A Method for Constructing a General Model for Dry Clutches

Abstract

This invention belongs to the field of clutch simulation technology, specifically relating to a method for constructing a general model of a dry clutch. This general model includes: a clutch driving plate model, which receives engine speed and output parameters from the clutch driven plate model; and, based on the relationship between the engine speed and the output parameters of the clutch driven plate, obtains the clutch driving plate output parameters through logical operations; a clutch driven plate model, which obtains the clutch output parameters by judging and mathematically performing calculations on the output parameters of the clutch driving plate model and the transmission input parameters; simultaneously, the clutch driven plate model also feeds back the clutch output parameters to the clutch driving plate model. This invention enables the prediction of control system performance, solves the problem of not being able to obtain the clutch torque and speed change patterns during gear shifting, and provides strong support for clutch control in the development of AMT and DCT systems.

Description

Technical Field

[0001] This invention belongs to the field of clutch simulation technology, specifically relating to a method for constructing a general model of a dry clutch. Background Technology

[0002] Currently, most AMT and DCT system simulation platforms in China only provide a simple setup for the clutch and cannot perform dynamic analysis of the gear shifting process, thus failing to provide rapid support for control system design.

[0003] Therefore, designing a universal model for dry clutches to accelerate the design progress of simulation platforms and provide support for the design and debugging of AMT control systems has become an important task. Summary of the Invention

[0004] (a) Technical problems to be solved

[0005] The technical problem to be solved by this invention is: how to provide a general model construction method for dry clutches, which can be applied to the simulation of AMT and DCT systems to complete the dynamic analysis of the clutch during the gear shifting process, and provide a foundation for the research of control strategies and road surface recognition technology.

[0006] (II) Technical Solution

[0007] To solve the above technical problems, the present invention provides a method for constructing a general model of a dry clutch, the general model of a dry clutch including: a clutch driving plate model and a clutch driven plate model;

[0008] The clutch driving plate model is used to receive engine speed and output parameters of the clutch driven plate model. Based on the relationship between engine speed and output parameters of the clutch driven plate model, the clutch driving plate output parameters are obtained through logical operations.

[0009] The clutch driven plate model generates clutch driven plate model output parameters by judging and mathematically calculating the output parameters of the clutch driving plate and the gearbox output parameters. The clutch driven plate model output parameters and the clutch driving plate output parameters are combined as the clutch output parameters and output as the input parameters of the gearbox model. At the same time, the clutch driven plate model also feeds back the clutch driven plate model output parameters to the clutch driving plate model.

[0010] The output parameters of the clutch drive plate include: clutch drive plate output speed, clutch drive plate output torque, and clutch drive plate output moment of inertia.

[0011] The output parameters of the clutch driven plate model include: clutch driven plate output speed, clutch driven plate output torque, and clutch driven plate output moment of inertia.

[0012] The output parameters of the transmission include: transmission input shaft speed, transmission input shaft torque, and transmission input shaft moment of inertia.

[0013] The clutch drive plate model includes: a drive plate damping model and a drive plate force model;

[0014] The active disc damping model is used to receive the clutch active disc output parameters output by the engine speed and the active disc force model, and to calculate the clutch active disc output torque.

[0015] The active plate force model is used to receive the clutch active plate output torque and the clutch driven plate model output parameters from the active plate damping model, and output the clutch active plate output parameters through calculation.

[0016] The clutch drive plate model obtains the clutch drive plate output torque through the following formula;

[0017] Clutch drive plate output torque T dumper The calculation is as follows:

[0018] θ=θ0+∫(ω eng -ω dumper )dt

[0019]

[0020] in:

[0021] θ: Current angular velocity of the engine;

[0022] The derivative of θ;

[0023] θ0: Angular velocity of the engine at idle speed, provided by the engine manufacturer;

[0024] ω eng Engine speed;

[0025] ω dumper : The output speed of the clutch drive plate;

[0026] k: Spring stiffness, obtained experimentally;

[0027] c: Spring damping coefficient, obtained experimentally.

[0028] The clutch drive plate model obtains the clutch drive plate output speed through the following formula:

[0029] Clutch drive plate output speed ω dumper The calculation is as follows:

[0030]

[0031] in:

[0032] ω driven The output speed of the clutch driven plate model is numerically equal to the input shaft speed of the gearbox;

[0033] ω0: Initial angular velocity of the gearbox input shaft, equal to the angular velocity of the engine at idle speed;

[0034] T driven The output torque of the clutch driven plate model is numerically equal to the input shaft torque of the gearbox;

[0035] T dumper : The output torque of the clutch drive plate;

[0036] J dumper The output moment of inertia of the clutch drive plate is the sum of the equivalent inertia of the gearbox and the moment of inertia of the clutch drive plate, which are provided by the gearbox manufacturer and the clutch manufacturer, respectively.

[0037] The clutch driven plate model generates the clutch driven plate model output parameters in the following way:

[0038] Clutch driven plate output torque

[0039] Clutch driven plate output speed ω out =ω dumper ;

[0040] Clutch driven plate output rotational inertia

[0041] in:

[0042] T trans The clutch transmits torque;

[0043] When the current clutch torque T act When ≤0, the clutch transmits torque T trans The value is 0; the current torque T act When the torque is greater than 0, the clutch transmits torque T. trans for:

[0044]

[0045] Where: Δω=ω dumper -ω primary ;

[0046] ω primary : Gearbox input shaft speed;

[0047] Δω1 and Δω2 refer to Δω between adjacent sampling times;

[0048]

[0049] Clutch equivalent torque T d_tq The calculation method is as follows:

[0050] T d_tq =(J primary *T primary -J dumper *T dumper ) / (J primary +J dumper )

[0051] Among them: J primary : Moment of inertia of the gearbox input shaft;

[0052] T primary : Transmission input shaft torque;

[0053] The general model for dry clutches divides dry clutches into a driving disc model and a driven disc model; the driving disc model is further divided into a damping model and a force model.

[0054] First, based on the relationship between engine speed and clutch output parameters, logical calculations are performed to obtain the output parameters of the drive disc, including speed, torque, and moment of inertia. Second, these parameters and the transmission input parameters are mathematically calculated to obtain the equivalent clutch torque. Finally, combined with the clutch status and the current clutch torque, logical judgments are performed to output the clutch output parameters, namely speed, torque, and moment of inertia.

[0055] The implementation method of the general model of the dry clutch is carried out using the Matlab tool.

[0056] (III) Beneficial Effects

[0057] Compared with existing technologies, this invention provides a general method for constructing a clutch dynamic model. The establishment of the clutch dynamic simulation model enables the prediction of control system performance and solves the problem of not being able to obtain the clutch torque and speed change law during the shifting process. It provides strong support for clutch control in the development process of AMT and DCT systems, and also greatly helps to improve the shifting shock of vehicles and improve the reliability of friction elements.

[0058] The dry clutch model of this invention has been successfully applied to the simulation analysis and control system design of an 8x8 wheeled armored vehicle and road surface recognition technology. Verification with the aforementioned vehicle models has shown that the dry clutch model not only achieves dynamic clutch simulation but also meets the requirements of whole-vehicle simulation. This platform can replace the actual clutch for research on control systems and hydraulic systems.

[0059] The technical solution of this invention can shorten the development cycle of automatic transmission systems, reduce R&D costs, and improve work efficiency, which is of great significance to the development of projects. It can be widely applied in the development of gearboxes for various MT, AMT, DCT, and AST systems, saving design time and costs for control systems. Attached Figure Description

[0060] Figure 1 This is a block diagram of the general model structure of the dry clutch of the present invention.

[0061] Figure 2 This is a block diagram of the clutch drive disc model of the present invention.

[0062] Figure 3 This is a block diagram illustrating the operational principle of the clutch driven disc model of the present invention. Detailed Implementation

[0063] To make the objectives, contents, and advantages of the present invention clearer, the specific embodiments of the present invention will be described in further detail below with reference to the accompanying drawings and examples.

[0064] Based on the functional characteristics of dry clutches, this invention unifies the dry clutch into two parts: a driving plate and a driven plate. The driving plate is further divided into damping and force-bearing parts. According to the different stages of clutch disengagement and engagement, the output speed, torque, and inertia of the clutch are calculated.

[0065] First, based on the relationship between the vehicle transmission system status, engine speed, and driven plate parameters, logical calculations are performed to obtain the output parameters of the driving plate, including speed, torque, and moment of inertia. Second, these parameters and the transmission input parameters are mathematically calculated to obtain the clutch output parameters. Finally, combined with the clutch status and current clutch torque provided by the control system, logical judgments are made to output the clutch output speed, torque, and moment of inertia.

[0066] Specifically, to solve the above-mentioned technical problems, the present invention provides a method for constructing a general model of a dry clutch, such as... Figure 1 As shown, the general model of the dry clutch includes: a clutch driving plate model and a clutch driven plate model;

[0067] The clutch driving plate model is used to receive engine speed and output parameters of the clutch driven plate model. Based on the relationship between engine speed and output parameters of the clutch driven plate model, the clutch driving plate output parameters are obtained through logical operations.

[0068] The clutch driven plate model generates clutch driven plate model output parameters by judging and mathematically calculating the output parameters of the clutch driving plate and the gearbox output parameters. The clutch driven plate model output parameters and the clutch driving plate output parameters are combined as the clutch output parameters and output as the input parameters of the gearbox model. At the same time, the clutch driven plate model also feeds back the clutch driven plate model output parameters to the clutch driving plate model.

[0069] The output parameters of the clutch drive plate include: clutch drive plate output speed, clutch drive plate output torque, and clutch drive plate output moment of inertia.

[0070] The output parameters of the clutch driven plate model include: clutch driven plate output speed, clutch driven plate output torque, and clutch driven plate output moment of inertia.

[0071] The output parameters of the transmission include: transmission input shaft speed, transmission input shaft torque, and transmission input shaft moment of inertia.

[0072] Among them, such as Figure 2 As shown, the clutch drive plate model includes: a drive plate damping model and a drive plate force model;

[0073] The active disc damping model is used to receive the clutch active disc output parameters output by the engine speed and the active disc force model, and to calculate the clutch active disc output torque.

[0074] The active plate force model is used to receive the clutch active plate output torque and the clutch driven plate model output parameters from the active plate damping model, and output the clutch active plate output parameters through calculation.

[0075] The clutch drive plate model obtains the clutch drive plate output torque through the following formula;

[0076] Clutch drive plate output torque T dumper The calculation is as follows:

[0077] θ=θ0+∫(ω eng -ω dumper )dt

[0078]

[0079] in:

[0080] θ: Current angular velocity of the engine;

[0081] The derivative of θ;

[0082] θ0: Angular velocity of the engine at idle speed, provided by the engine manufacturer;

[0083] ω eng Engine speed;

[0084] ω dumper : The output speed of the clutch drive plate;

[0085] k: Spring stiffness, obtained experimentally;

[0086] c: Spring damping coefficient, obtained experimentally.

[0087] The clutch drive plate model obtains the clutch drive plate output speed through the following formula:

[0088] Clutch drive plate output speed ω dumper The calculation is as follows:

[0089]

[0090] in:

[0091] ω driven The output speed of the clutch driven plate model is numerically equal to the input shaft speed of the gearbox;

[0092] ω0: Initial angular velocity of the gearbox input shaft, equal to the angular velocity of the engine at idle speed;

[0093] T driven The output torque of the clutch driven plate model is numerically equal to the input shaft torque of the gearbox;

[0094] T dumper : The output torque of the clutch drive plate;

[0095] J dumper The output moment of inertia of the clutch drive plate is the sum of the equivalent inertia of the gearbox and the moment of inertia of the clutch drive plate, which are provided by the gearbox manufacturer and the clutch manufacturer, respectively.

[0096] Among them, such as Figure 3 As shown, the clutch driven plate model generates the clutch driven plate model output parameters in the following way:

[0097] Clutch driven plate output torque

[0098] Clutch driven plate output speed ω out =ω dumper ;

[0099] Clutch driven plate output rotational inertia

[0100] in:

[0101] T trans The clutch transmits torque;

[0102] When the current clutch torque T act When ≤0, the clutch transmits torque T trans The value is 0; the current torque T act When the torque is greater than 0, the clutch transmits torque T. trans for:

[0103]

[0104] Where: Δω=ω dumper -ω primary ;

[0105] ω primary : Gearbox input shaft speed;

[0106] Δω1 and Δω2 refer to Δω between adjacent sampling times;

[0107]

[0108] Clutch equivalent torque T d_tq The calculation method is as follows:

[0109] T d_tq =(J primary *T primary -J dumper *T dumper ) / (J primary +J dumper )

[0110] Among them: J primary : Moment of inertia of the gearbox input shaft;

[0111] T primary : Transmission input shaft torque;

[0112] The general model for dry clutches divides dry clutches into a driving disc model and a driven disc model; the driving disc model is further divided into a damping model and a force model.

[0113] First, based on the relationship between engine speed and clutch output parameters, logical calculations are performed to obtain the output parameters of the drive disc, including speed, torque, and moment of inertia. Second, these parameters and the transmission input parameters are mathematically calculated to obtain the equivalent clutch torque. Finally, combined with the clutch status and the current clutch torque, logical judgments are performed to output the clutch output parameters, namely speed, torque, and moment of inertia.

[0114] The implementation method of the general model of the dry clutch is carried out using the Matlab tool.

[0115] Example 1

[0116] This implementation example Figures 1-3 As shown, attached Figure 1 A structural block diagram of a dry clutch model is shown, which consists of a driving plate model and a driven plate model. The driving plate model calculates the clutch driving plate output parameters, including the clutch driving plate output speed, torque, and moment of inertia. The driven plate model judges the output parameters of the driving plate model and the parameters of the gearbox input shaft, and outputs the clutch output parameters. Simultaneously, the driven plate model feeds back the final parameters to the driving plate model. The clutch output parameters include speed, torque, and moment of inertia.

[0117] Appendix Figure 2 The diagram shows the structural block of the driving disc model, which is divided into a damping characteristic model and a force model. The clutch damping characteristic model calculates the output torque of the clutch driving disc using angular velocity, while the driving disc force model calculates the output parameters of the clutch driving / driven discs, outputting the clutch driving disc's output speed, output torque, and moment of inertia.

[0118] Clutch drive plate output torque T dumper The calculation is as follows:

[0119] θ=θ0+∫(ω eng -ω dumper )dt

[0120]

[0121] in:

[0122] θ: Current angular velocity of the engine;

[0123] The derivative of θ;

[0124] θ0: Angular velocity of the engine at idle speed, provided by the engine manufacturer;

[0125] ω eng Engine speed;

[0126] ω dumper : The output speed of the clutch drive plate;

[0127] k: Spring stiffness, which can be obtained experimentally;

[0128] c: Spring damping coefficient, which can be obtained experimentally.

[0129] The clutch drive plate output speed is calculated as follows: (EMBED Equation.3)

[0130]

[0131] in:

[0132] ω0: Initial angular velocity of the gearbox input shaft, equal to the angular velocity of the engine at idle speed;

[0133] T primary : Transmission input shaft torque;

[0134] T dumper : Active disc output torque;

[0135] J eng Equivalent inertia of the engine, a fixed value, provided by the engine manufacturer;

[0136] Appendix Figure 3 The method for calculating the output parameters of the clutch driven plate is shown. The output parameters of the driven plate include the clutch driven plate output torque, speed, and moment of inertia.

[0137] Clutch driven plate output torque

[0138] Clutch driven plate output speed ω out =ω dumper

[0139] Clutch driven plate output rotational inertia EMBED Equation.3;

[0140] in:

[0141] T trans The clutch transmits torque;

[0142] When the current clutch torque T act When ≤0, the clutch transmits torque T trans The value is 0; the current torque T act When the torque is greater than 0, the clutch transmits torque T. trans for:

[0143]

[0144] Where: Δω=ω dumper -ω primary ;

[0145] ω primary : Gearbox input shaft speed;

[0146] Δω1 and Δω2 refer to Δω between adjacent sampling times;

[0147]

[0148] Clutch equivalent torque T d_tq The calculation method is as follows:

[0149] T d_tq =(I primary *T primary -I dumper *T dumper ) / (I primary +I dumper )

[0150] Among them: I primary : Moment of inertia of the gearbox input shaft;

[0151] I dumper The moment of inertia of the clutch driving plate is equal to J. eng ;

[0152] T primary : Transmission input shaft torque;

[0153] T dumper : The output torque of the clutch drive plate;

[0154] The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. A method of constructing a generic model of a dry clutch, characterized by, The dry clutch universal model comprises a clutch driving disc model and a clutch driven disc model; The clutch driving disc model is used for receiving an engine rotating speed and a clutch driven disc model output parameter, and obtaining a clutch driving disc output parameter through logical operation according to a relationship between the engine rotating speed and the clutch driven disc model output parameter; The clutch driven disc model generates the clutch driven disc model output parameter through judging and mathematical operation on the clutch driving disc output parameter and a gearbox output parameter, and outputs the clutch driven disc model output parameter and the clutch driving disc output parameter as a clutch output parameter for input parameter of a gearbox model; meanwhile, the clutch driven disc model feeds back the clutch driven disc model output parameter to the clutch driving disc model; The dry clutch universal model unifies the dry clutch into the driving disc model and the driven disc model; the driving disc model is divided into a damping model and a force model; Firstly, the driving disc output parameter including the rotating speed, the torque and the moment of inertia is obtained through logical calculation according to the relationship between the engine rotating speed and the clutch output parameter; secondly, the equivalent clutch torque is obtained through mathematical operation on the parameters and the gearbox input parameter; finally, the clutch output parameter including the rotating speed, the torque and the moment of inertia is output through logical judgment combining the clutch state and the current clutch torque.

2. The method of constructing a generic model of a dry clutch of claim 1, wherein, The clutch driving disc output parameter comprises a clutch driving disc output rotating speed, a clutch driving disc output torque and a clutch driving disc output moment of inertia.

3. The method of constructing a generic model of a dry clutch of claim 1, wherein, The clutch driven disc model output parameter comprises a clutch driven disc output rotating speed, a clutch driven disc output torque and a clutch driven disc output moment of inertia.

4. The method of constructing a generic model of a dry clutch of claim 1, wherein, The gearbox output parameter comprises a gearbox input shaft rotating speed, a gearbox input shaft torque and a gearbox input shaft moment of inertia.

5. The method of constructing a generic model of a dry clutch of claim 1, wherein, The clutch driving disc model comprises a driving disc damping model and a driving disc force model; The driving disc damping model is used for receiving the engine rotating speed and the clutch driving disc output parameter output by the driving disc force model, and obtaining the clutch driving disc output torque through calculation; The driving disc force model is used for receiving the clutch driving disc output torque output by the driving disc damping model and the clutch driven disc model output parameter, and outputting the clutch driving disc output parameter through operation.

6. The method of constructing a generic model of a dry clutch of claim 5, wherein, The clutch driving disc model obtains the clutch driving disc output torque through operation according to the following formula: Clutch drive plate output torque T dumper The calculation is as follows: θ = θ0+∫(ω eng -ω dumper )dt Wherein: θ: current angular velocity of the engine; The derivative of θ; θ0: angular velocity of the engine at idle speed, provided by the engine manufacturer; ω eng : engine speed; ω dumper : clutch driving disc output rotational speed; k: spring stiffness, obtained through experiment; c: spring damping coefficient, obtained through experiment.

7. The method of constructing a generic model of a dry clutch of claim 6, wherein, The clutch driving disc model obtains the clutch driving disc output rotating speed through operation according to the following formula: Clutch drive plate output rotational speed ω dumper is calculated as follows: Wherein: ω driven : clutch driven disc model output rotational speed, numerically equal to the transmission input shaft rotational speed; ω0: initial angular velocity of the gearbox input shaft, equal to the angular velocity of the engine at idle speed; T driven : clutch driven plate model output torque, numerically equal to the gearbox input shaft torque; T dumper : clutch driving disc output torque; J dumper : clutch driving disc output moment of inertia, the sum of the equivalent inertia of the gearbox and the moment of inertia of the clutch driving disc, provided by the gearbox manufacturer and the clutch manufacturer respectively.

8. The method of constructing a generic model of a dry clutch of claim 7, wherein, The clutch driven disc model generates the clutch driven disc model output parameter in the following manner: Clutch driven plate output torque Clutch driven disc output rotational speed ω out = ω dumper ; Clutch driven plate output moment of inertia Wherein: T trans : clutch transmission torque; When the clutch current torque T act = 0, the clutch transmits the torque T trans = 0; the clutch current torque T act > 0, the clutch transmits the torque T trans is: where: Δω = ω dumper -ω primary ; ω primary : transmission input shaft speed; Δω1, Δω2 refer to Δω of adjacent sampling time; Clutch equivalent torque T d_tq The calculation method is as follows: T d_tq = (J primary *T primary -J dumper *T dumper ) / (J primary +J dumper ) wherein: J primary : gear box input shaft moment of inertia; T primary : Transmission input shaft torque.

9. The method of constructing a generic model of a dry clutch of claim 1, wherein, The implementation method of the dry clutch universal model adopts Matlab tool.

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