention

[0006] The object of the present invention is to provide a parameter identification method based on the external dynamic characteristics of a suspension assembly, which can be achieved by using the existing quality inspection equipment and fixtures for production; it does not involve the simplification of numerical calculation models such as finite elements, and there is no need to develop additional complex and expensive hydraulic / hydraulic test equipment, and it can accurately reproduce the non-linear working state of the suspension assembly; it has low cost, short cycle, high efficiency, good consistency of identification results, and is accurate and reliable.

[0007] The object of the present invention can be achieved by the following technical solutions:

[0008] A method for identifying the parameters of an active hydraulic mount based on the significant characteristics of dynamic characteristics, characterized by comprising the following steps:

[0009] S1. Based on the origin or cross-point passive characteristic test curves in the high, medium, and low frequency bands of the active hydraulic mount in the liquid-free state, identify the storage dynamic stiffness and viscous damping of the rubber main spring;

[0010] S2. Based on the origin or cross-point passive characteristic test curves in the medium and low frequency bands of the active hydraulic mount in the liquid-filled state, its fixed-point frequency of storage dynamic stiffness and the storage dynamic stiffness of the first horizontal section, and combined with the storage dynamic stiffness of the rubber main spring, identify the natural frequency of the inertia passage, the volume stiffness of the upper liquid chamber, and the area of the main spring pump liquid piston;

[0011] S3. Based on the origin or cross-point active dynamic characteristic test curves in the high, medium, and low frequency bands of the active hydraulic mount in the liquid-filled state, its horizontal section, amplitude-frequency response peak value and peak frequency, and combined with the volume stiffness of the upper liquid chamber and the area of the main spring pump liquid piston, identify the decoupling membrane coupling parameter, the dynamic sub-damping ratio, and the dynamic sub-natural frequency;

[0012] S4. Based on the active characteristic test curves of the dynamic sub in the high, medium, and low frequency bands of the active hydraulic mount in the liquid-free state with or without additional mass, identify the net mass of the dynamic sub in the liquid-free state, the line stiffness of the decoupling membrane, the viscous damping of the decoupling membrane, the dynamic sub-natural frequency, and the dynamic sub-damping ratio;

[0013] S5. Based on the parameters identified in S1–S4, combined with the decoupling membrane coupling parameter, the line stiffness of the decoupling membrane, the volume stiffness of the upper liquid chamber, the dynamic sub-natural frequency, and the dynamic sub-damping ratio, further identify the area of the decoupling membrane pump liquid piston, the volume stiffness of the decoupling membrane, the volume stiffness of the rubber main spring, the total mass of the dynamic sub with attached liquid in the liquid-filled state, and the total viscous damping of the dynamic sub system including fluid damping and decoupling membrane damping, thereby realizing the parameter identification of the active hydraulic mount.

[0014] Furthermore, in S1, a suspension dynamic characteristic test device is used to perform a frequency sweep test with different displacement amplitudes to obtain the origin or cross-point passive characteristic test curves in the high, medium, and low frequency bands of the active hydraulic mount in the liquid-free state, and thereby identify the storage dynamic stiffness and viscous damping of the rubber main spring.

[0015] Further, the suspension dynamic characteristic test equipment includes, but is not limited to, MTS or inova.

[0016] Further, in the step S1, the displacement excitation amplitude Y1 = 0 - 50 mm, and the frequency f = 0 - 1000 Hz.

[0017] Further, in the step S2, a frequency sweep test with different displacement amplitudes is performed using the suspension dynamic characteristic test equipment to obtain the origin or cross-point passive characteristic test curve in the middle and low frequency bands of the active hydraulic mount in the filled state, and the fixed-point frequency of the energy storage dynamic stiffness and the first horizontal section energy storage dynamic stiffness are identified therefrom.

[0018] Further, in the step S2, based on the origin or cross-point passive characteristic in the middle and low frequency bands of the active hydraulic mount in the filled state and its fixed-point frequency f of the energy storage dynamic stiffness R and the first horizontal section energy storage dynamic stiffness k′ ∞，1 , combined with the energy storage dynamic stiffness k1 of the rubber main spring, the natural frequency f of the inertia channel n2 , the volume stiffness K of the upper liquid chamber u1 , and the area A1 of the main spring pump piston are identified:

[0019] f n2 = f R

[0020]

[0021]

[0022] wherein, A2 is the cross-sectional area of the inertia channel; l2 is the length of the inertia channel.

[0023] Further, in the step S2, the displacement excitation amplitude Y1 = 0 - 50 mm, and the frequency f = 0 - 1000 Hz.

[0024] Further, in the step S3, a burst random current excitation test is performed using the suspension dynamic characteristic test equipment, and the frequency response curve of the current to the upper and lower end forces of the suspension is obtained through data processing to obtain the origin or cross-point active dynamic characteristic test curve in the high, middle, and low frequency bands of the active hydraulic mount in the filled state, and the horizontal section, amplitude-frequency response peak value, and peak frequency are identified therefrom.

[0025] Further, in the step S3, based on the origin or cross-point active dynamic characteristic test curve in the high, middle, and low frequency bands of the active hydraulic mount in the filled state and its horizontal section F i,∞,4 , amplitude-frequency response peak value A p,1 and peak frequency f p,1, in combination with the volume stiffness of the upper liquid chamber and the area of the main spring pump liquid piston, identify the decoupling film coupling parameter A3·K3, the mover damping ratio ξ3, and the mover natural frequency f n3 :

[0026]

[0027]

[0028]

[0029] where k M is the voice coil constant.

[0030] Furthermore, in the step S3, the current excitation amplitude I = 0 - 100 A, the frequency f = 0 - 1000 Hz, and the time t = 0 - 1000 s.

[0031] Furthermore, the step S4 specifically includes:

[0032] Based on the mover active characteristic test curves in the high, medium, and low frequency bands with or without additional mass in the liquid-free state of the active hydraulic mount, and their horizontal sections, amplitude-frequency response peaks and peak frequencies, identify the mover mass with or without additional mass, the mover damping ratio with or without additional mass, and the mover natural frequency with or without additional mass, and then identify the net mass of the mover in the liquid-free state, the line stiffness of the decoupling film, the viscous damping of the decoupling film, the mover natural frequency, and the mover damping ratio.

[0033] Furthermore, in the step S4, a burst random current excitation test is carried out using a suspension dynamic characteristic test device, and the frequency response curve from current to mover acceleration is obtained through data processing, thereby obtaining the mover active characteristic test curves in the high, medium, and low frequency bands with or without additional mass in the liquid-free state of the active hydraulic mount, and then determining its horizontal section, amplitude-frequency response peak and peak frequency.

[0034] Furthermore, in the step S4, the current excitation amplitude I = 0 - 100 A, the frequency f = 0 - 1000 Hz, and the time t = 0 - 1000 s.

[0035] Furthermore, in the step S4, the following formula is used based on the mover active characteristic test curves in the high, medium, and low frequency bands with or without additional mass m ad and their horizontal sections of the amplitude-frequency response peak A p,3,nof,mad and the peak frequency f p,3,nof,mad , to identify the mover mass m ad with or without additional mass m 3,nof,mad , and the mover damping ratio ξ ad with or without additional mass m3,nof,mad and with or without an additional mass m ad , the natural frequency f of the mover n3,nof,mad , and then identify the net mass m of the mover in the liquid-free state 3,nof , the decoupling membrane line stiffness k3, the decoupling membrane viscous damping c 3,nof , the natural frequency f of the mover n3,nof , the damping ratio ξ of the mover 3,nof :

[0036]

[0037]

[0038]

[0039] m 3，nof = m 3，nof，mad - m ad

[0040]

[0041]

[0042]

[0043]

[0044] where k M is the voice coil constant

[0045] Furthermore, in the step S5, based on the parameters identified in S1–S4, the following formula is used to further identify the decoupling membrane pump liquid piston area A3, the decoupling membrane volume stiffness K3, the rubber main spring volume stiffness K1, the total mass m3 of the mover with attached liquid in the liquid-filled state, and the total viscous damping c3 of the mover system including fluid damping and decoupling membrane damping:

[0046] A3(A3K3)= k3

[0047]

[0048]

[0049]

[0050]

[0051] Furthermore, before the S1, there is also a step S0: collect the original data: fluid density ρ, inertial channel length l2, inertial channel cross-sectional area A2, voice coil constant k M ]>and gravitational acceleration g

[0052] Furthermore, the two-degree-of-freedom lumped parameter model of the active hydraulic mount is as follows:

[0053]

[0054] where ρ is the fluid density, l2 is the length of the inertia passage, y2 is the displacement of the inertia liquid column in the annular flow in the horizontal plane relative to the wall of the inertia passage, is the friction loss coefficient along the inertia passage, is the local loss coefficient, p1 is the pressure fluctuation of the upper liquid chamber relative to the static state, m3 is the total mass of the mover with attached liquid in the liquid-filled state, y3 is the displacement of the mover, c3 is the total viscous damping of the mover system including fluid damping and decoupling membrane damping, k3 is the line stiffness of the decoupling membrane, A3 is the piston area of the decoupling membrane pump, A2 is the cross-sectional area of the inertia passage, A1 is the piston area of the rubber main spring pump, y1 is the displacement at the engine end, K1 is the volume stiffness of the rubber main spring, f1 is the constraint reaction force, i.e., the force acting on the engine end, c1 is the viscous damping, k1 is the vertical energy storage dynamic stiffness of the rubber main spring, f5 is the force transmitted to the vehicle body end, represents the first derivative with respect to time, represents the second derivative with respect to time.

[0055] Furthermore, in the two-degree-of-freedom lumped parameter model of the active hydraulic mount, taking the natural frequency f n2 of the inertia passage and the natural frequency f n3 of the actuator as the boundaries, its dynamic characteristics are divided into low-frequency band, mid-frequency band, high-frequency band, mid-low-frequency band and mid-high-frequency band.

[0056] Furthermore, in the two-degree-of-freedom lumped parameter model of the active hydraulic mount, in the mid-low-frequency band, for the fluid in the inertia passage, the non-linear Bernoulli equation considering the friction loss along the passage and the local losses at the inlet and outlet is used; for the decoupling membrane / actuator, the inertia force and damping force of the decoupling membrane / actuator are ignored, and thus it is simplified to a single-degree-of-freedom non-linear model.

[0057] Furthermore, in the two-degree-of-freedom lumped parameter model of the active hydraulic mount, in the mid-high-frequency band, for the fluid in the inertia passage, the movement of the inertia liquid column is ignored, and thus it is simplified to a single-degree-of-freedom linear model.

[0058] Advantages of the present invention:

[0059] ⑴ For the method for identifying the parameters of the active hydraulic mount based on the significant characteristics of the dynamic characteristics of the present invention, for the external dynamic characteristic test of the mount assembly, only the existing mass detection equipment and fixtures for production can be used, with low cost, short cycle and high efficiency.

[0060] ⑵ The active hydraulic mount parameter identification method based on the significant dynamic characteristics of the present invention proposes a complete set of parameter identification methods and processes, and a complete set of parameters of the active hydraulic mount can be obtained; the identification results have good consistency, are accurate and reliable; it solves the requirements of the active control algorithm and algorithm stability for the model parameters and their accuracy, and provides a guarantee for ensuring the active control performance and the stability of active control.

[0061] ⑶ The active hydraulic mount parameter identification method based on the significant dynamic characteristics of the present invention solves the problem that it is inconvenient to directly measure the moving mass and damping of the liquid attached to the liquid filling state; it does not involve the simplification of numerical calculation models such as finite elements, and there is no need to develop additional complex and expensive hydraulic / hydraulic testing equipment, and the non-linear working state of the mount assembly can be accurately reproduced. Description of the Drawings

[0062] Figure 1 Shows the structure diagram of the inertia channel - decoupling membrane - oscillating coil type active hydraulic mount according to the technical solution of the present invention;

[0063] Figure 2 Shows the schematic diagram of the two-degree-of-freedom lumped parameter mechanical model of the inertia channel - decoupling membrane - oscillating coil type active hydraulic mount according to the technical solution of the present invention;

[0064] Figure 3 Shows the schematic diagram of the test curve of the passive characteristics of the inertia channel - decoupling membrane - oscillating coil type active hydraulic mount in the liquid filling state according to the technical solution of the present invention;

[0065] Figure 4 Shows the schematic diagram of the test curve of the active characteristics of the inertia channel - decoupling membrane - oscillating coil type active hydraulic mount in the liquid filling state according to the technical solution of the present invention;

[0066] Figure 5 Shows the schematic diagram of the test curve of the active characteristics of the inertia channel - decoupling membrane - oscillating coil type active hydraulic mount in the liquidless state according to the technical solution of the present invention.

[0067] Figure 1 Among them, 1. Rubber bottom film; 2. Lower liquid chamber; 3. Inertia channel; 4. Decoupling membrane; 5. Upper liquid chamber; 6. Rubber main spring; 7. Actuator mover; 8. Coil; 9. Permanent magnet. Specific Embodiment

[0068] To make the technical means, creative features, achieved purposes and effects of the present invention easy to understand, the present invention will be further described below in conjunction with specific embodiments.

[0069] Embodiment

[0070] The present invention provides an active hydraulic mount parameter identification method based on significant dynamic characteristics, including the following steps:

[0071] S1. Based on the origin or cross-point passive characteristic test curves in the high, medium, and low frequency bands of the active hydraulic mount in the liquid-free state, identify the storage dynamic stiffness k1 of the rubber main spring and the viscous damping c1. Preferably, in step S1, conventional mount dynamic characteristic test equipment such as MTS or inova is used to conduct sweep frequency tests with different displacement amplitudes to directly obtain the storage dynamic stiffness k1 of the rubber main spring and the viscous damping c1. Preferably, in step S1, the displacement excitation amplitude Y1 = 0 - 50 mm and the frequency f = 0 - 1000 Hz.

[0072] S2. Based on the origin or cross-point passive characteristic test curves in the medium and low frequency bands of the active hydraulic mount in the liquid-filled state and its storage dynamic stiffness fixed-point frequency f R and the storage dynamic stiffness k' of the first horizontal segment ∞，1 , identify the natural frequency f n2 of the inertia channel, the volume stiffness K u1 of the upper liquid chamber, and the area A1 of the main spring pump piston:

[0073] f n2 = f R

[0074]

[0075]

[0076] where A2 is the cross-sectional area of the inertia channel; l2 is the length of the inertia channel; k1 is the storage dynamic stiffness of the rubber main spring. Preferably, in step S2, conventional mount dynamic characteristic test equipment such as MTS or inova is used to conduct sweep frequency tests with different displacement amplitudes to obtain the origin or cross-point passive characteristics in the medium and low frequency bands of the active hydraulic mount in the liquid-filled state. Preferably, in step S2, the displacement excitation amplitude Y1 = 0 - 50 mm and the frequency f = 0 - 1000 Hz.

[0077] S3. Based on the origin or cross-point active dynamic characteristic test curves in the high, medium, and low frequency bands of the active hydraulic mount in the liquid-filled state and its horizontal segment F i,∞,4 , the amplitude-frequency response peak A p,1 and the peak frequency f p,1 , identify the decoupling membrane coupling parameter A3·K3, the mover damping ratio ξ3, and the mover natural frequency f n3 :

[0078]

[0079]

[0080]

[0081] where k Mis the voice coil constant. Preferably, in step S3, a conventional suspension dynamic characteristic test device such as MTS or inova is used to conduct a burst random current excitation test, and the frequency response curve of the current to the upper and lower end forces of the suspension is obtained through data processing. Preferably, in step S3, the current excitation amplitude I = 0 - 100 A, the frequency f = 0 - 1000 Hz, and the time t = 0 - 1000 s.

[0082] S4. Based on the active hydraulic mount in the liquid-free state, with or without additional mass m ad of the dynamic characteristics test curves of the actuator in the high, medium, and low frequency bands and their horizontal sections amplitude-frequency response peak A p,3,nof,mad and peak frequency f p,3,nof,mad , identify the mass m of the actuator with or without additional mass m ad , the damping ratio ξ of the actuator with or without additional mass m 3,nof,mad , the natural frequency f of the actuator with or without additional mass m ad , and further identify the net mass m of the actuator in the liquid-free state 3,nof,mad , the decoupling membrane line stiffness k3, the decoupling membrane viscous damping c ad , the natural frequency (without additional mass) f of the actuator n3,nof,mad , the damping ratio (without additional mass) ξ of the actuator 3,nof : 3,nof n3,nof 3,nof 3，nof 3，nof，mad :

[0083]

[0084]

[0085]

[0086] m 3，nof = m 3，nof，mad - m ad

[0087]

[0088]

[0089]

[0090]

[0091] where k M is the voice coil constant. Preferably, in step S4, based on the active hydraulic mount in the liquid-free state, with or without additional mass m ad of the dynamic characteristics test curves of the actuator in the high, medium, and low frequency bands and their horizontal sections amplitude-frequency response peak Ap,3,nof,mad With the peak frequency f p,3,nof,mad , identify the mover mass m ad with or without an additional mass m 3,nof,mad , the mover damping ratio ξ ad with or without an additional mass m 3,nof,mad , and the mover natural frequency f ad with or without an additional mass m n3,nof,mad . Specifically, it includes: using conventional suspension dynamic characteristic test equipment such as MTS or inova, etc., conducting a burst random current excitation test, processing the data to obtain the frequency response curve from current to mover acceleration, and then obtaining the above parameters. Then, the other parameters can be identified by calculating according to the latter five formulas in sequence. Preferably, in step S4, the current excitation amplitude I = 0 - 100A, the frequency f = 0 - 1000Hz, and the time t = 0 - 1000s.

[0092] S5. Based on the parameters identified in S1–S4, further identify the decoupling membrane pump liquid piston area A3, the decoupling membrane volume stiffness K3, the rubber main spring volume stiffness K1, the total mover mass m3 with attached liquid in the liquid-filled state, and the total viscous damping c3 of the mover system including fluid damping and decoupling membrane damping:

[0093] A3(A3K3)=k3

[0094]

[0095]

[0096]

[0097]

[0098] Thus, it can be seen that the method for identifying the parameters of the active hydraulic mount based on the significant dynamic characteristics is based on both the passive characteristics and the active characteristics of the active hydraulic mount; based on both the cross-point dynamic characteristics and the origin dynamic characteristics of the active hydraulic mount; based on both the dynamic characteristics of the active hydraulic mount in the liquid-filled state and the dynamic characteristics of the active hydraulic mount in the liquid-free state; based on the two-degree-of-freedom lumped parameter model of the active hydraulic mount; the two-degree-of-freedom lumped parameter model of the active hydraulic mount, with the inertial channel natural frequency f n2 and the actuator natural frequency f n3Taking [a certain boundary] as the boundary, its dynamic characteristics are divided into low-frequency band, medium-frequency band, high-frequency band, as well as medium-low-frequency band and medium-high-frequency band; for the two-degree-of-freedom lumped parameter model of the active hydraulic mount, in the medium-low-frequency band, ⑴ for the fluid in the inertia channel, the non-linear Bernoulli equation considering the along-way loss and the local losses at the inlet and outlet is used; ⑵ for the decoupling membrane / actuator, the inertia force and damping force of the decoupling membrane / actuator are ignored; ⑶ and then it is simplified to a single-degree-of-freedom non-linear model; for the two-degree-of-freedom lumped parameter model of the active hydraulic mount, in the medium-high-frequency band, ⑷ for the fluid in the inertia channel, the movement of the inertia liquid column is ignored; ⑸ and then it is simplified to a single-degree-of-freedom linear model.

[0099] Figure 1 The figure shows a schematic structural diagram of an oscillating coil actuator type active hydraulic mount with an inertia channel-decoupling membrane type passive hydraulic mount as the carrier. The upper end is connected to the engine / power assembly, and the lower end is connected to the body / frame. Among them, the coil skeleton is rigidly connected to the skeleton of the decoupling membrane 4 and serves as the actuator mover 7; an alternating current is applied to the coil 8, and the coil 8 is subjected to an alternating Ampere force in the magnetic field of the permanent magnet 9 and oscillates up and down. At this time, the Ampere force is the active force f a . The active force f a is transmitted to the body through the secondary channel and cancels out the force transmitted from the engine / power assembly to the body end through the primary channel with equal magnitude and opposite direction, achieving the purpose of reducing vehicle body vibration and noise. The action of the active force f a on the decoupling membrane also simultaneously changes the dynamic characteristics of the hydraulic mount. The working mechanism of the active vibration reduction of the active hydraulic mount can be understood from the perspective of the actuator actively reducing the force transmitted from the engine to the body end, or from the perspective of the actuator actively changing the dynamic characteristics of the hydraulic mount.

[0100]

[0101]

[0102] Table 1 shows the parameters involved in the example of parameter identification of the inertia channel-decoupling membrane-oscillating coil type active hydraulic mount. As described above, first, the original parameters are collected, then the test results are extracted and the parameters are identified based on the passive characteristics, then the test results are extracted and the parameters are identified based on the active characteristics (liquid-filled state), then the test results are extracted and the parameters are identified based on the active characteristics (liquid-free state), and finally, the mount parameters are calculated based on the identified parameters.

[0103] Figure 2 is the two-degree-of-freedom lumped parameter mechanical model of the inertia channel-decoupling membrane-oscillating coil type active hydraulic mount. Based on Figure 1The structure shown above establishes a lumped-parameter mechanical model of an inertia channel-decoupling membrane type active hydraulic mount, which is used for the parameter identification method of the mount. Among them, the displacement at the engine end is y1, and the constraint reaction force, that is, the force acting on the engine end, is f1; the displacement of the inertial liquid column flowing annularly in the horizontal plane relative to the wall of the inertia channel is y2, and the mover displacement is y3 (for a passive mount, it is the decoupling membrane); the displacement at the vehicle body end is y5, and the force transmitted to the vehicle body end is f5; the pressure fluctuations in the upper and lower liquid chambers relative to the static state are p1 and p2 respectively; the active force of the actuator is f a The above are the variables in the lumped-parameter model. Among them, the vertical energy storage dynamic stiffness of the rubber main spring is k1, the viscous damping is c1, and the equivalent concentrated mass at the main spring end is set as m1. The reciprocating motion of the rubber main spring has an extrusion and pumping effect on the fluid in the upper liquid chamber, and its equivalent piston area is set as A1. The volume stiffness is defined as the ratio of the pressure change to the corresponding liquid chamber volume change dp / dV, with the unit of N / m 5 , and the volume stiffness of the rubber main spring is set as K1, and the volume stiffness of the rubber bottom membrane is K2; considering that the volume stiffness of the lower liquid chamber surrounded by the wrinkled rubber bottom membrane is several orders of magnitude smaller than K1, let K2 = 0, so the pressure fluctuation in the lower liquid chamber is not considered in the model either, and let p2 = 0. Let the length of the inertia channel be l2, the cross-sectional area A2, the cross-sectional wetted perimeter L2, and the hydraulic diameter d2 = 4A2 / L2; in the laminar flow state (Reynolds number Re < 2320)

[30] , the friction loss coefficient of the inertia channel along the way is Let the local loss coefficient be Let the mass of the decoupling membrane / mover be m3, the linear stiffness be k3, and the viscous damping be c3; let the equivalent piston area of the decoupling membrane be A3, and the volume stiffness equivalent to the linear stiffness k3 be K3. These are the main parameters of the hydraulic mount.

[0104]

[0105] The above shows the lumped-parameter mathematical model of the inertia channel-decoupling membrane type active hydraulic mount. At Figure 2 Based on the mechanical model of the inertia channel-decoupling membrane type active hydraulic mount shown above, let m1 = 0, y5 = 0, f a = 0, and the mathematical model of the dynamic characteristics of the inertia channel-decoupling membrane type active hydraulic mount is obtained, which are successively the Bernoulli equation of the fluid flow in the inertia channel, the differential equation of the mover motion, the fluid continuity equation, and the equilibrium equation of the constraint reaction force f1 at the engine end of the mount and the force f5 transmitted to the vehicle body end.

[0106] Figure 3 It is the test curve of the passive characteristics of the inertia channel-decoupling membrane-oscillating coil type active hydraulic mount in the liquid-filled state. Based on this, the origin or cross-point passive characteristics in the mid-low frequency band and the fixed-point frequency f of the energy storage dynamic stiffness of the active hydraulic mount in the liquid-filled state are obtained RWith the first horizontal section energy storage dynamic stiffness k′ ∞，1 ; Using conventional suspension dynamic characteristic test equipment such as MTS or inova, etc., conduct sweep frequency tests with different displacement amplitudes to obtain the origin or cross-point passive characteristics in the mid-low frequency band of the active hydraulic mount in the liquid-filled state; The displacement excitation amplitude Y1 = 0 - 50 mm, and the frequency f = 0 - 1000 Hz.

[0107] Figure 4 Is the active characteristic test curve of the inertia channel - decoupling membrane - oscillating coil type active hydraulic mount in the liquid-filled state. Thus, obtain the origin or cross-point active dynamic characteristics and their horizontal section F in the high, mid, and low frequency bands of the active hydraulic mount in the liquid-filled state i,∞,4 、Amplitude-frequency response peak A p,1 And peak frequency f p,1 ; Using conventional suspension dynamic characteristic test equipment such as MTS or inova, etc., conduct burst random current excitation tests, and process the data to obtain the frequency response curve from current to the upper and lower end forces of the suspension; The current excitation amplitude I = 0 - 100 A, the frequency f = 0 - 1000 Hz, and the time t = 0 - 1000 s.

[0108] Figure 5 Is the active characteristic test curve of the inertia channel - decoupling membrane - oscillating coil type active hydraulic mount in the liquid-free state. Thus, obtain the mover active characteristics and their horizontal section in the high, mid, and low frequency bands of the active hydraulic mount in the liquid-free state Amplitude-frequency response peak A p,3,nof,mad And peak frequency f p,3,nof,mad ; Using conventional suspension dynamic characteristic test equipment such as MTS or inova, etc., conduct burst random current excitation tests, and process the data to obtain the frequency response curve from current to mover acceleration; The current excitation amplitude I = 0 - 100 A, the frequency f = 0 - 1000 Hz, and the time t = 0 - 1000 s.

[0109] Thus, based on steps S1 - S5 in the technical solution of the present invention, adopt the suspension dynamic characteristic test method, conduct tests on common dynamic characteristic test equipment, extract relevant results in the tests, and according to the process of S1 - S5, full parameter identification can be achieved.

[0110] Finally, it should be noted that the above embodiments are only used to illustrate the technical solution of the present invention rather than to limit it. Although the present invention has been described in detail with reference to the preferred embodiments, those of ordinary skill in the art should understand that the technical solution of the present invention can be modified or equivalently replaced without departing from the purpose and scope of the technical solution of the present invention, and it should be covered by the scope of the claims of the present invention.

Claims

1. A method for identifying the parameters of an active hydraulic mount based on the significant characteristics of dynamic characteristics, characterized in that, Including the following steps: S1. Based on the origin or cross-point passive characteristic test curves in the high, medium, and low frequency bands of the active hydraulic mount in the liquid-free state, identify the storage dynamic stiffness and viscous damping of the rubber main spring; S2. Based on the origin or cross-point passive characteristic test curves in the medium and low frequency bands of the active hydraulic mount in the liquid-filled state, its storage dynamic stiffness fixed-point frequency and the storage dynamic stiffness of the first horizontal section, and combining with the storage dynamic stiffness of the rubber main spring, identify the natural frequency of the inertia channel, the volume stiffness of the upper liquid chamber, and the area of the main spring pump piston; S3. Based on the origin or cross-point active dynamic characteristic test curves in the high, medium, and low frequency bands of the active hydraulic mount in the liquid-filled state, its horizontal section, amplitude-frequency response peak value and peak frequency, and combining with the volume stiffness of the upper liquid chamber and the area of the main spring pump piston, identify the decoupling membrane coupling parameter, the mover damping ratio, and the mover natural frequency; S4. Based on the mover active characteristic test curves in the high, medium, and low frequency bands of the active hydraulic mount in the liquid-free state with or without additional mass, identify the net mass of the mover in the liquid-free state, the line stiffness of the decoupling membrane, the viscous damping of the decoupling membrane, the mover natural frequency, and the mover damping ratio; S5. Based on the parameters identified in S1–S4, and combining with the decoupling membrane coupling parameter, the mover damping ratio, and the mover natural frequency, further identify the area of the decoupling membrane pump piston, the volume stiffness of the decoupling membrane, the volume stiffness of the rubber main spring, the total mass of the mover with attached liquid in the liquid-filled state, and the total viscous damping of the mover system including fluid damping and decoupling membrane damping, thereby realizing the parameter identification of the active hydraulic mount. Among them, in S1, a suspension dynamic characteristic test device is used to perform a swept-frequency test with different displacement amplitudes to obtain the origin or cross-point passive characteristic test curves in the high, medium, and low frequency bands of the active hydraulic mount in the liquid-free state, and thereby identify the storage dynamic stiffness and viscous damping of the rubber main spring; Among them, in step S2, a suspension dynamic characteristic test device is used to perform a swept-frequency test with different displacement amplitudes to obtain the origin or cross-point passive characteristic test curves in the medium and low frequency bands of the active hydraulic mount in the liquid-filled state, and thereby identify its storage dynamic stiffness fixed-point frequency and the storage dynamic stiffness of the first horizontal section; Among them, in step S3, a suspension dynamic characteristic test device is used to perform a burst random current excitation test, and data processing is performed to obtain the frequency response curve of the current to the upper and lower end forces of the suspension, and obtain the origin or cross-point active dynamic characteristic test curves in the high, medium, and low frequency bands of the active hydraulic mount in the liquid-filled state, and thereby identify its horizontal section, amplitude-frequency response peak value and peak frequency; Among them, in step S4, a suspension dynamic characteristic test device is used to perform a burst random current excitation test, and data processing is performed to obtain the frequency response curve of the current to the mover acceleration, and thereby obtain the mover active characteristic test curves in the high, medium, and low frequency bands of the active hydraulic mount in the liquid-free state with or without additional mass, and further determine its horizontal section, amplitude-frequency response peak value and peak frequency.

2. The active hydraulic mount parameter identification method according to claim 1, wherein In the step S2, based on the origin or cross-point passive characteristic test curve of the mid-low frequency band of the active hydraulic mount liquid filling state and its energy storage dynamic stiffness fixed-point frequency f, the following formula is used R and the energy storage dynamic stiffness k' of the first horizontal section ∞,1 , combined with the energy storage dynamic stiffness k1 of the rubber main spring, to identify the inertial channel natural frequency f n2 , the upper liquid chamber volume stiffness K u1 , and the main spring pump liquid piston area A1: f n2 = f R Among them, A2 is the cross-sectional area of the inertia channel; l2 is the length of the inertia channel; ρ is the fluid density.

3. The active hydraulic mount parameter identification method according to claim 1, characterized in that In the step S3, based on the origin or cross-point active dynamic characteristic test curves in the high, medium, and low frequency bands of the active liquid resistance mount's liquid filling state and their horizontal section F i,∞,4 , amplitude-frequency response peak value A p,1 and peak frequency f p,1 , combined with the volume stiffness of the upper liquid chamber and the area of the main spring pump liquid piston, identify the decoupling membrane coupling parameters A3·K3, mover damping ratio ξ3, and mover natural frequency f n3 : where k M is the voice coil constant, A3 is the decoupling membrane pump liquid piston area, and K3 is the decoupling membrane volume stiffness.

4. The active hydraulic mount parameter identification method according to claim 1, characterized in that, The specific content of step S4 includes: Based on the test curves of the active characteristics of the mover in the high, medium, and low frequency bands with or without additional mass in the liquid-free state of the active hydraulic mount, as well as their horizontal sections, amplitude-frequency response peaks, and peak frequencies, identify the mass of the mover with or without additional mass, the damping ratio of the mover with or without additional mass, and the natural frequency of the mover with or without additional mass. Furthermore, identify the net mass of the mover in the liquid-free state, the stiffness of the decoupling membrane line, the viscous damping of the decoupling membrane, the natural frequency of the mover, and the damping ratio of the mover.

5. The active hydraulic mount parameter identification method according to claim 4, characterized in that In the step S4, the following formula is adopted to identify the moving element net mass m, decoupling membrane line stiffness k3, decoupling membrane viscous damping c, moving element natural frequency f, and moving element damping ratio ξ without liquid based on the high, medium, and low frequency segment moving element active characteristic test curves and their horizontal segments of the active fluid resistance mount in the liquid-free state with or without additional mass m ad with or without additional mass m amplitude-frequency response peak A p,3,nof,mad and peak frequency f p,3,nof,mad , and identify the moving element mass m ad with or without additional mass m 3,nof,mad , the moving element damping ratio ξ ad with or without additional mass m 3,nof,mad , and the moving element natural frequency f ad with or without additional mass m n3,nof,mad , and then identify the moving element net mass m 3,nof , decoupling membrane line stiffness k3, decoupling membrane viscous damping c 3,nof , moving element natural frequency f n3,nof , and moving element damping ratio ξ 3,nof : m 3,nof = m 3,nof,mad -m ad where k M is the voice coil constant.

6. The active hydraulic mount parameter identification method according to claim 1, characterized in that In step S5, the following formulas are used to further identify the piston area A3 of the decoupling membrane pump, the volume stiffness K3 of the decoupling membrane, the volume stiffness K1 of the rubber main spring, the total mass m3 of the mover with attached liquid in the liquid-filled state, and the total viscous damping c3 of the mover system including fluid damping and decoupling membrane damping based on the parameters identified in S1–S4: A3(A3K3) = k3 7. The method for identifying the parameters of the active hydraulic mount according to claim 1, wherein Before the step S1, there is also a step S0: collecting original data: fluid density ρ, inertial channel length l2, inertial channel cross-sectional area A2, voice coil constant k M and gravitational acceleration g.

8. The method for identifying the parameters of the active hydraulic mount according to claim 1, characterized in that The two-degree-of-freedom lumped parameter model of the active hydraulic mount is as follows: where ρ is the fluid density, l2 is the length of the inertia channel, y2 is the displacement of the inertia liquid column in the annular flow in the horizontal plane relative to the wall of the inertia channel, is the coefficient of head loss along the inertia channel, is the local loss coefficient, p1 is the pressure fluctuation of the upper liquid chamber relative to static, m3 is the total mass of the mover with attached liquid in the liquid-filled state, y3 is the displacement of the mover, c3 is the total viscous damping of the mover system including fluid damping and decoupling membrane damping, k3 is the line stiffness of the decoupling membrane, A3 is the liquid pumping piston area of the decoupling membrane, A2 is the cross-sectional area of the inertia channel, A1 is the liquid pumping piston area of the main spring, y1 is the displacement at the engine end, K1 is the volume stiffness of the rubber main spring, f1 is the constraint reaction force, i.e., the force acting on the engine end, c1 is the viscous damping, k1 is the vertical energy storage dynamic stiffness of the rubber main spring, f5 is the force transmitted to the vehicle body end, represents the first derivative with respect to time, represents the second derivative with respect to time.

9. The method for identifying the parameters of the active hydraulic mount according to claim 8, wherein In the two-degree-of-freedom lumped parameter model of the active hydraulic mount, with the natural frequency f n2 of the inertia passage and the natural frequency f n3 of the actuator as the boundaries, its dynamic characteristics are divided into low-frequency band, mid-frequency band, high-frequency band, mid-low-frequency band and mid-high-frequency band.

10. The active hydraulic mount parameter identification method according to claim 8, characterized in that, In the two-degree-of-freedom lumped parameter model of the active hydraulic mount, in the medium and low frequency bands, for the fluid in the inertia channel, the nonlinear Bernoulli equation considering the frictional loss along the way and the local losses at the inlet and outlet is used; for the decoupling membrane / actuator, the inertial force and damping force of the decoupling membrane / actuator are ignored, and it is further simplified to a single-degree-of-freedom nonlinear model.

11. The method for identifying the parameters of the active hydraulic mount according to claim 8, wherein In the two-degree-of-freedom lumped parameter model of the active hydraulic mount, in the medium and high frequency bands, for the fluid in the inertia channel, the movement of the inertial liquid column is ignored, and it is further simplified to a single-degree-of-freedom linear model.

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