Hybrid drive device, control method, and vehicle

Abstract

The present invention provides a hybrid transmission device, a control method and a vehicle. The transmission device includes: a first planetary gear set, which includes a first planet carrier, a first planet gear, a first external gear ring and a first sun gear. The first sun gear is connected to a braking component, and both the first external gear ring and the first sun gear are connected to an engine or a motor through a clutch component. The first planet carrier is connected to an output shaft; a second planetary gear set, which includes a second planet carrier, a second planet gear, a second external gear ring and a second sun gear. The second external gear ring is connected to the braking component, and the second sun gear is connected to the engine or the motor through a clutch component. The second planet carrier is connected to the output shaft; the second sun gear is rigidly connected to the first external gear ring, and the second planet carrier is rigidly connected to the first planet carrier. The above structure realizes multi-gear power transmission and multi-power drive modes to meet the actual working conditions or actual requirements, which is beneficial to comprehensively reducing energy consumption.

Description

Technical Field

[0001] The present invention relates to the technical field of vehicle transmissions, and in particular, to a hybrid transmission device, a control method, and a vehicle. Background Art

[0002] With the continuous improvement of the awareness of energy conservation and emission reduction, conventional power vehicles are difficult to meet people's needs due to structural limitations. As a new type of vehicle power, hybrid vehicles are in a booming development stage in terms of technology and market, and the hybrid vehicle drive device occupies an extremely important position.

[0003] Currently, hybrid transmissions are restricted by their structures, with a single structure. The adjustment of vehicle speed and load capacity depends entirely on the motor, which requires a high level of motor technology. The hybrid mode is single, the number of gears is single, and the comprehensive fuel-saving rate is low, resulting in a relatively high comprehensive cost.

[0004] In view of the above problems, no effective solution has been proposed yet. Summary of the Invention

[0005] The main objective of the present invention is to provide a hybrid transmission device, a control method, and a vehicle to solve the technical problems of single hybrid mode, single gear, and low fuel-saving rate in the existing hybrid transmission structure.

[0006] To achieve the above objective, according to one aspect of the present invention, a hybrid transmission device is provided, which includes an engine and a motor, and further includes: a first planetary gear set, the first planetary gear set including a first planet carrier, first planet gears, a first external gear ring, and a first sun gear, the first sun gear being connected to a braking component, both the first external gear ring and the first sun gear being connected to the engine or the motor through a clutch component, the first planet carrier being connected to an output shaft; a second planetary gear set, the second planetary gear set including a second planet carrier, second planet gears, a second external gear ring, and a second sun gear, the second external gear ring being connected to the braking component, the second sun gear being connected to the engine or the motor through a clutch component, the second planet carrier being connected to the output shaft; wherein, the second sun gear is rigidly connected to the first external gear ring, and the second planet carrier is rigidly connected to the first planet carrier.

[0007] Furthermore, the clutch component includes: a first clutch, a first end of the first clutch being connected to the motor, a second end of the first clutch being connected to the engine through an input shaft; a second clutch, a first end of the second clutch being connected to the motor, a second end of the second clutch being connected to the first sun gear through a second intermediate shaft; a third clutch, a first end of the third clutch being connected to the engine through the input shaft, a second end of the third clutch being connected to the first external gear ring or the second sun gear through a first intermediate shaft; wherein, the third clutch is connected in series on the input shaft, and the third clutch is located between the first clutch and the engine.

[0008] Further, the braking assembly includes: a first brake, which is connected to the second external gear ring; a second brake, which is connected to the first sun gear; wherein, the first brake and the second brake are independent of each other.

[0009] According to another aspect of the present invention, there is provided a control method for a hybrid power transmission device, the hybrid power transmission device being the above-mentioned hybrid power transmission device, and the control method includes: obtaining a first working state of the clutch assembly, wherein the first working state includes at least one of the following: the first external gear ring and the second sun gear are connected to the engine, the first external gear ring and the second sun gear are connected to the motor, the first sun gear is connected to the engine, and the first sun gear is connected to the motor; obtaining a second working state of the braking assembly, wherein the second working state includes at least one of the following: the first sun gear is in a locked state, the second external gear ring is in a locked state, and both the first sun gear and the second external gear ring are in an unlocked state; based on the first working state and the second working state, starting at least one of the engine and the motor to achieve kinetic energy transfer.

[0010] Further, based on the first working state and the second working state, starting at least one of the engine and the motor to achieve kinetic energy transfer includes: when the second external gear ring is in a locked state and the first external gear ring and the second sun gear are connected to the engine, starting the engine, and the second planet carrier drives the output shaft to rotate to achieve the first gear transmission of the engine; when the first sun gear is in a locked state and the first external gear ring and the second sun gear are connected to the engine, starting the engine, and the first planet carrier drives the output shaft to rotate to achieve the second gear transmission of the engine; when both the first sun gear and the second external gear ring are in an unlocked state, the first sun gear is connected to the engine, and the first external gear ring and the second sun gear are connected to the engine, starting the engine, and the first planet carrier drives the output shaft to rotate to achieve the third gear transmission of the engine.

[0011] Further, based on the first working state and the second working state, starting at least one of the engine and the motor to achieve kinetic energy transfer further includes: when the second external gear ring is in a locked state and the first external gear ring and the second sun gear are connected to the motor, starting the motor, and the second planet carrier drives the output shaft to rotate to achieve the first gear transmission of the motor; when the first sun gear is in a locked state and the first external gear ring and the second sun gear are connected to the motor, starting the motor, and the first planet carrier drives the output shaft to rotate to achieve the second gear transmission of the motor; when both the first sun gear and the second external gear ring are in an unlocked state, the first sun gear is connected to the motor, and the first external gear ring and the second sun gear are connected to the motor, starting the motor, and the first planet carrier drives the output shaft to rotate to achieve the third gear transmission of the motor.

[0012] Further, based on the first working state and the second working state, at least one of the engine and the motor is turned on to achieve kinetic energy transfer, and it further includes: when the second external gear ring is in a locked state and the first external gear ring and the second sun gear are simultaneously connected to the motor and the engine, the motor and the engine are turned on simultaneously, and the second planetary carrier drives the output shaft to rotate to achieve parallel first-gear transmission; when the first sun gear is in a locked state and the first external gear ring and the second sun gear are simultaneously connected to the motor and the engine, the motor and the engine are turned on simultaneously, and the first planetary carrier drives the output shaft to rotate to achieve parallel second-gear transmission; when both the first sun gear and the second external gear ring are in an unlocked state, the first sun gear is simultaneously connected to the motor and the engine, and the first external gear ring and the second sun gear are simultaneously connected to the motor and the engine, the motor and the engine are turned on simultaneously, and the first planetary carrier drives the output shaft to rotate to achieve parallel third-gear transmission.

[0013] Further, based on the first working state and the second working state, at least one of the engine and the motor is turned on to achieve kinetic energy transfer, and it further includes: when both the first sun gear and the second external gear ring are in an unlocked state, the first sun gear is connected to the motor, and the first external gear ring and the second sun gear are connected to the engine, the motor and the engine are turned on simultaneously, and the first planetary carrier drives the output shaft to rotate to achieve continuously variable transmission.

[0014] Further, based on the first working state and the second working state, at least one of the engine and the motor is turned on to achieve kinetic energy transfer, and it further includes: when the second external gear ring is in a locked state and the first sun gear is connected to the motor, the motor is turned on, and the first planetary carrier and the second planetary carrier drive the output shaft to rotate simultaneously to achieve reverse gear transmission.

[0015] According to another aspect of the present invention, a vehicle is provided, including a hybrid power transmission device, and the hybrid power transmission device is the above-mentioned hybrid power transmission device.

[0016] Applying the technical solution of the present invention, the first external gear ring of the first planetary gear set is rigidly connected to the second sun gear of the second planetary gear set, and the second planetary carrier of the second planetary gear set is rigidly connected to the first planetary carrier of the first planetary gear set. The first sun gear and the second external gear ring are connected to the braking component. Both the first planetary gear set and the second planetary gear set are connected to the engine or the motor through the clutch component. The two planetary gear sets and the connection relationship between the planetary gear sets, in cooperation with the clutch component and the braking component, realize multi-gear power transmission of the engine, multi-gear power transmission of the motor, and combined multi-gear power transmission of the engine and the motor to meet the actual working conditions or actual needs, which is beneficial to comprehensively reducing energy consumption. Description of the Drawings

[0017] The accompanying drawings of the specification, which form a part of the present application, are used to provide a further understanding of the present invention. The schematic embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the drawings:

[0018] Figure 1 shows a schematic structural diagram of an embodiment of a hybrid powertrain according to the present invention;

[0019] Figure 2 shows a flowchart of a control method for a hybrid powertrain in the present invention;

[0020] Figure 3 shows a driving mode diagram of a hybrid powertrain in the present invention;

[0021] Figure 4 shows a schematic diagram of the power transmission path of the engine in the first gear in the present invention;

[0022] Figure 5 shows a schematic diagram of the power transmission path of the engine in the second gear in the present invention;

[0023] Figure 6 shows a schematic diagram of the power transmission path of the engine in the third gear in the present invention;

[0024] Figure 7 shows a schematic diagram of the power transmission path of the motor in the first gear in the present invention;

[0025] Figure 8 shows a schematic diagram of the power transmission path of the motor in the second gear in the present invention;

[0026] Figure 9 shows a schematic diagram of the power transmission path of the motor in the third gear in the present invention;

[0027] Figure 10 shows a schematic diagram of the power transmission path of the parallel first gear in the present invention;

[0028] Figure 11 shows a schematic diagram of the power transmission path of the parallel second gear in the present invention;

[0029] Figure 12 shows a schematic diagram of the power transmission path of the parallel third gear in the present invention;

[0030] Figure 13 shows a schematic diagram of the power transmission path of the continuously variable transmission gear in the present invention;

[0031] Figure 14 shows a schematic diagram of the power transmission path of the reverse gear in the present invention;

[0032] Figure 15Shows the schematic diagram of the power transmission path for parking power generation in the present invention;

[0033] Figure 16 Shows the gear composition diagram of the engine gear and the continuously variable transmission gear in the present invention;

[0034] Figure 17 Shows the gear composition diagram of the motor gear and the reverse gear in the present invention;

[0035] Figure 18 Shows the gear composition diagram of the parallel gear in the present invention.

[0036] Among them, the above-mentioned drawings include the following reference numerals:

[0037] 11. First planet carrier; 12. First planet gear; 13. First external gear ring; 14. First sun gear;

[0038] 21. Second planet carrier; 22. Second planet gear; 23. Second external gear ring; 24. Second sun gear;

[0039] 31. First clutch; 32. Second clutch; 33. Third clutch;

[0040] 41. First brake; 42. Second brake;

[0041] 50. Engine;

[0042] 60. Motor;

[0043] 71. Output shaft; 72. Input shaft; 73. First intermediate shaft; 74. Second intermediate shaft. Detailed implementation manners

[0044] It should be noted that, without conflict, the embodiments in the present application and the features in the embodiments can be combined with each other. The present invention will be described in detail below with reference to the drawings and in combination with the embodiments.

[0045] It should be noted that the terms used herein are only for describing the specific implementation manners and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular forms are also intended to include the plural forms. In addition, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0046] It should be noted that the terms "first", "second", etc. in the description, claims and the above-mentioned drawings of this application are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that such terms can be interchanged under appropriate circumstances, so that the embodiments of the present application described herein can be implemented in an order other than those illustrated or described herein. In addition, the terms "comprising" and "having" and any variations thereof are intended to cover non-exclusive inclusion. For example, a process, method, system, product or device comprising a series of steps or units does not necessarily have to be limited to those steps or units clearly listed, but may include other steps or units not clearly listed or inherent to these processes, methods, products or devices.

[0047] Now, exemplary embodiments according to the present application will be described in more detail with reference to the accompanying drawings. However, these exemplary embodiments can be implemented in many different forms and should not be construed as being limited only to the embodiments set forth herein. It should be understood that these embodiments are provided so that the disclosure of the present application is thorough and complete, and the concept of these exemplary embodiments is fully conveyed to those of ordinary skill in the art. In the drawings, for clarity, the thickness of layers and regions may be exaggerated, and the same reference numerals are used to denote the same devices, and thus their description will be omitted.

[0048] Embodiment 1

[0049] In combination with Figure 1 As shown, according to a specific embodiment of the present application, a hybrid transmission device is provided.

[0050] Specifically, the hybrid transmission device includes: an engine 50, a motor 60, a first planetary gear set, a second planetary gear set, a clutch assembly, and a brake assembly. The first planetary gear set includes a first planetary carrier 11, a first planetary gear 12, a first external gear ring 13, and a first sun gear 14. The first sun gear 14 is connected to the brake assembly. Both the first external gear ring 13 and the first sun gear 14 are connected to the engine 50 or the motor 60 through the clutch assembly. The first planetary carrier 11 is connected to the output shaft 71. The second planetary gear set includes a second planetary carrier 21, a second planetary gear 22, a second external gear ring 23, and a second sun gear 24. The second external gear ring 23 is connected to the brake assembly. The second sun gear 24 is connected to the engine 50 or the motor 60 through the clutch assembly. The second planetary carrier 21 is connected to the output shaft 71. Among them, the second sun gear 24 is rigidly connected to the first external gear ring 13, and the second planetary carrier 21 is rigidly connected to the first planetary carrier 11.

[0051] In an embodiment of the present application, the first outer ring gear 13 of the first planetary gear set is rigidly connected to the second sun gear 24 of the second planetary gear set, and the second planetary carrier 21 of the second planetary gear set is rigidly connected to the first planetary carrier 11 of the first planetary gear set. The first sun gear 14 and the second outer ring gear 23 are connected to a braking assembly. Both the first planetary gear set and the second planetary gear set are connected to the engine 50 or the motor 60 through a clutch assembly. The connection relationships between the two planetary gear sets and between the planetary gear sets, in cooperation with the clutch assembly and the braking assembly, realize multi-gear power transmission of the engine 50, multi-gear power transmission of the motor 60, and combined multi-gear power transmission of the engine 50 and the motor 60, so as to meet the actual working conditions or actual requirements, and is conducive to comprehensively reducing energy consumption.

[0052] As Figure 1 shown, the clutch assembly includes: a first clutch 31, a second clutch 32, and a third clutch 33. The first end of the first clutch 31 is connected to the motor 60, and the second end of the first clutch 31 is connected to the engine 50 through an input shaft 72. The first end of the second clutch 32 is connected to the motor 60, and the second end of the second clutch 32 is connected to the first sun gear 14 through a second intermediate shaft 74. The first end of the third clutch 33 is connected to the engine 50 through the input shaft 72, and the second end of the third clutch 33 is connected to the first outer ring gear 13 or the second sun gear 24 through a first intermediate shaft 73. Among them, the third clutch 33 is connected in series on the input shaft 72, and the third clutch 33 is located between the first clutch 31 and the engine 50.

[0053] It should be noted that the first clutch 31 can be directly connected to the motor 60 and the engine 50. The second clutch 32 can be directly connected to the motor 60, and the second clutch 32 needs to be connected to the engine 50 after passing through the first clutch 31. The third clutch 33 is connected to the input shaft 72, that is, after the third clutch 33 is engaged, the first clutch 31 can be connected to the engine 50. The connection relationships of the first clutch 31, the second clutch 32, and the third clutch 33 determine the power sources of the hybrid power transmission, that is, being driven by the motor 60 alone, being driven by the engine 50 alone, and being jointly driven by the motor 60 and the engine 50, so as to achieve multi-mode driving.

[0054] As Figure 1 shown, the braking assembly includes: a first brake 41 and a second brake 42. The first brake 41 is connected to the second outer ring gear 23, and the second brake 42 is connected to the first sun gear 14, where the first brake 41 and the second brake 42 are independent of each other.

[0055] It should be noted that for the planetary gear set to operate, one of the gears needs to be locked or the rotational speed of one of the gears needs to be fixed. That is, if the planetary gear set is to drive the output shaft 71 to work, the conditions to be met are: one of the first brake 41 and the second brake 42 is opened to lock one gear, or both the first brake 41 and the second brake 42 are closed to fix the rotational speed of one gear.

[0056] Embodiment 2

[0057] Combined with Figures 2 to 18 , according to a specific embodiment of the present application, a control method for a hybrid power transmission device is provided. The control method includes the following steps:

[0058] Step S1: Obtain the first working state of the clutch assembly, where the first working state includes at least one of the following: the first outer gear ring 13 and the second sun gear 24 are connected to the engine 50, the first outer gear ring 13 and the second sun gear 24 are connected to the motor 60, the first sun gear 14 is connected to the engine 50, and the first sun gear 14 is connected to the motor 60.

[0059] Step S2: Obtain the second working state of the brake assembly, where the second working state includes at least one of the following: the first sun gear 14 is in a locked state, the second outer gear ring 23 is in a locked state, and both the first sun gear 14 and the second outer gear ring 23 are in a non-locked state.

[0060] Step S3: Based on the first working state and the second working state, start at least one of the engine 50 and the motor 60 to achieve kinetic energy transfer.

[0061] In the above steps S1 to S3, the power source is selected through the clutch assembly, and the gears of the planetary gear set are locked or the rotational speed of the gears is fixed through the brake assembly so that the output shaft 71 can output normally, so as to achieve multi-power mode transmission and multi-gear transmission, meet the actual working conditions or actual needs, and help to comprehensively reduce energy consumption.

[0062] It should be noted that as Figure 3 shown, the above control method for the hybrid power transmission device can achieve three-gear power transmission of the engine 50 (ENG1, ENG2, and ENG3), three-gear power transmission of the motor 60 (EV1, EV2, and EV3), continuously variable transmission (ECVT), parallel three-gear transmission of the engine 50 and the motor 60 (parallel 1, parallel 2, and parallel 3), reverse gear transmission (R), and parking power generation mode. Figure 3 Among them, B1 represents the first brake 41, B2 represents the second brake 42, C1 represents the first clutch 31, C2 represents the second clutch 32, and A represents the third clutch 33.

[0063] As Figures 4 to 6As shown, it is a schematic diagram of the power transmission path for the three-speed power transmission of the engine 50. Among them, the thickened part represents the power transmission path. The specific control method is as follows:

[0064] Step S311: As Figure 4 shown, when the second outer gear ring 23 is in the locked state and the first outer gear ring 13 and the second sun gear 24 are connected to the engine 50, start the engine 50, and the second planet carrier 21 drives the output shaft 71 to rotate to achieve the first-speed transmission of the engine 50.

[0065] It should be noted that the first brake 41 is opened to lock the second outer gear ring 23 to enable the normal operation of the second planetary gear set; the third clutch 33 is engaged so that the engine 50 drives the second sun gear 24 to rotate; the second outer gear ring 23 is fixed, the second sun gear 24 is the driving gear, the second planetary gear 22 meshes with the second sun gear 24, and the power is transmitted to the second planet carrier 21 through the second planetary gear 22. The second planet carrier 21 outputs the power through the output shaft 71. Among them, the rotation direction of the second sun gear 24 is the same as that of the engine 50, the rotation direction of the second planetary gear 22 is opposite to that of the second sun gear 24, and the rotation direction of the second planetary gear 22 is opposite to that of the second planet carrier 21. Therefore, the rotation direction of the second planet carrier 21 is the same as that of the engine 50.

[0066] Step S312: As Figure 5 shown, when the first sun gear 14 is in the locked state and the first outer gear ring 13 and the second sun gear 24 are connected to the engine 50, start the engine 50, and the first planet carrier 11 drives the output shaft 71 to rotate to achieve the second-speed transmission of the engine 50.

[0067] It should be noted that the second brake 42 is opened to lock the first sun gear 14 to enable the normal operation of the first planetary gear set; the third clutch 33 is engaged so that the engine 50 drives the first outer gear ring 13 to rotate; the first sun gear 14 is fixed, the first outer gear ring 13 is the driving gear, the first outer gear ring 13 meshes with the first planetary gear 12, and the power is transmitted to the first planet carrier 11 through the first planetary gear 12. The first planet carrier 11 outputs the power through the output shaft 71. Among them, the rotation direction of the first outer gear ring 13 is the same as that of the engine 50, the rotation direction of the first outer gear ring 13 is opposite to that of the first planetary gear 12, and the rotation direction of the first planetary gear 12 is opposite to that of the first planet carrier 11. Therefore, the rotation direction of the first planet carrier 11 is the same as that of the engine 50.

[0068] Step S313: As Figure 6 shown, when both the first sun gear 14 and the second outer gear ring 23 are in the unlocked state, the first sun gear 14 is connected to the engine 50, and the first outer gear ring 13 and the second sun gear 24 are connected to the engine 50, start the engine 50, and the first planet carrier 11 drives the output shaft 71 to rotate to achieve the third-speed transmission of the engine 50.

[0069] It should be noted that both the first brake 41 and the second brake 42 are in the closed state, the first clutch 31, the second clutch 32 and the third clutch 33 are all in the engaged state, and the engine 50 serves as the power source. The power of the engine 50 is split through the input shaft 72 and the third clutch 33. Part of the power is transmitted to the first sun gear 14 through the first clutch 31, the second clutch 32 and the second intermediate shaft 74 in sequence, and the other part of the power is transmitted to the first ring gear 13 through the first intermediate shaft 73. In the first planetary gear set, the first ring gear 13 and the first sun gear 14 have the same rotational speed, and the first planetary gear 12 has no self-rotation, so that the first planetary gear set rotates as a whole at the output rotational speed of the engine 50, and the first carrier 11 outputs power through the output shaft 71. Among them, the rotation direction of the first carrier 11 is the same as that of the engine 50.

[0070] As Figure 16 shown, it is the gear composition diagram of four gears, namely ENG1, ENG2, ENG3 and ECVT. Among them, B1 represents the first brake 41, B2 represents the second brake 42, C1 represents the first clutch 31, C2 represents the second clutch 32, and A represents the third clutch 33; S1 represents the first sun gear 14, R1 represents the first ring gear 13, H1 represents the first carrier 11, S2 represents the second sun gear 24, R2 represents the second ring gear 23, and H1 represents the second carrier 21; EM represents the motor 60, and ENG represents the engine 50. The first-gear transmission (ENG1) of the engine 50: The power is transmitted from A to H2, and the rotational speed connection line is from A (maximum rotational speed) to R2 (rotational speed is 0); The second-gear transmission (ENG2) of the engine 50: The power is transmitted from A to H1, and the rotational speed connection line is from A (maximum rotational speed) to S1 (rotational speed is 0); The third-gear transmission (ENG3) of the engine 50: The power is transmitted from A to H1, and the rotational speed connection line is from A (maximum rotational speed) to C1, C2 (rotational speed remains unchanged). It can be seen that the rotational speeds of ENG1, ENG2 and ENG3 increase in sequence.

[0071] As Figures 7 to 9 shown, it is the schematic diagram of the power transmission path of the three-gear power transmission of the motor 60. Among them, the thick lines represent the power transmission paths, and the specific control method is as follows:

[0072] Step S321: As Figure 7 shown, when the second ring gear 23 is in the locked state and the first ring gear 13 and the second sun gear 24 are connected to the motor 60, the motor 60 is turned on, and the second carrier 21 drives the output shaft 71 to rotate to achieve the first-gear transmission of the motor 60.

[0073] It should be noted that the first brake 41 is opened to lock the second external gear ring 23, enabling the normal operation of the second planetary gear set; the first clutch 31 is engaged so that the motor 60 drives the second sun gear 24 to rotate; the second external gear ring 23 is fixed, the second sun gear 24 is the driving gear, the second planetary gear 22 meshes with the second sun gear 24, and the power is transmitted to the second planetary carrier 21 through the second planetary gear 22. The second planetary carrier 21 outputs the power through the output shaft 71. Among them, the rotation direction of the second sun gear 24 is the same as that of the motor 60, the rotation direction of the second planetary gear 22 is opposite to that of the second sun gear 24, and the rotation direction of the second planetary gear 22 is opposite to that of the second planetary carrier 21. Therefore, the rotation direction of the second planetary carrier 21 is the same as that of the motor 60.

[0074] Step S322: As Figure 8 shown, when the first sun gear 14 is in the locked state and the first external gear ring 13 and the second sun gear 24 are connected to the motor 60, the motor 60 is turned on, and the first planetary carrier 11 drives the output shaft 71 to rotate to achieve the second gear transmission of the motor 60.

[0075] It should be noted that the second brake 42 is opened to lock the first sun gear 14, enabling the normal operation of the first planetary gear set; the first clutch 31 is engaged so that the motor 60 drives the first external gear ring 13 to rotate; the first sun gear 14 is fixed, the first external gear ring 13 is the driving gear, the first external gear ring 13 meshes with the first planetary gear 12, and the power is transmitted to the first planetary carrier 11 through the first planetary gear 12. The first planetary carrier 11 outputs the power through the output shaft 71. Among them, the rotation direction of the first external gear ring 13 is the same as that of the motor 60, the rotation direction of the first external gear ring 13 is opposite to that of the first planetary gear 12, and the rotation direction of the first planetary gear 12 is opposite to that of the first planetary carrier 11. Therefore, the rotation direction of the first planetary carrier 11 is the same as that of the motor 60.

[0076] Step S323: As Figure 9 shown, when both the first sun gear 14 and the second external gear ring 23 are in the unlocked state, the first sun gear 14 is connected to the motor 60, and the first external gear ring 13 and the second sun gear 24 are connected to the motor 60, the motor 60 is turned on, and the first planetary carrier 11 drives the output shaft 71 to rotate to achieve the third gear transmission of the motor 60.

[0077] It should be noted that both the first brake 41 and the second brake 42 are in the closed state, both the first clutch 31 and the second clutch 32 are in the engaged state, and the motor 60 serves as the power source. The power of the motor 60 is split. A part of the power is transmitted to the first outer gear ring 13 through the first clutch 31 and the first intermediate shaft 73 in sequence, and another part of the power is transmitted to the first sun gear 14 through the second clutch 32 and the second intermediate shaft 74. In the first planetary gear set, the first outer gear ring 13 and the first sun gear 14 have the same rotational speed, and the first planetary gear 12 has no self-rotation, so that the first planetary gear set rotates as a whole, and the rotational speed is the output rotational speed of the motor 60. The first planetary carrier 11 outputs power through the output shaft 71. Among them, the rotational direction of the first planetary carrier 11 is the same as that of the motor 60.

[0078] As Figure 17 shown, it is a gear composition diagram of four gears, namely EV1, EV2, EV3, and R. Among them, B1 represents the first brake 41, B2 represents the second brake 42, C1 represents the first clutch 31, C2 represents the second clutch 32, and A represents the third clutch 33; S1 represents the first sun gear 14, R1 represents the first outer gear ring 13, H1 represents the first planetary carrier 11, S2 represents the second sun gear 24, R2 represents the second outer gear ring 23, and H1 represents the second planetary carrier 21; EM represents the motor 60, and ENG represents the engine 50. The first gear transmission (EV1) of the motor 60: The power is transmitted from C1 to H2, and the rotational speed connection line is from C1 (maximum rotational speed) to R2 (rotational speed is 0); The second gear transmission (EV2) of the motor 60: The power is transmitted from C1 to H1, and the rotational speed connection line is from C1 (maximum rotational speed) to S1 (rotational speed is 0); The third gear transmission (EV3) of the motor 60: The power is transmitted from C1 to H1, and the rotational speed connection line is from C1 (maximum rotational speed) to C2 (maximum rotational speed). It can be seen that the rotational speeds of EV1, EV2, and EV3 increase in sequence.

[0079] As Figures 10 to 12 shown, it is a schematic diagram of the power transmission path of the parallel three-gear power transmission of the motor 60 and the engine 50. Among them, the thick lines represent the power transmission paths, and the specific control method is as follows:

[0080] Step S331: As Figure 10 shown, when the second outer gear ring 23 is in the locked state and the first outer gear ring 13 and the second sun gear 24 are simultaneously connected to the motor 60 and the engine 50, the motor 60 and the engine 50 are started simultaneously, and the second planetary carrier 21 drives the output shaft 71 to rotate to achieve parallel first gear transmission.

[0081] It should be noted that in combination with Figure 4 and Figure 7As shown, the first brake 41 is opened, the first clutch 31 is engaged, and the third clutch 33 is engaged. The power of the engine 50 is transmitted to the second sun gear 24 via the third clutch 33 and the first intermediate shaft 73, and the power of the motor 60 is transmitted to the second sun gear 24 via the first clutch 31 and the first intermediate shaft 73. That is, the power of the engine 50 and the power of the motor 60 are in parallel drive at the second sun gear 24. The total power is transmitted to the second planet carrier 21 via the second planet gear 22, and the second planet carrier 21 outputs the power via the output shaft 71. Among them, the rotation direction of the second planet carrier 21 is the same as that of the engine 50 and the motor 60.

[0082] Step S332: As Figure 11 shown, when the first sun gear 14 is in the locked state and the first outer gear ring 13 and the second sun gear 24 are simultaneously connected to the motor 60 and the engine 50, the motor 60 and the engine 50 are simultaneously started, and the first planet carrier 11 drives the output shaft 71 to rotate to achieve parallel two-gear drive.

[0083] It should be noted that in combination with Figure 5 and Figure 8 shown, the second brake 42 is opened, the first clutch 31 is engaged, and the third clutch 33 is engaged. The power of the engine 50 is transmitted to the first outer gear ring 13 via the third clutch 33, and the power of the motor 60 is transmitted to the first outer gear ring 13 via the first clutch 31. That is, the power of the engine 50 and the power of the motor 60 are in parallel drive at the first outer gear ring 13. The total power is transmitted to the first planet carrier 11 via the first planet gear 12, and the first planet carrier 11 outputs the power via the output shaft 71. Among them, the rotation direction of the first planet carrier 11 is the same as that of the engine 50 and the motor 60.

[0084] Step S333: As Figure 12 shown, when the first sun gear 14 and the second outer gear ring 23 are both in the unlocked state, the first sun gear 14 is simultaneously connected to the motor 60 and the engine 50, and the first outer gear ring 13 and the second sun gear 24 are simultaneously connected to the motor 60 and the engine 50, the motor 60 and the engine 50 are simultaneously started, and the first planet carrier 11 drives the output shaft 71 to rotate to achieve parallel three-gear drive.

[0085] It should be noted that in combination with Figure 6 and Figure 9As shown in the figure, both the first brake 41 and the second brake 42 are in the closed state, and the first clutch 31, the second clutch 32, and the third clutch 33 are all in the engaged state. A part of the power of the engine 50 is transmitted to the first sun gear 14 through the first clutch 31, the second clutch 32, and the second intermediate shaft 74. A part of the power of the motor 60 is transmitted to the first sun gear 14 through the second clutch 32 and the second intermediate shaft 74. Another part of the power of the engine 50 is transmitted to the first external gear ring 13 through the first intermediate shaft 73. Another part of the power of the motor 60 is sequentially transmitted to the first external gear ring 13 through the first clutch 31 and the first intermediate shaft 73. In the first planetary gear set, the rotational speeds of the first external gear ring 13 and the first sun gear 14 are the same, and the first planetary gear 12 has no self-rotation, so that the first planetary gear set rotates as a whole, and the rotational speed is the total output rotational speed of the motor 60 and the engine 50. The first planetary carrier 11 outputs power through the output shaft 71. Among them, the rotational direction of the first planetary carrier 11 is the same as that of the motor 60 and the engine 50.

[0086] As Figure 18 shown, it is a gear composition diagram of three gears, namely parallel 1, parallel 2, and parallel 3. Among them, B1 represents the first brake 41, B2 represents the second brake 42, C1 represents the first clutch 31, C2 represents the second clutch 32, and A represents the third clutch 33; S1 represents the first sun gear 14, R1 represents the first external gear ring 13, H1 represents the first planetary carrier 11, S2 represents the second sun gear 24, R2 represents the second external gear ring 23, and H1 represents the second planetary carrier 21; EM represents the motor 60, and ENG represents the engine 50. Parallel 1 gear transmission: The power is transmitted from A / C1 to H2, and the rotational speed connection line is from A / C1 (maximum rotational speed) to R2 (rotational speed is 0); Parallel 2 gear transmission: The power is transmitted from A / C1 to H1, and the rotational speed connection line is from A / C1 (maximum rotational speed) to S1 (rotational speed is 0); Parallel 3 gear transmission: The power is transmitted from C1 / A to H1, and the rotational speed connection line is from A / C1 (maximum rotational speed) to C1 / C2 (maximum rotational speed). It can be seen that the rotational speeds of parallel 1, parallel 2, and parallel 3 increase in sequence.

[0087] As Figure 13 shown, it is a schematic diagram of the power transmission path of continuously variable transmission. Among them, the thickened part is the power transmission path, and the specific control method is as follows:

[0088] When both the first sun gear 14 and the second external gear ring 23 are in the unlocked state, the first sun gear 14 is connected to the motor 60, and the first external gear ring 13 and the second sun gear 24 are connected to the engine 50, the motor 60 and the engine 50 are started simultaneously, and the first planetary carrier 11 drives the output shaft 71 to rotate to achieve continuously variable transmission.

[0089] It should be noted that when the second clutch 32 is engaged and the third clutch 33 is engaged, the power of the engine 50 is transmitted to the first external gear ring 13 via the third clutch 33 and the first intermediate shaft 73, and the power of the motor 60 is transmitted to the first sun gear 14 via the second clutch 32 and the second intermediate shaft 74. The power of the engine 50 and the power of the motor 60 are coupled on the first planetary gear set, and the total power is output by the first planetary carrier 11.

[0090] As Figure 16 shown, it is a gear constitution diagram of four gears, namely ENG1, ENG2, ENG3 and ECVT. Among them, B1 represents the first brake 41, B2 represents the second brake 42, C1 represents the first clutch 31, C2 represents the second clutch 32, and A represents the third clutch 33; S1 represents the first sun gear 14, R1 represents the first external gear ring 13, H1 represents the first planetary carrier 11, S2 represents the second sun gear 24, R2 represents the second external gear ring 23, and H1 represents the second planetary carrier 21; EM represents the motor 60, and ENG represents the engine 50. Continuously variable transmission (ECVT): The power is transmitted from C2 / A to H1, the speed connection line is from C2 to A, and the power is coupled bidirectionally.

[0091] As Figure 14 shown, it is a schematic diagram of the power transmission path for reverse gear power transmission. Among them, the thick line represents the power transmission path, and the specific control method is as follows:

[0092] When the second external gear ring 23 is in the locked state and the first sun gear 14 is connected to the motor 60, the motor 60 is turned on, and the first planetary carrier 11 and the second planetary carrier 21 drive the output shaft 71 to rotate simultaneously to achieve reverse gear transmission.

[0093] It should be noted that when the second clutch 32 is engaged and the first brake 41 is turned on, the power of the motor 60 is transmitted to the first sun gear 14 via the second clutch 32. The first sun gear 14 rotates forward, the rotational speed of the second external gear ring 23 is 0, the first sun gear 14 meshes with the first planetary gear 12, the first planetary gear 12 meshes with the first external gear ring 13, the first external gear ring 13 is rigidly integrated with the second sun gear 24, the second sun gear 24 meshes with the second planetary gear 22, the first planetary carrier 11 is rigidly integrated with the second planetary carrier 21, and under the interaction of the first planetary gear 12 and the second planetary gear 22, the output rotational speed of the planetary carrier is opposite to the rotational speed of the motor 60.

[0094] As Figure 17As shown, it is a gear composition diagram of four gears: EV1, EV2, EV3, and R. Among them, B1 represents the first brake 41, B2 represents the second brake 42, C1 represents the first clutch 31, C2 represents the second clutch 32, and A represents the third clutch 33; S1 represents the first sun gear 14, R1 represents the first external gear ring 13, H1 represents the first planet carrier 11, S2 represents the second sun gear 24, R2 represents the second external gear ring 23, and H1 represents the second planet carrier 21; EM represents the motor 60, and ENG represents the engine 50. Reverse gear transmission (R): Power is transmitted from C2 to H1 / H2, and the speed connection line is from C2 to H1 / H2.

[0095] As Figure 15 shown, it is a schematic diagram of the power transmission path for power generation during parking. Among them, the thickened part is the power transmission path, and the specific control method is as follows:

[0096] In the parked state, the third clutch 33 is engaged, the first clutch 31 is engaged, the engine 50 idles, and the power of the engine 50 is transmitted from the third clutch 33 and the first clutch 31 to the motor 60 to generate electricity.

[0097] The above hybrid power transmission device has an in - motion energy recovery mode, which is specifically as follows:

[0098] When in the engine 50 driving mode, when the driver steps on the brake pedal, the system detects the driver's intention to decelerate. The system controller issues an instruction to engage the first clutch 31 and reverse - drag the motor 60 to rotate. When the driver's deceleration intention is clear and the duration exceeds a certain threshold, through the motor 60 controller, excitation is applied to the motor 60 to provide a load, and kinetic energy is converted into electrical energy. The current flows from the motor 60 to the battery, forming an in - motion energy recovery mode.

[0099] When in the parallel driving mode or the motor 60 driving mode, the connection method between the power source and the mechanical coupling device remains unchanged. When the driver steps on the brake pedal, the system detects the driver's intention to decelerate, reduces the speed of the motor 60 to form reverse - drag, and provides a load. Kinetic energy is converted into electrical energy, and the current flows from the dual - motor 60 to the battery, forming an in - motion energy recovery mode.

[0100] Embodiment III

[0101] According to another specific embodiment of the present invention, a vehicle is provided, including a hybrid power transmission device, and the hybrid power transmission device is the hybrid power transmission device in the above - mentioned embodiment.

[0102] For ease of description, spatial relative terms, such as "above", "over", "on the upper surface", "upper", etc., may be used herein to describe the spatial positional relationship of one device or feature to other devices or features as shown in the figures. It should be understood that the spatial relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is inverted, a device described as "above" or "over" other devices or structures will then be positioned "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both orientations of "above" and "below". The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and corresponding interpretations of the spatial relative descriptions used herein will be made accordingly.

[0103] In addition to the above, it should also be noted that the "one embodiment", "another embodiment", "embodiment", etc. mentioned in this specification refer to the specific features, structures or characteristics described in connection with that embodiment being included in at least one embodiment generally described in this application. The same expression appearing in multiple places in the specification does not necessarily refer to the same embodiment. Further, when describing a specific feature, structure or characteristic in connection with any one embodiment, it is intended that the implementation of such feature, structure or characteristic in connection with other embodiments also falls within the scope of the present invention.

[0104] In the above embodiments, the descriptions of each embodiment have their own emphases. For parts not detailed in a certain embodiment, reference may be made to the relevant descriptions of other embodiments.

[0105] The above are only the preferred embodiments of the present invention and are not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and changes. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention shall be included within the protection scope of the present invention.

Claims

1. A hybrid drive device, comprising an engine (50) and an electric motor (60), characterized in that, Further included are: A first planetary gear set, the first planetary gear set including a first planet carrier (11), a first planet gear (12), a first external gear ring (13), and a first sun gear (14), the first sun gear (14) being connected to a braking assembly, the first external gear ring (13) and the first sun gear (14) both being connected to the engine (50) or the motor (60) through a clutch assembly, and the first planet carrier (11) being connected to an output shaft (71); A second planetary gear set, the second planetary gear set including a second planet carrier (21), a second planet gear (22), a second external gear ring (23), and a second sun gear (24), the second external gear ring (23) being connected to the braking assembly, the second sun gear (24) being connected to the engine (50) or the motor (60) through the clutch assembly, and the second planet carrier (21) being connected to the output shaft (71); Wherein, the second sun gear (24) is rigidly connected to the first external gear ring (13), and the second planet carrier (21) is rigidly connected to the first planet carrier (11); The clutch assembly includes: A first clutch (31), a first end of the first clutch (31) being connected to the motor (60), and a second end of the first clutch (31) being connected to the engine (50) through an input shaft (72); A second clutch (32), a first end of the second clutch (32) being connected to the motor (60), and a second end of the second clutch (32) being connected to the first sun gear (14) through a second intermediate shaft (74); A third clutch (33), a first end of the third clutch (33) being connected to the engine (50) through the input shaft (72), and a second end of the third clutch (33) being connected to the first external gear ring (13) or the second sun gear (24) through a first intermediate shaft (73); Wherein, the third clutch (33) is connected in series on the input shaft (72), and the third clutch (33) is located between the first clutch (31) and the engine (50); The braking assembly includes: A first brake (41), the first brake (41) being connected to the second external gear ring (23); A second brake (42), the second brake (42) being connected to the first sun gear (14); Wherein, the first brake (41) and the second brake (42) are independent of each other.

2. A control method for a hybrid powertrain, characterized in that, The hybrid power transmission device is the hybrid power transmission device according to claim 1, and the control method includes: Obtaining a first working state of the clutch assembly, wherein the first working state includes at least one of the following: the first external gear ring (13) and the second sun gear (24) are connected to the engine (50), the first external gear ring (13) and the second sun gear (24) are connected to the motor (60), the first sun gear (14) is connected to the engine (50), and the first sun gear (14) is connected to the motor (60); Obtain the second working state of the braking assembly, where the second working state includes at least one of the following: the first sun gear (14) is in a locked state, the second outer gear ring (23) is in a locked state, and both the first sun gear (14) and the second outer gear ring (23) are in an unlocked state; Based on the first working state and the second working state, turn on at least one of the engine (50) and the motor (60) to achieve kinetic energy transfer.

3. The control method according to claim 2, wherein Based on the first working state and the second working state, turn on at least one of the engine (50) and the motor (60) to achieve kinetic energy transfer, including: When the second outer gear ring (23) is in a locked state and the first outer gear ring (13) and the second sun gear (24) are connected to the engine (50), turn on the engine (50), and the second planet carrier (21) drives the output shaft (71) to rotate to achieve the first gear transmission of the engine (50); When the first sun gear (14) is in a locked state and the first outer gear ring (13) and the second sun gear (24) are connected to the engine (50), turn on the engine (50), and the first planet carrier (11) drives the output shaft (71) to rotate to achieve the second gear transmission of the engine (50); When both the first sun gear (14) and the second outer gear ring (23) are in an unlocked state, the first sun gear (14) is connected to the engine (50), and the first outer gear ring (13) and the second sun gear (24) are connected to the engine (50), turn on the engine (50), and the first planet carrier (11) drives the output shaft (71) to rotate to achieve the third gear transmission of the engine (50).

4. The control method according to claim 2, wherein Based on the first working state and the second working state, turn on at least one of the engine (50) and the motor (60) to achieve kinetic energy transfer, further including: When the second outer gear ring (23) is in a locked state and the first outer gear ring (13) and the second sun gear (24) are connected to the motor (60), turn on the motor (60), and the second planet carrier (21) drives the output shaft (71) to rotate to achieve the first gear transmission of the motor (60); When the first sun gear (14) is in a locked state and the first outer gear ring (13) and the second sun gear (24) are connected to the motor (60), turn on the motor (60), and the first planet carrier (11) drives the output shaft (71) to rotate to achieve the second gear transmission of the motor (60); When the first sun gear (14) and the second external gear ring (23) are both in the unlocked state, the first sun gear (14) is connected to the motor (60), and the first external gear ring (13) and the second sun gear (24) are connected to the motor (60), the motor (60) is turned on, and the first planet carrier (11) drives the output shaft (71) to rotate, so as to realize the three-speed transmission of the motor (60).

5. The control method according to claim 2, characterized in that, Based on the first working state and the second working state, at least one of the engine (50) and the motor (60) is turned on to realize kinetic energy transfer, and further includes: When the second external gear ring (23) is in the locked state and the first external gear ring (13) and the second sun gear (24) are simultaneously connected to the motor (60) and the engine (50), the motor (60) and the engine (50) are simultaneously turned on, and the second planet carrier (21) drives the output shaft (71) to rotate, so as to realize the parallel first-gear transmission; When the first sun gear (14) is in the locked state and the first external gear ring (13) and the second sun gear (24) are simultaneously connected to the motor (60) and the engine (50), the motor (60) and the engine (50) are simultaneously turned on, and the first planet carrier (11) drives the output shaft (71) to rotate, so as to realize the parallel second-gear transmission; When the first sun gear (14) and the second external gear ring (23) are both in the unlocked state, the first sun gear (14) is simultaneously connected to the motor (60) and the engine (50), and the first external gear ring (13) and the second sun gear (24) are simultaneously connected to the motor (60) and the engine (50), the motor (60) and the engine (50) are simultaneously turned on, and the first planet carrier (11) drives the output shaft (71) to rotate, so as to realize the parallel third-gear transmission.

6. The control method according to claim 2, wherein Based on the first working state and the second working state, at least one of the engine (50) and the motor (60) is turned on to realize kinetic energy transfer, and further includes: When the first sun gear (14) and the second external gear ring (23) are both in the unlocked state, the first sun gear (14) is connected to the motor (60), and the first external gear ring (13) and the second sun gear (24) are connected to the engine (50), the motor (60) and the engine (50) are simultaneously turned on, and the first planet carrier (11) drives the output shaft (71) to rotate, so as to realize the continuously variable transmission.

7. The control method according to claim 2, wherein Based on the first working state and the second working state, at least one of the engine (50) and the motor (60) is turned on to realize kinetic energy transfer, and further includes: When the second external gear ring (23) is in the locked state and the first sun gear (14) is connected to the motor (60), the motor (60) is turned on, and the first planet carrier (11) and the second planet carrier (21) simultaneously drive the output shaft (71) to rotate, so as to realize the reverse gear transmission.

8. A vehicle, comprising a hybrid drive, characterized in that, The hybrid transmission device is the hybrid transmission device described in claim 1.

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