An AT transmission modeling method, a moment of inertia equivalent method and a device

Abstract

The present invention discloses a method for modeling an AT transmission, a method and device for equivalent moment of inertia, which relate to the technical field of vehicle dynamic performance simulation. The method for equivalent moment of inertia of the AT transmission includes: obtaining the transmission structure of the AT transmission and the distribution of clutches, brakes and one-way clutches in each gear; according to the rotating components related to the clutches, brakes and one-way clutches, taking the clutch, brake or synchronizer as the demarcation point, dividing the moment of inertia of the AT transmission into multiple parts of moment of inertia; obtaining the tooth ratio of the transmission structure of the AT transmission, the corresponding speed ratios on the transmission routes of each gear, and the moment of inertia equivalent to the input shaft when the AT transmission is in each gear, and calculating the moment of inertia of each divided part according to the equivalent relationship of the moment of inertia of the gear pair. The present invention can not only obtain a more accurate moment of inertia of the AT transmission, but also reduce the calculation amount of the moment of inertia.

Description

Technical Field

[0001] The present invention relates to the technical field, and particularly to a method for modeling an AT transmission, a method and device for equivalent rotational inertia. Background Art

[0002] In a conventional vehicle limit power performance analysis and calculation model, a steady-state model is usually built based on commercial software, ignoring the gear shifting process of the transmission, that is, assuming that the automatic transmission is in a certain fixed gear position and the clutch device is in a certain fixed disengaged or engaged state, and using the rotational inertia of each fixed gear position provided in the transmission specification parameter table.

[0003] In the field of system real-time simulation, there are mainly two existing simulation schemes for transmissions. One is the development of a full-physical system, and the other is pure digital simulation. The development cost of a full-physical system is high, it is particularly inflexible, and the R & D cycle is long; while pure digital simulation is flexible in means, but the difference from the real system may be large.

[0004] The steady-state modeling method is simple and effective, but its disadvantage is that it is difficult to accurately reflect the gear shifting process of a dynamic transmission. Considering that the clutch engagement and gear shifting process of the transmission also require a certain amount of time, and the vehicle state will also change during the clutch engagement and gear shifting process, rather than the vehicle speed remaining unchanged as assumed in automotive theory, it is necessary to dynamically correct the steady-state model, and this part of the calculation can only rely on empirical correction.

[0005] During the driving process of a vehicle including a transmission, the rotational inertia is different when the transmission is in different gear positions. The transmission specification parameter table usually includes the rotational inertia preset for a certain gear position. Most current vehicle models in the industry are static simulation models, that is, the transmission is in a certain fixed gear position and the clutch device is in an engaged or disengaged state. Usually, the rotational inertia of each gear position provided in the transmission variable specification parameter table can meet the requirements of the static simulation model.

[0006] With the gradual improvement of vehicle performance development and the development of simulation technology, the industry has gradually put forward simulation requirements including dynamic processes such as the gear shifting process of the transmission and the engagement and disengagement of the clutch device. Dynamic simulation needs to fully consider the rotational inertia of components.

[0007] The shifting process of an automatic transmission is a dynamic process. The rotational speeds of various components change to a certain extent, and thus there is angular acceleration. Each component has a certain moment of inertia, so dynamic loads are generated during the shifting process. The control of the actuator generally uses the PID control algorithm. During the shifting process of an automatic transmission, the changes in the shaft gears participating in power transmission will cause the equivalent moment of inertia to change accordingly, which deteriorates the performance of the PID control with fixed parameters, and further makes the algorithms of fuzzy, intelligent, and robust control methods more complex and difficult for high-speed and precision motion control. Therefore, the moment of inertia is an important influencing factor in the control of the transmission shifting process. When simulating the shifting process of an automatic transmission, it is necessary to consider the change process of the moment of inertia in different gears, which poses new requirements for dynamic modeling.

[0008] The moment of inertia only depends on the shape of the rigid body, the mass distribution, and the position of the axis of rotation, and is independent of the rotational state of the rigid body around the axis (such as the magnitude of the angular velocity). For a regular-shaped homogeneous rigid body, its moment of inertia can be directly calculated using the formula. For the moment of inertia of an irregular or non-homogeneous rigid body, it is generally measured by experimental methods.

[0009] In the research on the control simulation model of the shifting process, based on the transmission route diagram of the transmission, the moment of inertia of a single part is input into the existing modules of rotating components such as clutches, gears, shafts, and synchronizers provided by the simulation platform.

[0010] An automatic transmission contains multiple rotating components such as input shafts, output shafts, gears, synchronizers, and wet clutches. Although most of them are relatively regular, the number is large. Due to the large number of rotating components that need to be calculated, the calculation amount is large, and detailed component drawings are required for calculation. Usually, only the transmission manufacturers have such conditions, and there is a large dependence on the transmission manufacturers. Summary of the Invention

[0011] Aiming at the defects existing in the prior art, the first aspect of the present invention provides an equivalent method for the moment of inertia of an AT transmission, which can obtain a more accurate moment of inertia of the AT transmission while reducing the calculation amount of the moment of inertia.

[0012] To achieve the above object, the technical solution adopted by the present invention is:

[0013] Obtain the transmission structure of the AT transmission and the distribution of clutches, brakes, and one-way clutches in each gear;

[0014] According to the rotating components related to the clutch, brake, and one-way clutch, with the clutch, brake, or synchronizing element as the demarcation point, divide the moment of inertia of the AT transmission into multiple parts of the moment of inertia;

[0015] Obtain the tooth ratio of the transmission structure of the AT transmission and the corresponding speed ratios on the transmission routes of each gear, as well as the moment of inertia equivalent to the input shaft when the AT transmission is in each gear, and calculate the moment of inertia of each divided part according to the equivalent relationship of the moment of inertia of the gear pair.

[0016] In some embodiments, the moment of inertia of the AT transmission is divided into multiple parts according to the rotating components related to the clutch, brake and one-way clutch, with the clutch, brake or synchronizer as the demarcation point, including:

[0017] Regard the shaft tooth part between the second clutch and the single planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor of the moment of inertia of the AT transmission;

[0018] Regard the shaft tooth part between the first clutch and the single planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor of the moment of inertia of the AT transmission;

[0019] Regard the shaft tooth part between the second clutch and the Ravigneaux compound planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor of the moment of inertia of the AT transmission;

[0020] Regard the shaft tooth part between the first clutch and the Ravigneaux compound planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor of the moment of inertia of the AT transmission;

[0021] Regard the shaft tooth part between the third clutch and the Ravigneaux compound planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor of the moment of inertia of the AT transmission;

[0022] Regard the shaft tooth part between the final drive and the Ravigneaux compound planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor of the moment of inertia of the AT transmission.

[0023] In some embodiments, the obtaining of the tooth ratio of the transmission structure of the AT transmission and the corresponding speed ratios on the transmission routes of each gear, as well as the moment of inertia equivalent to the input shaft when the AT transmission is in each gear, and the calculation of the moment of inertia of each divided part according to the equivalent relationship of the moment of inertia of the gear pair, includes:

[0024] Obtain the tooth speed ratio of the ring gear and the sun gear of the single planetary gear set, the tooth ratios of the ring gear, the large sun gear and the small sun gear of the Ravigneaux compound planetary gear set and the speed ratios of each gear of the AT transmission, as well as the moment of inertia equivalent to the input shaft when the AT transmission is in each gear;

[0025] Express the moment of inertia equivalent to the input shaft when the AT transmission is in each gear using the moment of inertia of each part used as the equivalent factor;

[0026] Calculate the moment of inertia of each part as an equivalent factor according to the moment of inertia of the AT transmission in each gear equivalent to the input shaft.

[0027] In some embodiments, according to the equivalent inertia to the input shaft = the inertia of the output shaft * (the speed ratio between the output shaft and the input shaft) 2 , represent the moment of inertia of the AT transmission in each gear equivalent to the input shaft by using the moment of inertia of each part as an equivalent factor.

[0028] The second aspect of the present invention provides an equivalent device for the moment of inertia of an AT transmission, which can reduce the calculation amount of the moment of inertia while obtaining a more accurate moment of inertia of the AT transmission.

[0029] An equivalent device for the moment of inertia of an AT transmission includes:

[0030] A collection module, which is used to obtain the transmission structure of the AT transmission, the distribution of clutches, brakes and one-way clutches in each gear, the tooth ratio of the AT transmission structure and the corresponding speed ratio on the transmission route of each gear, and the moment of inertia of the AT transmission in each gear equivalent to the input shaft:

[0031] A division module, which is used to divide the moment of inertia of the AT transmission into the moments of inertia of multiple parts according to the rotating components related to the clutch, brake and one-way clutch, with the clutch, brake or synchronizing element as the demarcation point;

[0032] A calculation module, which calculates the moments of inertia of the divided parts according to the tooth ratio of the AT transmission structure, the corresponding speed ratio on the transmission route of each gear, the moment of inertia of the AT transmission in each gear equivalent to the input shaft, and the equivalent relationship of the moment of inertia of the gear pair.

[0033] The third aspect of the present invention provides a modeling method for an AT transmission model applicable to vehicle power performance simulation that can reflect the gear shifting process of the transmission.

[0034] A modeling method for an AT transmission, the method includes a shaft system module modeling step, and the shaft system module modeling step includes:

[0035] Obtain the transmission structure of the AT transmission and the distribution of clutches, brakes and one-way clutches in each gear;

[0036] Divide the moment of inertia of the AT transmission into the moments of inertia of multiple parts according to the rotating components related to the clutch, brake and one-way clutch, with the clutch, brake or synchronizing element as the demarcation point;

[0037] Obtain the tooth ratio of the transmission structure of the AT transmission and the corresponding speed ratios on the transmission routes of each gear, as well as the moment of inertia equivalent to the input shaft when the AT transmission is engaged in each gear, and calculate the moment of inertia of each divided part according to the equivalent relationship of the moment of inertia of the gear pair;

[0038] Build the shafting module according to the power transmission path, the equivalent position of the equivalent moment of inertia, the selection of the speed ratio and the gear position;

[0039] Mount the moment of inertia of each part on the equivalent position of the equivalent moment of inertia.

[0040] In some embodiments, the moment of inertia of the AT transmission is divided into multiple parts according to the rotating components related to the clutch, brake and one-way clutch, with the clutch, brake or synchronizer as the demarcation point, including:

[0041] Regard the shaft tooth part between the second clutch and the single planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor of the moment of inertia of the AT transmission;

[0042] Regard the shaft tooth part between the first clutch and the single planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor of the moment of inertia of the AT transmission;

[0043] Regard the shaft tooth part between the second clutch and the Ravigneaux compound planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor of the moment of inertia of the AT transmission;

[0044] Regard the shaft tooth part between the first clutch and the Ravigneaux compound planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor of the moment of inertia of the AT transmission;

[0045] Regard the shaft tooth part between the third clutch and the Ravigneaux compound planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor of the moment of inertia of the AT transmission;

[0046] Regard the shaft tooth part between the final drive and the Ravigneaux compound planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor of the moment of inertia of the AT transmission.

[0047] In some embodiments, the obtaining of the tooth ratio of the transmission structure of the AT transmission and the corresponding speed ratios on the transmission routes of each gear, as well as the moment of inertia equivalent to the input shaft when the AT transmission is engaged in each gear, and the calculation of the moment of inertia of each divided part according to the equivalent relationship of the moment of inertia of the gear pair, includes:

[0048] Obtain the tooth speed ratio of the ring gear and the sun gear of the single planetary gear set, the tooth number ratios of the ring gear, the large sun gear and the small sun gear of the Ravigneaux compound planetary gear set and the speed ratios of each gear of the AT transmission, as well as the moment of inertia equivalent to the input shaft when the AT transmission is engaged in each gear;

[0049] The rotational inertia equivalent to each gear of the AT transmission on the input shaft is represented by the rotational inertia of each part used as an equivalent factor;

[0050] According to the magnitude of the rotational inertia equivalent to each gear of the AT transmission on the input shaft, calculate the magnitude of the rotational inertia of each part used as an equivalent factor.

[0051] In some embodiments, according to the inertia equivalent to the input shaft = output shaft inertia * (speed ratio between the output shaft and the input shaft) 2 , the rotational inertia equivalent to each gear of the AT transmission on the input shaft is represented by the rotational inertia of each part used as an equivalent factor.

[0052] In some embodiments, it further includes a modeling step of a torque converter module, and the modeling step of the torque converter module includes:

[0053] Obtain the T / C characteristic parameters of the torque converter, and the T / C characteristic parameters include speed ratio, pump impeller torque coefficient, torque coefficient, and transmission efficiency;

[0054] Obtain the rotational inertia of the torque converter;

[0055] Obtain the damping characteristic curve of the torque converter;

[0056] Build a torque converter module according to the T / C characteristic parameters, the rotational inertia of the torque converter, and the damping characteristic curve.

[0057] Compared with the prior art, the advantages of the present invention are:

[0058] The method for equivalent rotational inertia of the AT transmission in the present invention obtains the transmission structure of the AT transmission and the distribution of clutches, brakes, and one-way clutches in each gear; according to the rotating components related to the clutches, brakes, and one-way clutches, taking the clutch, brake, or synchronizing element as the demarcation point, divides the rotational inertia of the AT transmission into multiple parts of rotational inertia; obtains the tooth number ratio of the AT transmission structure and the corresponding speed ratios on the transmission routes of each gear, as well as the rotational inertia equivalent to the input shaft when the AT transmission is in each gear, and calculates the rotational inertia of each divided part according to the equivalent relationship of the rotational inertia of the gear pair. That is, it realizes the AT transmission rotational inertia applicable to dynamic performance simulation based on the conventional transmission specification table and the transmission route schematic diagram, can effectively reduce the problem of difficult to obtain a more accurate equivalent rotational inertia in the process of building a dynamic simulation model using a certain mature AT transmission, reduces the calculation amount, and reduces the dependence on AT manufacturers. BRIEF DESCRIPTION OF THE DRAWINGS

[0059] Figure 1 is a flowchart of the method for equivalent rotational inertia of the AT transmission in an embodiment of the present invention;

[0060] Figure 2 It is a schematic diagram of the shafting module of the AT transmission in the embodiments of the present invention. Detailed implementation manners

[0061] The technical solutions (including the preferred technical solutions) of the present invention will be further described in detail below by means of the accompanying drawings and by listing some optional embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without making creative efforts shall fall within the protection scope of the present invention.

[0062] In the description of the present application, it should be noted that the orientation or positional relationship indicated by terms such as "upper" and "lower" is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as a limitation of the present application. Unless otherwise clearly specified and limited, the terms "installed", "connected" and "connected" shall be understood in a broad sense. For example, it may be a fixed connection, a detachable connection or an integral connection; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, and it may be the internal communication of two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present application can be understood according to specific circumstances.

[0063] Furthermore, in the present application, relational terms such as "first" and "second" are only used to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any actual relationship or sequence between these entities or operations. Moreover, the term "comprising", "including" or any other variant thereof is intended to cover non-exclusive inclusion, so that a process, method, article or device including a series of elements not only includes those elements, but also includes other elements not expressly listed, or also includes elements inherent to such process, method, article or device. Without further limitation, an element defined by the statement "including a..." does not exclude the existence of another identical element in the process, method, article or device including the element.

[0064] It should be noted that an automatic transmission contains multiple rotating components such as multiple input shafts, output shafts, gears, synchronizers, wet clutches, etc. Although most of them are relatively regular, the quantity is large. Taking a certain six-speed AT as an example, it includes 1 single planetary gear set, 1 Ravigneaux compound planetary gear set, 3 clutches, 2 brakes, 1 one-way clutch, and the main reducer gear pair. Each planetary gear set includes at least 1 ring gear, 1 planetary carrier, 3 planet gears, and 3 planetary gear shafts. There are at least more than 40 rotating components whose moments of inertia need to be calculated. The calculation amount is large, and detailed component drawings are required for the calculation. Usually, only the transmission manufacturer has such conditions, and there is a large dependence on the transmission manufacturer.

[0065] To solve the problems existing in the prior art, refer to Figure 1 As shown, an equivalent method for the moment of inertia of an AT transmission according to an embodiment of the present invention is disclosed, and the method includes the following steps:

[0066] S1. Obtain the transmission structure of the AT transmission, and the distribution of clutches, brakes, and one-way clutches in each gear.

[0067] It can be understood that the transmission structure of the AT transmission, and the distribution of clutches, brakes, and one-way clutches in each gear can be determined according to the transmission specification parameter table and the transmission route schematic diagram.

[0068] S2. According to the rotating components related to the clutch, brake, and one-way clutch, taking the clutch, brake, or synchronizing element as the demarcation point, divide the moment of inertia of the AT transmission into the moments of inertia of multiple parts.

[0069] S3. Obtain the tooth ratio of the transmission structure of the AT transmission, the corresponding speed ratios on the transmission routes of each gear, and the moment of inertia equivalent to the input shaft when the AT transmission is engaged in each gear, and calculate the moments of inertia of the divided parts according to the equivalent relationship of the moment of inertia of the gear pair.

[0070] The purpose of the embodiment of the present invention is to equivalent the AT transmission to simplify the calculation of the moment of inertia. For this purpose, each shaft and the components commonly connected to the shaft (including fixed connection and external tooth meshing connection) can be regarded as a whole, and taking the clutch, brake, or synchronizing element as the demarcation point, perform equivalent inertia equivalence. The AT transmission can be divided into multiple parts of equivalent moment of inertia, and equations can be listed and solved in combination with the equivalent moment of inertia of each gear provided in a parameter table of the transmission to obtain the equivalent multiple parts of equivalent moment of inertia.

[0071] The following will be described with a specific example:

[0072] Refer to Figure 2As shown in the figure, the distribution of clutches, brakes, and one-way clutches in each gear of a 6-speed AT transmission is given. It can be understood that the embodiments of the present invention do not limit the structure of the AT transmission. For other types of AT transmissions, the same method can also be used for processing.

[0073] For Figure 2 the AT transmission in , this six-speed AT includes 1 single planetary gear set, 1 Ravigneaux compound planetary gear set, 3 clutches, 2 brakes, 1 one-way clutch, and a final drive gear pair. The 3 clutches are respectively denoted as the first clutch (C-1 clutch), the second clutch (C-2 clutch), and the third clutch (C-3 clutch). The 2 brakes are respectively denoted as the first brake (B-1 brake) and the second brake (B-2 brake). Since the one-way clutch is parallel to the B2 brake and can directly control the B2 brake, the one-way clutch is omitted in the figure.

[0074] Specifically in Figure 2 , when dividing the rotational inertia of the AT transmission into multiple parts of rotational inertia according to the relevant rotating components on the clutches, brakes, and one-way clutches, with the clutch, brake, or synchronizer as the demarcation point, this embodiment of the AT transmission is equivalent to six parts of equivalent rotational inertia, and equations are listed and solved by combining the equivalent rotational inertia of each gear provided in the parameter table of the transmission to obtain these six parts of rotational inertia. The specific process is as follows:

[0075] S21. Regard the shaft gear part between the second clutch and the single planetary gear set as a whole, and use the rotational inertia of this whole as an equivalent factor of the rotational inertia of the AT transmission.

[0076] In this embodiment, the second clutch is a clutch connected to the Ravigneaux compound planetary gear set through the planet carrier. The rotational inertia of this part is denoted as J C21 , and is called the input shaft inertia.

[0077] S22. Regard the shaft gear part between the first clutch and the single planetary gear set as a whole, and use the rotational inertia of this whole as an equivalent factor of the rotational inertia of the AT transmission.

[0078] In this embodiment, the first clutch is a clutch connected to the Ravigneaux compound planetary gear set through the sun gear. The rotational inertia of this part is denoted as J C11C31 , and is called the C1, C3 inertia.

[0079] S23. Regard the shaft gear part between the second clutch and the Ravigneaux compound planetary gear set as a whole, and use the rotational inertia of this whole as an equivalent factor of the rotational inertia of the AT transmission.

[0080] In this embodiment, the rotational inertia of this part is denoted as J C22B2, which is called the inertia of C2 and B2.

[0081] S24. Regard the shaft gear part between the first clutch and the Ravigneaux compound planetary gear set as a whole, and take the moment of inertia of this whole as the equivalent factor of the moment of inertia of the AT transmission.

[0082] In this embodiment, the moment of inertia of this part is denoted as J C12 , which is called the inertia of C1.

[0083] S25. Regard the shaft gear part between the third clutch and the Ravigneaux compound planetary gear set as a whole, and take the moment of inertia of this whole as the equivalent factor of the moment of inertia of the AT transmission.

[0084] In this embodiment, the third clutch is the clutch connected to the Ravigneaux compound planetary gear set through the large sun gear, and the moment of inertia of this part is denoted as J C32B1 , which is called the inertia of C3 and B1.

[0085] S26. Regard the shaft gear part between the final drive and the Ravigneaux compound planetary gear set as a whole, and take the moment of inertia of this whole as the equivalent factor of the moment of inertia of the AT transmission.

[0086] In this embodiment, the moment of inertia of this part is denoted as J out , which is called the output shaft inertia.

[0087] After the equivalent division of the moment of inertia of the AT transmission is completed, the moment of inertia of each divided part can be calculated according to the tooth ratio of the AT transmission structure, the corresponding speed ratios on the transmission routes of each gear, and the equivalent relationship of the moment of inertia of the gear pair. The specific process is as follows:

[0088] S31. Obtain the tooth speed ratio of the ring gear and the sun gear of a single planetary gear set, the tooth ratios of the ring gear of the Ravigneaux compound planetary gear set to the large sun gear and the small sun gear, the speed ratios of each gear of the AT transmission, and the moment of inertia equivalent to the input shaft when the AT transmission is in each gear.

[0089] For Figure 2 the AT transmission in, the speed ratios of its sixth gear are respectively denoted as: i1, i2, i3, i4, i5, i6; let the tooth ratio of the ring gear to the sun gear of a single planetary gear set be k1, and the tooth ratio of the ring gear of the Ravigneaux compound planetary gear set to the large sun gear be k 21 , and the tooth ratio of the ring gear of the Ravigneaux compound planetary gear set to the small sun gear be k 22 , then the speed ratios of each gear are:

[0090]

[0091]

[0092]

[0093]

[0094]

[0095]

[0096] S32. The rotational inertia of the AT transmission in each gear equivalent to the input shaft is represented by the rotational inertia of each part used as the equivalent factor.

[0097] In this embodiment, according to the equivalent inertia to the input shaft = output shaft inertia * (speed ratio between the output shaft and the input shaft) 2 , the rotational inertia of the AT transmission input shaft in each gear is represented by the rotational inertia of each part used as the equivalent factor.

[0098] S33. Calculate the magnitudes of the rotational inertias of the respective parts used as the equivalent factor based on the magnitude of the rotational inertia of the AT transmission in each gear equivalent to the input shaft.

[0099] For Figure 2 the AT transmission in

[0100]

[0101]

[0102]

[0103]

[0104]

[0105]

[0106]

[0107] The rotational inertias J1, J2, J3, J4, J5, J6, and J R of the AT transmission in each gear equivalent to the input shaft in the above formula can be obtained from the specification parameter table in the AT transmission, and then can be substituted into the above system of equations to solve for J C21 , J C11C31 , J C22B2 , J C12 , J C32B1 and J out . Thus, the equivalent process of the rotational inertia of the AT transmission is completed.

[0108] In summary, for the AT transmission inertia equivalent method in the present invention, the transmission structure of the AT transmission and the distribution of clutches, brakes, and one-way clutches in each gear are obtained; according to the rotating components related to the clutches, brakes, and one-way clutches, with the clutch, brake, or synchronizer as the demarcation point, the AT transmission inertia is divided into multiple parts of inertia; the tooth ratio of the AT transmission structure, the corresponding speed ratios on the transmission routes of each gear, and the inertia equivalent to the input shaft when the AT transmission is engaged in each gear are obtained, and the inertia of each divided part is calculated according to the gear pair inertia equivalent relationship. That is, the AT transmission inertia applicable to dynamic performance simulation is obtained based on the conventional transmission specification table and the transmission route schematic diagram, which can effectively solve the problem of difficult to obtain a relatively accurate equivalent inertia during the process of building a dynamic simulation model using a certain mature AT transmission, reduce the calculation amount, and reduce the dependence on AT manufacturers.

[0109] At the same time, the embodiment of the present invention also provides an AT transmission inertia equivalent device, which includes a collection module, a division module, and a calculation module.

[0110] Among them, the collection module is used to obtain the transmission structure of the AT transmission, the distribution of clutches, brakes, and one-way clutches in each gear, the tooth ratio of the AT transmission structure, the corresponding speed ratios on the transmission routes of each gear, and the inertia equivalent to the input shaft when the AT transmission is engaged in each gear. The division module is used to divide the AT transmission inertia into multiple parts of inertia according to the rotating components related to the clutches, brakes, and one-way clutches, with the clutch, brake, or synchronizer as the demarcation point. The calculation module calculates the inertia of each divided part according to the tooth ratio of the AT transmission structure, the corresponding speed ratios on the transmission routes of each gear, the inertia equivalent to the input shaft when the AT transmission is engaged in each gear, and the gear pair inertia equivalent relationship.

[0111] In some embodiments, the division module divides the AT transmission inertia into multiple parts of inertia according to the rotating components related to the clutches, brakes, and one-way clutches, with the clutch, brake, or synchronizer as the demarcation point, including:

[0112] Regarding the shaft teeth part between the second clutch and the single planetary row as a whole, and taking the inertia of this whole as the equivalent factor of the AT transmission inertia;

[0113] Regarding the shaft teeth part between the first clutch and the single planetary row as a whole, and taking the inertia of this whole as the equivalent factor of the AT transmission inertia;

[0114] Regard the shaft gear part between the second clutch and the Ravigneaux compound planetary gear set as a whole, and take the moment of inertia of this whole as the equivalent factor of the AT transmission's moment of inertia;

[0115] Regard the shaft gear part between the first clutch and the Ravigneaux compound planetary gear set as a whole, and take the moment of inertia of this whole as the equivalent factor of the AT transmission's moment of inertia;

[0116] Regard the shaft gear part between the third clutch and the Ravigneaux compound planetary gear set as a whole, and take the moment of inertia of this whole as the equivalent factor of the AT transmission's moment of inertia;

[0117] Regard the shaft gear part between the final drive and the Ravigneaux compound planetary gear set as a whole, and take the moment of inertia of this whole as the equivalent factor of the AT transmission's moment of inertia.

[0118] In some embodiments, the calculation module obtains the tooth number ratio of the AT transmission's transmission structure and the corresponding speed ratios on each gear transmission route, and calculates the moment of inertia of each divided part according to the equivalent relationship of the moment of inertia of the gear pair, including:

[0119] Obtain the tooth speed ratio between the ring gear and the sun gear of a single planetary gear set, the tooth number ratios between the ring gear of the Ravigneaux compound planetary gear set and the large sun gear and the small sun gear, and the speed ratios of each gear of the AT transmission;

[0120] Express the moment of inertia of the AT transmission's input shaft in each gear using the moments of inertia of the respective parts used as equivalent factors;

[0121] Calculate the magnitudes of the moments of inertia of the respective parts used as equivalent factors according to the magnitudes of the moments of inertia of the AT transmission's input shaft in each gear.

[0122] Further, the calculation module is based on the equivalent inertia to the input shaft = output shaft inertia * (speed ratio between the output shaft and the input shaft) 2 , and express the moments of inertia of the AT transmission in each gear equivalent to the input shaft using the moments of inertia of the respective parts used as equivalent factors.

[0123] In summary, the AT transmission inertia equivalent device in the present invention obtains the transmission structure of the AT transmission, as well as the distribution of clutches, brakes, and one-way clutches in each gear; according to the rotating components related to the clutches, brakes, and one-way clutches, with the clutch, brake, or synchronizer as the demarcation point, divides the AT transmission inertia into multiple parts of inertia; obtains the tooth ratio of the AT transmission structure and the corresponding speed ratios on the transmission routes of each gear, as well as the inertia equivalent to the input shaft when the AT transmission is in each gear, and calculates the inertia of each divided part according to the inertia equivalent relationship of the gear pair. That is, it realizes the AT transmission inertia applicable to dynamic performance simulation based on the conventional transmission specification table and the transmission route schematic diagram, effectively reduces the problem of difficult to obtain a relatively accurate equivalent inertia during the process of building a dynamic simulation model using a certain mature AT transmission, reduces the calculation amount, and reduces the dependence on AT manufacturers.

[0124] Meanwhile, the present invention also provides an AT transmission modeling method, which mainly involves a torque converter module, a shafting module, and a shifting mechanism module.

[0125] Among them, the modeling steps of the shafting module include:

[0126] Obtain the transmission structure of the AT transmission, as well as the distribution of clutches, brakes, and one-way clutches in each gear;

[0127] According to the rotating components related to the clutches, brakes, and one-way clutches, with the clutch, brake, or synchronizer as the demarcation point, divide the AT transmission inertia into multiple parts of inertia;

[0128] Obtain the tooth ratio of the AT transmission structure and the corresponding speed ratios on the transmission routes of each gear, as well as the inertia equivalent to the input shaft when the AT transmission is in each gear, and calculate the inertia of each divided part according to the inertia equivalent relationship of the gear pair;

[0129] Build the shafting module according to the power transmission path, the equivalent position of the equivalent inertia, the selection of speed ratio and gear;

[0130] Mount the inertia of each part on the equivalent position of the equivalent inertia.

[0131] In some embodiments, the step of dividing the AT transmission inertia into multiple parts of inertia according to the rotating components related to the clutches, brakes, and one-way clutches, with the clutch, brake, or synchronizer as the demarcation point, includes:

[0132] Regard the shaft teeth part between the second clutch and the single planetary gear set as a whole, and take the inertia of this whole as the equivalent factor of the AT transmission inertia;

[0133] Regard the shaft gear part between the first clutch and the single planetary gear set as a whole, and take the moment of inertia of this whole as the equivalent factor of the moment of inertia of the AT transmission.

[0134] Regard the shaft gear part between the second clutch and the Ravigneaux compound planetary gear set as a whole, and take the moment of inertia of this whole as the equivalent factor of the moment of inertia of the AT transmission.

[0135] Regard the shaft gear part between the first clutch and the Ravigneaux compound planetary gear set as a whole, and take the moment of inertia of this whole as the equivalent factor of the moment of inertia of the AT transmission.

[0136] Regard the shaft gear part between the third clutch and the Ravigneaux compound planetary gear set as a whole, and take the moment of inertia of this whole as the equivalent factor of the moment of inertia of the AT transmission.

[0137] Regard the shaft gear part between the final drive and the Ravigneaux compound planetary gear set as a whole, and take the moment of inertia of this whole as the equivalent factor of the moment of inertia of the AT transmission.

[0138] In some embodiments, obtain the tooth ratio of the AT transmission's transmission structure, the corresponding speed ratios on the transmission routes of each gear, and the moment of inertia equivalent to the input shaft when the AT transmission is in each gear, and calculate the moment of inertia of each divided part according to the equivalent relationship of the moment of inertia of the gear pair, including:

[0139] Obtain the tooth speed ratio between the ring gear and the sun gear of the single planetary gear set, the tooth ratios of the ring gear, the large sun gear and the small sun gear of the Ravigneaux compound planetary gear set and the speed ratios of each gear of the AT transmission, and the moment of inertia equivalent to the input shaft when the AT transmission is in each gear;

[0140] Express the moment of inertia equivalent to the input shaft when the AT transmission is in each gear in terms of the moment of inertia of each part used as the equivalent factor;

[0141] Calculate the magnitude of the moment of inertia of each part used as the equivalent factor according to the magnitude of the moment of inertia equivalent to the input shaft when the AT transmission is in each gear.

[0142] Further, according to the equivalent inertia to the input shaft = output shaft inertia * (speed ratio between the output shaft and the input shaft) 2 , express the moment of inertia equivalent to the input shaft when the AT transmission is in each gear in terms of the moment of inertia of each part used as the equivalent factor.

[0143] See Figure 2As shown, taking the above six-speed AT transmission as an example, after determining the moment of inertia of each part, the shafting module can be built according to the power transmission path, the equivalent position of the equivalent moment of inertia, the selection of the speed ratio and the gear position, and then the moment of inertia of each part can be mounted on the equivalent position of the equivalent moment of inertia. That is Figure 2 the input shaft inertia, the C1 and C3 inertias, the C2 and B2 inertias, the C1 inertia, the C3 and B1 inertias, and the output shaft inertia. Thus, the construction of the shafting module is completed. In some preferred embodiments, the AT efficiency module is also designed considering the shafting efficiency MAP. The AT efficiency module reflects the transmission efficiency of the AT under various working conditions such as temperature and speed. It is not a fixed value and can reflect the transmission efficiency under different working conditions, which is closer to the actual situation in terms of the accuracy of the model.

[0144] For the torque converter module, its modeling steps include:

[0145] Obtain the T / C characteristic parameters of the torque converter, where the T / C characteristic parameters include the speed ratio, the pump impeller torque coefficient, the torque coefficient, and the transmission efficiency;

[0146] Obtain the moment of inertia of the torque converter;

[0147] Obtain the damping characteristic curve of the torque converter;

[0148] Build the torque converter module according to the T / C characteristic parameters, the moment of inertia of the torque converter, and the damping characteristic curve.

[0149] For the shift mechanism module, it mainly obtains the shafting gear position change command and the gear position signal for modeling, which is well-known to those skilled in the art and will not be elaborated in the embodiments of the present invention. After that, by integrating the torque converter module, the shafting module, and the shift mechanism module, the modeling of the AT transmission can be completed.

[0150] In summary, the present invention proposes a modeling method for an AT transmission model applicable to vehicle power performance simulation that can reflect the gearshift process of the transmission. It divides the moment of inertia of the AT transmission into multiple parts of the moment of inertia to build the shafting module, effectively solving the problem of difficultly obtaining a more accurate equivalent moment of inertia in the process of building a dynamic simulation model using a certain mature AT transmission.

[0151] The above are only specific embodiments of the present application, enabling those skilled in the art to understand or implement the present application. Various modifications to these embodiments will be obvious to those skilled in the art, and the general principles defined herein can be implemented in other embodiments without departing from the spirit or scope of the present application. Therefore, the present application will not be limited to these embodiments shown herein, but rather will be accorded the widest scope consistent with the principles and novel features claimed herein.

Claims

1. An equivalent method for the moment of inertia of an AT transmission, characterized in that The method includes the following steps: Obtain the transmission structure of the AT transmission, as well as the distribution of clutches, brakes, and one-way clutches for each gear; According to the rotating components related to the clutches, brakes, and one-way clutches, and taking the clutch, brake, or synchronizer as the demarcation point, divide the rotational inertia of the AT transmission into multiple parts of rotational inertia; Obtain the tooth ratio of the transmission structure of the AT transmission, the corresponding speed ratios on the transmission routes for each gear, and the rotational inertia equivalent to the input shaft when the AT transmission is in each gear, and calculate the rotational inertia of each divided part according to the equivalent relationship of the rotational inertia of the gear pair; The step of dividing the rotational inertia of the AT transmission into multiple parts of rotational inertia according to the rotating components related to the clutches, brakes, and one-way clutches, and taking the clutch, brake, or synchronizer as the demarcation point, includes: Regard the shaft gear part between the second clutch and the single planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor J of the moment of inertia of the AT transmission C21 ; Regard the shaft gear part between the first clutch and the single planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor J of the moment of inertia of the AT transmission C11C31 ; Regard the shaft gear part between the second clutch and the Ravigneaux compound planetary gear set as a whole, and take the moment of inertia of this whole as the equivalent factor J of the moment of inertia of the AT transmission C22B2 ; Regard the shaft gear part between the first clutch and the Ravigneaux compound planetary gear set as a whole, and take the moment of inertia of this whole as the equivalent factor J of the moment of inertia of the AT transmission C12 ; Regard the shaft gear part between the third clutch and the Ravigneaux compound planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor J of the moment of inertia of the AT transmission C32B1 ; Regard the shaft gear part between the main reducer and the Ravigneaux compound planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor J of the moment of inertia of the AT transmission out ; The step of obtaining the tooth ratio of the transmission structure of the AT transmission, the corresponding speed ratios on the transmission routes for each gear, and the rotational inertia equivalent to the input shaft when the AT transmission is in each gear, and calculating the rotational inertia of each divided part according to the equivalent relationship of the rotational inertia of the gear pair, includes: Obtain the tooth speed ratio k1 of the ring gear and the sun gear of the single planetary gear set, the tooth speed ratio k 21 of the ring gear and the large sun gear of the Ravigneaux compound planetary gear set, and the tooth number ratio k 22， of the ring gear and the small sun gear of the Ravigneaux compound planetary gear set, as well as the gear ratios of each gear of the AT transmission, and the gear ratios of the sixth gear are denoted as i1, i2, i3, i4, i5, i6 respectively, and the moments of inertia J1, J2, J3, J4, J5, J6 equivalent to the input shaft when the AT transmission is engaged in each gear; The speed ratios for each gear are: Express the rotational inertia equivalent to the input shaft when the AT transmission is in each gear using the rotational inertia of each part as the equivalent factor; Calculate the magnitude of the rotational inertia of each part as the equivalent factor according to the magnitude of the rotational inertia equivalent to the input shaft when the AT transmission is in each gear; The magnitude of the rotational inertia equivalent to the input shaft when the AT transmission is in each gear is specifically expressed as:

2. An equivalent device for the moment of inertia of an AT transmission, characterized in that, Including: A collection module for obtaining the transmission structure of the AT transmission, the distribution of clutches, brakes, and one-way clutches for each gear, the tooth ratio of the transmission structure of the AT transmission, the corresponding speed ratios on the transmission routes for each gear, and the rotational inertia equivalent to the input shaft when the AT transmission is in each gear; A division module for dividing the rotational inertia of the AT transmission into multiple parts of rotational inertia according to the rotating components related to the clutches, brakes, and one-way clutches, and taking the clutch, brake, or synchronizer as the demarcation point; A calculation module for calculating the rotational inertia of each divided part according to the tooth ratio of the transmission structure of the AT transmission, the corresponding speed ratios on the transmission routes for each gear, the rotational inertia equivalent to the input shaft when the AT transmission is in each gear, and the equivalent relationship of the rotational inertia of the gear pair; The step of dividing the rotational inertia of the AT transmission into multiple parts of rotational inertia according to the rotating components related to the clutches, brakes, and one-way clutches, and taking the clutch, brake, or synchronizer as the demarcation point, includes: Regard the shaft gear part between the second clutch and the single planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor J of the moment of inertia of the AT transmission C21 ; Regard the shaft gear part between the first clutch and the single planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor J of the moment of inertia of the AT transmission C11C31 ; Regard the shaft gear part between the second clutch and the Ravigneaux compound planetary gear set as a whole, and take the moment of inertia of this whole as the equivalent factor J of the moment of inertia of the AT transmission C22B2 ; Regard the shaft gear part between the first clutch and the Ravigneaux compound planetary gear set as a whole, and take the moment of inertia of this whole as the equivalent factor J of the moment of inertia of the AT transmission C12 ; Regard the shaft gear part between the third clutch and the Ravigneaux compound planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor J of the moment of inertia of the AT transmission C32B1 ; Regard the shaft gear part between the main reducer and the Ravigneaux compound planetary gear set as a whole, and take the moment of inertia of this whole as the equivalent factor J of the moment of inertia of the AT transmission out ; The step of obtaining the tooth ratio of the transmission structure of the AT transmission, the corresponding speed ratios on the transmission routes for each gear, and the rotational inertia equivalent to the input shaft when the AT transmission is in each gear, and calculating the rotational inertia of each divided part according to the equivalent relationship of the rotational inertia of the gear pair, includes: Obtain the tooth speed ratio k1 of the single planetary gear ring and the sun gear, and the tooth number ratios k 21 of the Ravigneaux compound planetary gear ring and the large sun gear, and the tooth number ratio k 22， of the Ravigneaux compound planetary gear ring and the small sun gear, as well as the gear ratios of each gear of the AT transmission, with the gear ratios of the sixth gear denoted as i1, i2, i3, i4, i5, i6 respectively, and the moments of inertia J1, J2, J3, J4, J5, J6 equivalent to the input shaft when the AT transmission is engaged in each gear; The speed ratios for each gear are: Express the rotational inertia equivalent to the input shaft when the AT transmission is in each gear using the rotational inertia of each part as the equivalent factor; Calculate the magnitude of the rotational inertia of each part as the equivalent factor according to the magnitude of the rotational inertia equivalent to the input shaft when the AT transmission is in each gear; The rotational inertia equivalent to the input shaft when the AT transmission is in each gear is specifically expressed as:

3. A modeling method for an AT transmission, characterized in that, This method includes the steps of modeling the shafting module, and the steps of modeling the shafting module include: Obtain the transmission structure of the AT transmission, as well as the distribution of clutches, brakes, and one-way clutches in each gear; According to the rotating components related to the clutches, brakes, and one-way clutches, with the clutch, brake, or synchronizer as the demarcation point, divide the rotational inertia of the AT transmission into multiple parts of rotational inertia; Obtain the tooth ratio of the transmission structure of the AT transmission, the corresponding speed ratios on the transmission routes of each gear, and the rotational inertia equivalent to the input shaft when the AT transmission is in each gear, and calculate the rotational inertia of each divided part according to the equivalent relationship of the rotational inertia of the gear pair; Build the shafting module according to the power transmission path, the equivalent position of the equivalent rotational inertia, the speed ratio, and the selection of gears; Mount the rotational inertia of each part at the equivalent position of the equivalent rotational inertia; The step of dividing the rotational inertia of the AT transmission into multiple parts of rotational inertia according to the rotating components related to the clutches, brakes, and one-way clutches, with the clutch, brake, or synchronizer as the demarcation point, includes: Regard the shaft gear part between the second clutch and the single planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor J of the moment of inertia of the AT transmission C21 ; Regard the shaft gear part between the first clutch and the single planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor J of the moment of inertia of the AT transmission C11C31 ; Regard the shaft gear part between the second clutch and the Ravigneaux compound planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor J of the moment of inertia of the AT transmission C22B2 ; Regard the shaft gear part between the first clutch and the Ravigneaux compound planetary gear set as a whole, and use the moment of inertia of this whole as the equivalent factor J of the moment of inertia of the AT transmission C12 ; Regard the shaft gear part between the third clutch and the Ravigneaux compound planetary gear set as a whole, and take the moment of inertia of this whole as the equivalent factor J of the moment of inertia of the AT transmission C32B1 ; Regard the shaft gear part between the main reducer and the Ravigneaux compound planetary gear set as a whole, and take the moment of inertia of this whole as the equivalent factor J of the moment of inertia of the AT transmission out ; The step of obtaining the tooth ratio of the transmission structure of the AT transmission, the corresponding speed ratios on the transmission routes of each gear, and the rotational inertia equivalent to the input shaft when the AT transmission is in each gear, and calculating the rotational inertia of each divided part according to the equivalent relationship of the rotational inertia of the gear pair, includes: Obtain the tooth speed ratio k1 of the ring gear and the sun gear of the single planetary gear train, and the tooth number ratios k 21 of the ring gear of the Ravigneaux compound planetary gear train and the large sun gear, and the tooth number ratio k 22， of the ring gear of the Ravigneaux compound planetary gear train and the small sun gear, as well as the gear ratios of each gear of the AT transmission. The gear ratios of its sixth gear are denoted as i1, i2, i3, i4, i5, i6 respectively, and the moments of inertia J1, J2, J3, J4, J5, J6 equivalent to the input shaft when the AT transmission is engaged in each gear; The speed ratio of each gear is: The rotational inertia equivalent to the input shaft when the AT transmission is in each gear is expressed by the rotational inertia of each part used as an equivalent factor; Calculate the magnitude of the rotational inertia of each part used as an equivalent factor according to the magnitude of the rotational inertia equivalent to the input shaft when the AT transmission is in each gear; The rotational inertia equivalent to the input shaft when the AT transmission is in each gear is specifically expressed as:

4. The AT transmission modeling method according to claim 3, wherein It also includes the steps of modeling the torque converter module, and the steps of modeling the torque converter module include: Obtain the T / C characteristic parameters of the torque converter, and the T / C characteristic parameters include the speed ratio, pump impeller torque coefficient, torque coefficient, and transmission efficiency; Obtain the rotational inertia of the torque converter; Obtain the damping characteristic curve of the torque converter; Build the torque converter module according to the T / C characteristic parameters, the rotational inertia of the torque converter, and the damping characteristic curve.

Images