Anti-folding height valve swing rod system and parameter determination method thereof

Abstract

The invention provides an anti-turnover height valve swing rod system and a parameter determination method thereof.The anti-turnover height valve swing rod system comprises a transverse rod, a longitudinal rod and a height sensor, one end of the transverse rod is connected with a rotating shaft of the height sensor, the other end of the transverse rod is hinged to one end of the longitudinal rod, and the other end of the longitudinal rod is hinged to the other end of the transverse rod; a first limiting device is arranged at the hinged position of the longitudinal rod and the transverse rod. One end of the first limiting device is fixedly installed at the hinged position of the longitudinal rod and the transverse rod, a limiting block is arranged at the other end of the first limiting device, and the limiting block is used for limiting the included angle between the transverse rod and the longitudinal rod to be smaller than the preset maximum included angle when the height between an axle and a chassis is increased. According to the method, the height valve swing rod system composed of the longitudinal rod and the transverse rod is limited in advance by arranging the first limiting device, the situation that the height valve swing rod system reaches the dead point position and is turned over is prevented, and the vehicle running stability is improved.

Description

Technical Field

[0001] The present invention relates to the technical field of air suspension, and in particular to an anti-folding height valve swing rod system and a method for determining its parameters. Background Art

[0002] An air suspension is an automotive suspension system that can reduce the impact on cargo and improve riding comfort. Using an air suspension can also adjust the height between the chassis and the axle. Its working principle is to inflate or deflate the air spring through an air compressor, change the air pressure in the air spring, and then adjust the height of the vehicle body from the ground to adapt to different road conditions or different vehicle loads.

[0003] Currently, many buses and trucks adopt an electronically controlled air suspension system (ECAS, Electronically Controlled Air Suspension). In the electronically controlled air suspension system, a height valve swing rod system (also called an airbag height adjustment system) is provided. As Figure 1 shown, the height valve swing rod system generally includes a cross bar, a longitudinal rod, and a height sensor fixed on the axle. One end of the cross bar is connected to the height sensor, and the other end is hinged to the longitudinal rod. The other end of the longitudinal rod is connected to the chassis. Its working principle is that when the distance between the chassis and the axle changes, the longitudinal rod pushes the cross bar, and at the same time, the cross bar drives the rotating shaft of the height sensor to rotate together, thereby changing the height signal output by the height sensor.

[0004] However, the above height valve swing rod system (composed of a cross bar and a longitudinal rod) generally has the problems of easily passing through the dead point and breaking the rod system, which in turn leads to out-of-control airbag inflation and deflation, air pressure leakage, and the vehicle being unable to carry the load, greatly affecting the vehicle's handling stability and driving safety. Summary of the Invention

[0005] The present invention provides an anti-folding height valve swing rod system and a method for determining its parameters to solve the defect that the height valve swing rod system in the prior art is prone to folding through the dead point, realize preventing the height rod from folding, and enable users to independently mark the scale and adjust the height between the axle and the chassis.

[0006] The present invention provides an anti-folding height valve swing rod system, including a cross bar, a longitudinal rod, and a height sensor. One end of the cross bar is connected to the rotating shaft of the height sensor, and the other end of the cross bar is hinged to one end of the longitudinal rod. A first limiting device is provided at the hinged joint of the longitudinal rod and the cross bar; one end of the first limiting device is fixedly installed at the hinged joint of the longitudinal rod and the cross bar, and the other end is provided with a limiting block, and the limiting block is used to limit the included angle between the cross bar and the longitudinal rod to be less than a preset maximum included angle when the height between the axle and the chassis increases.

[0007] A height valve swing rod system for preventing folding according to the present invention, wherein the material of the first limiting device is rubber material.

[0008] A height valve swing rod system for preventing folding according to the present invention, wherein a second limiting device is provided at the connection between the longitudinal rod and the chassis, one end of the second limiting device is fixedly connected to the chassis, and the other end of the second limiting device is hinged to the longitudinal rod.

[0009] A height valve swing rod system for preventing folding according to the present invention, wherein the material of the second limiting device is rubber material.

[0010] A height valve swing rod system for preventing folding according to the present invention, wherein the cross bar includes a first cross bar and a second cross bar, and the first cross bar and the second cross bar are connected by a spiral spring; the spiral spring is used for absorbing energy by swinging when the road condition is bumpy, and absorbing energy by stretching when being pulled extremely downward.

[0011] A height valve swing rod system for preventing folding according to the present invention, wherein height scales are provided on the longitudinal rod.

[0012] A height valve swing rod system for preventing folding according to the present invention, wherein the preset maximum included angle is 150°.

[0013] A height valve swing rod system for preventing folding according to the present invention, increasing the length of the first cross bar or the second cross bar to expand the movement range of the height valve swing rod system for preventing folding.

[0014] A height valve swing rod system for preventing folding according to the present invention, increasing the length of the spiral spring so as to increase the stability of the height valve swing rod system for preventing folding when the vehicle jumps down to the dead point position of the height valve swing rod system for preventing folding.

[0015] The present invention also provides a parameter determination method, which is applied to each of the above-mentioned height valve swing rod system embodiments for preventing folding, and includes the following steps: Determine the stiffness of the spiral spring; Calculate the pitch and elastic coefficient of the spiral spring according to the stiffness of the spring.

[0016] The present invention also provides an electronic device, including a memory, a processor, and a computer program stored on the memory and executable on the processor, wherein when the processor executes the computer program, the parameter determination method as described in any one of the above is implemented.

[0017] The present invention also provides a non-transitory computer-readable storage medium, on which a computer program is stored, and when the computer program is executed by a processor, the parameter determination method as described in any one of the above is implemented.

[0018] The anti - folding height valve swing rod system provided by the present invention and its parameter determination method. The anti - folding height valve swing rod system includes a cross - bar, a longitudinal rod, and a height sensor. One end of the cross - bar is connected to the rotating shaft of the height sensor, the other end of the cross - bar is hinged to one end of the longitudinal rod, and a first limiting device is arranged at the hinged part of the longitudinal rod and the cross - bar; one end of the first limiting device is fixedly installed at the hinged part of the longitudinal rod and the cross - bar, and the other end is provided with a limiting block. The limiting block is used to limit the included angle between the cross - bar and the longitudinal rod to be less than a preset maximum included angle when the height between the axle and the chassis increases. This method limits the height valve swing rod system composed of the longitudinal rod and the cross - bar in advance by setting the first limiting device, preventing it from reaching the dead - point position and causing folding, and improving the running stability of the vehicle. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the technical solutions in the present invention or the prior art, the following will briefly introduce the drawings required for use in the description of the embodiments or the prior art. Obviously, the following - described drawings are some embodiments of the present invention. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative efforts.

[0020] Figure 1 is a schematic structural diagram of the height valve swing rod system provided in the prior art.

[0021] Figure 2 is one of the schematic structural diagrams of the anti - folding height valve swing rod system provided by the present invention.

[0022] Figure 3 is another schematic structural diagram of the anti - folding height valve swing rod system provided by the present invention.

[0023] Figure 4 is yet another schematic structural diagram of the anti - folding height valve swing rod system provided by the present invention.

[0024] Figure 5 is a schematic diagram of the variation law of the included - angle of the height valve swing rod system provided by the present invention.

[0025] Figure 6 is a schematic flow diagram of the parameter determination method provided by the present invention.

[0026] Figure 7 is a schematic structural diagram of the electronic device provided by the present invention.

[0027] Reference numerals: 101: Cross bar; 102: Longitudinal bar; 103: Height sensor; 201: Cross bar; 2011: First cross bar; 2012: Helical spring; 2013: Second cross bar; 202: Longitudinal bar; 203: Height sensor; 204: Height limiting device; 2041: First limiting block; 205: Second limiting block. Detailed implementation mode

[0028] To make the objectives, technical solutions and advantages of the present invention clearer, the technical solutions in the present invention will be clearly and completely described below with reference to the accompanying drawings in the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, rather than all the embodiments. Based on the embodiments in the present invention, all other embodiments obtained by those of ordinary skill in the art without making creative efforts shall fall within the protection scope of the present invention.

[0029] The following will be combined with Figures 1-7 Describe the anti-folding height valve swing rod system of the present invention and its parameter determination method.

[0030] Figure 1 It is a structural schematic diagram of a height valve swing rod system in the prior art. As Figure 1 shown, the existing height valve swing rod system includes a cross bar 101, a longitudinal bar 102 and a height sensor 103, where the height sensor is also called a height valve.

[0031] Figure 2 It is a structural schematic diagram of the anti-folding height valve swing rod system provided by the present invention. The system includes a cross bar 201, a longitudinal bar 202 and a height sensor 203; one end of the cross bar 201 is connected to the rotating shaft of the height sensor 203, and the other end is hinged to one end of the longitudinal bar 202. A first limiting device 204 is provided at the hinge joint of the longitudinal bar 202 and the cross bar 201; one end of the first limiting device is fixedly installed at the hinge joint of the longitudinal bar and the cross bar, and the other end is provided with a limiting block 2041. The limiting block 2041 is used to limit the included angle between the cross bar and the longitudinal bar to be less than a preset maximum included angle when the height between the axle and the chassis increases.

[0032] Optionally, the preset maximum included angle is 150°.

[0033] Optionally, the material of the above-mentioned first limiting device 2041 is a rubber material.

[0034] In the present application, the use of the first limiting device 204 can prevent the link mechanism from passing through the dead center.

[0035] Among them, the dead center of the link mechanism refers to a state in the link mechanism where the movement of certain parts or systems is blocked and cannot continue. In this state, none of the components in the system can operate.

[0036] Specifically, in the existing height valve swing rod system, dead points are likely to occur between the cross bar and the longitudinal rod, which has a negative impact on the normal driving of the vehicle. Therefore, in this embodiment, a mechanism for protecting against dead points is provided, that is Figure 2 the first limiting device 204 in Figure 2 is used to limit the movement range between the cross bar and the longitudinal rod to avoid reaching the dead point position.

[0037] In this embodiment, a model of the combined system of the four-link system of the vehicle rear suspension and the two-link system of the height valve swing rod system is first established, and kinematic and dynamic analyses are performed on this mathematical model using simulation software. The optimization ranges of the structural parameters (such as the lengths of the two rods, the cross-sectional shapes and sizes of the rods, the connection point positions, the material types, the spring modulus, etc.) and the performance parameters (such as the load-bearing capacity, stiffness, strength, etc.) of the combined two-link system are initially determined. It is initially determined that the dynamic impact load range and the contribution ratio of the dead point flip to causing system imbalance are the largest. Combining displacement, velocity, and acceleration to deduce angular displacement, angular velocity, angular acceleration, and the impact load of the rod system, and taking acceptable values for the impact loads at each flipping angle and the flipping limit angle (reducing the instability of the height value caused by impact vibration). After adding the index of the easy deformation amount of the additional rubber and the welding deformation amount, the value is rounded up, and the first limiting device is welded at a space angle of 150° to limit in advance on the premise of ensuring the stability of the combined two-link system, so as to reduce the system imbalance and vehicle shutdown caused by flipping through the dead point.

[0038] In the above embodiment, by setting the first limiting device, the height valve swing rod system composed of the longitudinal rod and the cross bar is limited in advance to prevent it from reaching the dead point position and causing flipping, thereby improving the running stability of the vehicle.

[0039] In one embodiment, as Figure 3 shown, a second limiting device 205 is provided at the connection between the longitudinal rod 202 and the chassis. One end of the second limiting device 205 is fixedly connected to the chassis, and the other end of the second limiting device 205 is hinged to the longitudinal rod 202.

[0040] Optionally, the material of the second limiting device 205 is a rubber material.

[0041] The second limiting device 205 is used for anti-impact limiting. That is to say, as a buffer medium, when the vehicle bridge jumps down, the second limiting device 205 can limit the stroke range of the moving part (i.e., the above-mentioned longitudinal rod) and absorb the impact energy when the part reaches the limit position, thereby protecting the equipment from damage.

[0042] In the above embodiment, anti-impact is achieved through the second limiting device 205.

[0043] In one embodiment, as Figure 4 shown, Figure 4The overall structure diagram of the anti - folding height valve swing rod system proposed in this application is shown. Among them, the cross bar 201 includes a first cross bar 2011 and a second cross bar 2013, and the first cross bar 2011 and the second cross bar 2013 are connected by a spiral spring 2012; the spiral spring 2012 is used for absorbing energy by swinging when the road condition is bumpy, and absorbing energy by stretching when being pulled down extremely.

[0044] Optionally, height scales are provided on the longitudinal rod 202.

[0045] Specifically, an adjustable adjusting rod system that resists vibration and shock and allows free calibration is designed. The suspension height is calibrated by the vehicle manufacturer when the vehicle leaves the factory. Users cannot adjust the height by themselves through the adjusting rod system, or irreversible failures such as loosening, folding, and rod system flashing will occur after adjustment. The horizontal cross bar is combined with the spring rod system, supplemented by anti - shock limit. When the road condition is bumpy, the spiral spring swings within its own stiffness range to absorb energy and avoid the cross bar from flashing; when being pulled down extremely, it stretches to absorb energy and can automatically recover; when users have the need to avoid tire rubbing due to different cargo box specifications, they can adjust the suspension height value by themselves according to the scale markings on the longitudinal rod without worrying about the risks of easy folding, unstable horizontal swing force, or excessive stretching.

[0046] In the above - mentioned embodiment, after adding a spiral spring to the original basic cross bar and installing an anti - folding limiting device, the parking failure rate and the maintenance rate of related adjusting components (the instability of the load - bearing airbag and the failure of the rod system) can be effectively reduced.

[0047] Furthermore, in the above - mentioned embodiment, by designing an ECAS adjusting rod system that allows users to freely calibrate the horizontal position, it can be realized that without replacing any components of the system, it can be freely adjusted according to different transportation requirements, completely avoiding non - standard operations of users caused by phenomena such as too low tire rubbing and too high over - height caused by changes in the side height of the cargo box.

[0048] As Figure 5 shown, Figure 5 The schematic diagram of the change law of the included angle of the height valve swing rod system is shown, that is, as the distance of the vehicle bridge jumping down increases, the included angle between the two connecting rods continuously changes, and the included angle becomes larger and larger. When the included angle reaches about 170°, the angle no longer changes. At this time, if the vehicle bridge continues to jump down, it may cause passing the dead point. Therefore, the maximum included angle in this application is set to 150°. When the vehicle bridge jumps down, the included angle of the connecting rod system reaches 150°, and the range of motion is restricted at this position, so as to protect the connecting rod mechanism from passing the dead point and ensure the overall stability of the vehicle.

[0049] This application also provides a parameter determination method, which is applied to the above - mentioned anti - folding height valve swing rod system. The steps of this method are as Figure 6 shown, including the following steps: Step 601, determine the stiffness of the spiral spring; Specifically, a simulation model of the whole vehicle, axle and airbag linkage system is established. In the model, the allowable misalignment of the height valve, the material properties of components (such as the stiffness curve of the rubber boot and the tensile deformation curve of the metal rod), the allowable coordinated deformation of the spring restoring force, the welding dimensional tolerance, etc. are considered. Taking the virtual displacement theorem as the leading factor, the kinematic parameters of the rod system combining the four-link suspension movement and the airbag height adjustment linkage are parameterized and adjustable, and a complete set of visual dynamic parameterized models is established.

[0050] Combined with the use of the visual double-rod system parameterized model and the anti-folding limit device, analyze the movement mode of the rod system after the rod system movement interference limit in the extreme working conditions of the double-rod system. Combine the impact road spectrum to calculate the load of the rod system spring deformation when the axle impacts at an acceleration of 12g. Select 60Si2Mn spring steel material (silicon and manganese are added to this material, which can improve the elastic limit and fatigue strength of the material, making it suitable for manufacturing springs), and an appropriate number of turns. When the road condition is normal, the springs are used in parallel. When the road condition exceeds the use limit, within the linear elastic range, combined with the calculation formula of the spring stiffness: ; Among them, is the stiffness of the helical spring, G is the shear modulus of the spring material, d is the diameter of the spring wire, D is the pitch of the spring, that is, the diameter from the center of the spring coil to the center of the adjacent coil, and n is the number of effective turns of the helical spring.

[0051] Combining the above formula with the simulation stiffness correction coefficient, select the helical spring and weld it with the horizontal rod systems on both sides. When the vehicle driving condition is poor, although the rotation angle will exceed the range involved in the height adjustment system, under the interference of the adjustment redundancy of the double-rod system when the axle drops to the limit, the redundant limit device of the double-rod system allows to be overstretched to adapt to the movement of the suspension system, and at the same time can restore the original length to intervene in the height adjustment system when the suspension system restores, so as to ensure the normal driving of the vehicle.

[0052] Step 602, calculate the pitch and elastic coefficient of the helical spring according to the stiffness of the helical spring.

[0053] Specifically, calculate the pitch and elastic coefficient of the helical spring according to the above formula and the spring stiffness.

[0054] Furthermore, the length of the cross bar can also be calculated. The calculation method is as follows: Set up a control group experiment. Initially, it is determined that among the rod systems of the height adjusting valve, the lengths of the longitudinal rod and the horizontal balance rod have a greater impact on the system imbalance caused by excessive folding. Design specific simulation control groups through the method of controlling variables: 1) the original state, 2) the longitudinal rod is lengthened by 5%, 10%, 15%, 20%, 3) the cross bar is lengthened by 5%, 10%, 15%, 20%. Taking the folding dead point limit as the evaluation basis and combining with displacement and angle sensors for on-vehicle mapping as the evaluation basis, considering factors such as the interaction of the double rod systems, the limit length of the shock absorber pulling down the axle, and the stiffness and deformation of rubber parts, select the cross bar lengthening scheme (two lengthening methods: lengthening the body or elastic elongation) as the optimization direction.

[0055] Among them, lengthening the body means increasing the length of the first cross bar or the second cross bar to expand the movement range of the anti-folding height valve swing rod system. Lengthening the cross bar length enables the swing rod system to have a larger movement range when the vehicle jounces, for example, the included angle between the two rods can have a larger change interval, further avoiding the possibility of passing through the dead point.

[0056] Elastic elongation means increasing the length of the helical spring so that when the vehicle jounces to the dead point position of the anti-folding height valve swing rod system (such as the above-mentioned maximum preset included angle position), the vehicle can still have a certain jounce space and will not break, ensuring the overall stability of the vehicle.

[0057] In the above embodiments, by establishing a parametric kinematic rod system dynamic simulation model, considering the changes in rod system length and the adjustment of the rotation center point position, elastic stretching of the spring, etc., it provides an accurate, intuitive and convenient solution for subsequent angle verification of the ECAS self-adjusting system, verification of frame hard points, and matching of the kinematic relationship of the axle.

[0058] Furthermore, the present application also provides a set of performance evaluation index systems, including the axle jounce distance, speed, and angle, which are used to evaluate the variation law of the included angle of the internal rod systems of the above-mentioned height valve swing rod system with the axle jounce displacement and the axle jounce speed, and can comprehensively and accurately evaluate the application possibility of the ECAS system applicable to different suspension height changes.

[0059] Figure 7 Illustrates a schematic physical structure diagram of an electronic device, such as Figure 7As shown, the electronic device may include: a processor 710, a communications interface 720, a memory 730, and a communication bus 740. Among them, the processor 710, the communications interface 720, and the memory 730 complete mutual communication through the communication bus 740. The processor 710 may call logical instructions in the memory 730 to execute a parameter determination method, which includes: determining the stiffness of a helical spring; calculating the pitch and elastic coefficient of the helical spring according to the stiffness of the helical spring.

[0060] In addition, when the logical instructions in the above-mentioned memory 730 are implemented in the form of software functional units and sold or used as independent products, they can be stored in a computer-readable storage medium. Based on such an understanding, the technical solution of the present invention, in essence, or the part that contributes to the prior art, or a part of this technical solution, can be embodied in the form of a software product. This computer software product is stored in a storage medium and includes several instructions for causing a computer device (which may be a personal computer, a server, or a network device, etc.) to execute all or part of the steps of the methods described in various embodiments of the present invention. The aforementioned storage medium includes: various media such as USB flash drives, mobile hard disks, read-only memories (ROM, Read-Only Memory), random access memories (RAM, Random Access Memory), magnetic disks, or optical discs that can store program codes.

[0061] On the other hand, the present invention also provides a computer program product. The computer program product includes a computer program that can be stored on a non-transitory computer-readable storage medium. When the computer program is executed by a processor, the computer can execute the parameter determination method provided by the above-mentioned various methods. The method includes: determining the stiffness of a helical spring; calculating the pitch and elastic coefficient of the helical spring according to the stiffness of the helical spring.

[0062] On yet another aspect, the present invention also provides a non-transitory computer-readable storage medium, on which a computer program is stored. When the computer program is executed by a processor, it is implemented to execute the parameter determination method provided by the above-mentioned various methods. The method includes: determining the stiffness of a helical spring; calculating the pitch and elastic coefficient of the helical spring according to the stiffness of the helical spring.

[0063] The device embodiments described above are merely illustrative. The units described as separate components may or may not be physically separated, and the components shown as units may or may not be physical units, that is, they may be located in one place or distributed to multiple network units. Some or all of the modules can be selected according to actual needs to achieve the purpose of the solution of this embodiment. Those of ordinary skill in the art can understand and implement it without creative effort.

[0064] Through the description of the above embodiments, those skilled in the art can clearly understand that each embodiment can be implemented by means of software plus a necessary general hardware platform, and of course, it can also be implemented by hardware. Based on such an understanding, the essence of the above technical solution, or the part that contributes to the prior art, can be embodied in the form of a software product. The computer software product can be stored in a computer-readable storage medium, such as ROM / RAM, magnetic disk, optical disk, etc., and includes several instructions for causing a computer device (which can be a personal computer, a server, or a network device, etc.) to execute the methods described in each embodiment or some parts of the embodiments.

[0065] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and are not intended to limit them. Although the present invention has been described in detail with reference to the foregoing embodiments, those of ordinary skill in the art should understand that they can still modify the technical solutions described in the foregoing embodiments, or perform equivalent replacements for some of the technical features. However, these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. An anti-folding height valve swing arm system, comprising a crossbar, a longitudinal rod and a height sensor, wherein one end of the crossbar is connected to the rotating shaft of the height sensor, and the other end of the crossbar is hinged to one end of the longitudinal rod, characterized in that: A first limit device is provided at the hinge of the longitudinal rod and the cross rod; one end of the first limit device is fixedly installed at the hinge of the longitudinal rod and the cross rod, and the other end is provided with a limit block, and the limit block is used to limit the angle between the cross rod and the longitudinal rod to be less than a preset maximum angle when the height between the axle and the chassis increases.

2. The anti-flip height valve swing arm system according to claim 1, characterized in that: The first limiting device is made of rubber material.

3. The anti-flip height valve swing arm system according to claim 2, characterized in that: A second limiting device is provided at the connection between the longitudinal rod and the chassis, one end of the second limiting device is fixedly connected to the chassis, and the other end of the second limiting device is hinged to the longitudinal rod.

4. The anti-flip height valve swing arm system according to claim 3, characterized in that: The second limiting device is made of rubber material.

5. The anti-flip height valve swing arm system according to claim 1, characterized in that: The cross bar comprises a first cross bar and a second cross bar, and the first cross bar is connected to the second cross bar via a coil spring; the coil spring is used for swinging to absorb energy when the road condition is bumpy, and for stretching to absorb energy when being pulled down to an extreme extent.

6. The anti-flip height valve swing arm system according to claim 1, characterized in that: The longitudinal rod is provided with a height scale.

7. The anti-flip height valve swing arm system according to claim 1, characterized in that: The preset maximum angle is 150°.

8. The anti-flip height valve swing arm system according to claim 5, characterized in that: The length of the first cross bar or the second cross bar is increased to expand the movement range of the anti-folding height valve rocker arm system.

9. The anti-flip height valve swing arm system according to claim 5, characterized in that: The length of the coil spring is increased so that when the vehicle jumps down to the dead point position of the anti-folding height valve swing arm system, the stability of the anti-folding height valve swing arm system is increased.

10. A parameter determination method, applied to the anti-flip height valve swing arm system according to claim 5, characterized in that: include: Determine the stiffness of the coil spring; The pitch and elastic coefficient of the coil spring are calculated according to the stiffness of the coil spring.

11. An electronic device comprising a memory, a processor, and a computer program stored in the memory and running on the processor, characterized in that: When the processor executes the computer program, the parameter determination method according to claim 10 is implemented.

12. A non-transitory computer-readable storage medium having a computer program stored thereon, characterized in that: When the computer program is executed by a processor, the parameter determination method according to claim 10 is implemented.

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