CN112413030A - Shock absorber damping control and performance evaluation method, shock absorber optimized by using same and vehicle adopting shock absorber - Google Patents
Shock absorber damping control and performance evaluation method, shock absorber optimized by using same and vehicle adopting shock absorber Download PDFInfo
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- CN112413030A CN112413030A CN202010780692.1A CN202010780692A CN112413030A CN 112413030 A CN112413030 A CN 112413030A CN 202010780692 A CN202010780692 A CN 202010780692A CN 112413030 A CN112413030 A CN 112413030A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
- F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
- F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
- F16F9/19—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein with a single cylinder and of single-tube type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/3207—Constructional features
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/3207—Constructional features
- F16F9/3214—Constructional features of pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/3207—Constructional features
- F16F9/3221—Constructional features of piston rods
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/3207—Constructional features
- F16F9/3235—Constructional features of cylinders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/48—Arrangements for providing different damping effects at different parts of the stroke
Abstract
The method uses the difference value of the gravity of a vehicle body part supported by a supporting spring minus the supporting force value of a current stroke position of a set supporting spring or an equivalent supporting spring as the basis for calculating the reference force value of the tensile damping force value or the compression damping force value of the current stroke position of the shock absorber; and the reference force value of the shock absorber at the stroke position is used as a basis for controlling or setting the damping force value of the shock absorber and as a basis for judging the performance of the shock absorber. The method can visually judge the comfort degree of the shock absorber, the supporting spring and the vehicle weight after being matched, so that the debugging of the vehicle suspension, the selection and the matching of the shock absorber and the supporting spring become easier, and simultaneously, the optimal damping control scheme of the shock absorber is also disclosed, and the problem of how to achieve the optimal damping of the shock absorber, which troubles the shock absorber industry for a long time, is solved.
Description
Technical Field
The present invention relates generally to design, manufacture and performance evaluation of vehicle shock absorbers.
Background
For a long time, the consistent view of the damping control method of the shock absorber by engineering technicians is as follows: when the road surface is uneven, the rigidity of the supporting spring is smaller, the damping of the shock absorber is smaller, and the comfort is better. Due to the technical consciousness of engineering technicians engaged in the shock absorber, the problems of design and manufacture of the shock absorber and matching of the shock absorber with a vehicle and a supporting spring are not effectively solved, even the most advanced shock absorber damping control technology at present cannot fundamentally solve the essential problems related to the design of the shock absorber, so that the problems of complex processes such as obtaining road condition information according to 3D camera shooting to control the damping of the shock absorber, controlling the damping of the shock absorber according to the vibration condition of the vehicle, and adopting manual setting of different damping or automatic adjustment of the damping of the shock absorber according to certain vehicle condition information cannot effectively solve the damping control problem of the shock absorber, and the optimal damping control effect cannot be achieved. Therefore, there is also no most direct quantitative determination criterion as to the superiority and inferiority of the damper performance. There is of course no associated quantitative criterion for matching the shock absorber to the vehicle support spring to determine how well the damping force values of the shock absorber affect vehicle comfort.
The current standard for measuring the performance of the shock absorber is to use the tensile damping force values of the shock absorber at a plurality of specified speeds and the compressive damping force values at a plurality of specified speeds as the standard for judging whether the shock absorber is qualified or not, namely, the commonly used shock absorber indicator method is used for judging whether the shock absorber is qualified or not. But the qualified shock absorber taking the standard as the standard can not ensure the comfort after matching with the supporting spring and loading. The existing measuring method and the measured value of the shock absorber have no direct regular following correlation with the comfort of the shock absorber after being installed, so that the matching of the shock absorber and the rigidity of the supporting spring and the weight of the vehicle body is not better selected by a referential theoretical basis and a practical scheme, so that the matching of the shock absorber and the rigidity of the supporting spring and the weight of the vehicle body is completely dependent on the experience or subjective consciousness of vehicle design or debugging personnel to judge the matching reasonability or comfort. The characteristic of most common shock absorbers at the present stage is that the shock absorbers have approximately the same damping force value at different stroke positions. Even if a shock absorber is used in which a small number of different stroke positions correspond to different damping force values, there is no clear standard for the correspondence between the stroke positions and the damping force values.
Disclosure of Invention
Technical problem to be solved by the invention
The comfort of the vehicle in the running process is directly related to the resultant force of the support spring and the shock absorber on the support force of the vehicle body, the faster the change rate of the resultant force is, the larger the change amplitude is, the more the vehicle shakes or turns up and limps, and the worse the comfort is. On the contrary, the more the variation amplitude of the resultant force value is close to zero, the lower the frequency is, the better the comfort is, when the road surface is uneven, the supporting force value of the spring to the vehicle body can be changed along with the fluctuant road surface, and the shock absorber has the function of adjusting the supporting force value of the spring, so that the supporting force value of the supporting spring and the shock absorber to the vehicle is more gentle and stable, and the comfort in the driving process of the vehicle is improved. The support spring for vehicles is generally composed of a gas spring, a liquid gas spring, a leaf spring, or a coil spring. After the initial values of the gas spring, the liquid-gas spring, the steel plate spring and the spiral spring are determined, the rigidity value or the force value and the travel position of the gas spring, the liquid-gas spring, the steel plate spring and the spiral spring are changed according to a certain rule. In order to improve the comfort of the vehicle during the running process, the best method is to minimize the variation amplitude of the supporting resultant force value of the spring and the damper for supporting the vehicle, and to approach or equal the gravity of the part of the supporting spring and the damper for supporting the vehicle as much as possible.
The problem of a method for shock absorber damping control and performance assessment is solved according to the action of a vehicle supporting spring and the working principle of a shock absorber, and the method can visually judge the performance of the shock absorber according to test data. And the comfort degree of the shock absorber and the supporting spring matched with the vehicle weight can be visually judged according to the data according to the method for matching the performance of the shock absorber with the supporting spring and the quantitative standard. The tuning, selection and matching of the shock absorber and the supporting spring of the vehicle suspension is made easier. Meanwhile, an optimal damping control scheme is provided for the controllable damping shock absorber. The problem of how to achieve optimal damping of the shock absorber, which troubles the shock absorber industry for a long time, is solved.
Technical scheme of the invention
the difference F1 between the set force value F3 and the actual gravity value of the object and the support force value F2 of the set support spring or equivalent support spring (1) at each stroke position is used as a determination value, and the difference F1 is a set of functions corresponding to the stroke position s (the length of the spring after being stretched or compressed) of the set support spring or equivalent support spring one by one.
When the difference is negative, the absolute value of the difference F1 is used as the reference force value of the tensile damping force value at the current stroke position of the shock absorber. And when the difference value is not a negative value, taking the minimum damping force value which can be reached by the tensile damping force value as the reference force value of the tensile damping force value of the current stroke position of the shock absorber. Such as the absolute value corresponding to F1' in fig. 2. Namely the current stroke position, when the difference is negative, the reference force value of the tensile damping force value is equal to the absolute value of the difference; and when the difference value is positive or zero, taking the minimum force value which can be reached by the stretching damping force value as the reference force value of the stretching damping force value at the current position.
And if the difference value is positive, taking the difference value as a reference force value of the compression damping force value of the current stroke position of the shock absorber. And when the difference value is not a positive value, taking the minimum damping force value which can be reached by the compression damping force value as a reference force value of the compression damping force value of the current stroke position of the shock absorber. Such as the value corresponding to F1 "in fig. 2. Namely the current stroke position, and if the difference is positive, the reference force value of the compression damping force value is equal to the difference; and when the difference value is negative or zero, taking the minimum force value which can be reached by the compression damping force value as the reference force value of the compression damping force value at the current position.
The tension damping force reference value and the compression damping force reference value of the shock absorber are respectively a group of force value data and are functions corresponding to the stroke position of the support spring and the force value of the support spring; is directly related to the stiffness of the spring, the weight of the supported object, and the compression stroke of the spring, and corresponds to one another. Any stroke position of the shock absorber has a corresponding tensile damping reference force value and a corresponding compression damping reference force value. For example: at position S3 in fig. 2, the corresponding tensile damping reference force value is the absolute value of Fl' at position S3, the compressive damping reference force value is the minimum force value that can be achieved by compressive damping, and the corresponding stroke position of the spring and the shock absorber is S3.
And taking the reference force value of the shock absorber at the stroke position as a basis for controlling or setting the tensile damping force value or the compressive damping force value of the shock absorber at the stroke position, and enabling the tensile damping force value of the shock absorber to be as close to or equal to the reference force value of the tensile damping force value as possible or enabling the compressive damping force value of the shock absorber to be as close to or equal to the reference force value of the compressive damping force value as possible, so that the performance of the shock absorber is optimal, and the tensile damping force value or the compressive damping force value of the shock absorber is controlled.
And comparing the reference force value of each stroke position of the shock absorber with the tensile damping or compressive damping force value of the shock absorber at the stroke position, wherein the closer the tensile damping force value of the shock absorber is to the reference force value of the tensile damping force value or the compressive damping force value of the shock absorber is to the reference force value of the compressive damping force value of the shock absorber, the better the performance of the shock absorber is, and the more the performance of the shock absorber is taken as the basis for judging the performance of the shock absorber.
When the reference force value is used for controlling the stretching damping force value or the compression damping force value of the shock absorber, a force measuring device is not needed to measure the real-time supporting force value of the supporting spring, and the force measuring device can be used for measuring the real-time supporting force value of the supporting spring if necessary so as to achieve the purpose of accurately controlling the damping force value of the shock absorber under certain conditions.
The equivalent supporting spring refers to a supporting spring with the acting force effect the same as that of the equivalent substituted supporting spring, and the force direction and the force position of the equivalent spring and the shock absorber are approximately the same. Namely, the effect of the acting force of a specific or actual supporting spring on the supported object is equivalently converted into a supporting spring (for example, converted into a spiral spring) which is coaxially arranged with the shock absorber (the force direction and the force position are approximately the same), and the supporting spring which is coaxially arranged with the shock absorber is the equivalent supporting spring of the original supporting spring. The acting force effect of the equivalent supporting spring on the support is the same as that of the original supporting spring on the support, but the size parameters, the installation mode and the installation position of the spring are not necessarily the same as those of the equivalent supporting spring.
The strut type shock absorber, i.e. the shock absorber in which the shock absorber and the supporting spring are integrally installed, the primary spring of the shock absorber can be used as the equivalent supporting spring of the shock absorber.
The shock absorber and the supporting spring are separately installed, the acting force effect of the supporting spring on the support is equivalently converted into the supporting spring which is coaxially installed with the shock absorber, and the supporting spring which is coaxially installed with the shock absorber is the equivalent supporting spring of the original supporting spring.
The above-mentioned equivalent support springs include a coil spring, a gas spring, a plate spring, etc., which are commonly used.
The calibration of the compression damping force value or the tension damping force value of the shock absorber is divided into the following two conditions:
1. for the shock absorber which can not measure the compression damping force value or the tensile damping force value in real time, because the compression damping force value or the tensile damping force value of the current stroke position of the shock absorber is related to the compression speed or the tensile speed of the shock absorber, the tensile damping force value or the compression damping force value of the current position of the shock absorber at a specific speed is usually taken as a calibration value and compared with a reference force value, and the comparison result is taken as the basis for evaluating the performance judgment of the shock absorber or the basis for damping control of the shock absorber. And if the tensile damping force value of each corresponding position at the tensile speed of 0.52 meters per second is compared with the tensile damping reference force value or the compressive damping force value at the compressive speed of 0.52 meters per second is compared with the compressive damping reference force value, judging the performance of the shock absorber or controlling the damping of the shock absorber according to the comparison result. The tensile or compressive speed value during the test of the shock absorber can be different, such as 0.2 meter per second, 2 meters per second and the like, according to the actual shock absorption effect.
2. For the electronic control damping shock absorber capable of controlling the damping of the shock absorber in real time, the damping force value of the current position of the shock absorber can be controlled according to the reference force value of the current position of the shock absorber, so that the real-time tensile damping force value or the compressive damping force value of the shock absorber is close to or equal to the reference force value. The electronic control damping vibration absorber of the schemes 3 and 4.
Controlling the tensile damping force value or the compressive damping force value of the shock absorber by using the reference force value to enable the tensile damping force value or the compressive damping force value to be close to the reference force value, namely:
a. when the current stroke position of the shock absorber and the supporting force value of the supporting spring are larger than the gravity of an object supported by the supporting spring, the tensile damping force value of the shock absorber at the current stroke position is controlled or set to increase along with the increase of the reference force value or decrease along with the decrease of the reference force value so as to be close to the reference force value, and meanwhile, the compression damping force value of the shock absorber at the current stroke position is controlled or set to be close to zero, so that the better the performance of the shock absorber is.
b. When the supporting force value of the supporting spring at the current stroke position is smaller than the gravity of an object supported by the supporting spring, the compression damping force value of the current stroke position of the shock absorber is controlled or set to increase along with the increase of the reference force value or decrease along with the decrease of the reference force value, so that the compression damping force value is closer to the reference force value, and meanwhile, the tension damping force value of the shock absorber at the current stroke position is controlled or set to be close to zero, so that the performance of the shock absorber is better.
The damping force value (reference force value) of the shock absorber is shown schematically in relation to the stroke position (as shown in fig. 2):
in the figure, the shock absorbers s 0-s 5 are taken as specific stroke position points, and the force value F1 of the shock absorber is marked as F1 'when the tensile damping force value is taken, and the force value F1 of the shock absorber is marked as F1' when the compressive damping force value is taken. F1 'is the curve of the corresponding of the tensile damping force value and the stroke position of the shock absorber, F1' is the curve of the corresponding of the compressive damping force value and the stroke position of the shock absorber, F2 is the corresponding line of the supporting force value and the stroke position of the supporting spring, and F3 is the corresponding line of the gravity value and the stroke position of the vehicle body.
The optimal force values (reference force values) corresponding to the stroke positions of the shock absorber in the figure are as follows:
when the shock absorber is tending to or is compressing,
s0 should correspond to a compressive damping force value Fa that is close to F3 (Fe) minus Fb,
s1 should correspond to a compressive damping force value Fj that is close to F3 (Fe) minus Fc,
s2 should correspond to a compressive damping force value Fk that is close to F3 (Fe) minus Fd,
in the figure, when the shock absorber is at the compression stroke positions s3, s4 and s5, the support force value of the support spring is larger than the gravity of the vehicle body, and the force value of the shock absorber during compression cannot be a negative value, so that the compression damping force value can only be set to Fn which is the smallest in absolute value.
When the shock absorber is tending to or is being stretched,
in the figure, when the extension stroke position of the shock absorber is s0, s1 and s2, the force value of the supporting spring is smaller than the gravity of the vehicle body, the force value of the shock absorber in extension cannot be positive, so that the extension damping force value can only be set to Fk' with the minimum absolute value,
the tensile damping force value Fl 'for S3 should be close to F3 (Fe) minus Fg',
the tensile damping force value Fm 'for S4 should be close to F3 (Fe) minus Fh',
the tensile damping force value Fn 'for S5 should be close to F3 (Fe) minus Fi'.
The damping of the shock absorber in the solutions described in the solutions 5 to 8 herein is set by using the tensile damping force value or the compressive damping force value of the shock absorber at a specific speed as the measurement standard for evaluating or controlling the damping force value of the shock absorber, that is, the tensile damping force value or the compressive damping force value at the specific speed is compared with the reference force value of the shock absorber, and is controlled and determined, so that the closer the value is to the reference force value, the better the performance of the shock absorber is. For example, the tensile damping force value at each corresponding position at a tensile speed of 0.52 m/sec is set or controlled at a tensile damping reference value, or the compressive damping force value at a compressive speed of 0.52 m/sec is set or controlled at a compressive reference value such that the tensile damping force value or the compressive damping force value at a speed of 0.52 m/sec is close to or equal to the reference force value.
The shock absorber adopts the reference damping force value as the basis for controlling the tensile damping force value or the compression damping force value, and the damping force value is changed along with the stroke position.
The shock absorber according to the claim 3 (fig. 3, fig. 4) or the claim 2 comprises a measuring device (body height measuring device) for measuring the stroke position of the shock absorber, a controller and an electrically controlled damping valve, and is characterized in that: the stretching damping valve or the compressing damping valve of the shock absorber is an electric control damping valve, the stroke position of the shock absorber is provided for a controller by a shock absorber stroke position measuring device (vehicle body height measuring device), and the controller controls the damping force value of the electric control stretching damping valve or the electric control compressing damping valve according to the vehicle body height (stroke position of the shock absorber) and a reference force value.
The shock absorber stroke position measuring device refers to a device which can directly or indirectly measure the shock absorber stroke position, such as the shock absorber stroke position which can be indirectly measured by a vehicle body height measuring device.
The electric control damping valve refers to a valve component for controlling the tensile damping force value or the compressive damping force value of the electric control shock absorber, and the damping force value of the valve component is controlled by current or voltage, such as an electromagnetic valve, a magnetorheological damper and the like.
The electric control damping shock absorber refers to a shock absorber in which one damping force value of the damping force values in the stretching process or the compression process of the shock absorber is controlled by voltage or current, or both the damping force values are controlled by voltage or current. Namely, the stretching valve or the compression valve of the electric control shock absorber is an electric control damping valve, or the stretching valve and the compression valve are both electric control damping valves.
When the damping valve of the shock absorber is an electric control damping valve, the following two schemes can be adopted:
1. (figure 3) calibrating the corresponding relation between the tension damping force value and the compression damping force value of the electric control shock absorber at a specific tension or compression speed and the current or voltage, and then controlling the current value or the voltage value of the current electric control damping valve according to the reference force value of the current position, so that the tension damping force value and the compression damping force value of the current stroke position of the shock absorber increase and decrease along with the reference force value.
Because of the one-to-one correspondence relationship between the reference force value of the shock absorber at a specific speed and the stroke of the shock absorber, the tensile damping force value or the compressive damping force value of the shock absorber should also change following the stroke change of the shock absorber. The tension or compression damping force value of the shock absorber can be controlled according to the height of the vehicle body, the stroke of the shock absorber or the stroke of the spring according to the corresponding reference force value.
2. And additionally arranging a force transducer on the shock absorber, measuring the tensile damping force value or the compressive damping force value of the shock absorber in real time, comparing the real-time tensile damping force value or the compressive damping force value with the reference force value of the current position, and controlling the tensile damping or the compressive damping of the shock absorber in real time according to the comparison result.
Optimal correspondence of shock absorber stroke position and current value of the electrically controlled damping valve (as shown in fig. 2):
the ordinate represents the current value of the electronically controlled damping valve and the stroke position of the shock absorber, respectively, and the abscissa represents the force value, where the shock absorbers s 0-s 5 are taken as specific stroke position points in the figure, se is the intersection point when the supporting force is equal to the set force value or the weight of the object, the force value F1 of the shock absorber is marked as F1 'when the tensile damping force value is taken, and the force value F1 of the shock absorber is marked as F1' when the compressive damping force value is taken. F1 'is a curve of the corresponding of the tensile damping force value and the stroke position of the shock absorber, F1' is a curve of the corresponding of the compressive damping force value and the stroke position of the shock absorber, F2 is a corresponding line of the supporting force value and the stroke position of the supporting spring, F3 is a line segment of the corresponding of the gravity value and the stroke position of the vehicle body, Aa 'curve represents the corresponding relation of the tensile damping force value and the control current of the tensile damping valve when the electric control damping valve is the tensile valve, and Aa' curve represents the corresponding relation of the compressive damping force value and the control current of the compressive damping valve when the electric control damping valve is the compressive valve.
In the figure, the optimal force value corresponding to each stroke position of the shock absorber and the optimal control current value of the electric control damping valve are as follows:
when the shock absorber is tending to or compressing:
the compression damping force value Fa corresponding to s0 should be close to F3 (Fe) minus Fb, and when the value of Fa is reached, the control current value should be set to be close to A-Fa when the compression valve is an electric control damping valve;
the compression damping force value Fj corresponding to s1 should be close to F3 (Fe) minus Fc, and when the value of Fj is reached, the control current value should be set to be close to A-Fj when the compression valve is an electric control damping valve;
the compression damping force value Fk corresponding to s2 should be close to F3 (Fe) minus Fd, and when the value of Fk is reached, the control current value should be set to be close to A-Fk when the compression valve is an electric control damping valve;
in the figure, when the compression stroke position of the shock absorber is s3, s4 and s5, the support force value of the support spring is already larger than the gravity of the vehicle body, the force value of the shock absorber during compression cannot be negative, so that only the minimum compression damping force value Fn can be set, and the control current of the compression valve as the electric control damping valve can be set to 0.
When the damper is tending or stretching:
when the stretching stroke position of the shock absorber is s0, s1, s2, the supporting force value of the supporting spring is smaller than the gravity of the vehicle body, the force value of the shock absorber during stretching can not be positive, so that only the stretching damping force value can be set to Fk' with the minimum absolute value, and the control current of the stretching valve and the electric control damping valve can be set to 0 at the moment.
The tensile damping force value Fl 'corresponding to S3 is close to F3 (Fe) minus Fg', and when the force value Fl 'is reached, the control current value is set to be close to A-Fl' when the compression valve is an electric control damping valve;
the tensile damping force value Fm 'corresponding to S4 is close to F3 (Fe) minus Fh', and when the force value Fm 'is reached, the control current value is set to be close to A-Fm' when the compression valve is an electric control damping valve;
the tensile damping force value Fn 'corresponding to S5 should be close to F3 (Fe) minus Fi', and to achieve the Fn 'force value, the control current value should be set to be close to A-Fn' when the compression valve is an electrically controlled damping valve.
In the shock absorber according to the scheme 4 (fig. 4) or the scheme 3, the force sensor is arranged on the shock absorber, the force sensor measures the tensile or compressive damping force value of the shock absorber, the controller compares the reference force value corresponding to the current stroke position of the shock absorber with the real-time tensile damping force value or the real-time compressive damping force value of the current position, and controls the tensile damping force value or the compressive damping force value of the current stroke of the shock absorber to be close to or equal to the reference force value according to the comparison result.
The scheme measures the tensile damping force value or the compressive damping force value of the shock absorber in real time, compares the tensile damping force value or the compressive damping force value with the reference force value of the current position, and controls the tensile damping or the compressive damping of the shock absorber in real time according to a comparison result. The control method comprises the following steps:
a. when the electrically controlled stretching damping valve is arranged, and the current stroke position of the shock absorber is determined, and the value measured by the force sensor on the shock absorber is tensile force, the stretching damping valve of the shock absorber is controlled according to the stretching damping reference force value of the current position of the shock absorber, so that the stretching damping force value of the current stroke position of the shock absorber is close to or equal to the stretching damping reference force value of the current position of the shock absorber.
b. When the electric control compression damping valve is arranged, and the current stroke position of the shock absorber is the pressure value measured by the force transducer on the shock absorber, the compression damping valve of the shock absorber is controlled according to the compression damping reference force value of the current position of the shock absorber, so that the compression damping force value of the current stroke position of the shock absorber is close to or equal to the compression damping reference force value of the current position of the shock absorber.
The shock absorber of the scheme 5 and the scheme 2, wherein the damping force value is changed along with the stroke position (shown in figures 5, 6 and 7): the method is characterized in that: a damping hole with the drift diameter size changing along with the stroke position of the shock absorber is arranged between the stretching cavity and the compression cavity of the shock absorber, and the drift diameter size of the damping hole is based on the reference force value as the basis for controlling the stretching damping force value or the compression damping force value of the shock absorber, so that the damping force value of each stroke position of the shock absorber at the set stretching speed or the set compression speed is equal to or close to the reference force value.
Solution 6 (fig. 5), the shock absorber with damping force value varying with stroke position according to solution 5 is characterized in that: one of the damping valves mainly comprises a damping rod and a central damping hole, the piston rod is a hollow tube, the hollow part is communicated with the stretching cavity, the central damping hole is arranged at the end, close to the piston, of the piston rod, and the damping rod is a rod with different sectional areas of all parts; the damping rod can be connected to the bottom of the hydraulic cylinder, can be connected to a bottom valve of the shock absorber, and can also be connected to a bottom valve or a floating piston of the single-cylinder shock absorber; the damping rod passes through the central damping hole, and forms the tensile damping valve hole of different latus rectum corresponding with shock absorber stroke position with central damping hole. The drift diameter of the damping hole takes the reference force value of the tensile damping as the reference for controlling or setting the tensile damping force value of the shock absorber, so that the damping force value of each stroke position of the shock absorber at the set tensile speed is equal to or close to the reference force value.
The shock absorber with damping force value changing along with stroke position according to the scheme 7 (figure 6) and the scheme 5 is characterized in that: one of the damping valves mainly comprises a damping rod and a central damping hole, the piston rod is a hollow tube, the hollow part is communicated with the stretching cavity, the central damping hole is arranged at the end, close to the piston, of the piston rod, and the damping rod is a rod with different sectional areas of all parts; the stretching cavity is communicated with the liquid storage cavity through a one-way valve, and the damping rod can be connected to the bottom of the hydraulic cylinder, can be connected to a bottom valve of the shock absorber, and can also be connected to a bottom valve or a floating piston of the single-cylinder shock absorber; the damping rod passes through the central damping hole, and forms compression damping holes with different drift diameters corresponding to the stroke position of the shock absorber together with the central damping hole. The drift diameter of the damping hole is based on the reference force value of the compression damping force value as the basis for controlling or setting the compression damping force value of the vibration absorber, so that the compression damping force value of each stroke position of the vibration absorber at the set compression speed is equal to or close to the reference force value.
When the shock absorber is compressed, liquid flows into the liquid storage cavity through the damping hole, the stretching cavity and the one-way valve. When the shock absorber is stretched, liquid flows into the compression cavity through the damping hole, the check valve on the piston and the check valve on the bottom valve.
Scheme 8 (figure 7), a shock absorber that the damping force value changes along with the stroke position according to the scheme 5, comprising a variable cross section hydraulic cylinder, a piston and a one-way valve; the method is characterized in that: the size of the inner section area of the variable-section cylinder barrel is changed along the center line of the cylinder barrel, the inner section of the cylinder barrel and the piston form a damping hole with different diameters between the stretching cavity and the compression cavity, and the diameter of the damping hole takes the reference force value of the tensile damping force value as the basis for controlling or setting the tensile damping force value of the shock absorber, so that the tensile damping force value of each stroke position of the shock absorber at the set stretching speed is equal to or close to the reference force value.
When the shock absorber is compressed, liquid flows into the stretching cavity through the one-way valve and the damping gap, the one-way valve is closed when the shock absorber is stretched, and the liquid flows out of the stretching cavity through the damping gap to form stretching damping force.
A vehicle, characterized by: the vehicle adopts one of the shock absorbers in the schemes 2-8.
The invention has the advantages of
1. The performance of the shock absorber can be visually judged according to the test parameters of the shock absorber;
2. the damping control method or standard of the shock absorber is provided, so that the damping control of the shock absorber becomes more accurate and easier;
3. the method for matching the shock absorber with the supporting spring and the vehicle is provided, so that the shock absorber can be matched with the supporting spring and the vehicle very easily, and the comfort of the vehicle can be greatly improved;
4. the problem that the damping matching of the shock absorber can not be optimized for a long time is solved;
5. the method provides a better scheme for designing and manufacturing the shock absorber;
6. the vehicle using the shock absorber has smaller fluctuation and bump amplitude in the driving process, so that the vehicle can run more stably and comfortably.
Drawings
FIG. 1 is a schematic diagram showing the stroke correspondence between the shock absorber and the supporting spring
FIG. 2 is a schematic diagram showing the relationship between the force values, the stroke, the current of the electrically controlled damper valve, etc. related to the shock absorber
FIG. 3 is a schematic view of a damping control scheme of an electronically controlled damping valve of an electronically controlled shock absorber
FIG. 4 is a schematic diagram of an electric control principle of an electric control damper with a load cell
FIG. 5 is a schematic view of a shock absorber with a tensile damping gap path that changes with stroke position
FIG. 6 is a schematic view of a shock absorber with the compression damping gap path varying with stroke position
FIG. 7 is a schematic view of a shock absorber with a variable cross-section hydraulic cylinder
FIG. 8 is a schematic diagram of the damping gap formed by the A-A sectioning position variable cross-section hydraulic cylinder and the piston of the shock absorber in FIG. 7
FIG. 9 is a schematic diagram of the damping gap formed by the variable cross-section hydraulic cylinder and the piston at the cutting position of the B-B of the shock absorber in FIG. 7
FIG. 10 is a schematic diagram of damping clearance formed by the C-C cutting position variable cross-section hydraulic cylinder and the piston of the shock absorber in FIG. 7
Graphic numbering names:
1-supporting spring 2-shock absorber 3-stretching cavity
4-liquid storage cavity 5-one-way valve 6-damping valve control cable
7-electric control damping valve 8-hydraulic pipeline 9-controller
10-piston 11-compression chamber 12-bottom valve
13-piston rod 14-center damping hole
15-flow path in tension (part of flow also passes here in compression)
16-one-way back pressure valve 17-damping rod 18-damping rod cross section view
23-flow path 27 during compression-sealing ring 28-variable cross-section hydraulic cylinder
29-damping gap formed by the variable cross section hydraulic cylinder and the piston 30-load cell.
Detailed Description
Preferred embodiment 1: a method for determining the performance of a shock absorber (as shown in figure 1 and figure 2)
The force value F1 for the shock absorber is labeled F1 'for a tensile damping force value and F1' for a compressive damping force value of the shock absorber force value F1.
When the supporting force value of the supporting spring is F2, and the gravity value of the vehicle body supported by the supporting spring and the shock absorber is F3, the more the tensile damping force value F1 'and the compression resistance value F1' of the shock absorber are close to F3 minus F2, the better the performance of the shock absorber is.
The relationship between the damping force value and the stroke position of the shock absorber is shown schematically (as shown in figure 2):
in the figure, the shock absorbers s 0-s 5 are taken as specific stroke position points, F1 'is a curve corresponding to the tensile damping force value and the stroke position of the shock absorber, F1' is a curve corresponding to the compression damping force value and the stroke position of the shock absorber, F2 is a curve corresponding to the supporting force value and the stroke position of a supporting spring, and F3 is a curve corresponding to the gravity value and the stroke position of a vehicle body.
The optimal force values for each stroke position of the shock absorber in the figure are as follows:
when the shock absorber is tending to or is compressing,
s0 should correspond to a compressive damping force value Fa that is close to F3 (Fe) minus Fb,
s1 should correspond to a compressive damping force value Fj that is close to F3 (Fe) minus Fc,
s2 should correspond to a compressive damping force value Fk that is close to F3 (Fe) minus Fd,
in the figure, when the compression stroke positions of the shock absorber are s3, s4 and s5, the support force value of the support spring is already larger than the gravity of the vehicle body, so that only the minimum compression damping force value Fn can be set.
When the shock absorber is tending to or is being stretched,
in the drawing, when the shock absorber is in the extension stroke positions s0, s1 and s2, the support force value of the support spring is smaller than the body weight, so that the extension damping force value can only be set to Fk' closest to zero.
The tensile damping force value Fl 'for S3 should be close to F3 (Fe) minus Fg',
the tensile damping force value Fm 'for S4 should be close to F3 (Fe) minus Fh',
the tensile damping force value Fn 'for S5 should be close to F3 (Fe) minus Fi'.
Preferred embodiment 2: an electrically controlled damping vibration absorber with damping force value varying with stroke position (as shown in figures 1, 2 and 3)
The electronically controlled shock absorber shown in fig. 3 comprises: the two electric control damping valves (7), wherein one of the two electric control damping valves is an electric control compression damping valve which is communicated with the compression cavity and the liquid storage cavity, and the other one of the two electric control damping valves is an electric control stretching damping valve, a one-way valve (5) and a controller (9) which is communicated with the stretching cavity and the compression cavity; the electric control damping valve provides control current according to the corresponding relation curve of the tensile damping force value and the compression damping force value and the control current value shown by the curves Aa 'and Aa' in figure 2:
optimal correspondence of shock absorber stroke position and current value of the electrically controlled damping valve (as shown in fig. 2):
the ordinate represents the current value of the electric control damping valve and the stroke position of the shock absorber, the abscissa represents the force value, in the figure, the shock absorbers s 0-s 5 are taken as specific stroke position points, F1 'is a curve of the shock absorber with the tensile damping force value corresponding to the stroke position, F1' is a curve of the shock absorber with the compressive damping force value corresponding to the stroke position, F2 is a line of the supporting force value corresponding to the stroke position of the supporting spring, F3 is a line segment of the vehicle body gravity value corresponding to the stroke position, Aa 'is a curve of the control relation of the tensile damping force value and the tensile damping valve when the electric control damping valve is the tensile valve, and Aa' is a curve of the control relation of the compressive damping force value and the compressive damping valve control current when the electric control damping valve is the compressive valve.
In the figure, reference force values corresponding to stroke positions of the shock absorber and the optimal control current value of the electric control damping valve are as follows:
when the shock absorber is tending to or is compressing,
s0, the corresponding compression damping force value Fa should be close to F3 (Fe) minus Fb, and when the force value Fa is reached, the control current value should be set to be close to A-Fa (A0) when the compression valve is an electric control damping valve;
the compression damping force value Fj corresponding to s1 should be close to F3 (Fe) minus Fc, and when the value of Fj is reached, the control current value should be set to be close to A-Fj when the compression valve is an electric control damping valve;
the compression damping force value Fk corresponding to s2 should be close to F3 (Fe) minus Fd, and when the value of Fk is reached, the control current value should be set to be close to A-Fk when the compression valve is an electric control damping valve;
in the figure, when the compression stroke position of the shock absorber is s3, s4 and s5, the support force value of the support spring is already larger than the gravity of the vehicle body, the force value of the shock absorber during compression cannot be negative, so that only the minimum compression damping force value Fn can be set, and the control current of the compression valve as the electric control damping valve can be set to 0.
When the shock absorber is tending to or is being stretched,
when the extension stroke position of the shock absorber is s0, s1, s2, the support force value of the support spring is smaller than the gravity of the vehicle body, so that the extension damping force value can only be set to Fk' which is closest to zero, and the control current of the extension valve which is the electrically controlled damping valve can be set to 0.
The tensile damping force value Fl 'corresponding to S3 is close to F3 (Fe) minus Fg', and when the force value Fl 'is reached, the control current value is set to be close to A-Fl' when the compression valve is an electric control damping valve;
the tensile damping force value Fm 'corresponding to S4 is close to F3 (Fe) minus Fh', and when the force value Fm 'is reached, the control current value is set to be close to A-Fm' when the compression valve is an electric control damping valve;
the tensile damping force value Fn 'corresponding to S5 should be close to F3 (Fe) minus Fi', and to achieve the Fn 'force value, the control current value should be set to be close to A-Fn' when the compression valve is an electrically controlled damping valve.
Preferred embodiment 3: shock absorber with tensile damping force value changing along with stroke position (as shown in figure 5)
The shock absorber shown in fig. 5 includes: the hydraulic cylinder barrel, the piston rod, the damping rod, central damping hole. The vibration damper is characterized in that: the piston rod is a hollow tube, the hollow part is communicated with the stretching cavity, the central damping hole is arranged at the end of the piston rod close to the piston, and the damping rod is a rod with different sectional areas of all parts; the damping rod can be connected to the bottom of the hydraulic cylinder, can be connected to a bottom valve of the shock absorber, and can also be connected to a bottom valve or a floating piston of the single-cylinder shock absorber; the damping rod passes through the central damping hole, and forms stretching damping holes with different drift diameters corresponding to the stroke position of the shock absorber together with the central damping hole; the drift diameter of the damping hole is based on the reference force value of the tensile damping as the basis for controlling or setting the tensile damping force value of the shock absorber, so that the damping force value of each stroke position of the shock absorber at the set tensile speed is equal to or close to the reference force value.
For different vehicles and supporting springs, the cross-sectional areas of the parts of the damping rod of the shock absorber are different to adapt to different conditions, so that the optimal damping effect is achieved relative to the specific vehicle and the specific spring.
Preferred embodiment 4: vibration damper (as shown in figure 6)
The damper shown in fig. 3 includes: the hydraulic cylinder barrel, the piston rod, the damping rod, the central damping hole and the compression oil return pipeline. The method is characterized in that: the piston rod is a hollow tube, the hollow part is communicated with the compression cavity, the central damping hole is arranged at the end of the piston rod close to the piston, and the damping rod is a rod with different sectional areas of all parts; the compression oil return pipe communicates the stretching cavity with the liquid storage cavity through a one-way valve, and the damping rod can be connected to the bottom of the hydraulic cylinder, can be connected to a bottom valve of the shock absorber, and can also be connected to a bottom valve or a floating piston of the single-cylinder shock absorber; the damping rod forms compression damping holes with different drift diameters corresponding to the stroke position of the shock absorber through the central damping hole and the central damping hole; the drift diameter of the damping hole is based on the reference force value of the compression damping force value to control or set the compression damping force value of the shock absorber, so that the compression damping force value of each stroke position of the shock absorber at the set compression speed is equal to or close to the reference force value.
When the shock absorber is compressed, liquid flows into the liquid storage cavity through the damping hole, the stretching cavity and the compression oil return pipeline. When the shock absorber is stretched, liquid flows into the compression cavity through the damping hole, the check valve on the piston and the check valve on the bottom valve.
Preferred embodiment 5: shock absorber with tensile damping force value changing along with stroke position (as shown in figure 7)
This shock absorber includes: the hydraulic cylinder comprises a hydraulic cylinder outer barrel, a variable cross-section hydraulic cylinder barrel, a piston rod and a one-way valve. The vibration damper is characterized in that: the sectional area of the variable-section hydraulic cylinder barrel is changed along the axis of the hydraulic cylinder barrel, damping gaps with different diameters are formed between the variable-section hydraulic cylinder barrel and the piston, the diameter of each damping gap is based on the reference force value of the tensile damping to control or set the tensile damping force value of the shock absorber, and the damping force value of each stroke position of the shock absorber at the set tensile speed is equal to or close to the reference force value.
When the shock absorber is compressed, liquid flows into the stretching cavity through the one-way valve and the damping gap. When the shock absorber is stretched, the check valve is closed, and liquid flows out through a damping gap formed by the piston and the variable cross-section cylinder barrel, so that the shock absorber has different stretching damping force values at different stroke positions.
Claims (10)
1. The damping control and performance evaluation method of the shock absorber comprises the following steps:
the difference value of the set force value or the actual gravity value of the object minus the support force value of the set support spring or the equivalent support spring at each stroke position is taken as a judgment value,
when the difference value is negative, taking the absolute value of the difference value as the reference force value of the tensile damping force value of the current stroke position of the shock absorber, and when the difference value is not negative, taking the minimum damping force value which can be reached by the tensile damping force value as the reference force value of the tensile damping force value of the current stroke position of the shock absorber;
if the difference value is positive, taking the difference value as a reference force value of the compression damping force value of the current stroke position of the shock absorber, and if the difference value is not a positive value, taking the minimum damping force value which can be reached by the compression damping force value as the reference force value of the compression damping force value of the current stroke position of the shock absorber;
the reference force value of the shock absorber at each stroke position is used as a basis for controlling or setting the tensile damping force value or the compressive damping force value of the shock absorber at the stroke position, so that the tensile damping force value of the shock absorber is close to or equal to the reference force value of the tensile damping force value as much as possible, or the compressive damping force value of the shock absorber is close to or equal to the reference force value of the compressive damping force value as much as possible, and the performance of the shock absorber is optimal, so that the tensile damping force value or the compressive damping force value of the shock absorber is controlled;
and comparing the reference force value of each stroke position of the shock absorber with the tensile damping or compressive damping force value of the shock absorber at the stroke position, wherein the closer the tensile damping force value of the shock absorber is to the reference force value of the tensile damping force value or the compressive damping force value of the shock absorber is to the reference force value of the compressive damping force value of the shock absorber, the better the performance of the shock absorber is, and the more the performance of the shock absorber is taken as the basis for judging the performance of the shock absorber.
2. The method for damping control and performance assessment of shock absorbers according to claim 1, wherein the damping force values of the shock absorbers are tensile damping force values or compressive damping force values at a specific tensile speed or compressive speed,
alternatively, the first and second electrodes may be,
the tensile damping force value or the compressive damping force value of the shock absorber is measured by the force transducer in real time.
3. A shock absorber having a damping force value that varies with stroke position, comprising: the hydraulic cylinder barrel, the piston rod and the damping valve; the method is characterized in that: the shock absorber adopts the shock absorber damping control and performance evaluation method as claimed in claim 1, and uses the reference force value as the basis for controlling or setting the tensile damping force value or the compressive damping force value of the shock absorber at each stroke position, so that the damping force value of the shock absorber is changed along with the stroke position of the shock absorber, and the damping force value of the shock absorber at each stroke position is equal to or close to the reference force value.
4. The shock absorber with a damping force value that varies with stroke position as set forth in claim 3, comprising: the measuring device is characterized in that a stretching damping valve or a compression damping valve of the shock absorber is an electric control damping valve, the stroke position of the shock absorber is provided to the controller by the shock absorber stroke position measuring device, and the controller controls the damping force value of the shock absorber according to the stroke position of the shock absorber and a reference force value.
5. The shock absorber with a damping force value that varies with stroke position as set forth in claim 4 wherein: the shock absorber is provided with a force transducer which measures the stretching or compressing damping force value of the shock absorber in real time, the controller compares the reference force value corresponding to the current stroke position of the shock absorber with the real-time stretching damping force value or the real-time compressing damping force value of the current stroke position, and controls the stretching damping force value or the compressing damping force value of the current stroke position to be close to or equal to the reference force value according to the comparison result.
6. A shock absorber having a damping force value that varies with stroke position as set forth in claim 3 wherein: a damping hole with the drift diameter size changing along with the stroke position of the shock absorber is arranged between the stretching cavity and the compression cavity of the shock absorber, and the drift diameter size of the damping hole is based on the reference force value as the basis for controlling or setting the stretching damping force value or the compression damping force value of the shock absorber, so that the damping force value of each stroke position of the shock absorber at the set stretching speed or compression speed is equal to or close to the reference force value.
7. The shock absorber with a damping force value that varies with stroke position as set forth in claim 6 wherein: one of the damping valves mainly comprises a damping rod and a central damping hole, the piston rod is a hollow tube, the hollow part is communicated with the stretching cavity, the central damping hole is arranged at the end, close to the piston, of the piston rod, and the damping rod is a rod with different sectional areas of all parts; the damping rod can be connected to the bottom of the hydraulic cylinder, can be connected to a bottom valve of the shock absorber, and can also be connected to a bottom valve or a floating piston of the single-cylinder shock absorber; the damping rod forms stretching damping valve holes with different diameters corresponding to the stroke position of the shock absorber through the central damping hole and the central damping hole; the drift diameter of the damping hole is based on the reference force value of the tensile damping as the basis for controlling or setting the tensile damping force value of the shock absorber, so that the damping force value of each stroke position of the shock absorber at the set tensile speed is equal to or close to the reference force value.
8. The shock absorber with a damping force value that varies with stroke position as set forth in claim 6,
the method is characterized in that: one of the damping valves mainly comprises a damping rod and a central damping hole, the piston rod is a hollow tube, the hollow part is communicated with the stretching cavity, the central damping hole is arranged at the end, close to the piston, of the piston rod, and the damping rod is a rod with different sectional areas of all parts; the stretching cavity is communicated with the liquid storage cavity through a one-way valve, and the damping rod can be connected to the bottom of the hydraulic cylinder; the damping rod forms compression damping holes with different drift diameters corresponding to the stroke position of the shock absorber through the central damping hole and the central damping hole; the drift diameter of the damping hole is based on the reference force value of the compression damping force value to control or set the compression damping force value of the shock absorber, so that the compression damping force value of each stroke position of the shock absorber at the set compression speed is equal to or close to the reference force value; when the shock absorber is compressed, liquid flow of the compression cavity enters the stretching cavity through the damping hole and flows into the liquid storage cavity through the stretching cavity.
9. The shock absorber with a damping force value that varies with stroke position as set forth in claim 6 wherein: the hydraulic cylinder barrel of the shock absorber is a variable cross-section hydraulic cylinder barrel, the size of the inner sectional area of the variable cross-section cylinder barrel is changed along the center line of the cylinder barrel, the inner cross section of the cylinder barrel and the piston form damping holes with different diameters between a stretching cavity and a compression cavity, and the diameters of the damping holes are based on the reference force value of the tensile damping force value to control or set the tensile damping force value of the shock absorber, so that the tensile damping force value of each stroke position of the shock absorber at the set stretching speed is equal to or close to the reference force value.
10. A vehicle, characterized by: the vehicle employs a shock absorber as claimed in any one of claims 3 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/CN2020/107672 WO2021031876A1 (en) | 2019-08-22 | 2020-08-07 | Damping control and performance assessment method for shock absorber, shock absorber optimized by means of method, and vehicle using shock absorber |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910776512X | 2019-08-22 | ||
| CN201910776512 | 2019-08-22 |
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| CN202010780692.1A Pending CN112413030A (en) | 2019-08-22 | 2020-08-06 | Shock absorber damping control and performance evaluation method, shock absorber optimized by using same and vehicle adopting shock absorber |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114216705A (en) * | 2021-12-09 | 2022-03-22 | 浙江永贵电器股份有限公司 | Simulation debugging method for damping performance of oil pressure shock absorber |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114216705A (en) * | 2021-12-09 | 2022-03-22 | 浙江永贵电器股份有限公司 | Simulation debugging method for damping performance of oil pressure shock absorber |
| CN114216705B (en) * | 2021-12-09 | 2023-06-13 | 浙江永贵电器股份有限公司 | Damping performance simulation debugging method of oil pressure damper |
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