Pressure compensation method and device for clutch hydraulic system

Abstract

The present invention provides a clutch hydraulic system pressure compensation method and device. This method monitors the actual pressure of the clutch hydraulic system in real time and compares it with the pressures corresponding to the clutch half-engagement point KP and the clutch nonlinear point VKP. If the actual pressure is greater than the pressure corresponding to KP but less than the pressure corresponding to VKP, a base compensation amount is determined based on the pressure corresponding to VKP and the actual pressure. A correction coefficient is determined based on the current valve body oil temperature and the target pressure change rate. The clutch hydraulic system is pressure compensated using the base compensation amount and the correction coefficient. In this solution, by monitoring the actual pressure in real time and comparing it with the pressures corresponding to the clutch half-engagement point KP and the clutch nonlinear point VKP, pressure compensation is performed on the clutch hydraulic system when the actual pressure is between the pressures corresponding to KP and VKP, thereby reducing response delays and errors in the clutch hydraulic system.

Description

Technical Field

[0001] The present invention relates to the technical field of engine control, and in particular to a pressure compensation method and device for a clutch hydraulic system. Background Art

[0002] A dual-clutch transmission (DCT) transmits torque through both clutches during upshifts and downshifts, ensuring constant power transmission and enabling shifts without power interruption. During this torque interaction, the vehicle is very sensitive to fluctuations in output torque, and excessively high or low pressure can easily cause shifting jerkiness.

[0003] In the prior art, the clutch in a wet dual-clutch transmission usually achieves pressure control through a pressure control valve. In steady state, the curve of the current and pressure of the solenoid valve (PC curve) is measured. In actual control, the PC curve of the solenoid valve is checked according to the target pressure, and the pressure of the pressure valve is further controlled to achieve control of the clutch pressure. The PC curve reflects the steady-state characteristics of the solenoid valve. In actual control, the target pressure changes dynamically, so the actual pressure is a dynamic response process. The steady-state PC curve cannot reflect the response process of the actual pressure. In the low-torque stage, the clutch pressure plate and the friction plate have just started to contact. Due to the sudden change in stiffness, the clutch pressure characteristics appear nonlinear, resulting in large hydraulic response delays and large errors.

[0004] It can be seen from this that the existing clutch pressure control method has the following problems: the hydraulic response delay and error at low torque are relatively large, resulting in the clutch transmission torque being smaller than the required torque, which easily causes a sense of frustration when shifting; under low-speed conditions, the actual pressure response rate is greater than the target pressure rate. Summary of the Invention

[0005] In view of this, an embodiment of the present invention provides a pressure compensation method and device for a clutch hydraulic system to solve the problems of large response delay and large error of the clutch hydraulic system in the prior art.

[0006] To achieve the above objectives, the embodiments of the present invention provide the following technical solutions:

[0007] A first aspect of an embodiment of the present invention discloses a pressure compensation method for a clutch hydraulic system, the method comprising:

[0008] monitoring the actual pressure of the clutch hydraulic system in real time, and comparing the actual pressure with the pressure corresponding to the clutch half-engagement point KP and the clutch nonlinear point VKP;

[0009] If the actual pressure is greater than the pressure corresponding to the KP and less than the pressure corresponding to the VKP, a basic compensation amount is obtained based on the pressure corresponding to the VKP and the actual pressure;

[0010] According to the current valve body oil temperature and the target pressure change rate, a correction coefficient is obtained;

[0011] Pressure compensation is performed on the clutch hydraulic system using the basic compensation amount and the correction coefficient.

[0012] Optionally, also include:

[0013] During the real-time monitoring of the actual pressure, if the actual pressure is equal to the pressure corresponding to the VKP, the pressure compensation is exited.

[0014] Optionally, obtaining the correction coefficient according to the current valve body oil temperature and the target pressure change rate includes:

[0015] According to the current valve body oil temperature and the target pressure change rate, a correction coefficient is obtained from a preset data table, where the correction coefficient is inversely proportional to the valve body oil temperature and directly proportional to the target pressure change rate.

[0016] Optionally, performing pressure compensation on the clutch hydraulic system by using the basic compensation amount and the correction coefficient includes:

[0017] Calculating the product of the basic compensation amount and the correction coefficient, and using the product as the actual pressure compensation amount;

[0018] Pressure compensation is performed on the clutch hydraulic system based on the actual pressure compensation amount.

[0019] Optionally, performing pressure compensation on the hydraulic system based on the actual pressure compensation amount includes:

[0020] Determining whether the actual pressure compensation amount is within a limit range;

[0021] If so, pressure compensation is performed on the hydraulic system according to the actual pressure compensation amount.

[0022] A second aspect of an embodiment of the present invention discloses a pressure compensation device for a clutch hydraulic system, the device comprising:

[0023] a comparison module, configured to monitor the actual pressure of the clutch hydraulic system in real time and compare the actual pressure with the pressures corresponding to the clutch half-engagement point KP and the clutch nonlinear point VKP;

[0024] a first obtaining module, configured to obtain a basic compensation amount based on the pressure corresponding to the VKP and the actual pressure if the actual pressure is greater than the pressure corresponding to the KP and less than the pressure corresponding to the VKP;

[0025] The second obtaining module is used to obtain a correction coefficient according to the current valve body oil temperature and the target pressure change rate;

[0026] A pressure compensation module is used to perform pressure compensation on the clutch hydraulic system using the basic compensation amount and the correction coefficient.

[0027] Optionally, it also includes: an exit module;

[0028] The exit module is configured to exit pressure compensation if the actual pressure is equal to the pressure corresponding to the VKP during real-time monitoring of the actual pressure.

[0029] Optionally, the second obtaining module is specifically configured to:

[0030] According to the current valve body oil temperature and the target pressure change rate, a correction coefficient is obtained from a preset data table, where the correction coefficient is inversely proportional to the valve body oil temperature and directly proportional to the target pressure change rate.

[0031] Optionally, the pressure compensation module includes:

[0032] a calculation unit, configured to calculate a product of the basic compensation amount and the correction coefficient, and use the product as an actual pressure compensation amount;

[0033] A pressure compensation unit is used to perform pressure compensation on the clutch hydraulic system based on the actual pressure compensation amount.

[0034] Optionally, the pressure compensation unit is specifically used to:

[0035] Determine whether the actual pressure compensation amount is within a limit range; if so, perform pressure compensation on the hydraulic system according to the actual pressure compensation amount.

[0036] Based on the above-described embodiments of the present invention, a clutch hydraulic system pressure compensation method and device are provided. The method includes: real-time monitoring of the actual pressure of the clutch hydraulic system, comparing the actual pressure with the pressures corresponding to the clutch half-engagement point KP and the clutch nonlinear point VKP; if the actual pressure is greater than the pressure corresponding to the KP and less than the pressure corresponding to the VKP, determining a base compensation amount based on the pressure corresponding to the VKP and the actual pressure; determining a correction coefficient based on the current valve body oil temperature and the target pressure change rate; and performing pressure compensation on the clutch hydraulic system using the base compensation amount and the correction coefficient. In this embodiment, by real-time monitoring of the actual pressure and comparing it with the pressures corresponding to the clutch half-engagement point KP and the clutch nonlinear point VKP, pressure compensation is performed on the clutch hydraulic system when the actual pressure is between the pressures corresponding to the KP and VKP pressures, thereby reducing response delay and error in the clutch hydraulic system. BRIEF DESCRIPTION OF THE DRAWINGS

[0037] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are merely embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on the provided drawings without paying any creative work.

[0038] Figure 1 A schematic structural diagram of a clutch hydraulic system provided by an embodiment of the present invention;

[0039] Figure 2 A schematic flow chart of a pressure compensation method for a clutch hydraulic system provided by an embodiment of the present invention;

[0040] Figure 3 An application scenario diagram of a pressure control waveform and the corresponding position of VKP provided by an embodiment of the present invention;

[0041] Figure 4 A schematic diagram of a pressure compensation process provided by an embodiment of the present invention;

[0042] Figure 5 A schematic diagram of another pressure compensation process provided by an embodiment of the present invention;

[0043] FIG6( a ) and FIG6 ( b ) are diagrams showing an application scenario of pressure compensation for a hydraulic system in a nonlinear stage according to an embodiment of the present invention;

[0044] FIG7( a ) and FIG7 ( b ) are diagrams showing the results of a real vehicle test according to an embodiment of the present invention;

[0045] Figure 8 A schematic flow chart of another pressure compensation method for a clutch hydraulic system provided by an embodiment of the present invention;

[0046] Figure 9 A schematic structural diagram of a pressure compensation device for a clutch hydraulic system provided by an embodiment of the present invention;

[0047] Figure 10 A schematic structural diagram of another pressure compensation device of a clutch hydraulic system provided by an embodiment of the present invention. DETAILED DESCRIPTION

[0048] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0049] In this application, the terms "comprises," "comprising," or any other variations thereof are intended to encompass non-exclusive inclusion, such that a process, method, article, or apparatus that includes a list of elements includes not only those elements but also other elements not explicitly listed, or elements inherent to such process, method, article, or apparatus. In the absence of further limitations, an element defined by the phrase "comprising a ..." does not preclude the presence of additional identical elements in the process, method, article, or apparatus that includes the element.

[0050] The terms "first," "second," "third," "fourth," and so on (if any) in the specification and claims of this application and the accompanying drawings are used to distinguish similar objects and are not necessarily used to describe a particular order or sequence. It should be understood that the terms used in this manner are interchangeable where appropriate, so that the embodiments described herein can be implemented in an order other than that shown or described herein.

[0051] As can be seen from the background technology, the existing clutch pressure control method has the following problems: the hydraulic response delay and error at low torque are relatively large, resulting in the clutch transmission torque being smaller than the required torque, which easily causes a sense of frustration when shifting; under low-speed conditions, the actual pressure response rate is greater than the target pressure rate.

[0052] Therefore, an embodiment of the present invention provides a pressure compensation method and device for a clutch hydraulic system. In this solution, the actual pressure is monitored in real time and compared with the pressure corresponding to the clutch half-engagement point KP and the clutch nonlinear point VKP. When the actual pressure is between the pressures corresponding to KP and VKP, the clutch hydraulic system is pressure compensated, thereby reducing the response delay and error of the clutch hydraulic system.

[0053] like Figure 1 As shown in FIG, a schematic diagram of the structure of a clutch hydraulic system provided by an embodiment of the present invention, the clutch hydraulic system is composed of a mechanical pump 1, a clutch piston 2, a return spring 3, a pressure plate 4, a friction plate 5 and a pressure control valve 6. The connection relationship is as follows Figure 1 shown.

[0054] During the clutch oil filling process, the mechanical pump 1 provides power, and the oil pushes the clutch piston 2 through the pressure control valve 6, overcoming the pressure of the return spring 3, eliminating the gap between the clutch piston 2, the friction plate 5 and the pressure plate 4, and finally pressing the friction plate 4 and the pressure plate 5 to complete the torque transmission.

[0055] In the process of eliminating the gap between the pressure plate 4 and the friction plate 5, the clutch pressure characteristic exhibits nonlinearity. At the same time, the oil film thickness of the clutch viscous torque changes rapidly, causing the torque characteristic to also show obvious nonlinearity. At this time, it is necessary to compensate the target pressure in the nonlinear stage until the gap between the friction plate 5 is completely eliminated and the clutch reaches the linear region, thereby making the actual pressure more traceable.

[0056] Based on the clutch hydraulic system provided by the above embodiment of the present invention, Figure 2 FIG. 1 is a flow chart of a pressure compensation method for a clutch hydraulic system according to an embodiment of the present invention. The method mainly includes the following steps:

[0057] Step S201: monitor the actual pressure of the clutch hydraulic system in real time, and compare the actual pressure with the pressure corresponding to the clutch half-engagement point (Kiss Point, KP) and the clutch nonlinear point (Volume Kiss Point, VKP).

[0058] In step S201 , the clutch half-engagement point KP refers to the position where the clutch is just in contact but does not transmit torque.

[0059] Clutch nonlinear point VKP: refers to the position where the stiffness suddenly changes during the clutch engagement process.

[0060] Between KP and VKP, the clutch pressure characteristic is nonlinear, and above VKP, the clutch pressure characteristic is linear.

[0061] It should be noted that the actual pressure can be expressed as P sensor .

[0062] In the process of specifically implementing step S201, the actual pressure of the clutch hydraulic system is monitored in real time, and the pressure corresponding to the position where the stiffness suddenly changes during the current clutch engagement process is obtained, as well as the pressure corresponding to the position where the current clutch is just in contact but does not transmit torque, that is, the pressure corresponding to the clutch nonlinear point VKP and the clutch half-engagement point KP are obtained. First, the actual pressure monitored in real time is compared with the pressure corresponding to the clutch half-engagement point KP, and then the actual pressure monitored in real time is compared with the pressure corresponding to the clutch nonlinear point VKP to obtain a comparison result.

[0063] Preferably, in a specific embodiment, the actual pressure monitored in real time may be compared with the pressure corresponding to the clutch nonlinear point VKP first, and then the actual pressure monitored in real time may be compared with the pressure corresponding to the clutch semi-engagement point KP.

[0064] like Figure 3 , which is an application scenario diagram of a pressure control waveform and the position corresponding to VKP provided by an embodiment of the present invention.

[0065] exist Figure 3 In the figure, t0 is when the target pressure exceeds KP, and t1 is when the actual pressure exceeds VKP, marking the subsequent pressure compensation phase. During this phase, the maximum error and maximum delay time are used to measure the clutch hydraulic system's following performance.

[0066] The maximum error refers to the maximum value of the difference between the target pressure and the actual pressure during the period from t0 to t1.

[0067] Delay time: refers to the time required for the actual pressure curve to reach the target value for the first time. In actual application, calculate the delay time for each target pressure and take the maximum value as the maximum delay time for that stage.

[0068] Step S202: Determine whether the actual pressure is greater than the pressure corresponding to KP and less than the pressure corresponding to VKP. If so, execute step S203; if not, return to execute step S201.

[0069] In the process of implementing step S202, based on the comparison result obtained, it is determined that the actual pressure is greater than the pressure corresponding to KP and less than the pressure corresponding to VKP. If so, it means that the actual pressure is greater than the pressure corresponding to KP and less than the pressure corresponding to VKP, that is, the actual pressure of the clutch hydraulic system is between KP and VKP. At this time, nonlinear compensation needs to be activated, that is, pressure compensation needs to be performed, then step S103 is executed. If not, it means that the actual pressure is less than the pressure corresponding to KP or greater than the pressure corresponding to VKP, that is, the actual pressure of the clutch hydraulic system is not between KP and VKP. At this time, nonlinear compensation does not need to be activated, that is, pressure compensation is not required, then return to execute step S101.

[0070] Step S203: Obtain a basic compensation amount based on the pressure corresponding to the VKP and the actual pressure.

[0071] In the specific implementation of step S203 , the pressure corresponding to the VKP and the actual pressure monitored are calculated based on the obtained pressure corresponding to the VKP to obtain the basic compensation amount.

[0072] Preferably, in a specific embodiment, the difference between the pressure corresponding to the VKP and the actual pressure is calculated to obtain the basic compensation amount.

[0073] Specifically, basic compensation amount = VKP-P sensor .

[0074] Optional, such as Figure 3 As shown, basic compensation amount = VKP-P sensor , which is equivalent to Figure 3 The error in the delay time is P sensor The time required to reach VKP for the first time.

[0075] It should be noted that the basic compensation amount is inversely proportional to the actual pressure. In other words, the basic compensation amount will gradually decrease as the actual pressure increases.

[0076] Step S204: Obtain a correction coefficient according to the current valve body oil temperature and the target pressure change rate.

[0077] In step S204, the current valve body oil temperature can be expressed as T, and the target pressure change rate can be expressed as P c ' md , the correction coefficient can be expressed as C.

[0078] In the specific implementation of step S204 , the valve body oil temperature in the current clutch hydraulic system and the target pressure change rate are obtained, and a correction coefficient is obtained according to the current valve body oil temperature and the target pressure change rate.

[0079] Preferably, in a specific embodiment, the correction coefficient is obtained from a preset data table according to the current valve body oil temperature and the target pressure change rate.

[0080] It should be noted that the corresponding calibration amount is set in the preset data table according to the valve body oil temperature and the target pressure change rate.

[0081] It should be noted that the correction coefficient is inversely proportional to the valve body oil temperature and directly proportional to the target pressure change rate. In other words, as the valve body oil temperature increases, the correction coefficient gradually decreases, and as the target pressure change rate increases, the correction coefficient gradually increases.

[0082] Step S205: Perform pressure compensation on the clutch hydraulic system using the basic compensation amount and the correction coefficient.

[0083] Optionally, step 205 is performed to perform pressure compensation on the clutch hydraulic system using the basic compensation amount and the correction coefficient, such as Figure 4 FIG. 1 is a flow chart of a pressure compensation process according to an embodiment of the present invention, which mainly includes the following steps:

[0084] Step S401: Calculate the product of the basic compensation amount and the correction coefficient, and use the product as the actual pressure compensation amount.

[0085] In step S401, the actual pressure compensation amount can be expressed as P 补偿 .

[0086] In the specific implementation of step S401 , the obtained basic compensation amount and the correction coefficient are multiplied to obtain specific data, which is used as the actual pressure compensation amount.

[0087] Specifically, P 补偿 =C*(VKP-P sensor ).

[0088] Step S402: Perform pressure compensation on the clutch hydraulic system based on the actual pressure compensation amount.

[0089] In the specific implementation of step S402 , the obtained actual pressure compensation amount is used to perform pressure compensation on the clutch hydraulic system.

[0090] Optionally, step 402 is performed to perform pressure compensation on the clutch hydraulic system based on the actual pressure compensation amount, such as Figure 5 FIG. 1 is a flow chart of another pressure compensation process provided by an embodiment of the present invention, which mainly includes the following steps:

[0091] Step S501: Determine whether the actual pressure compensation amount is within a limit range. If so, execute step S502; if not, continue to execute step S501.

[0092] It should be noted that, in order to ensure the robustness of pressure control, the actual pressure compensation amount needs to be limited to a certain range. The limiting condition is determined according to the characteristics of the clutch hydraulic system and is not limited in the present invention.

[0093] Step S502: Perform pressure compensation on the hydraulic system according to the actual pressure compensation amount.

[0094] In the specific implementation of step S502 , if it is determined that the actual pressure compensation amount is within the limit range, pressure compensation is performed on the hydraulic system based on the actual pressure compensation amount.

[0095] As shown in FIG6( a ) and FIG6 ( b ), an application scenario diagram of pressure compensation for a hydraulic system in a nonlinear stage provided by an embodiment of the present invention is shown.

[0096] In Figures 6(a) and 6(b), pressure compensation begins when the actual pressure is between KP and VKP. In all cases, the pressure compensation value decreases as the actual pressure increases. When the actual pressure reaches VKP, the pressure compensation value reaches 0, and pressure compensation is terminated.

[0097] At the same temperature, the pressure compensation value increases with the increase of the target pressure change rate, as shown in Figure 6(a).

[0098] At the same target pressure change rate, the pressure compensation value increases as the valve body oil temperature decreases, as shown in Figure 6(b).

[0099] Finally, the upper limit of pressure compensation is set to improve the robustness of control, that is, the actual pressure compensation value must be within the limit range.

[0100] As shown in FIG. 7( a ) and FIG. 7 ( b ), they are result diagrams of a real vehicle test provided by an embodiment of the present invention.

[0101] In Figure 7(a) and Figure 7(b), the two tests were performed on the same vehicle and the test conditions were consistent, wherein Figure 7(a) is the test result without pressure compensation for the vehicle's clutch hydraulic system, and Figure 7(b) is the test result with pressure compensation for the vehicle's clutch hydraulic system.

[0102] It can be seen from the experimental results that after pressure compensation of the vehicle's clutch hydraulic system, the maximum delay is reduced from 134ms to 46ms, and the maximum error is reduced from 150kPa to 25kPa, which effectively improves the following performance of the clutch hydraulic system and reduces the delay of the clutch hydraulic system.

[0103] A clutch hydraulic system pressure compensation method, based on an embodiment of the present invention, monitors the actual pressure of the clutch hydraulic system in real time and compares it with the pressures corresponding to the clutch half-engagement point KP and the clutch nonlinear point VKP. If the actual pressure is greater than the pressure corresponding to KP but less than the pressure corresponding to VKP, a base compensation amount is determined based on the pressure corresponding to VKP and the actual pressure. A correction coefficient is obtained based on the current valve body oil temperature and the target pressure change rate. The clutch hydraulic system is pressure compensated using the base compensation amount and the correction coefficient. In this solution, by monitoring the actual pressure in real time and comparing it with the pressures corresponding to the clutch half-engagement point KP and the clutch nonlinear point VKP, pressure compensation is performed on the clutch hydraulic system when the actual pressure is between the pressures corresponding to KP and VKP, thereby reducing response delay and error in the clutch hydraulic system.

[0104] Based on the above embodiment of the present invention, a pressure compensation method for a clutch hydraulic system is provided. Figure 8 FIG. 1 is a flow chart of another pressure compensation method for a clutch hydraulic system according to an embodiment of the present invention, which mainly includes the following steps:

[0105] Step S801: monitor the actual pressure of the clutch hydraulic system in real time, and compare the actual pressure with the pressure corresponding to the clutch half-engagement point KP and the clutch nonlinear point VKP respectively.

[0106] Step S802: Determine whether the actual pressure is greater than the pressure corresponding to KP and less than the pressure corresponding to VKP. If so, execute step S803; if not, return to execute step S801.

[0107] Step S803: Obtain a basic compensation amount based on the pressure corresponding to the VKP and the actual pressure.

[0108] Step S804: Obtain a correction coefficient according to the current valve body oil temperature and the target pressure change rate.

[0109] Step S805: Perform pressure compensation on the clutch hydraulic system using the basic compensation amount and the correction coefficient.

[0110] It should be noted that the execution principle and process of the above steps S801 to S805 are the same as those of Figure 2 The execution principles and processes of steps S201 to S205 disclosed in are the same as those of steps S201 to S205 disclosed in , and are not described again here.

[0111] Step S806: Determine whether the actual pressure is equal to the pressure corresponding to VKP. If so, execute step S807; if not, return to execute step S801.

[0112] In the specific implementation of step S806, during the real-time monitoring of the actual pressure, it is determined whether the actual pressure is equal to the pressure corresponding to the VKP. If so, step S807 is executed; if not, the process returns to step S801.

[0113] Step S807: Exit pressure compensation.

[0114] In the specific implementation of step S807 , during the real-time monitoring of the actual pressure, if it is determined that the actual pressure of the clutch hydraulic system currently monitored is equal to the pressure corresponding to VKP, the pressure compensation is exited.

[0115] A pressure compensation method for a clutch hydraulic system provided in an embodiment of the present invention monitors the actual pressure in real time and compares the actual pressure with the pressures corresponding to the clutch half-engagement point KP and the clutch nonlinear point VKP. When the actual pressure is between the pressures corresponding to KP and VKP, pressure compensation is performed on the clutch hydraulic system. During the process of real-time monitoring of the actual pressure, when the actual pressure is equal to the pressure corresponding to VKP, pressure compensation is exited, thereby reducing the response delay and error of the clutch hydraulic system.

[0116] The above-mentioned embodiment of the present invention Figure 2A pressure compensation method for a clutch hydraulic system is shown, and an embodiment of the present invention also provides a pressure compensation device for a clutch hydraulic system, such as Figure 9 As shown, the pressure compensation device of the clutch hydraulic system includes: a comparison module 91 , a first obtaining module 92 , a second obtaining module 93 and a pressure compensation module 94 .

[0117] The comparison module 91 is used to monitor the actual pressure of the clutch hydraulic system in real time and compare the actual pressure with the pressure corresponding to the clutch half-engagement point KP and the clutch nonlinear point VKP.

[0118] The first obtaining module 92 is configured to obtain a basic compensation amount based on the pressure corresponding to the VKP and the actual pressure if the actual pressure is greater than the pressure corresponding to the KP and less than the pressure corresponding to the VKP.

[0119] The second obtaining module 93 is used to obtain a correction coefficient according to the current valve body oil temperature and the target pressure change rate.

[0120] The pressure compensation module 94 is used to perform pressure compensation on the clutch hydraulic system using a basic compensation amount and a correction coefficient.

[0121] Optional, based on the above Figure 9 The second obtaining module 93 is shown, and the second obtaining module 93 is specifically used to:

[0122] According to the current valve body oil temperature and the target pressure change rate, a correction coefficient is obtained from a preset data table. The correction coefficient is inversely proportional to the valve body oil temperature and directly proportional to the target pressure change rate.

[0123] The calculation unit is used to calculate the product of the basic compensation amount and the correction coefficient, and use the product as the actual pressure compensation amount.

[0124] The pressure compensation unit is used to perform pressure compensation on the clutch hydraulic system based on an actual pressure compensation amount.

[0125] Optional, based on the above Figure 9 The pressure compensation module 94 is shown, and the pressure compensation unit is specifically used to:

[0126] Determine whether the actual pressure compensation amount is within a limit range; if so, perform pressure compensation on the hydraulic system according to the actual pressure compensation amount.

[0127] It should be noted that the specific principles and execution processes of each module or unit in the pressure compensation device of the clutch hydraulic system disclosed in the above embodiment of the present invention are the same as those of the pressure compensation method of the clutch hydraulic system implemented in the above embodiment of the present invention. Please refer to the corresponding parts of the pressure compensation method of the clutch hydraulic system disclosed in the above embodiment of the present invention, and they will not be repeated here.

[0128] According to an embodiment of the present invention, a pressure compensation device for a clutch hydraulic system is provided. This device monitors the actual pressure of the clutch hydraulic system in real time and compares it with the pressures corresponding to the clutch half-engagement point KP and the clutch nonlinear point VKP. If the actual pressure is greater than the pressure corresponding to KP but less than the pressure corresponding to VKP, a base compensation amount is determined based on the pressure corresponding to VKP and the actual pressure. A correction coefficient is determined based on the current valve body oil temperature and the target pressure change rate. Pressure compensation of the clutch hydraulic system is performed using the base compensation amount and the correction coefficient. In this solution, by monitoring the actual pressure in real time and comparing it with the pressures corresponding to the clutch half-engagement point KP and the clutch nonlinear point VKP, pressure compensation is performed on the clutch hydraulic system when the actual pressure is between the pressures corresponding to KP and VKP, thereby reducing response delay and error in the clutch hydraulic system.

[0129] Optional, based on the above Figure 9 The pressure compensation device of the clutch hydraulic system shown, combined with Figure 9 ,like Figure 10 As shown, the pressure compensation device of the clutch hydraulic system is further provided with an exit module 95 .

[0130] The exit module 95 is used to exit the pressure compensation if the actual pressure is equal to the pressure corresponding to the VKP during the process of real-time monitoring of the actual pressure.

[0131] A pressure compensation device for a clutch hydraulic system provided in an embodiment of the present invention monitors the actual pressure in real time and compares the actual pressure with the pressures corresponding to the clutch half-engagement point KP and the clutch nonlinear point VKP. When the actual pressure is between the pressures corresponding to KP and VKP, pressure compensation is performed on the clutch hydraulic system. During the process of real-time monitoring of the actual pressure, when the actual pressure is equal to the pressure corresponding to VKP, pressure compensation is exited, thereby reducing response delays and errors of the clutch hydraulic system.

[0132] Each embodiment in this specification is described in a progressive manner. The same or similar parts between the embodiments can be referred to each other. Each embodiment focuses on the differences from other embodiments. In particular, for system or system embodiments, since they are basically similar to method embodiments, the description is relatively simple. For relevant parts, refer to the partial description of the method embodiment. The system and system embodiments described above are merely schematic, wherein the units described as separate components may or may not be physically separated, and the components displayed as units may or may not be physical units, that is, they may be located in one place, or they may be distributed on multiple network units. Some or all of the modules can be selected according to actual needs to achieve the purpose of the solution of this embodiment. A person of ordinary skill in the art can understand and implement it without expending creative work.

[0133] Professionals may further appreciate that the units and algorithm steps of each example described in conjunction with the embodiments disclosed herein can be implemented in electronic hardware, computer software, or a combination of the two. In order to clearly illustrate the interchangeability of hardware and software, the above description has generally described the components and steps of each example according to their functions. Whether these functions are performed in hardware or software depends on the specific application and design constraints of the technical solution. Professionals and technicians may use different methods to implement the described functions for each specific application, but such implementation should not be considered beyond the scope of the present invention.

[0134] The above description of the disclosed embodiments is intended to enable one skilled in the art to implement or use the present invention. Various modifications to these embodiments will be readily apparent to one skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the present invention. Therefore, the present invention is not limited to the embodiments shown herein but is intended to conform to the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A pressure compensation method for a clutch hydraulic system, characterized in that: The method comprises: monitoring the actual pressure of the clutch hydraulic system in real time, and comparing the actual pressure with the pressure corresponding to the clutch half-engagement point KP and the clutch nonlinear point VKP; If the actual pressure is greater than the pressure corresponding to the KP and less than the pressure corresponding to the VKP, a basic compensation amount is obtained based on the pressure corresponding to the VKP and the actual pressure; According to the current valve body oil temperature and the target pressure change rate, a correction coefficient is obtained; performing pressure compensation on the clutch hydraulic system using the basic compensation amount and the correction coefficient; The step of performing pressure compensation on the clutch hydraulic system by using the basic compensation amount and the correction coefficient includes: Calculating the product of the basic compensation amount and the correction coefficient, and using the product as the actual pressure compensation amount; Pressure compensation is performed on the clutch hydraulic system based on the actual pressure compensation amount.

2. The method according to claim 1, characterized in that Also includes: During the real-time monitoring of the actual pressure, if the actual pressure is equal to the pressure corresponding to the VKP, the pressure compensation is exited.

3. The method according to claim 1, characterized in that The correction coefficient is obtained according to the current valve body oil temperature and the target pressure change rate, including: According to the current valve body oil temperature and the target pressure change rate, a correction coefficient is obtained from a preset data table, where the correction coefficient is inversely proportional to the valve body oil temperature and directly proportional to the target pressure change rate.

4. The method according to claim 3, characterized in that The performing pressure compensation on the hydraulic system based on the actual pressure compensation amount includes: Determining whether the actual pressure compensation amount is within a limit range; If so, pressure compensation is performed on the hydraulic system according to the actual pressure compensation amount.

5. A pressure compensation device for a clutch hydraulic system, characterized in that: The device comprises: a comparison module, configured to monitor the actual pressure of the clutch hydraulic system in real time and compare the actual pressure with the pressures corresponding to the clutch half-engagement point KP and the clutch nonlinear point VKP; a first obtaining module, configured to obtain a basic compensation amount based on the pressure corresponding to the VKP and the actual pressure if the actual pressure is greater than the pressure corresponding to the KP and less than the pressure corresponding to the VKP; The second obtaining module is used to obtain a correction coefficient according to the current valve body oil temperature and the target pressure change rate; a pressure compensation module, configured to perform pressure compensation on the clutch hydraulic system using the basic compensation amount and the correction coefficient; Wherein, the pressure compensation module includes: a calculation unit, configured to calculate a product of the basic compensation amount and the correction coefficient, and use the product as an actual pressure compensation amount; A pressure compensation unit is used to perform pressure compensation on the clutch hydraulic system based on the actual pressure compensation amount.

6. The device according to claim 5, characterized in that Also includes: Exit the module; The exit module is configured to exit pressure compensation if the actual pressure is equal to the pressure corresponding to the VKP during real-time monitoring of the actual pressure.

7. The device according to claim 5, characterized in that The second obtaining module is specifically used for: According to the current valve body oil temperature and the target pressure change rate, a correction coefficient is obtained from a preset data table, where the correction coefficient is inversely proportional to the valve body oil temperature and directly proportional to the target pressure change rate.

8. The device according to claim 5, characterized in that The pressure compensation unit is specifically used for: Determine whether the actual pressure compensation amount is within a limit range; if so, perform pressure compensation on the hydraulic system according to the actual pressure compensation amount.

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