Wet dual clutch temperature determination method and program product

Abstract

The invention discloses a method for determining the temperature of a wet-type double clutch and a program product. According to the corresponding relation between different friction powers corresponding to a first clutch and different cooling liquid flows and the corresponding relation between different heating coefficients and different cooling coefficients, the temperature of the first clutch is determined according to the corresponding relation between different friction powers corresponding to the first clutch and different cooling liquid flows. The first heating coefficient and the first cooling coefficient corresponding to the first clutch under the first friction power corresponding to the current operation condition and the cooling liquid flow can be determined. Therefore, the cooling liquid temperature corresponding to the current moment of the first clutch can be further calculated according to the first data, the first heating coefficient, the first cooling coefficient, the cooling liquid temperature corresponding to the last moment of the first clutch and the interval duration. And according to the first data, the first heating coefficient, the first cooling coefficient, the friction plate temperature corresponding to the previous moment of the first clutch, the cooling liquid temperature corresponding to the previous moment of the first clutch and the interval duration, the friction plate temperature corresponding to the current moment of the first clutch is calculated. The temperature rise change of the friction plate of the first clutch in the actual working process can be obtained in real time.

Description

Technical Field

[0001] The present application belongs to the technical field of vehicle clutches, and in particular, relates to a method for determining the temperature of a wet dual clutch and a program product. Background Art

[0002] Due to the advantages of good acceleration continuity, low fuel consumption, smooth shifting, and high transmission efficiency, DCT (Dual Clutch Transmission) automatic transmission is widely used in passenger cars. As the core component of DCT automatic transmission, the relative sliding between the dual steel plate and the friction plate during the engagement process will generate a large amount of friction heat. Part of the generated heat is taken away by the cooling oil, and part enters the clutch body, causing the temperature of each clutch component to rise, among which the temperature of the friction plate rises most significantly. If the heat dissipation capacity of the clutch cooling system is insufficient and the heat cannot be taken away in time, the temperature of the friction plate will rise, causing the friction plate to burn and other faults, resulting in clutch failure.

[0003] Due to the structural characteristics of the clutch, it is difficult to arrange temperature sensors on the friction plate and the dual steel plate during the operation of the vehicle. Therefore, the temperature of the wet dual clutch friction plate cannot be monitored by sensors.

[0004] Patent document 201911226122.1 discloses a control method and device based on the surface temperature of a wet dual clutch. The temperature of the clutch friction plate and the dual steel plate is indirectly calculated using the clutch outlet cooling oil temperature. An outlet cooling oil temperature sensor needs to be installed, which is costly and causes cumulative errors due to multiple conversions in the middle. Patent document 201410217118.X discloses a DCT wet dual clutch temperature measurement method based on neural network prediction. A clutch temperature prediction model is established based on a neural network. The main problem to be solved is that the oil temperature at the oil outlet of the wet dual clutch collected by the oil temperature sensor in the prior art has a delay, and the temperature of the clutch is predicted by the oil outlet temperature. However, a large number of experiments are required to obtain oil outlet oil temperature samples during the model training process, which is costly and time-consuming. Summary of the invention

[0005] The embodiments of the present application provide a method and program product for determining the temperature of a wet dual clutch, which can at least accurately determine the temperature of the friction plate of the first clutch in the wet dual clutch, that is, can obtain in real time the temperature rise change of the friction plate of the first clutch during actual operation.

[0006] Other features and advantages of the present application will become apparent from the following detailed description, or may be learned in part by the practice of the present application.

[0007] According to a first aspect of an embodiment of the present application, a method for determining a temperature of a wet dual clutch is provided, wherein the wet dual clutch includes a first clutch, and the method includes:

[0008] Collecting first data, wherein the first data includes an input shaft speed of the dual clutch, an output shaft speed of the first clutch, an actual transmission torque of the first clutch, a coolant flow rate, and an oil tank oil temperature;

[0009] Calculating a first friction power corresponding to the first clutch according to the input shaft speed of the dual clutch, the output shaft speed of the first clutch and the actual transmission torque of the first clutch;

[0010] Determining a first heating coefficient and a first cooling coefficient corresponding to the first clutch under the first friction power and the coolant flow rate according to a correspondence between different friction powers corresponding to the first clutch and different coolant flow rates, different heating coefficients, and different cooling coefficients;

[0011] The coolant temperature corresponding to the current moment of the first clutch is calculated based on the first data, the first heating coefficient, the first cooling coefficient, the coolant temperature corresponding to the previous moment of the first clutch, and the interval time, wherein the interval time is the interval time between the current moment and the previous moment;

[0012] The friction plate temperature corresponding to the first clutch at the current moment is calculated based on the first data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and the coolant temperature corresponding to the first clutch at the previous moment, and the interval duration. The friction plate temperature corresponding to the first clutch at the current moment is greater than or equal to the coolant temperature corresponding to the first clutch at the current moment.

[0013] In some embodiments of the present application, based on the above scheme, the first friction power corresponding to the first clutch is calculated according to the input shaft speed of the dual clutch, the output shaft speed of the first clutch and the actual transmission torque of the first clutch, including:

[0014] calculating an absolute value of a speed difference between a speed of an input shaft of the dual clutch and a speed of an output shaft of the first clutch;

[0015] The product of the absolute value of the rotational speed difference and the actual transmission torque of the first clutch is calculated to obtain a first friction power corresponding to the first clutch.

[0016] In some embodiments of the present application, based on the aforementioned solution, determining the first heating coefficient and the first cooling coefficient corresponding to the first clutch under the first friction power and the coolant flow rate according to the correspondence between different friction powers corresponding to the first clutch and different coolant flow rates, different heating coefficients, and different cooling coefficients includes:

[0017] Determining a first heating coefficient corresponding to the first clutch under the first friction power and the coolant flow rate according to a first corresponding relationship between different friction powers corresponding to the first clutch and different coolant flow rates and different heating coefficients;

[0018] According to a second corresponding relationship between different friction powers corresponding to the first clutch and different coolant flow rates and different cooling coefficients, a first cooling coefficient corresponding to the first clutch under the first friction power and the coolant flow rate is determined.

[0019] In some embodiments of the present application, based on the above scheme, the coolant temperature corresponding to the first clutch at the current moment is calculated according to the first data, the first heating coefficient, the first cooling coefficient, the coolant temperature corresponding to the first clutch at the previous moment, and the interval duration, and is performed by the following formula:

[0020]

[0021] Where, T O1n represents the coolant temperature of the first clutch at the current moment, T O1n-1 represents the coolant temperature of the first clutch at the last moment, M1 represents the actual transmission torque of the first clutch, n in represents the input shaft speed of the dual clutch, n out1 represents the output shaft speed of the first clutch, Q represents the coolant flow rate, T s represents the oil temperature of the oil tank, x1 represents the first heating coefficient, y1 represents the first cooling coefficient, and Δt represents the interval duration.

[0022] In some embodiments of the present application, based on the aforementioned solution, the friction plate temperature corresponding to the first clutch at the current moment is calculated according to the first data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and the coolant temperature corresponding to the first clutch at the previous moment, and the interval duration, and is executed by the following formula:

[0023]

[0024] Where, T C1n represents the friction plate temperature of the first clutch at the current moment, TO1n-1 represents the coolant temperature of the first clutch at the last moment, T C1n-1 represents the friction plate temperature of the first clutch at the last moment, M1 represents the actual transmission torque of the first clutch, n in represents the input shaft speed of the dual clutch, n out1 represents the output shaft speed of the first clutch, Q represents the coolant flow rate, T s represents the oil temperature of the oil tank, x1 represents the first heating coefficient, y1 represents the first cooling coefficient, and Δt represents the interval duration.

[0025] In some embodiments of the present application, based on the above solution, the wet dual clutch further includes a second clutch, and the method further includes:

[0026] collecting second data, wherein the second data includes a speed of an input shaft of the dual clutch, a speed of an output shaft of the second clutch, an actual transmission torque of the second clutch, and a coolant flow rate;

[0027] Calculating a second friction power corresponding to the second clutch according to the input shaft speed of the dual clutch, the output shaft speed of the second clutch and the actual transmission torque of the second clutch;

[0028] Determining a second heating coefficient and a second cooling coefficient corresponding to the second clutch under the second friction power and the coolant flow rate according to a correspondence between different friction powers corresponding to the second clutch and different coolant flow rates, different heating coefficients, and different cooling coefficients;

[0029] The coolant temperature corresponding to the second clutch at the current moment is calculated according to the second data, the second heating coefficient, the second cooling coefficient, the coolant temperature corresponding to the previous moment of the second clutch, the coolant temperature corresponding to the previous moment of the first clutch, and the interval time, wherein the interval time is the interval time between the current moment and the previous moment;

[0030] The friction plate temperature corresponding to the second clutch at a current moment is calculated based on the second data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and the coolant temperature corresponding to the previous moment of the second clutch, the coolant temperature corresponding to the previous moment of the first clutch and the interval duration. The friction plate temperature corresponding to the second clutch at a current moment is greater than or equal to the coolant temperature corresponding to the second clutch at a current moment.

[0031] In some embodiments of the present application, based on the above scheme, determining the second heating coefficient and the second cooling coefficient corresponding to the second clutch under the second friction power and the coolant flow rate according to the corresponding relationship between the different friction powers corresponding to the second clutch and the different coolant flow rates, different heating coefficients, and different cooling coefficients includes:

[0032] determining a second heating coefficient corresponding to the second clutch under the second friction power and the coolant flow rate according to a third corresponding relationship between different friction powers corresponding to the second clutch and different coolant flow rates and different heating coefficients;

[0033] According to a fourth corresponding relationship between different friction powers corresponding to the second clutch and different coolant flow rates and different cooling coefficients, a second cooling coefficient corresponding to the second clutch under the second friction power and the coolant flow rate is determined.

[0034] In some embodiments of the present application, based on the above scheme, the coolant temperature corresponding to the second clutch at the current moment is calculated according to the second data, the second heating coefficient, the second cooling coefficient, the coolant temperature corresponding to the second clutch at the previous moment, the coolant temperature corresponding to the first clutch at the previous moment, and the interval duration, and is performed by the following formula:

[0035]

[0036] Where, T O2n represents the coolant temperature of the second clutch at the current moment, T O2n-1 represents the coolant temperature of the second clutch at the last moment, M2 represents the actual transmission torque of the second clutch, and n in represents the input shaft speed of the dual clutch, n out2 represents the output shaft speed of the second clutch, Q represents the coolant flow rate, T O1n-1 represents the coolant temperature of the first clutch corresponding to the last moment, x2 represents the second heating coefficient, y2 represents the second cooling coefficient, and Δt represents the interval duration.

[0037] In some embodiments of the present application, based on the aforementioned solution, the friction plate temperature corresponding to the second clutch at the current moment is calculated according to the second data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and the coolant temperature corresponding to the last moment of the second clutch, the coolant temperature corresponding to the last moment of the first clutch, and the interval duration, and is performed by the following formula:

[0038]

[0039] Where, T C2n represents the friction plate temperature of the second clutch at the current moment, T O2n-1 represents the coolant temperature of the second clutch at the last moment, T C2n-1 represents the friction plate temperature of the second clutch at the last moment, M2 represents the actual transmission torque of the second clutch, and n in represents the input shaft speed of the dual clutch, n out2 represents the output shaft speed of the second clutch, Q represents the coolant flow rate, T O1n-1 represents the coolant temperature of the first clutch corresponding to the last moment, x2 represents the second heating coefficient, y2 represents the second cooling coefficient, and Δt represents the interval duration.

[0040] According to a second aspect of an embodiment of the present application, a computer program product is provided, which includes computer instructions stored in a computer-readable storage medium and suitable for being read and executed by a processor, so that a computer device having the processor executes the method described in the first aspect of the embodiment of the present application.

[0041] Based on the technical solution proposed in the present application, according to the input shaft speed of the dual clutch, the output shaft speed of the first clutch and the actual transmission torque of the first clutch, the first friction power corresponding to the first clutch under the current operating condition can be calculated. According to the corresponding relationship between the different friction powers corresponding to the first clutch and the different coolant flows, different heating coefficients and different cooling coefficients, the first friction power corresponding to the first clutch under the current operating condition, the first heating coefficient and the first cooling coefficient corresponding to the coolant flow can be determined. Thus, the coolant temperature corresponding to the first clutch at the current moment can be further calculated according to the first data (including the input shaft speed of the dual clutch, the output shaft speed of the first clutch, the actual transmission torque of the first clutch, the coolant flow and the oil temperature of the oil tank), the first heating coefficient, the first cooling coefficient, the coolant temperature corresponding to the previous moment of the first clutch and the interval length. And after calculating the coolant temperature corresponding to the current moment of the first clutch, the friction plate temperature corresponding to the current moment of the first clutch can be further calculated according to the first data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and the coolant temperature corresponding to the previous moment of the first clutch and the interval length. The heat exchange relationship between the friction plate of the first clutch and the coolant in the oil tank is taken into consideration, which can better conform to the structural characteristics of the wet dual-clutch cooling system, making the calculation of the friction plate temperature of the first clutch more accurate and able to obtain the temperature rise change of the friction plate of the first clutch in the actual working process in real time.

[0042] It should be understood that the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0043] The drawings herein are incorporated into the specification and constitute a part of the specification, showing embodiments consistent with the present application, and together with the specification, are used to explain the principles of the present application. Obviously, the drawings described below are only some embodiments of the present application, and for ordinary technicians in this field, other drawings can be obtained based on these drawings without creative work. In the drawings:

[0044] Figure 1 It is a schematic diagram of a wet dual clutch;

[0045] Figure 2 It is a schematic diagram of the wet dual clutch cooling system;

[0046] Figure 3 A flow chart showing a method for determining the temperature of a wet dual clutch in an embodiment of the present application is shown;

[0047] Figure 4 A flowchart showing the steps of calculating the first friction power corresponding to the first clutch according to the input shaft speed of the dual clutch, the output shaft speed of the first clutch and the actual transmission torque of the first clutch is shown;

[0048] Figure 5 A flowchart of the steps of determining a first heating coefficient and a first cooling coefficient corresponding to the first clutch at a first friction power and a coolant flow rate is shown according to the corresponding relationship between different friction powers corresponding to the first clutch and different coolant flow rates, different heating coefficients and different cooling coefficients;

[0049] Figure 6 Another flow chart showing a method for determining the temperature of a wet dual clutch;

[0050] Figure 7 A flowchart showing the steps of calculating the second friction power corresponding to the second clutch according to the input shaft speed of the dual clutch, the output shaft speed of the second clutch, and the actual transmission torque of the second clutch;

[0051] Figure 8 A flowchart of the steps of determining the second heating coefficient and the second cooling coefficient corresponding to the second clutch under the second friction power and the coolant flow rate is shown according to the corresponding relationship between different friction powers corresponding to the second clutch and different coolant flow rates, different heating coefficients and different cooling coefficients;

[0052] Fig. 9 A schematic diagram of the structure of a computer program product in an embodiment of the present application is shown.

[0053] Reference numerals:

[0054] First clutch 1, second clutch 2, return spring 3, coolant oil chamber 4, dual clutch input shaft 5, first clutch output shaft 6, second clutch output shaft 7;

[0055] Oil tank 210, cooling motor 220, oil pump 230, oil temperature sensor 240, cooling oil channel 250, check valve 260, oil cooler 270;

[0056] Processor 901 , memory 902 , input / output interface 903 , communication interface 904 , bus 905 . DETAILED DESCRIPTION

[0057] The following will be combined with the drawings in the embodiments of the present application to clearly and completely describe the technical solutions in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of this application.

[0058] In addition, described feature, structure or characteristic can be combined in one or more embodiments in any suitable manner. In the following description, many specific details are provided to provide a full understanding of the embodiments of the present application. However, those skilled in the art will appreciate that the technical scheme of the present application can be put into practice without one or more of the specific details, or other methods, components, devices, steps, etc. can be adopted. In other cases, known methods, devices, realizations or operations are not shown or described in detail to avoid blurring the various aspects of the application.

[0059] The block diagrams shown in the accompanying drawings are merely functional entities and do not necessarily correspond to physically independent entities. That is, these functional entities may be implemented in software form, or in one or more hardware modules or integrated circuits, or in different networks and / or processor devices and / or microcontroller devices.

[0060] The flowcharts shown in the accompanying drawings are only exemplary and do not necessarily include all the contents and operations / steps, nor must they be executed in the order described. For example, some operations / steps can be decomposed, and some operations / steps can be combined or partially combined, so the actual execution order may change according to actual conditions.

[0061] In the description of this application, it should be understood that the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of the feature. In the description of this application, unless otherwise specified, "plurality" means two or more.

[0062] In order to enable those skilled in the art to better understand the present application, the application scenarios involved in the present application are first briefly described.

[0063] During the driving of a vehicle equipped with a dual-clutch, especially on special roads and under harsh driving conditions, frequent starting or gear shifting of the vehicle can easily cause the clutch temperature to rise too high, reducing the clutch torque transmission accuracy, affecting driving comfort, and even burning the clutch, causing the vehicle to break down.

[0064] Reference Figure 1 , Figure 1 It is a schematic diagram of a wet double clutch. Figure 1 As shown, the wet dual clutch includes a first clutch 1 and a second clutch 2. The two clutches are mounted on the same drum, and their structures are the same as the principle of the internal gear transmission mechanism. The first clutch 1 and the second clutch 2 are composed of a steel diaphragm, a friction plate, an inner diaphragm and an outer diaphragm. The outer diaphragm body and the steel diaphragm are connected together under the action of hydraulic oil, and the friction plate is connected to the inner diaphragm under the action of hydraulic oil. The outer diaphragms of the two clutches are welded to the clutch active disc, and the inner diaphragms are connected to the transmission input shaft to transmit power to the transmission input shaft. The wet dual clutch also includes a return spring 3, a coolant oil chamber 4, an input shaft 5 of the dual clutch, a first clutch output shaft 6, and a second clutch output shaft 7.

[0065] Compared with the dry clutch, the wet dual clutch can quickly cool the friction plate of the first clutch through the heat exchange between the coolant in the coolant oil chamber 4 and the friction plate of the first clutch. During the driving process of the vehicle, the wet dual clutch rotates at a high speed, and the temperature sensor is difficult to arrange and install. Therefore, it is necessary to establish a relatively accurate temperature determination method for real-time acquisition of the temperature rise change of the wet dual clutch during the actual working process.

[0066] The traditional clutch temperature calculation method is generally based on the principles of thermal theory. Parameters such as specific heat capacity, introduction coefficient, clutch mass, etc. are input into the theoretical formula to calculate the clutch temperature. However, due to the influence of parameter accuracy and changes in the clutch thermal field in actual driving conditions, there is a large difference between the clutch temperature calculated theoretically and under actual conditions.

[0067] In addition, in the prior art, there are also methods using finite element or neural network to calculate the clutch temperature through the clutch thermal model. However, on the one hand, it does not consider the influence relationship between the first clutch and the second clutch. On the other hand, the thermal model calculation is too complicated to meet the real-time requirements and cannot be downloaded to the actual vehicle controller for use.

[0068] Based on this, an embodiment of the present application provides a method for determining the temperature of a wet dual clutch, which can at least accurately determine the temperature of the friction plate of the first clutch, and can obtain in real time the temperature rise change of the friction plate of the first clutch during actual operation.

[0069] Reference Figure 2 , Figure 2 This is a schematic diagram of the wet dual clutch cooling system. Figure 2 As shown, the coolant in the oil tank 210 is pressurized by the cooling motor 220 and the oil pump 230, and then flows into the cooling oil channel 250, first flows through the first clutch 1, and then flows through the second clutch 2 through the cooling oil channel 250. The heated coolant flows into the oil cooler 270 through the one-way valve 260 for cooling, and then flows back to the oil tank 210. Among them, the oil temperature sensor 240 arranged at the cooling oil channel 250 can measure the oil temperature flowing into the cooling oil channel 250 in real time, that is, the oil temperature in the oil tank 210. It can be seen that in this wet dual clutch cooling system, there is heat exchange between the first clutch 1 and the coolant in the oil tank 210, and heat exchange between the first clutch 1 and the second clutch 2.

[0070] Reference Figure 3 , shows a flow chart of a method for determining the temperature of a wet dual clutch in an embodiment of the present application, which can accurately determine the temperature of the friction plate of the first clutch 1, including but not limited to steps S310 to S350.

[0071] Step S310, collecting first data, the first data including the input shaft speed of the dual clutch, the output shaft speed of the first clutch, the actual transmission torque of the first clutch, the coolant flow rate and the oil tank oil temperature.

[0072] In the embodiment of the present application, in order to determine the temperature of the friction plate of the first clutch 1, it is necessary to collect first data related to the first clutch 1, and the first data includes the input shaft speed of the dual clutch, the output shaft speed of the first clutch, the actual transmission torque of the first clutch, the coolant flow rate and the oil tank oil temperature.

[0073] Step S320: Calculate the first friction power corresponding to the first clutch according to the input shaft speed of the dual clutch, the output shaft speed of the first clutch and the actual transmission torque of the first clutch.

[0074] In the present application embodiment, Figure 2It can be seen from the wet dual clutch cooling system shown that the cooling of the first clutch 1 is mainly achieved based on the heat exchange of the coolant in the first clutch 1 and the oil tank 210. The heat exchange of the coolant in the first clutch 1 and the oil tank 210 is related to the heating coefficient and cooling coefficient corresponding to the first clutch 1. The heating coefficient and cooling coefficient of the first clutch 1 are related to the friction power and cooling flow corresponding to the first clutch 1. Therefore, it is necessary to first obtain the cooling flow of the first friction power corresponding to the first clutch 1 under the current operating condition. Specifically, the first friction power corresponding to the first clutch can be calculated based on the input shaft speed of the dual clutch under the current operating condition, the output shaft speed of the first clutch, and the actual transmission torque of the first clutch, and the cooling flow under the current operating condition can be directly collected.

[0075] Reference Figure 4 , Figure 4 A flow chart of steps for calculating the first friction power corresponding to the first clutch according to the input shaft speed of the dual clutch, the output shaft speed of the first clutch and the actual transmission torque of the first clutch is shown, including but not limited to steps S410 to S420.

[0076] Step S410, calculating the absolute value of the speed difference between the input shaft speed of the dual clutch and the output shaft speed of the first clutch.

[0077] Step S420: Calculate the product of the absolute value of the speed difference and the actual torque transmitted by the first clutch to obtain a first friction power corresponding to the first clutch.

[0078] In the embodiment of the present application, the first friction power corresponding to the first clutch 1 is the product of the actual transmission torque of the first clutch and the absolute value of the speed difference, that is, P1=M1*dn1, in kw. Wherein, P1 represents the first friction power, M1 represents the actual transmission torque of the first clutch, and dn1 represents the absolute value of the speed difference, that is, the absolute value of the speed difference between the input shaft speed of the dual clutch and the output shaft speed of the first clutch. Wherein, the input shaft of the dual clutch is the common input shaft of the first clutch 1 and the second clutch 2.

[0079] Step S330, determining the first heating coefficient and the first cooling coefficient corresponding to the first clutch at the first friction power and the coolant flow rate according to the corresponding relationship between different friction powers corresponding to the first clutch and different coolant flow rates, different heating coefficients and different cooling coefficients.

[0080] In the embodiment of the present application, after the first friction power corresponding to the first clutch is calculated according to the input shaft speed of the dual clutch, the output shaft speed of the first clutch and the actual transmission torque of the first clutch, the first heating coefficient and the first cooling coefficient corresponding to the first friction power and the coolant flow rate of the first clutch 1 under the current operating condition can be further determined according to the corresponding relationship between the different friction powers corresponding to the first clutch 1 and the different coolant flow rates, the different heating coefficients and the different cooling coefficients. Among them, the corresponding relationship between the different friction powers corresponding to the first clutch 1 and the different coolant flow rates, the different heating coefficients and the different cooling coefficients can be obtained by designing a first clutch temperature measurement test bench according to different working conditions, taking the first data as input, taking the mathematical model of the coolant temperature corresponding to the first clutch 1 and the mathematical model of the friction plate temperature corresponding to the first clutch 1 as the temperature calculation model, and taking the friction plate temperature of the first clutch 1 under each working condition as the target, and solving the heating coefficient and the cooling coefficient of the first clutch 1 through iterative optimization.

[0081] Specifically, in the first clutch temperature measurement test bench, the friction power axis parameters can generally be set to 0.5, 1, 1.5, 2, 2.5, 3, 3.5, in kw. The cooling flow axis parameters can generally be set to 0.5, 1, 3, 5, 7, 10, in L / min. The mathematical model of the coolant temperature corresponding to the first clutch 1 is: In formula 1, T O1n represents the coolant temperature of the first clutch at the current moment, T O1n-1 represents the coolant temperature of the first clutch at the last moment, M1 represents the actual torque transmitted by the first clutch, and n in Indicates the input shaft speed of the dual clutch, n out1 represents the output shaft speed of the first clutch, Q represents the coolant flow rate, T s represents the oil temperature of the oil tank, x1 represents the first heating coefficient, y1 represents the first cooling coefficient, Δt represents the interval time, and the interval time is the interval time between the current moment and the previous moment. The mathematical model of the friction plate temperature corresponding to the first clutch 1 is In formula 2, T C1n Indicates the friction plate temperature of the first clutch at the current moment, T O1n-1 represents the coolant temperature of the first clutch at the last moment, T C1n-1 represents the friction plate temperature of the first clutch at the last moment, M1 represents the actual transmission torque of the first clutch, n in Indicates the input shaft speed of the dual clutch, n out1 represents the output shaft speed of the first clutch, Q represents the coolant flow rate, T srepresents the oil temperature of the oil tank, x1 represents the first heating coefficient, y1 represents the first cooling coefficient, Δt represents the interval time, and the interval time is the interval time between the current moment and the previous moment. By taking the friction plate temperature of the first clutch 1 under various working conditions as the target and iteratively optimizing the temperature calculation model, the heating coefficient and cooling coefficient of the first clutch 1 can be solved.

[0082] Reference Figure 5 , Figure 5 A flow chart of steps for determining the first heating coefficient and the first cooling coefficient corresponding to the first clutch at the first friction power and the coolant flow rate is shown according to the correspondence between different friction powers corresponding to the first clutch and different coolant flow rates, different heating coefficients and different cooling coefficients, including but not limited to steps S510 to S520.

[0083] Step S510, determining a first heating coefficient corresponding to the first clutch under a first friction power and a coolant flow rate according to a first corresponding relationship between different friction powers corresponding to the first clutch and different coolant flow rates and different heating coefficients.

[0084] Step S520, determining a first cooling coefficient corresponding to the first clutch under a first friction power and a coolant flow rate according to a second corresponding relationship between different friction powers corresponding to the first clutch and different coolant flow rates and different cooling coefficients.

[0085] In the embodiment of the present application, refer to Table 1 and Table 2, wherein Table 1 is a table of correspondence between different friction powers corresponding to the first clutch 1 and different coolant flows and different heating coefficients. Table 2 is a table of correspondence between different friction powers corresponding to the first clutch 1 and different coolant flows and different cooling coefficients. Through the three-dimensional parameter table shown in Table 1 and the first friction power and coolant flow corresponding to the first clutch 1 under the current operating condition, the first heating coefficient x1 corresponding to the first clutch 1 under the current operating condition can be determined. For example, if the first friction power corresponding to the first clutch 1 under the current operating condition is 2kw and the corresponding coolant flow is 3L / min, it can be determined that the first heating coefficient x1 corresponding to the first clutch 1 under the current operating condition is 1024J / ℃. Similarly, through the three-dimensional parameter table shown in Table 2 and the first friction power and coolant flow corresponding to the first clutch 1 under the current operating condition, the first cooling coefficient y1 corresponding to the first clutch 1 under the current operating condition can be determined. For example, if the first friction power corresponding to the first clutch 1 under the current operating condition is 2 kW and the corresponding coolant flow rate is 3 L / min, it can be determined that the first cooling coefficient y1 corresponding to the first clutch 1 under the current operating condition is 874S*L / min.

[0086] Table 1 Corresponding relationship between different friction powers corresponding to the first clutch 1 and different coolant flow rates and different heating coefficients

[0087]

[0088]

[0089] Table 2 Corresponding relationship between different friction powers corresponding to the first clutch 1 and different coolant flow rates and different cooling coefficients

[0090]

[0091] Step S340, calculate the coolant temperature corresponding to the current moment of the first clutch based on the first data, the first heating coefficient, the first cooling coefficient, the coolant temperature corresponding to the previous moment of the first clutch and the interval duration, wherein the interval duration is the interval duration between the current moment and the previous moment.

[0092] In the embodiment of the present application, the heat source of the coolant corresponding to the first clutch 1 is the friction work of the first clutch 1, and the main factors of cooling are the cooling flow rate and the temperature difference between the coolant temperature corresponding to the first clutch 1 and the coolant in the oil tank 210. Therefore, after the first friction power and coolant flow rate corresponding to the first clutch 1 under the current operating conditions according to the above three-dimensional parameter tables 1 and 2, the coolant temperature corresponding to the first clutch at the current moment can be further calculated according to the first data, the first heating coefficient, the first cooling coefficient, the coolant temperature corresponding to the previous moment of the first clutch, and the interval length. Specifically, according to the first data, the first heating coefficient, the first cooling coefficient, the coolant temperature corresponding to the previous moment of the first clutch, and the interval length, the above formula 1 is used to calculate the coolant temperature corresponding to the first clutch at the current moment. That is, according to the oil tank oil temperature T s The coolant temperature corresponding to the first clutch 1 is calculated.

[0093] Step S350, calculates the friction plate temperature corresponding to the current moment of the first clutch based on the first data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and the coolant temperature corresponding to the previous moment of the first clutch, and the interval duration. The friction plate temperature corresponding to the current moment of the first clutch is greater than or equal to the coolant temperature corresponding to the current moment of the first clutch.

[0094] In the embodiment of the present application, the heat source of the friction plate of the first clutch 1 is the friction work of the first clutch 1, and the main factors for cooling are the cooling flow rate and the temperature difference between the friction plate of the first clutch 1 and the coolant in the oil tank 210. Therefore, after the first friction power and coolant flow rate corresponding to the first clutch 1 under the current operating conditions according to the above three-dimensional parameter tables 1 and 2, the friction plate temperature corresponding to the current moment of the first clutch can be further calculated according to the first data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and coolant temperature corresponding to the previous moment of the first clutch, and the interval time. Specifically, according to the first data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and coolant temperature corresponding to the previous moment of the first clutch, and the interval time, the friction plate temperature corresponding to the current moment of the first clutch can be calculated using the above formula 2. That is, according to the oil tank oil temperature T s The friction plate temperature corresponding to the first clutch 1 is calculated by the coolant temperature corresponding to the first clutch 1. Since the friction plate of the first clutch 1 is the heat source and the coolant is the heat dissipation unit, the friction plate temperature of the first clutch 1 is not less than the coolant temperature of the first clutch 1, that is, T C1n ≥T O1n .

[0095] In the embodiment of the present application, the first friction power corresponding to the first clutch under the current operating condition is calculated based on the input shaft speed of the dual clutch, the output shaft speed of the first clutch and the actual transmission torque of the first clutch. Then, according to the corresponding relationship between the different friction powers corresponding to the first clutch and the different coolant flows, different heating coefficients and different cooling coefficients, the first friction power corresponding to the first clutch under the current operating condition, the first heating coefficient and the first cooling coefficient corresponding to the coolant flow rate can be determined. Thus, the coolant temperature corresponding to the first clutch at the current moment can be further calculated based on the first data (including the input shaft speed of the dual clutch, the output shaft speed of the first clutch, the actual transmission torque of the first clutch, the coolant flow rate and the oil temperature of the oil tank), the first heating coefficient, the first cooling coefficient, the coolant temperature corresponding to the previous moment of the first clutch and the interval length. And after calculating the coolant temperature corresponding to the first clutch at the current moment, the friction plate temperature corresponding to the first clutch at the current moment can be further calculated based on the first data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and the coolant temperature corresponding to the previous moment of the first clutch and the interval length. The heat exchange relationship between the first clutch 1 and the coolant in the oil tank 210 is taken into consideration, that is, the heat exchange relationship between the friction plate of the first clutch and the coolant in the oil tank is taken into consideration, which can be more in line with the structural characteristics of the wet dual-clutch cooling system, making the calculation of the friction plate temperature of the first clutch 1 more accurate, and the temperature rise change of the friction plate of the first clutch 1 during the actual working process can be obtained in real time.

[0096] In the embodiment of the present application, the wet dual clutch further includes a second clutch 2. The method for determining the temperature of the wet dual clutch provided in the embodiment of the present application can accurately determine the temperature of the friction plate of the first clutch 1 as well as the temperature of the friction plate of the second clutch 2. Figure 6 , Figure 6 Another flow chart of a method for determining the temperature of a wet dual clutch is shown, which can accurately determine the temperature of the friction plate of the second clutch 2, including but not limited to steps S610 to S650.

[0097] Step S610, collecting second data, the second data including the input shaft speed of the dual clutch, the output shaft speed of the second clutch, the actual transmission torque of the second clutch and the coolant flow rate.

[0098] In the embodiment of the present application, in order to determine the temperature of the friction plate of the second clutch 2, it is necessary to collect second data related to the second clutch 2, and the second data includes the input shaft speed of the dual clutch, the output shaft speed of the second clutch, the actual transmission torque of the second clutch and the coolant flow rate.

[0099] Step S620: Calculate the second friction power corresponding to the second clutch according to the input shaft speed of the dual clutch, the output shaft speed of the second clutch and the actual transmission torque of the second clutch.

[0100] In the present application embodiment, Figure 2 It can be seen from the wet dual clutch cooling system shown that the cooling of the second clutch 2 is mainly achieved based on the coolant heat exchange between the first clutch 1 and the second clutch 2. The coolant heat exchange between the second clutch 2 and the first clutch 1 is related to the heating coefficient and cooling coefficient corresponding to the second clutch 2. The heating coefficient and cooling coefficient of the second clutch 2 are related to the friction power and cooling flow corresponding to the first clutch 2. Therefore, it is necessary to first calculate the second friction power and cooling flow corresponding to the second clutch 2 under the current operating condition. Specifically, the second friction power corresponding to the second clutch can be calculated based on the input shaft speed of the dual clutch under the current operating condition, the output shaft speed of the second clutch, and the actual transmission torque of the second clutch, and the cooling flow under the current operating condition can be directly collected.

[0101] Reference Figure 7 , Figure 7 A flow chart of steps for calculating the second friction power corresponding to the second clutch according to the input shaft speed of the dual clutch, the output shaft speed of the second clutch and the actual transmission torque of the second clutch is shown, including but not limited to steps S710 to S720.

[0102] Step S710, calculating the absolute value of the speed difference between the input shaft speed of the dual clutch and the output shaft speed of the second clutch.

[0103] Step S720: Calculate the product of the absolute value of the speed difference and the actual torque transmitted by the second clutch to obtain the second friction power corresponding to the second clutch.

[0104] In the embodiment of the present application, the second friction power corresponding to the second clutch 2 is the product of the actual transmission torque of the second clutch and the absolute value of the speed difference, that is, P2=M2*dn2, in kw. Wherein, P2 represents the second friction power, M2 represents the actual transmission torque of the second clutch, and dn2 represents the absolute value of the speed difference, that is, the absolute value of the speed difference between the input shaft speed of the dual clutch and the output shaft speed of the second clutch. Wherein, the input shaft of the dual clutch is the common input shaft of the first clutch 1 and the second clutch 2.

[0105] Step S630, according to the correspondence between different friction powers corresponding to the second clutch and different coolant flow rates, different heating coefficients and different cooling coefficients, determine the second heating coefficient and the second cooling coefficient corresponding to the second clutch under the second friction power and coolant flow rate.

[0106] In the embodiment of the present application, after the second friction power corresponding to the second clutch is calculated according to the input shaft speed of the dual clutch, the output shaft speed of the second clutch and the actual transmission torque of the second clutch, the second heating coefficient and the second cooling coefficient corresponding to the second friction power and the coolant flow rate of the second clutch 2 under the current operating condition can be further determined according to the corresponding relationship between the different friction powers corresponding to the second clutch 2 and the different coolant flow rates, different heating coefficients and different cooling coefficients. Among them, the corresponding relationship between the different friction powers corresponding to the second clutch 2 and the different coolant flow rates, different heating coefficients and different cooling coefficients can be obtained by designing a second clutch temperature measurement test bench according to different working conditions, taking the second data as input, taking the mathematical model of the coolant temperature corresponding to the second clutch 2 and the mathematical model of the friction plate temperature corresponding to the second clutch 2 as the temperature calculation model, and taking the friction plate temperature of the second clutch 2 under each working condition as the target, and solving the heating coefficient and cooling coefficient of the second clutch 2 through iterative optimization.

[0107] Specifically, in the second clutch temperature measurement test bench, the friction power coordinate axis parameters can generally be set to 0.5, 1, 1.5, 2, 2.5, 3, 3.5, in kw; the cooling flow coordinate axis parameters can generally be set to 0.5, 1, 3, 5, 7, 10, in L / min. The mathematical model of the coolant temperature corresponding to the second clutch 2 is: In formula 3, T O2nrepresents the coolant temperature of the second clutch at the current moment, T O2n-1 represents the coolant temperature of the second clutch at the last moment, M2 represents the actual transmission torque of the second clutch, and n in Indicates the input shaft speed of the dual clutch, n out2 represents the output shaft speed of the second clutch, Q represents the coolant flow rate, T O1n-1 represents the coolant temperature corresponding to the last moment of the first clutch, x2 represents the second heating coefficient, y2 represents the second cooling coefficient, Δt represents the interval time, and the interval time is the interval time between the current moment and the last moment. The mathematical model of the friction plate temperature corresponding to the second clutch 2 is In formula 4, T C2n Indicates the friction plate temperature of the second clutch at the current moment, T O2n-1 Indicates the coolant temperature of the second clutch at the last moment, T C2n-1 represents the friction plate temperature of the second clutch at the last moment, M2 represents the actual transmission torque of the second clutch, n in Indicates the input shaft speed of the dual clutch, n out2 represents the output shaft speed of the second clutch, Q represents the coolant flow rate, T O1n-1 represents the coolant temperature corresponding to the last moment of the first clutch, x2 represents the second heating coefficient, y2 represents the second cooling coefficient, Δt represents the interval time, and the interval time is the interval time between the current moment and the last moment. By taking the friction plate temperature of the first clutch 1 under various working conditions as the target, the heating coefficient and cooling coefficient of the second clutch 2 can be solved by iteratively optimizing the temperature calculation model. According to the above formula 3, it is known that the coolant temperature of the first clutch 1 must be calculated by the above formula 1, so that the coolant temperature of the second clutch 2 can be further calculated according to the coolant temperature of the first clutch 1 and the above formula 3. According to the above formula 4, it is known that the coolant temperature of the first clutch 1 must be calculated according to the above formula 1, and the coolant temperature of the second clutch 2 must be calculated according to the above formula 3, so that the friction plate temperature of the second clutch 2 can be further calculated according to the coolant temperature of the first clutch 1, the coolant temperature of the second clutch 2 and the above formula 4.

[0108] Reference Figure 8 , Figure 8 A flow chart of steps for determining the second heating coefficient and the second cooling coefficient corresponding to the second clutch at the second friction power and coolant flow rate is shown based on the correspondence between different friction powers corresponding to the second clutch and different coolant flow rates, different heating coefficients and different cooling coefficients, including but not limited to steps S810 to S820.

[0109] Step S810, determining a second heating coefficient corresponding to the second clutch under a second friction power and a coolant flow rate according to a third corresponding relationship between different friction powers corresponding to the second clutch and different coolant flow rates and different heating coefficients.

[0110] Step S820, determining a second cooling coefficient corresponding to the second clutch under a second friction power and a second coolant flow rate according to a fourth corresponding relationship between different friction powers corresponding to the second clutch and different coolant flow rates and different cooling coefficients.

[0111] In the embodiment of the present application, refer to Table 3 and Table 4, wherein Table 3 is a table of correspondence between different friction powers corresponding to the second clutch 2 and different coolant flows and different heating coefficients. Table 4 is a table of correspondence between different friction powers corresponding to the second clutch 2 and different coolant flows and different cooling coefficients. Through the three-dimensional parameter table shown in Table 3 and the second friction power and coolant flow corresponding to the second clutch 2 under the current operating condition, the second heating coefficient x2 corresponding to the second clutch 2 under the current operating condition can be determined. For example, if the second friction power corresponding to the second clutch 2 under the current operating condition is 2kw and the corresponding coolant flow is 3L / min, it can be determined that the second heating coefficient x2 corresponding to the second clutch 2 under the current operating condition is 1019J / ℃. Similarly, through the three-dimensional parameter table shown in Table 4 and the second friction power and coolant flow corresponding to the second clutch 2 under the current operating condition, the second cooling coefficient y2 corresponding to the second clutch 2 under the current operating condition can be determined. For example, if the second friction power corresponding to the second clutch 2 under the current operating condition is 2 kW and the corresponding coolant flow rate is 3 L / min, it can be determined that the second cooling coefficient y2 corresponding to the second clutch 2 under the current operating condition is 871 S*L / min.

[0112] Table 3 Corresponding relationship between different friction powers corresponding to the second clutch 2 and different coolant flow rates and different heating coefficients

[0113]

[0114]

[0115] Table 4 Corresponding relationship between different friction powers corresponding to the second clutch 2 and different coolant flow rates and different cooling coefficients

[0116]

[0117] Step S640, calculates the coolant temperature corresponding to the second clutch at the current moment based on the second data, the second heating coefficient, the second cooling coefficient, the coolant temperature corresponding to the second clutch at the previous moment, the coolant temperature corresponding to the first clutch at the previous moment and the interval duration, wherein the interval duration is the interval duration between the current moment and the previous moment.

[0118] In the embodiment of the present application, the heat source of the coolant of the second clutch 2 is the friction work of the second clutch 2, and the main cooling factors are the cooling flow rate and the temperature difference between the coolant of the second clutch 2 and the coolant of the first clutch 1. Therefore, after the second friction power and coolant flow rate corresponding to the second clutch 1 under the current operating conditions according to the above three-dimensional parameter tables 3 and 4, the coolant temperature corresponding to the second clutch at the last moment, the coolant temperature corresponding to the first clutch at the last moment and the interval length can be further calculated to obtain the coolant temperature corresponding to the second clutch at the current moment. Specifically, according to the second data, the second heating coefficient, the second cooling coefficient, the coolant temperature corresponding to the second clutch at the last moment, the coolant temperature corresponding to the first clutch at the last moment and the interval length, the coolant temperature corresponding to the second clutch at the current moment can be calculated using the above formula 3. That is, the coolant temperature of the second clutch 2 can be calculated according to the coolant temperature of the first clutch 1.

[0119] Step S650, calculates the friction plate temperature corresponding to the second clutch at the current moment based on the second data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and coolant temperature corresponding to the previous moment of the second clutch, the coolant temperature corresponding to the previous moment of the first clutch and the interval duration, and the friction plate temperature corresponding to the second clutch at the current moment is greater than or equal to the coolant temperature corresponding to the second clutch at the current moment.

[0120] In the embodiment of the present application, the heat source of the friction plate of the second clutch 2 is the friction work of the second clutch 2, and the main factors of cooling are the cooling flow rate and the temperature difference between the friction plate of the second clutch 2 and the coolant of the first clutch 1. Therefore, after the second friction power and coolant flow rate corresponding to the second clutch 2 under the current operating conditions according to the above three-dimensional parameter tables 3 and 4, the friction plate temperature and coolant temperature corresponding to the last moment of the second clutch, the coolant temperature and interval time corresponding to the last moment of the first clutch can be further calculated to obtain the friction plate temperature corresponding to the current moment of the second clutch. Specifically, according to the second data, the second heating coefficient, the second cooling coefficient, the friction plate temperature and coolant temperature corresponding to the last moment of the second clutch, the coolant temperature and interval time corresponding to the last moment of the first clutch, the friction plate temperature corresponding to the current moment of the second clutch can be calculated using the above formula 3. That is, the friction plate temperature of the second clutch 2 can be calculated according to the coolant temperature of the first clutch 1 and the coolant temperature of the second clutch 2. Since the friction plate of the second clutch 2 is the heat source and the coolant is the heat dissipation unit, the temperature of the friction plate of the second clutch 2 is not less than the temperature of the coolant of the second clutch 2, that is, T C2n ≥T O2n .

[0121] In the embodiment of the present application, after the coolant temperature corresponding to the last moment of the first clutch is calculated, the second friction power corresponding to the second clutch under the current operating condition is calculated based on the input shaft speed of the dual clutch, the output shaft speed of the second clutch, and the actual transmission torque of the second clutch. Then, according to the corresponding relationship between different friction powers corresponding to the second clutch and different coolant flows, different heating coefficients, and different cooling coefficients, the second friction power corresponding to the second clutch under the current operating condition, the second heating coefficient and the second cooling coefficient corresponding to the coolant flow rate can be determined. Thus, the coolant temperature corresponding to the second clutch at the current moment can be further calculated based on the second data (including the input shaft speed of the dual clutch, the output shaft speed of the second clutch, the actual transmission torque of the second clutch, and the coolant flow rate), the second heating coefficient, the second cooling coefficient, the coolant temperature corresponding to the last moment of the second clutch, the coolant temperature corresponding to the last moment of the first clutch, and the interval time. After calculating the coolant temperature corresponding to the second clutch at the current moment, the friction plate temperature corresponding to the second clutch at the current moment can be further calculated based on the second data, the second heating coefficient, the second cooling coefficient, the friction plate temperature and coolant temperature corresponding to the previous moment of the second clutch, and the coolant temperature and interval length corresponding to the previous moment of the first clutch. The heat exchange relationship between the friction plate of the second clutch 2 and the coolant after passing through the first clutch 1 is taken into account, which can better meet the structural characteristics of the wet dual clutch cooling system, making the calculation of the friction plate temperature of the second clutch 2 more accurate, and being able to obtain the temperature rise change of the friction plate of the second clutch 2 in the actual working process in real time.

[0122] Based on the same inventive concept, an embodiment of the present application also provides a computer program product, which includes computer instructions, which are stored in a computer-readable storage medium and are suitable for being read and executed by a processor, so that a computer device with the processor executes a method provided in any of the above embodiments.

[0123] See also Fig. 9 , Fig. 9 The hardware structure of the computer program product of the embodiment of the present application is illustrated, and the computer program product includes:

[0124] The processor 901 may be implemented by a general-purpose CPU (Central Processing Unit), a microprocessor, an application-specific integrated circuit (ASIC), or one or more integrated circuits, and is used to execute relevant programs to implement the technical solutions provided in the embodiments of the present application;

[0125] The memory 902 can be implemented in the form of a read-only memory (ROM), a static storage device, a dynamic storage device, or a random access memory (RAM). The memory 902 can store an operating system and other application programs. When the technical solution provided in the embodiment of this specification is implemented by software or firmware, the relevant program code is stored in the memory 902, and the processor 901 calls and executes the method for determining the temperature of the wet dual clutch described in the embodiment of this application;

[0126] Input / output interface 903, used to implement information input and output;

[0127] Communication interface 904, used to realize communication interaction between the device and other devices, which can be realized by wired mode (such as USB, network cable, etc.) or wireless mode (such as mobile network, WIFI, Bluetooth, etc.);

[0128] A bus 905 that transmits information between various components of the device (e.g., the processor 901, the memory 902, the input / output interface 903, and the communication interface 904);

[0129] The processor 901 , the memory 902 , the input / output interface 903 and the communication interface 904 are connected to each other in communication within the device via a bus 905 .

[0130] The functions described herein may be implemented in hardware, software executed by a processor, firmware, or any combination thereof. If implemented in software executed by a processor, the functions may be stored as one or more instructions or codes on a computer-readable medium or transmitted via a computer-readable medium. Other examples and implementations are within the scope and spirit of the present application and the appended claims. For example, due to the nature of software, the functions described above may be implemented using software executed by a processor, hardware, firmware, hard wiring, or a combination of any of these. In addition, each functional unit may be integrated into a processing unit, each unit may exist physically separately, or two or more units may be integrated into one unit.

[0131] In the several embodiments provided in this application, it should be understood that the disclosed technical content can be implemented in other ways. Among them, the device embodiments described above are only schematic. For example, the division of the units can be a logical function division. There may be other division methods in actual implementation. For example, multiple units or components can be combined or integrated into another system, or some features can be ignored or not executed. Another point is that the mutual coupling or direct coupling or communication connection shown or discussed can be through some interfaces, indirect coupling or communication connection of units or modules, which can be electrical or other forms.

[0132] The units described as separate components may or may not be physically separated, and the components of the control device may or may not be physical units, that is, they may be located in one place or distributed in multiple units. Some or all of the units may be selected according to actual needs to achieve the purpose of the present embodiment.

[0133] If the integrated unit is implemented in the form of a software functional unit and sold or used as an independent product, it can be stored in a computer-readable storage medium. Based on this understanding, the technical solution of the present application can be essentially or partly or all or partly embodied in the form of a software product that contributes to the prior art. The computer software product is stored in a storage medium, including several instructions for a computer device (which can be a personal computer, a server or a network device, etc.) to perform all or part of the steps of the method described in each embodiment of the present application. The aforementioned storage medium includes: U disk, read-only memory (ROM, Read-Only Memory), random access memory (RAM, Random Access Memory), mobile hard disk, disk or optical disk, etc., which can store computer program instructions.

[0134] The above description is only an embodiment of the present application and is not intended to limit the present application. For those skilled in the art, the present application may have various modifications and variations. Any modification, equivalent substitution, improvement, etc. made within the spirit and principle of the present application shall be included in the scope of the claims of the present application.

Claims

1. A method for determining the temperature of a wet dual clutch, characterized in that: The wet dual clutch includes a first clutch, and the method includes: Collecting first data, wherein the first data includes an input shaft speed of the dual clutch, an output shaft speed of the first clutch, an actual transmission torque of the first clutch, a coolant flow rate, and an oil tank oil temperature; Calculating a first friction power corresponding to the first clutch according to the input shaft speed of the dual clutch, the output shaft speed of the first clutch and the actual transmission torque of the first clutch; Determining a first heating coefficient and a first cooling coefficient corresponding to the first clutch under the first friction power and the coolant flow rate according to a correspondence between different friction powers corresponding to the first clutch and different coolant flow rates, different heating coefficients, and different cooling coefficients; The coolant temperature corresponding to the current moment of the first clutch is calculated based on the first data, the first heating coefficient, the first cooling coefficient, the coolant temperature corresponding to the previous moment of the first clutch, and the interval time, wherein the interval time is the interval time between the current moment and the previous moment; The friction plate temperature corresponding to the first clutch at the current moment is calculated based on the first data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and the coolant temperature corresponding to the first clutch at the previous moment, and the interval duration. The friction plate temperature corresponding to the first clutch at the current moment is greater than or equal to the coolant temperature corresponding to the first clutch at the current moment.

2. The method according to claim 1, characterized in that The first friction power corresponding to the first clutch is calculated according to the input shaft speed of the dual clutch, the output shaft speed of the first clutch and the actual transmission torque of the first clutch, and comprises: calculating an absolute value of a speed difference between a speed of an input shaft of the dual clutch and a speed of an output shaft of the first clutch; The product of the absolute value of the rotational speed difference and the actual transmission torque of the first clutch is calculated to obtain a first friction power corresponding to the first clutch.

3. The method according to claim 1, characterized in that The determining, according to the correspondence between different friction powers corresponding to the first clutch and different coolant flows, different heating coefficients, and different cooling coefficients, a first heating coefficient and a first cooling coefficient corresponding to the first clutch under the first friction power and the coolant flow rate comprises: Determining a first heating coefficient corresponding to the first clutch under the first friction power and the coolant flow rate according to a first corresponding relationship between different friction powers corresponding to the first clutch and different coolant flow rates and different heating coefficients; According to a second corresponding relationship between different friction powers corresponding to the first clutch and different coolant flow rates and different cooling coefficients, a first cooling coefficient corresponding to the first clutch under the first friction power and the coolant flow rate is determined.

4. The method according to claim 1, characterized in that: The calculation of the coolant temperature corresponding to the first clutch at the current moment according to the first data, the first heating coefficient, the first cooling coefficient, the coolant temperature corresponding to the first clutch at the previous moment and the interval duration is performed by the following formula: Where, T O1n represents the coolant temperature of the first clutch at the current moment, T O1n-1 represents the coolant temperature of the first clutch at the last moment, M1 represents the actual transmission torque of the first clutch, n in represents the input shaft speed of the dual clutch, n out1 represents the output shaft speed of the first clutch, Q represents the coolant flow rate, T s represents the oil temperature of the oil tank, x1 represents the first heating coefficient, y1 represents the first cooling coefficient, and Δt represents the interval duration.

5. The method according to claim 1, characterized in that The calculation of the friction plate temperature corresponding to the current moment of the first clutch according to the first data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and the coolant temperature corresponding to the previous moment of the first clutch, and the interval duration is performed by the following formula: Where, T C1|n represents the friction plate temperature of the first clutch at the current moment, T O1|n-1 represents the coolant temperature of the first clutch at the last moment, T C1|n-1 represents the friction plate temperature of the first clutch at the last moment, M1 represents the actual transmission torque of the first clutch, n in represents the input shaft speed of the dual clutch, n out1 represents the output shaft speed of the first clutch, Q represents the coolant flow rate, T s represents the oil temperature of the oil tank, x1 represents the first heating coefficient, y1 represents the first cooling coefficient, and Δt represents the interval duration.

6. The method according to claim 1, characterized in that The wet dual clutch further includes a second clutch, and the method further includes: collecting second data, wherein the second data includes a speed of an input shaft of the dual clutch, a speed of an output shaft of the second clutch, an actual transmission torque of the second clutch, and a coolant flow rate; Calculating a second friction power corresponding to the second clutch according to the input shaft speed of the dual clutch, the output shaft speed of the second clutch and the actual transmission torque of the second clutch; Determining a second heating coefficient and a second cooling coefficient corresponding to the second clutch under the second friction power and the coolant flow rate according to a correspondence between different friction powers corresponding to the second clutch and different coolant flow rates, different heating coefficients, and different cooling coefficients; The coolant temperature corresponding to the second clutch at the current moment is calculated according to the second data, the second heating coefficient, the second cooling coefficient, the coolant temperature corresponding to the previous moment of the second clutch, the coolant temperature corresponding to the previous moment of the first clutch, and the interval time, wherein the interval time is the interval time between the current moment and the previous moment; The friction plate temperature corresponding to the second clutch at a current moment is calculated based on the second data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and the coolant temperature corresponding to the previous moment of the second clutch, the coolant temperature corresponding to the previous moment of the first clutch and the interval duration. The friction plate temperature corresponding to the second clutch at a current moment is greater than or equal to the coolant temperature corresponding to the second clutch at a current moment.

7. The method according to claim 6, characterized in that The determining, according to the correspondence between different friction powers corresponding to the second clutch and different coolant flows, different heating coefficients, and different cooling coefficients, the second heating coefficient and the second cooling coefficient corresponding to the second clutch under the second friction power and the coolant flow rate comprises: determining a second heating coefficient corresponding to the second clutch under the second friction power and the coolant flow rate according to a third corresponding relationship between different friction powers corresponding to the second clutch and different coolant flow rates and different heating coefficients; According to a fourth corresponding relationship between different friction powers corresponding to the second clutch and different coolant flow rates and different cooling coefficients, a second cooling coefficient corresponding to the second clutch under the second friction power and the coolant flow rate is determined.

8. The method according to claim 6, characterized in that The coolant temperature corresponding to the second clutch at the current moment is calculated based on the second data, the second heating coefficient, the second cooling coefficient, the coolant temperature corresponding to the second clutch at the previous moment, the coolant temperature corresponding to the first clutch at the previous moment, and the interval duration by the following formula: Where, T O2|n represents the coolant temperature of the second clutch at the current moment, T O2|n-1 represents the coolant temperature of the second clutch at the last moment, M2 represents the actual transmission torque of the second clutch, and n in represents the input shaft speed of the dual clutch, n out2 represents the output shaft speed of the second clutch, Q represents the coolant flow rate, T O1n-1 represents the coolant temperature of the first clutch corresponding to the last moment, x2 represents the second heating coefficient, y2 represents the second cooling coefficient, and Δt represents the interval duration.

9. The method according to claim 6, characterized in that The friction plate temperature corresponding to the second clutch at the current moment is calculated based on the second data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and the coolant temperature corresponding to the last moment of the second clutch, the coolant temperature corresponding to the last moment of the first clutch, and the interval duration by the following formula: Where, T C2|n represents the friction plate temperature of the second clutch at the current moment, T O2|n-1 represents the coolant temperature of the second clutch at the last moment, T C2|n-1 represents the friction plate temperature of the second clutch at the last moment, M2 represents the actual transmission torque of the second clutch, and n in represents the input shaft speed of the dual clutch, n out2 represents the output shaft speed of the second clutch, Q represents the coolant flow rate, T O1|n-1 represents the coolant temperature of the first clutch corresponding to the last moment, x2 represents the second heating coefficient, y2 represents the second cooling coefficient, and Δt represents the interval duration.

10. A computer program product, characterized in that The computer program product includes computer instructions, which are stored in a computer-readable storage medium and are suitable for being read and executed by a processor, so that a computer device having the processor performs the method according to any one of claims 1 to 9.

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