Method and program product for determining temperature of a wet dual clutch

Abstract

The application discloses a kind of wet dual clutch temperature determination method and program product, according to the corresponding relationship between different friction power corresponding to first clutch and different cooling liquid flow, different heating coefficient and different cooling coefficient, the first friction power corresponding to first clutch under the current operating condition corresponding first cooling liquid flow, corresponding first heating coefficient and first cooling coefficient can be determined.Thereby, the cooling liquid temperature corresponding to first clutch at current time can be calculated further according to first data, first heating coefficient, first cooling coefficient, the cooling liquid temperature corresponding to first clutch at last time and interval duration.Again according to first data, first heating coefficient, first cooling coefficient, the friction plate temperature and cooling liquid temperature corresponding to first clutch at last time and interval duration, the friction plate temperature corresponding to first clutch at current time is calculated.The temperature rise change of the friction plate of first clutch in actual working process can be obtained in real time.

Description

TECHNICAL FIELD

[0001] The application belongs to the technical field of vehicle clutches, and particularly relates to a wet double clutch temperature determination method and program product. BACKGROUND

[0002] Since a DCT (Dual Clutch Transmission) automatic transmission has the advantages of good acceleration continuity, low fuel consumption, smooth gear shifting, high transmission efficiency, etc., it is widely used in passenger cars, and a wet double clutch, as a core component of the DCT automatic transmission, generates a large amount of friction heat in the relative sliding between the mating steel sheets and the friction plates during engagement. Part of the generated heat is taken away by the cooling oil, and part of the generated heat enters the clutch body, causing the temperature of each element of the clutch to rise, among which the temperature of the friction plates rises most obviously. If the heat dissipation capacity of the clutch cooling system is insufficient, the heat cannot be taken away in time, which causes the temperature of the friction plates to rise, resulting in ablation and other faults of the friction plates, and causing the clutch to fail.

[0003] Due to the structural characteristics of the clutch, it is difficult to arrange temperature sensors on the friction plates and the mating steel sheets during the operation of the automobile, and therefore the temperature of the wet double clutch friction plates cannot be monitored by the sensor.

[0004] Patent document 201911226122.1 discloses a control method and device based on the surface temperature of a wet double clutch, which indirectly calculates the temperature of the clutch friction plates and the mating steel sheets by using the outlet cooling oil temperature of the clutch, needs to install an outlet cooling oil temperature sensor, has high cost, and causes cumulative errors through multiple conversions. Patent document 201410217118.X discloses a DCT wet double clutch temperature measurement method based on neural network prediction, establishes a clutch temperature prediction model based on a neural network, mainly solves the problem that the wet double clutch outlet oil temperature collected by the oil temperature sensor in the prior art has a delay, and predicts the temperature of the clutch by the outlet oil temperature, but a large number of tests are needed to obtain the outlet oil temperature samples in the model training process, which has high test cost and takes a long time. SUMMARY

[0005] The embodiments of the application provide a wet double clutch temperature determination method and program product, which can at least accurately determine the temperature of the friction plates of the first clutch in the wet double clutch, that is, can obtain the temperature rise change of the friction plates of the first clutch in the actual working process in real time.

[0006] Other characteristics and advantages of the application will become apparent from the following detailed description, or will be learned by practice of the application.

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

[0008] collecting first data, the first data comprising the input shaft speed of the dual clutch, the output shaft speed of the first clutch, the actual transmitted torque of the first clutch, the coolant flow and the oil tank temperature;

[0009] 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 transmitted torque of the first clutch;

[0010] determining the first heating coefficient and the first cooling coefficient corresponding to the first clutch under the first friction power and the coolant flow according to the corresponding relationship between the different friction powers corresponding to the first clutch and the different coolant flows, the different heating coefficients and the different cooling coefficients;

[0011] calculating the coolant temperature corresponding to the first clutch at the current time according to the first data, the first heating coefficient, the first cooling coefficient, the coolant temperature corresponding to the first clutch at the previous time and the interval duration, wherein the interval duration is the interval duration between the current time and the previous time;

[0012] calculating the friction plate temperature corresponding to the first clutch at the current time 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 time and the interval duration, the friction plate temperature corresponding to the first clutch at the current time being greater than or equal to the coolant temperature corresponding to the first clutch at the current time.

[0013] In some embodiments of the present application, based on the foregoing scheme, the calculation of 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 transmitted torque of the first clutch comprises:

[0014] 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;

[0015] calculating the product of the absolute value of the speed difference and the actual transmitted torque of the first clutch to obtain the first friction power corresponding to the first clutch.

[0016] In some embodiments of the present application, based on the foregoing scheme, the determination of the first heating coefficient and the first cooling coefficient of the first clutch corresponding to the first friction power and the cooling liquid flow rate comprises:

[0017] determining the first heating coefficient of the first clutch corresponding to the first friction power and the cooling liquid flow rate according to the first correspondence relationship between different friction powers and different cooling liquid flow rates and different heating coefficients corresponding to the first clutch;

[0018] determining the first cooling coefficient of the first clutch corresponding to the first friction power and the cooling liquid flow rate according to the second correspondence relationship between different friction powers and different cooling liquid flow rates and different cooling coefficients corresponding to the first clutch.

[0019] In some embodiments of the present application, based on the foregoing scheme, the calculation of the cooling liquid temperature corresponding to the first clutch at the current time according to the first data, the first heating coefficient, the first cooling coefficient, the cooling liquid temperature corresponding to the first clutch at the previous time and the interval time length is performed by the following formula:

[0020]

[0021] In the formula, T O1n represents the cooling liquid temperature corresponding to the first clutch at the current time, T O1n-1 represents the cooling liquid temperature corresponding to the first clutch at the previous time, M1 represents the actual transmission torque of the first clutch, n in represents the input shaft speed of the double clutch, n out1 represents the output shaft speed of the first clutch, Q represents the cooling liquid flow rate, T s represents the oil tank temperature, x1 represents the first heating coefficient, y1 represents the first cooling coefficient, and Δt represents the interval time length.

[0022] In some embodiments of the present application, based on the foregoing scheme, the calculation of the friction plate temperature corresponding to the first clutch at the current time according to the first data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and the cooling liquid temperature corresponding to the first clutch at the previous time and the interval time length is performed by the following formula:

[0023]

[0024] In the formula, T C1n represents the friction plate temperature corresponding to the first clutch at the current time, TO1n-1 represents the cooling liquid temperature corresponding to the previous moment of the first clutch, T C1n-1 represents the friction plate temperature corresponding to the previous moment of the first clutch, M1 represents the actual transmission torque of the first clutch, n in represents the input shaft speed of the double clutch, n out1 represents the output shaft speed of the first clutch, Q represents the cooling liquid flow, T s represents the oil tank oil temperature, 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 foregoing scheme, the wet double clutch further comprises a second clutch, and the method further comprises:

[0026] collecting second data, the second data comprising the input shaft speed of the double clutch, the output shaft speed of the second clutch, the actual transmission torque of the second clutch, and the cooling liquid flow;

[0027] According to the input shaft speed of the double clutch, the output shaft speed of the second clutch, and the actual transmission torque of the second clutch, the second friction power corresponding to the second clutch is calculated.

[0028] According to the corresponding relationship between different friction powers and different cooling liquid flows, different heating coefficients, and different cooling coefficients corresponding to the second clutch, the second heating coefficient and the second cooling coefficient corresponding to the second clutch under the second friction power and the cooling liquid flow are determined.

[0029] According to the second data, the second heating coefficient, the second cooling coefficient, the cooling liquid temperature corresponding to the previous moment of the second clutch, the cooling liquid temperature corresponding to the previous moment of the first clutch, and the interval duration, the cooling liquid temperature corresponding to the current moment of the second clutch is calculated, wherein the interval duration is the interval duration between the current moment and the previous moment.

[0030] According to the second data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and the cooling liquid temperature corresponding to the previous moment of the second 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 second clutch is calculated, which is greater than or equal to the cooling liquid temperature corresponding to the current moment of the second clutch.

[0031] In some embodiments of the present application, based on the aforementioned solution, 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 correspondence between different friction powers corresponding to the second clutch and 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 correspondence between different friction powers corresponding to the second clutch, different coolant flow rates, and different heating coefficients;

[0033] According to a fourth correspondence between different friction powers corresponding to the second clutch, 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 aforementioned solution, 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 previous moment of the second clutch, the coolant temperature corresponding to the previous moment of the first clutch, and the interval duration, 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 previous 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 at 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 calculation of 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 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 at 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, 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 executes the method described in the first aspect of the embodiment of the present application.

[0041] Based on the technical solution proposed in this application, the first friction power corresponding to the first clutch under the current operating condition can be calculated based on the dual clutch input shaft speed, the first clutch output shaft speed, and the actual transmitted torque of the first clutch. Furthermore, based on the corresponding relationships between different friction powers corresponding to the first clutch and different coolant flow rates, different heating coefficients, and different cooling coefficients, the first friction power, first heating coefficient, and first cooling coefficient corresponding to the coolant flow rate of the first clutch under the current operating condition can be determined. Thus, the coolant temperature corresponding to the first clutch at the current moment can be calculated based on first data (including the dual clutch input shaft speed, the first clutch output shaft speed, the actual transmitted torque of the first clutch, the coolant flow rate, and the oil tank temperature), the first heating coefficient, the first cooling coefficient, the coolant temperature corresponding to the previous moment of the first clutch, and the interval duration. 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 based on 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 duration. 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 changes of the friction plate of the first clutch during actual operation in real time.

[0042] It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the application, as claimed. BRIEF DESCRIPTION OF DRAWINGS

[0043] The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the application and serve to explain the principles of the application. It is readily apparent to one skilled in the art that the following figures are merely some embodiments of the present application, and other figures can be obtained from these figures without creative efforts, for those skilled in the art. In the drawings:

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

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

[0046] Figure 3 shows a flow chart of a method for determining a temperature of a wet dual clutch according to an embodiment of the application;

[0047] Figure 4 shows a flow chart of a step of calculating a first friction power corresponding to a first clutch according to an input shaft speed of the dual clutch, an output shaft speed of the first clutch and an actual transmission torque of the first clutch;

[0048] Figure 5 shows a flow chart of a step of determining a first heating coefficient and a first cooling coefficient corresponding to the first clutch at the first friction power and a cooling fluid flow rate according to a corresponding relationship between different friction powers corresponding to the first clutch and different cooling fluid flow rates, different heating coefficients and different cooling coefficients;

[0049] Figure 6 shows another flow chart of a method for determining a temperature of a wet dual clutch according to an embodiment of the application;

[0050] Figure 7 shows a flow chart of a step of calculating a second friction power corresponding to a second clutch according to an input shaft speed of the dual clutch, an output shaft speed of the second clutch and an actual transmission torque of the second clutch;

[0051] Figure 8 shows a flow chart of a step of determining a second heating coefficient and a second cooling coefficient corresponding to the second clutch at the second friction power and a cooling fluid flow rate according to a corresponding relationship between different friction powers corresponding to the second clutch and different cooling fluid flow rates, different heating coefficients and different cooling coefficients;

[0052] Figure 9 shows a structural schematic diagram of a computer program product according to an embodiment of the application.

[0053] Reference signs:

[0054] First clutch 1, second clutch 2, return spring 3, cooling oil cavity 4, input shaft of dual clutch 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 passage 250, one-way valve 260, oil cooler 270;

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

[0057] The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments of the present application. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative work belong to the scope of protection of the present application.

[0058] In addition, the described features, structures or characteristics can be combined in any suitable manner in one or more embodiments. In the following description, many specific details are provided to give a full understanding of the embodiments of the present application. However, those skilled in the art will realize that the technical solutions of the present application can be practiced without one or more of the specific details, or other methods, components, devices, steps, etc. can be used. In other cases, well-known methods, devices, implementations or operations are not shown or described in detail to avoid obscuring the aspects of the present application.

[0059] The block diagram shown in the drawings is only a functional entity, which does not necessarily correspond to a physically independent entity. That is, the functional entities can be implemented in the form of software, or in one or more hardware modules or integrated circuits, or in different networks and / or processor devices and / or microcontroller devices.

[0060] The flowchart shown in the drawings is only an exemplary description, which does not necessarily include all the contents and operations / steps, and does not necessarily be executed in the described order. For example, some operations / steps can be further decomposed, and some operations / steps can be combined or partially combined, so that the actual execution order may be changed according to the actual situation.

[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 to indicate or imply relative importance or implicitly specify the number of the technical features indicated. Therefore, a feature specified as "first" or "second" may explicitly or implicitly include one or more of the features. 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] When a vehicle equipped with a dual-clutch is driving, especially on special roads and under harsh driving conditions, frequent starting or 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 This 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. These two clutches are mounted on the same drum and share the same structural principle as an internal gear transmission mechanism. The first and second clutches 1 and 2 consist of a steel diaphragm, a friction plate, an inner diaphragm, and an outer diaphragm. The outer diaphragm and the steel diaphragm are connected by hydraulic fluid, while the friction plate is also connected to the inner diaphragm by hydraulic fluid. The outer diaphragms of both clutches are welded to the clutch drive disc, while the inner diaphragms are connected to the transmission input shaft, transmitting power to the transmission input shaft. The wet dual clutch also includes a return spring 3, a coolant oil chamber 4, a dual clutch input shaft 5, a first clutch output shaft 6, and a second clutch output shaft 7.

[0065] Compared to a dry clutch, a wet dual clutch rapidly cools the friction plates of the first clutch through heat exchange between the coolant in coolant chamber 4 and the friction plates of the first clutch. The wet dual clutch rotates at high speeds during vehicle operation, making it difficult to arrange and install temperature sensors. Therefore, it is necessary to develop a relatively accurate temperature determination method to obtain real-time temperature rise changes of the wet dual clutch during actual operation.

[0066] Traditional clutch temperature calculation methods are generally based on thermal theory principles, inputting parameters such as specific heat capacity, introduction coefficient, and clutch mass into a theoretical formula to calculate the clutch temperature. However, due to the accuracy of the parameters and the changes in the clutch thermal field during actual driving conditions, there is a large difference between the theoretical calculation and the clutch temperature under actual conditions.

[0067] In addition, in the prior art, a method of calculating clutch temperature by clutch thermal model through finite element or neural network is also used, however, on the one hand, the influence relationship between the first clutch and the second clutch is not considered, and on the other hand, the thermal model calculation is too complex to meet the real-time requirement and cannot be downloaded to the real vehicle controller for use.

[0068] Based on this, the embodiment of the present application provides a wet double clutch temperature determination method, which can accurately determine the friction plate temperature of the first clutch and can obtain the temperature rise change of the friction plate of the first clutch in the actual working process in real time.

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

[0070] Reference Figure 3 , a flow chart of the wet double clutch temperature determination method in the embodiment of the present application is shown, 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 double clutch, the output shaft speed of the first clutch, the actual transmission torque of the first clutch, the cooling liquid flow 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, the first data related to the first clutch 1 needs to be collected, the first data including the input shaft speed of the double clutch, the output shaft speed of the first clutch, the actual transmission torque of the first clutch, the cooling liquid flow and the oil tank oil temperature.

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

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

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

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

[0077] Step S420, calculate the product of the absolute value of the speed difference and the first clutch actual transmission torque to obtain the first friction power corresponding to the first clutch.

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

[0079] Step S330, according to the corresponding relationship between different friction powers and different cooling liquid flows, different heating coefficients and different cooling coefficients corresponding to the first clutch, determine the first heating coefficient and the first cooling coefficient corresponding to the first clutch under the first friction power and the cooling liquid flow.

[0080] In the embodiments of the present application, after the first friction power corresponding to the first clutch 1 is calculated according to the input shaft speed of the double 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, the cooling liquid flow rate, the first heating coefficient and the first cooling coefficient of the first clutch 1 in the current operating condition can be determined according to the corresponding relationship between the different friction powers corresponding to the first clutch 1 and the different cooling liquid flow rates, the different heating coefficients and the different cooling coefficients. The corresponding relationship between the different friction powers corresponding to the first clutch 1 and the different cooling liquid flow rates, the different heating coefficients and the different cooling coefficients can be obtained by designing different operating conditions in the first clutch temperature measurement test bench, taking the first data as the input, taking the mathematical model of the cooling liquid 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 in each operating condition as the target, and then 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 coordinate axis parameters can generally be set as 0.5, 1, 1.5, 2, 2.5, 3, 3.5, and the unit is kw. The cooling flow coordinate axis parameters can generally be set as 0.5, 1, 3, 5, 7, 10, and the unit is L / min. The mathematical model of the cooling liquid temperature corresponding to the first clutch 1 is: In formula 1, T O1n represents the cooling liquid temperature corresponding to the first clutch at the current moment, T O1n-1 represents the cooling liquid temperature corresponding to the first clutch at the previous moment, M1 represents the actual transmission torque of the first clutch, n in represents the input shaft speed of the double clutch, n out1 represents the output shaft speed of the first clutch, Q represents the cooling liquid flow rate, T s represents the oil tank oil temperature, x1 represents the first heating coefficient, y1 represents the first cooling coefficient, and Δt represents the interval length, which is the interval length 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 represents the friction plate temperature corresponding to the first clutch at the current moment, T O1n-1 represents the cooling liquid temperature corresponding to the first clutch at the previous moment, T C1n-1 represents the friction plate temperature corresponding to the first clutch at the previous moment, M1 represents the actual transmission torque of the first clutch, n in represents the input shaft speed of the double clutch, n out1 represents the output shaft speed of the first clutch, Q represents the cooling liquid flow rate, T sThe oil tank oil temperature is represented by x1, the first heating coefficient is represented by y1, and the interval duration is represented by Δt, which is the interval duration between the current time and the last time. By taking the friction plate temperature of the first clutch 1 under each working condition as the target, and by iteratively optimizing the temperature calculation model, the heating coefficient and the cooling coefficient of the first clutch 1 can be solved.

[0082] Referring to Figure 5 , Figure 5 A flowchart showing the steps of determining the first heating coefficient and the first cooling coefficient of the first clutch corresponding to the first friction power and the coolant flow rate is shown, including but not limited to steps S510 to S520.

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

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

[0085] In the embodiments of the present application, refer to Table 1 and Table 2, wherein Table 1 is a corresponding relationship table between different friction powers corresponding to the first clutch 1 and different coolant flow rates and different heating coefficients. Table 2 is a corresponding relationship table between different friction powers corresponding to the first clutch 1 and different coolant flow rates and different cooling coefficients. By the three-dimensional parameter table shown in Table 1 and the first friction power and the coolant flow rate 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 rate is 3L / min, then the first heating coefficient x1 corresponding to the first clutch 1 under the current operating condition can be determined as 1024J / ℃. Similarly, by the three-dimensional parameter table shown in Table 2 and the first friction power and the coolant flow rate 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 2kw, and the corresponding coolant flow rate is 3L / min, then the first cooling coefficient y1 corresponding to the first clutch 1 under the current operating condition can be determined as 874S*L / min.

[0086] Table 1 corresponding relationship table between different friction powers of the first clutch 1 and different cooling liquid flow rates and different heating coefficients

[0087]

[0088]

[0089] Table 2 corresponding relationship table between different friction powers of the first clutch 1 and different cooling liquid flow rates and different cooling coefficients

[0090]

[0091] In step S340, the cooling liquid temperature corresponding to the first clutch at the current time is calculated according to the first data, the first heating coefficient, the first cooling coefficient, the cooling liquid temperature corresponding to the first clutch at the last time, and the interval duration.

[0092] In the embodiment, the cooling liquid heat source corresponding to the first clutch 1 is the friction power of the first clutch 1, and the main factors for cooling are the cooling flow rate and the temperature difference between the cooling liquid temperature corresponding to the first clutch 1 and the cooling liquid in the oil tank 210. Therefore, after the first friction power and the cooling liquid flow rate corresponding to the first clutch 1 under the current operating condition are obtained according to the three-dimensional parameter tables 1 and 2, the cooling liquid temperature corresponding to the first clutch at the current time can be further calculated according to the first data, the first heating coefficient, the first cooling coefficient, the cooling liquid temperature corresponding to the first clutch at the last time, and the interval duration. Specifically, the cooling liquid temperature corresponding to the first clutch at the current time can be calculated by using the above formula 1 according to the first data, the first heating coefficient, the first cooling coefficient, the cooling liquid temperature corresponding to the first clutch at the last time, and the interval duration. That is, the oil tank oil temperature T s The cooling liquid temperature corresponding to the first clutch 1 is calculated.

[0093] In step S350, the friction plate temperature corresponding to the first clutch at the current time is calculated according to the first data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and the cooling liquid temperature corresponding to the first clutch at the last time, and the interval duration, and the friction plate temperature corresponding to the first clutch at the current time is greater than or equal to the cooling liquid temperature corresponding to the first clutch at the current time.

[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, the main factor of cooling is the cooling flow, and the temperature difference between the friction plate of the first clutch 1 and the cooling liquid in the oil tank 210. Therefore, after the first friction power corresponding to the first clutch 1 and the cooling liquid flow under the current operating condition are determined according to the three-dimensional parameter tables 1 and 2 and the first friction power corresponding to the first clutch 1, the first friction plate temperature corresponding to the first clutch 1 at the current time can be further calculated according to the first data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and the cooling liquid temperature corresponding to the first clutch at the previous time, and the interval time. Specifically, the friction plate temperature corresponding to the first clutch at the current time can be calculated by using the above formula 2 according to the first data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and the cooling liquid temperature corresponding to the first clutch at the previous time, and the interval time. That is, the friction plate temperature corresponding to the first clutch 1 at the current time can be calculated according to the oil temperature T s and the cooling liquid temperature corresponding to the first clutch 1. Since the friction plate of the first clutch 1 is the heat source and the cooling liquid is the heat dissipation unit, the friction plate temperature of the first clutch 1 is not less than the cooling liquid 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 according to the input shaft speed of the double clutch, the output shaft speed of the first clutch, and the actual transmission torque of the first clutch. Then, the first friction power corresponding to the first clutch under the current operating condition, the first heating coefficient corresponding to the first friction power and the cooling liquid flow, and the first cooling coefficient are determined according to the corresponding relationship between the different friction power corresponding to the first clutch and the different cooling liquid flow, the different heating coefficient, and the different cooling coefficient. Thus, the cooling liquid temperature corresponding to the first clutch at the current time can be further calculated according to the first data (including the input shaft speed of the double clutch, the output shaft speed of the first clutch, the actual transmission torque of the first clutch, the cooling liquid flow, and the oil temperature of the oil tank), the first heating coefficient, the first cooling coefficient, the cooling liquid temperature corresponding to the first clutch at the previous time, and the interval time. After the cooling liquid temperature corresponding to the first clutch at the current time is calculated, the friction plate temperature corresponding to the first clutch at the current time can be further calculated according to the first data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and the cooling liquid temperature corresponding to the first clutch at the previous time, and the interval time. The heat exchange relationship between the first clutch 1 and the cooling liquid in the oil tank 210 is considered, that is, the heat exchange relationship between the friction plate of the first clutch and the cooling liquid in the oil tank is considered, which is more in line with the structural characteristics of the wet-type double clutch cooling system, so that the calculation of the friction plate temperature of the first clutch 1 is more accurate, and the temperature rise of the friction plate of the first clutch 1 in the actual working process can be obtained in real time.

[0096] In the embodiments of the present application, the wet double clutch further comprises a second clutch 2, and the method for determining the temperature of the wet double clutch provided in the embodiments of the present application can not only accurately determine the temperature of the friction plate of the first clutch 1, but also accurately determine the temperature of the friction plate of the second clutch 2. Referring to Figure 6 , Figure 6 Another flowchart of the method for determining the temperature of the wet double clutch is shown, which can accurately determine the temperature of the friction plate of the second clutch 2, and includes but is not limited to steps S610 to S650.

[0097] In step S610, second data is collected, and the second data includes the input shaft speed of the double clutch, the output shaft speed of the second clutch, the actual transmission torque of the second clutch and the cooling liquid flow rate.

[0098] In the embodiments of the present application, in order to determine the temperature of the friction plate of the second clutch 2, second data related to the second clutch 2 needs to be collected, and the second data includes the input shaft speed of the double clutch, the output shaft speed of the second clutch, the actual transmission torque of the second clutch and the cooling liquid flow rate.

[0099] In step S620, the second friction power corresponding to the second clutch is calculated according to the input shaft speed of the double clutch, the output shaft speed of the second clutch and the actual transmission torque of the second clutch.

[0100] In the embodiments of the present application, as shown in the cooling system of the wet double clutch, Figure 2 It can be known from the cooling system of the wet double clutch shown in the embodiments of the present application that the cooling of the second clutch 2 is mainly realized based on the heat exchange of the cooling liquid between the first clutch 1 and the second clutch 2. The heat exchange of the cooling liquid in the second clutch 2 and the first clutch 1 is related to the heating coefficient and the cooling coefficient corresponding to the second clutch 2. The heating coefficient and the cooling coefficient of the second clutch 2 are related to the friction power and the cooling flow rate corresponding to the first clutch 2, and therefore, the second friction power corresponding to the second clutch 2 and the cooling flow rate under the current operating condition need to be calculated first. Specifically, the second friction power corresponding to the second clutch can be calculated according to the input shaft speed of the double clutch, the output shaft speed of the second clutch and the actual transmission torque of the second clutch collected under the current operating condition, and the cooling flow rate under the current operating condition can be directly collected.

[0101] Referring to Figure 7 , Figure 7 A step flowchart for calculating the second friction power corresponding to the second clutch according to the input shaft speed of the double clutch, the output shaft speed of the second clutch and the actual transmission torque of the second clutch is shown, and includes but is not limited to steps S710 to S720.

[0102] Step S710, calculate the absolute value of the speed difference between the input shaft speed of the double 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 transmission torque of 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, the unit is kw. Wherein, P2 represents the second friction power, M2 represents the actual transmission torque of the second clutch, 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 double clutch and the output shaft speed of the second clutch. Wherein, the input shaft of the double clutch is the common input shaft of the first clutch 1 and the second clutch 2.

[0105] Step S630, according to the corresponding relationship between different friction powers corresponding to the second clutch and different cooling liquid 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 the cooling liquid 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 double 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 clutch 2 under the second friction power and the cooling liquid flow rate of the current operating condition can be further determined according to the corresponding relationship between different friction powers corresponding to the second clutch 2 and different cooling liquid flow rates, different heating coefficients and different cooling coefficients. Wherein, the corresponding relationship between different friction powers corresponding to the second clutch 2 and different cooling liquid flow rates, different heating coefficients and different cooling coefficients can be obtained by designing different operating conditions in the second clutch temperature measurement test bench, taking the second data as input, taking the mathematical model of the cooling liquid 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 operating condition as the target, and solving the heating coefficient and the 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 parameter can be generally set to 0.5, 1, 1.5, 2, 2.5, 3, 3.5, the unit is kw; the cooling flow coordinate axis parameter can be generally set to 0.5, 1, 3, 5, 7, 10, the unit is L / min. The mathematical model of the cooling liquid temperature corresponding to the second clutch 2 is: In formula 3, T O2nrepresents the cooling liquid temperature corresponding to the current moment of the second clutch, T O2n-1 represents the cooling liquid temperature corresponding to the previous moment of the second clutch, M2 represents the actual transmission torque of the second clutch, 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 cooling liquid flow, T O1n-1 represents the cooling liquid temperature corresponding to the previous moment of the first clutch, x2 represents the second heating coefficient, y2 represents the second cooling coefficient, and Δt represents the interval duration, which is the interval duration between the current moment and the previous moment. The mathematical model of the friction plate temperature corresponding to the second clutch 2 is In formula 4, T C2n represents the friction plate temperature corresponding to the current moment of the second clutch, T O2n-1 represents the cooling liquid temperature corresponding to the previous moment of the second clutch, T C2n-1 represents the friction plate temperature corresponding to the previous moment of the second clutch, M2 represents the actual transmission torque of the second clutch, 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 cooling liquid flow, T O1n-1 represents the cooling liquid temperature corresponding to the previous moment of the first clutch, x2 represents the second heating coefficient, y2 represents the second cooling coefficient, and Δt represents the interval duration, which is the interval duration between the current moment and the previous moment. By taking the friction plate temperature of the first clutch 1 under each working condition as the target, the heating coefficient and the cooling coefficient of the second clutch 2 can be solved by iterative optimization of the temperature calculation model. According to formula 3, the cooling liquid temperature of the first clutch 1 needs to be calculated by formula 1 first, so that the cooling liquid temperature of the second clutch 2 can be further calculated according to formula 3. According to formula 4, the cooling liquid temperature of the first clutch 1 needs to be calculated according to formula 1 first, and the cooling liquid temperature of the second clutch 2 needs to be calculated according to formula 3, so that the friction plate temperature of the second clutch 2 can be further calculated according to formula 4.

[0108] Referring to Figure 8 , Figure 8 The step flow chart for determining the second heating coefficient and the second cooling coefficient of the second clutch corresponding to the second friction power and the cooling liquid flow of the second clutch is shown, including but not limited to steps S810 to S820.

[0109] Step S810, according to the third correspondence relationship between different friction powers corresponding to the second clutch and different cooling liquid flows and different heating coefficients, a second heating coefficient corresponding to the second clutch under the second friction power and the cooling liquid flow is determined.

[0110] Step S820, according to the fourth correspondence relationship between different friction powers corresponding to the second clutch and different cooling liquid flows and different cooling coefficients, a second cooling coefficient corresponding to the second clutch under the second friction power and the cooling liquid flow is determined.

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

[0112] Table 3 correspondence relationship table between different friction powers corresponding to the second clutch 2 and different cooling liquid flows and different heating coefficients

[0113]

[0114]

[0115] Table 4 correspondence relationship table between different friction powers corresponding to the second clutch 2 and different cooling liquid flows and different cooling coefficients

[0116]

[0117] Step S640, according to the second data, the second heating coefficient, the second cooling coefficient, the cooling liquid temperature corresponding to the last time of the second clutch, the cooling liquid temperature corresponding to the last time of the first clutch and the interval time length, the cooling liquid temperature corresponding to the current time of the second clutch is calculated, wherein the interval time length is the interval time length between the current time and the last time.

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

[0119] Step S650, according to the second data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and the cooling liquid temperature corresponding to the last time of the second clutch, the cooling liquid temperature corresponding to the last time of the first clutch and the interval time length, the friction plate temperature corresponding to the current time of the second clutch is calculated, and the friction plate temperature corresponding to the current time of the second clutch is greater than or equal to the cooling liquid temperature corresponding to the current time of the second clutch.

[0120] In the embodiments 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, the main factor of cooling is the cooling flow, and the temperature difference between the friction plate of the second clutch 2 and the cooling liquid of the first clutch 1. Therefore, after the second friction power and the cooling liquid flow corresponding to the second clutch 2 under the current operating condition are obtained according to the three-dimensional parameter tables 3 and 4, the second data, the second heating coefficient, the second cooling coefficient, the friction plate temperature and the cooling liquid temperature corresponding to the last time of the second clutch, the cooling liquid temperature corresponding to the last time of the first clutch and the interval time can be further used to calculate the friction plate temperature corresponding to the current time of the second clutch. Specifically, the friction plate temperature corresponding to the current time of the second clutch can be calculated by using the above formula 3 according to the second data, the second heating coefficient, the second cooling coefficient, the friction plate temperature and the cooling liquid temperature corresponding to the last time of the second clutch, the cooling liquid temperature corresponding to the last time of the first clutch and the interval time. That is, the friction plate temperature of the second clutch 2 can be calculated according to the cooling liquid temperature of the first clutch 1 and the cooling liquid temperature of the second clutch 2. And since the friction plate of the second clutch 2 is the heat source and the cooling liquid is the heat dissipation unit, the friction plate temperature of the second clutch 2 is not less than the cooling liquid temperature of the second clutch 2, that is, T C2n ≥T O2n .

[0121] In the embodiments of the present application, after the cooling liquid temperature corresponding to a previous moment of the first clutch is calculated, the second friction power corresponding to the second clutch under the current operating condition is calculated according to the input shaft rotating speed of the double clutch, the output shaft rotating speed of the second clutch, and the actual transmission torque of the second clutch. Then, the second friction power corresponding to the second clutch under the current operating condition, the second heating coefficient corresponding to the cooling liquid flow under the second friction power, and the second cooling coefficient corresponding to the cooling liquid flow are determined according to the corresponding relationship between the different friction powers corresponding to the second clutch and the different cooling liquid flows, the different heating coefficients, and the different cooling coefficients. Thus, the cooling liquid temperature corresponding to the current moment of the second clutch can be further calculated according to the second data (including the input shaft rotating speed of the double clutch, the output shaft rotating speed of the second clutch, the actual transmission torque of the second clutch, and the cooling liquid flow), the second heating coefficient, the second cooling coefficient, the cooling liquid temperature corresponding to the previous moment of the second clutch, the cooling liquid temperature corresponding to the previous moment of the first clutch, and the interval time length. After the cooling liquid temperature corresponding to the current moment of the second clutch is calculated, the friction plate temperature corresponding to the current moment of the second clutch can be further calculated according to the second data, the second heating coefficient, the second cooling coefficient, the friction plate temperature and the cooling liquid temperature corresponding to the previous moment of the second clutch, the cooling liquid temperature corresponding to the previous moment of the first clutch, and the interval time length. The heat exchange relationship between the friction plate of the second clutch 2 and the cooling liquid after passing through the first clutch 1 is considered, which is more in line with the structural characteristics of the wet-type double clutch cooling system, so that the calculation of the friction plate temperature of the second clutch 2 is more accurate, and the temperature rise change of the friction plate of the second clutch 2 in the actual working process can be obtained in real time.

[0122] Based on the same inventive concept, the embodiments of the present application also provide a computer program product. The computer program product includes computer instructions stored in a computer readable storage medium and adapted to be read and executed by a processor to enable a computer device having the processor to perform the method provided in any of the above embodiments.

[0123] Please refer to Figure 9 , Figure 9 The hardware structure of the computer program product of the embodiments of the present application is illustrated, and the computer program product includes:

[0124] The processor 901 can be implemented in the form of a general-purpose CPU (Central Processing Unit, central processor), a microprocessor, an application specific integrated circuit (ASIC), or one or more integrated circuits, and is used to execute related programs to implement the technical solutions provided by 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), etc. The memory 902 can store an operating system and other application programs, and when the technical solutions provided by the embodiments of the present specification are implemented by software or firmware, the related program codes are stored in the memory 902 and are called and executed by the processor 901 to perform the wet double clutch temperature determination method described in the embodiments of the present application;

[0126] The input / output interface 903 is configured to realize information input and output.

[0127] The communication interface 904 is configured to realize the communication interaction between the device and other devices, and the communication can be realized by a wired manner (for example, a USB, a network cable, etc.) or a wireless manner (for example, a mobile network, WIFI, Bluetooth, etc.).

[0128] The bus 905 is configured to transmit information between various components (for example, the processor 901, the memory 902, the input / output interface 903, and the communication interface 904) of the device.

[0129] The processor 901, the memory 902, the input / output interface 903, and the communication interface 904 are connected to each other through the bus 905 to realize the communication connection between the device.

[0130] The functions described herein can be implemented in hardware, software executed by a processor, firmware, or any combination thereof. If implemented in software, the functions can be stored on or transmitted over as one or more instructions or code on a computer-readable medium. Other examples and implementations are within the scope and spirit of the disclosure and appended claims. For example, due to the nature of software, the functions described above can be implemented using software executed by a processor, hardware, firmware, hardwiring, or combinations of any of these. Also, the various functions of the elements can be combined into a single unit, or separated into multiple units, or combined into a single unit or separated into multiple units, depending on implementation.

[0131] In several embodiments provided in the present application, it should be understood that the disclosed technology can be implemented in other ways. Among them, the above-mentioned device embodiments are only schematic, for example, the division of the units can be a logical function division, and actual implementation can have another division manner, for example, a plurality of units or components can be combined or integrated into another system, or some features can be ignored or not executed. In addition, the coupling or direct coupling or communication connection between the displayed or discussed each other can be through some interface, indirect coupling or communication connection between units or modules, which can be electrical or other forms.

[0132] The units described as separate components can or can not be physically separated, and the components of the control device can or can not be physical units, i.e. can be located in one place or can be distributed to multiple units. Part or all of the units can be selected according to actual needs to achieve the purpose of the embodiment.

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

[0134] The above is only an embodiment of the present application and is not used to limit the present application. For those skilled in the art, the present application can have various changes and modifications. Any modification, equivalent replacement, improvement, etc. made within the spirit and principles of the present application shall be included in the scope of 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, the first data including a speed of an input shaft of the dual clutch, a speed of an output shaft 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; Calculating the coolant temperature of the first clutch at a current moment based on the first data, the first heating coefficient, the first cooling coefficient, the coolant temperature of the first clutch at a previous moment, and an interval duration, wherein the interval duration is the interval duration between the current moment and the previous moment; The friction plate 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 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.

2. The method according to claim 1, characterized in that 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 includes: 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 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, based on correspondences between different friction powers corresponding to the first clutch and different coolant flow rates, 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 includes: determining a first heating coefficient corresponding to the first clutch under the first friction power and the coolant flow rate according to a first correspondence between different friction powers corresponding to the first clutch, different coolant flow rates, and different heating coefficients; According to a second correspondence between different friction powers corresponding to the first clutch, 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, wherein The coolant 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 coolant temperature corresponding to the first clutch at the previous moment, and the interval duration 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, and 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 time.

5. The method according to claim 1, wherein The calculation of the friction plate temperature of the first clutch at the current moment based on the first data, the first heating coefficient, the first cooling coefficient, the friction plate temperature and the coolant temperature of the first clutch at the previous moment, 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, and 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 time.

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, the second data including a speed of an input shaft of the dual clutch, a speed of an output shaft of the second clutch, an actual torque transmitted by 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; Calculating the coolant temperature of the second clutch at a current moment based on the second data, the second heating coefficient, the second cooling coefficient, the coolant temperature of the second clutch at a previous moment, the coolant temperature of the first clutch at a previous moment, and an interval duration, wherein the interval duration is the duration between the current moment and the previous moment; 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 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 the current moment is greater than or equal to the coolant temperature corresponding to the second clutch at the current moment.

7. The method according to claim 6, characterized in that The determining, 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, the second heating coefficient and the second cooling coefficient corresponding to the second clutch under the second friction power and the coolant flow rate includes: determining a second heating coefficient corresponding to the second clutch under the second friction power and the coolant flow rate according to a third correspondence between different friction powers corresponding to the second clutch, different coolant flow rates, and different heating coefficients; According to a fourth correspondence between different friction powers corresponding to the second clutch, 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 of 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 of the second clutch at the previous moment, the coolant temperature of 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 previous 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 at 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 of 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 coolant temperature of the second clutch at the previous moment, the coolant temperature of the first clutch at the previous moment, 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 at 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 stored in a computer-readable storage medium and adapted to be read and executed by a processor, so as to enable a computer device having the processor to perform the method according to any one of claims 1 to 9.

Images