Special hybrid transmission, hybrid driving system and vehicle

Abstract

The utility model discloses a special hybrid transmission, a hybrid driving system and a vehicle, the special hybrid transmission comprises a power input shaft, a power output shaft, a double clutch and a planetary gear mechanism, the output end of an engine is connected with the double clutch, the double clutch comprises a first clutch unit and a second clutch unit, the power input shaft comprises a first input shaft and a second input shaft, the planetary gear mechanism comprises a planet carrier, a sun gear and a gear ring, the first clutch unit is connected with the sun gear through the first input shaft, the second clutch unit is connected with the planet carrier through the second input shaft, and the engine is connected with or separated from the first input shaft through the first clutch unit. Or the engine is connected with or separated from the second input shaft through the second clutch unit, the gear ring is meshed with the planet wheel on the planet carrier and the motor gear of the motor, and the power output shaft is connected with the planet carrier or the gear ring. According to the utility model, stepless gear shifting can be realized, the gear shifting efficiency is improved, the gear shifting is stable and smooth, and the power loss is reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of vehicles, and in particular to a hybrid-specific transmission, a hybrid drive system and a vehicle. Background Art

[0002] Existing dedicated hybrid transmissions, also known as DHT (Dedicated Hybrid Transmission) transmissions require shifting through a large solenoid valve hydraulic system or shift fork system, have many redundant parts, low shifting efficiency, shifting frustration, and possible power loss. Utility Model Content

[0003] The utility model aims to provide a hybrid-specific transmission, a hybrid drive system and a vehicle, so as to solve the technical problems in the prior art that a huge solenoid valve hydraulic system or a shift fork system is required for shifting gears, there are many redundant parts, low shifting efficiency, gear shifting frustration, and possible power loss.

[0004] In order to solve the above technical problems, the utility model provides a hybrid-specific transmission, including a power input shaft, a power output shaft, a dual clutch and a planetary gear mechanism, the dual clutch is arranged between the engine and the planetary gear mechanism, the output end of the engine is connected to the dual clutch, the dual clutch includes a first clutch unit and a second clutch unit, the power input shaft includes a first input shaft and a second input shaft, the planetary gear mechanism includes a planet carrier, a sun gear and a ring gear, the first clutch unit is connected to the sun gear through the first input shaft, the second clutch unit is connected to the planet carrier through the second input shaft, the engine is engaged or disengaged with the first input shaft through the first clutch unit, or the engine is engaged or disengaged with the second input shaft through the second clutch unit, the ring gear is respectively meshed with the planetary gear on the planet carrier and the motor gear of the motor, and the power output shaft is connected to the planet carrier or the ring gear.

[0005] In some embodiments, the ring gear is a double-sided ring gear, which is arranged on the radial outside of the planetary carrier, the inner ring gear of the double-sided ring gear is meshed with the planetary gear, the outer ring gear of the double-sided ring gear is meshed with the motor gear, and the inner ring gear of the double-sided ring gear is connected to the power output shaft through a transmission gear or a transmission gear set.

[0006] In some embodiments, the first clutch unit and the second clutch unit are coaxially arranged, the second input shaft is a hollow shaft, and the second input shaft is sleeved outside the first input shaft.

[0007] In some embodiments, the first clutch unit includes a first driven plate, the second clutch unit includes a second driven plate, the outer hub of the dual clutch selectively engages with or disengages from the first driven plate, and the outer hub of the dual clutch selectively engages with or disengages from the second driven plate.

[0008] In some embodiments, a planetary carrier output shaft is provided on the planetary carrier, and the planetary carrier output shaft is connected to the power output shaft through a second transmission gear set, the second transmission gear set includes a second transmission gear and a third transmission gear that are meshed with each other, the second transmission gear is installed on the planetary carrier output shaft, the third transmission gear is installed on the power output shaft, and the third transmission gear is meshed with the inner gear ring of the double-sided gear ring.

[0009] In some embodiments, the dual clutch is a dry dual clutch.

[0010] The utility model also provides a hybrid drive system, including an engine and a motor, and the hybrid drive system also includes the above-mentioned hybrid-specific transmission.

[0011] In some embodiments, the hybrid drive system further includes a mechanical pump, wherein a liquid inlet pipeline of the mechanical pump is connected to a filter in an oil pan, and a liquid outlet pipeline of the mechanical pump is connected to an oil circuit of the hybrid-specific transmission.

[0012] In some embodiments, the mechanical pump is connected to the planet carrier or the ring gear through a transmission mechanism.

[0013] The utility model also provides a vehicle, comprising a hybrid-specific transmission as described in any one of the above technical solutions.

[0014] The hybrid transmission, hybrid drive system and vehicle provided by the embodiments of the utility model are provided with a power input shaft, a power output shaft, a dual clutch and a planetary gear mechanism. The dual clutch is provided between the engine and the planetary gear mechanism, the output end of the engine is connected with the dual clutch, the dual clutch includes a first clutch unit and a second clutch unit, the planetary gear mechanism includes a planetary carrier, a sun gear and a ring gear, the power input shaft includes a first input shaft and a second input shaft, the first clutch unit is connected with the sun gear through the first input shaft, the second clutch unit is connected with the planetary carrier through the second input shaft, the ring gear is respectively meshed with the planetary gear and the motor gear of the motor, and the engine is connected with the sun gear through the first clutch. The unit is engaged or disengaged with the first input shaft, or the engine is engaged or disengaged with the second input shaft through the second clutch unit, the ring gear is respectively meshed with the planetary gear on the planetary carrier and the motor gear of the motor, and the power output shaft is connected to the planetary carrier or the ring gear. The dual clutch can meet different gear shifting requirements and improve the gear shifting efficiency. In the hybrid mode, the vehicle speed ratio can be infinitely adjusted to ensure smooth gear shifting, and the motor power loss can be reduced in the pure electric mode to improve the pure electric endurance of the vehicle. In addition, the transmission cancels the hydraulic shifting system and the fork system, and the vehicle shifting is achieved by controlling the clutch, which can reduce redundant components, reduce power loss, and reduce the size and weight of the transmission, thereby realizing the lightweight design of the transmission and reducing the manufacturing cost of the transmission and the vehicle. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] In order to more clearly illustrate the embodiments of the utility model or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments recorded in the utility model. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative labor.

[0016] Figure 1 A schematic diagram of the structure of a hybrid transmission according to an embodiment of the utility model;

[0017] Figure 2 It is a schematic diagram of power transmission of the 1st speed regulating gear position of the hybrid transmission according to an embodiment of the utility model;

[0018] Figure 3 It is a schematic diagram of power transmission of the 2nd speed regulating gear position of the hybrid transmission according to the embodiment of the utility model;

[0019] Figure 4 It is a schematic diagram of power transmission of a hybrid-specific transmission in a pure electric mode according to an embodiment of the utility model;

[0020] Figure 5It is a schematic structural diagram of a hybrid drive system according to an embodiment of the utility model.

[0021] Reference numerals:

[0022] 1-power input shaft, 11-first input shaft, 12-second input shaft; 2-power output shaft; 3-dual clutch, 31-first clutch unit, 32-second clutch unit; 4-planetary gear mechanism, 41-planet carrier, 411-planet carrier output shaft, 42-sun gear, 43-ring gear, 431-inner ring gear, 432-outer ring gear, 44-planetary gear; 51-first transmission gear, 52-second transmission gear, 53-third transmission gear; 20-engine, 201-engine output shaft; 30-motor, 301-motor gear, 302-motor output shaft; 40-mechanical pump, 401-liquid inlet pipeline, 402-liquid outlet pipeline; 50-oil pan, 501-filter. DETAILED DESCRIPTION

[0023] Various aspects and features of the present invention are described herein with reference to the accompanying drawings.

[0024] It should be understood that various modifications may be made to the embodiments of the present application. Therefore, the above description should not be considered as limiting, but only as an example of the embodiments. Other modifications within the scope and spirit of the present utility model will occur to those skilled in the art.

[0025] The accompanying drawings, which are included in and constitute a part of the specification, illustrate embodiments of the present invention and, together with the general description of the present invention given above and the detailed description of the embodiments given below, are used to explain the principles of the present invention.

[0026] These and other characteristics of the invention will become apparent from the following description of a preferred form of embodiment given as a non-limiting example, with reference to the accompanying drawings.

[0027] It should also be understood that although the present invention has been described with reference to some specific examples, those skilled in the art will be able to realize many other equivalent forms of the present invention that have the features described in the claims and are therefore within the scope of protection defined thereby.

[0028] The above and other aspects, features and advantages of the present invention will become more apparent from the following detailed description when taken in conjunction with the accompanying drawings.

[0029] Specific embodiments of the present invention are described hereinafter with reference to the accompanying drawings; however, it should be understood that the embodiments applied for are merely examples of the present invention, which may be implemented in a variety of ways. Well-known and / or repeated functions and structures are not described in detail to avoid unnecessary or redundant details that obscure the present invention. Therefore, the specific structural and functional details applied for herein are not intended to be limiting, but merely serve as the basis and representative basis for the claims to teach those skilled in the art to use the present invention in a variety of ways with substantially any suitable detailed structure.

[0030] This specification may use the phrases "in one embodiment", "in another embodiment", "in yet another embodiment" or "in other embodiments", all of which may refer to one or more of the same or different embodiments according to the present invention.

[0031] Figures 1 to 4 The structure diagram of the hybrid transmission provided by the embodiment of the utility model is shown. Figures 1 to 4 As shown, the first embodiment of the utility model provides a hybrid transmission, including a power input shaft 1, a power output shaft 2, a dual clutch 3 and a planetary gear mechanism 4, the dual clutch 3 is arranged between the engine 20 and the planetary gear mechanism 4, the output end of the engine 20 is connected to the dual clutch 3, the dual clutch 3 includes a first clutch unit 31 and a second clutch unit 32, the planetary gear mechanism 4 includes a planet carrier 41, a sun gear 42 and a ring gear 43, the power input shaft 1 includes a first input shaft 11 and a second input shaft 12, the first clutch unit 31 is connected to the planetary gear mechanism 4 through the first clutch unit 31, and the planetary gear mechanism 4 includes a planet carrier 41, a sun gear 42 and a ring gear 43. An input shaft 11 is connected to the sun gear 42, the second clutch unit 32 is connected to the planetary carrier 41 through the second input shaft 12, the ring gear 43 is respectively meshed with the planetary gear 44 and the motor gear 301 of the motor 30, the engine 20 is engaged or disengaged with the first input shaft 11 through the first clutch unit 31, or the engine 20 is engaged or disengaged with the second input shaft 12 through the second clutch unit 32, the ring gear 43 is respectively meshed with the planetary gear 44 on the planetary carrier 41 and the motor gear 301 of the motor 30, and the power output shaft 2 is connected to the planetary carrier 41 or the ring gear 43.

[0032] Specifically, the planet carrier 41, the sun gear 42 and the ring gear 43 are arranged concentrically, the planet gear 44 can be installed on the planet gear shaft of the planet carrier 41 through a sliding bearing, the planet carrier 41 provides support for the planet gear 44, the planet gear 44 is arranged around the sun gear 42, and the planet gear 44 is located between the sun gear 42 and the ring gear 43, and the planet gear 44 is respectively meshed with the sun gear 42 and the ring gear 43; the motor gear 301 is hung on the motor output shaft 302 of the motor 30 and meshed with the ring gear 43.

[0033] One end of the first input shaft 11 is the power input end, which is connected to the first clutch unit 31; the other end of the first input shaft 11 is the power output end, which is connected to the center of the sun gear 42; one end of the second input shaft 12 is the power input end, which is connected to the second clutch unit 32, and the other end of the first input shaft 11 is the power output end, which is connected to the power input end of the planetary carrier 41.

[0034] The first clutch unit 31 can be selectively engaged or disengaged so that the engine output shaft 201 of the engine 20 is engaged or disengaged with the first input shaft 11. Figure 2 As shown, when the first clutch unit 31 is engaged, the power output shaft 2 is connected to the planetary carrier 41, and the power output of the engine 20 is transmitted to the sun gear 42 through the first input shaft 11, and then transmitted to the planetary carrier 41 through the planetary gear 44 meshing with the sun gear 42, and then output through the planetary carrier 41 and the power output shaft 2. Similarly, the second clutch unit 32 can be selectively engaged or disengaged, so that the engine output shaft 201 of the engine 20 is engaged or disengaged with the second input shaft 12. Figure 3 As shown, when the second clutch unit 32 is engaged, the power output shaft 2 is connected to the planetary carrier 41 , and the power output by the engine 20 is transmitted to the planetary carrier 41 through the second input shaft 12 , and then output through the planetary carrier 41 and the power output shaft 2 .

[0035] When the first clutch unit 31 is engaged or the second clutch unit 32 is engaged, the power output by the motor 30 is transmitted to the planetary carrier 41 through the motor shaft 302 , the motor gear 301 , the ring gear 43 , and the planetary gear 44 in sequence, and then output through the power output shaft 2 .

[0036] As described above, the engine 20 inputs power to the planetary gear mechanism 4 in two ways, cooperates with the motor 30 to synchronously input power to the planetary gear mechanism 4, and outputs power to the vehicle's drive wheels through the power output shaft 2 connected to the planetary carrier 41, thereby realizing hybrid drive of the vehicle.

[0037] When the first clutch unit 31 is engaged, the vehicle is in the first gear, and the sun gear 42 and the planetary gear 44 are meshed at the first speed ratio i. 1 (or the first transmission ratio) transmits power, so the speed ratio of the power output shaft 2 is i 1 When the second clutch unit 32 is engaged, the vehicle is in the 2nd gear. Since the power output by the engine 20 does not pass through the mutually meshing sun gear 42 and planetary gear 44, the speed ratio of the power output shaft 2 is 1 at this time.

[0038] As described above, in the hybrid mode, the power output by the engine 20 realizes two transmission speed ratios through the sun gear 42 or the planetary carrier 41, and the power of the motor 30 is synchronously input through the ring gear 43, and the power is output through the power output shaft 2 connected to the planetary carrier 41. The speed ratio of the vehicle can be adjusted infinitely, and the speed ratio changes infinitely and smoothly, and the gear shifting is smooth and there is no gear shifting setback, thereby improving the user's gear shifting experience.

[0039] like Figure 4 As shown, when the first clutch unit 31 and the second clutch unit 32 are both disconnected (the dual clutch 3 is disconnected), the vehicle is in pure electric mode, and the power output by the engine 20 cannot be transmitted to the above-mentioned power input shaft 1, that is, the power cannot be output through the planetary gear mechanism 4. At this time, the power output shaft 2 is connected to the ring gear 43, and the power output by the motor 30 is transmitted to the power output shaft 2 through the ring gear 43, and then output to the driving wheels of the vehicle, realizing the pure electric drive of the vehicle. In the pure electric mode, the motor power is directly output to the power output shaft 2 through the ring gear 43, reducing the force transmission path, thereby reducing power loss and improving the pure electric endurance of the vehicle.

[0040] In summary, the hybrid transmission provided by the embodiment of the utility model is provided with a power input shaft 1, a power output shaft 2, a dual clutch 3 and a planetary gear mechanism 4, the dual clutch 3 is arranged between the engine 20 and the planetary gear mechanism 4, the output end of the engine 20 is connected to the dual clutch 3, the dual clutch 3 includes a first clutch unit 31 and a second clutch unit 32, the planetary gear mechanism 4 includes a planet carrier 41, a sun gear 42 and a ring gear 43, the power input shaft 1 includes a first input shaft 11 and a second input shaft 12, the first clutch unit 31 is connected to the sun gear 42 through the first input shaft 11, the second clutch unit 32 is connected to the planet carrier 41 through the second input shaft 12, the ring gear 43 is respectively engaged with the planetary gear 44 and the motor gear 301 of the motor 30, and the engine 20 is connected to the second clutch unit 31 through the first clutch unit 31. An input shaft 11 is engaged or disengaged, or the engine 20 is engaged or disengaged with the second input shaft 12 through the second clutch unit 32, the ring gear 43 is respectively meshed with the planetary gear 44 on the planetary carrier 41 and the motor gear 301 of the motor 30, and the power output shaft 2 is connected to the planetary carrier 41 or the ring gear 43. The dual clutch 3 can meet different gear shifting requirements and improve the gear shifting efficiency. In the hybrid mode, the vehicle speed ratio can be infinitely adjusted to ensure smooth gear shifting, and the motor power loss can be reduced in the pure electric mode to improve the vehicle's pure electric endurance. In addition, the transmission cancels the hydraulic shifting system and the fork system, and the vehicle shifting is achieved by controlling the clutch, which can reduce redundant components, reduce power loss, and reduce the size and weight of the transmission, thereby realizing a lightweight design of the transmission and reducing the manufacturing cost of the transmission and the entire vehicle.

[0041] In the present embodiment, the forward gear and the reverse gear share a common structural design, and the reverse gear function is achieved by reversing the motor 30, thereby reducing the number of transmission components, reducing the size and weight of the transmission, achieving lightweight transmission, and reducing the manufacturing cost of the transmission; in addition, in the present embodiment, no spare gear positions are set, reducing the number of spare gear position gear sets, further reducing the size and weight of the transmission, and reducing the manufacturing cost of the transmission.

[0042] In some embodiments, the ring gear 43 is a double-sided ring gear, which is arranged on the radial outside of the planetary carrier 41, the inner ring gear 431 of the double-sided ring gear is meshed with the planetary gear 44, the outer ring gear 432 of the double-sided ring gear is meshed with the motor gear 301, and the inner ring gear 431 of the double-sided ring gear is connected to the power output shaft 2 through the first transmission gear 51 or the first transmission gear set.

[0043] like Figures 1 to 4 As shown, the frame body of the planetary carrier 41 is annular, and the annular outer side of the frame body is the radial outer side of the planetary carrier 41. The double-sided gear ring is installed on the annular outer side of the planetary carrier 41, and the inner gear ring 431 of the double-sided gear ring is meshed with the planetary gear 44, and the outer gear ring 432 of the double-sided gear ring is meshed with the motor gear 301, so that the power output by the motor 30 can be smoothly and reliably transmitted to the planetary carrier 41 connected to the planetary gear 44 through the double-sided gear ring. The double-sided gear ring has a certain axial length, and its inner gear ring 431 is meshed with the first transmission gear 51 installed on the power output shaft 2, and the motor power is output to the power output shaft 2 after passing through the gear ring 43. The inner gear ring 431 is connected to the power output shaft 2, which can reduce the size of the transmission along the vehicle height direction and the vehicle width direction, reduce the overall volume of the transmission, and meet the different layout requirements of the vehicle. For example, a compact layout of the whole vehicle can be achieved, or the height of the transmission can be reduced to provide a larger vehicle interior space. In this embodiment, only the first transmission gear 51 is provided to reduce the number of components, reduce the weight of the transmission, shorten the force transmission path, and reduce power loss.

[0044] In a specific implementation, the inner ring 431 can be connected to the power output shaft 2 through a first transmission gear set according to the distance between the motor output shaft 302 and the power output shaft 2, and the first transmission gear set includes at least two transmission gears.

[0045] In this embodiment, the use of an independent double-sided ring gear can set the frame size of the planet carrier 41 to be smaller, and the planetary gear 44 is installed on the outermost side of the annular frame along the circumference of the planetary carrier 41 to provide stable support for the planetary gear 44. A part of the planetary gear 44 is located on the radial inner side of the planetary carrier 41 and meshes with the sun gear 42, and the other part is located on the radial inner side of the planetary carrier 41 and meshes with the ring gear 43, which can reduce the volume and weight of the planetary gear mechanism 4. At the same time, the size of the ring gear 43 and the planetary carrier 41 can be adjusted as needed to facilitate disassembly, maintenance, replacement, etc.

[0046] In other embodiments, the ring gear 43 may include inner teeth arranged on the inner side of the ring of the planet carrier 41, and outer teeth arranged on the outer side of the ring of the planet carrier 41. The planetary gears 44 are all located on the radial inner side of the planet carrier 41 and mesh with the inner teeth. The outer teeth mesh with the motor gear 301. The outer teeth can also be connected to the power output shaft 2 through the first transmission gear 51 or the first transmission gear set. In this case, it is necessary to set an additional support member on the radial inner side of the planet carrier 41 to install the planetary gear 44, or set the radial size of the planet carrier 41 (along the vehicle height direction and the vehicle width direction) to be larger to mesh with the motor gear 301. Since the ring gear 43 is also connected to the power output shaft 2, the weight of the planet carrier 41 will be increased. In addition, when the ring gear 43 and the planet carrier 41 are an integrated structure, the replacement and maintenance costs are high.

[0047] In some embodiments, the first clutch unit 31 and the second clutch unit 32 are coaxially arranged, the second input shaft 12 is a hollow shaft, and the second input shaft 12 is sleeved outside the first input shaft 11. In this way, it is convenient for the two ends of the first input shaft 11 to be connected to the first clutch unit 31 and the sun gear 42 respectively, and the two ends of the second input shaft 12 to be connected to the second clutch unit 32 and the planetary carrier 41 respectively. By moving the first clutch unit 31 along the first input shaft 11 or the second clutch unit 32 along the axial direction of the second input shaft 12, the first clutch unit 31 or the second clutch unit 32 can be engaged or disengaged, thereby achieving gear shifting. The structure is simple and reasonable, and the overall volume of the dual clutch is small. For example, compared with the non-coaxial arrangement of the first clutch unit 31 and the second clutch unit 32 (the first input shaft 11 and the second input shaft are not parallel), the overall radial size of the dual clutch can be reduced, and the balance of power transmission can be ensured.

[0048] The center of the planet carrier 41 facing one end (power input end) of the dual clutch 3 can be provided with a planet carrier input shaft connected to the second input shaft 12. The planet carrier input shaft is also a hollow shaft. When the second clutch unit 32 is engaged, the power input shaft 1 rotates to drive the second clutch unit 32 to rotate, and then drives the second input shaft 12, the planet carrier input shaft, and the planet carrier 41 to rotate in sequence, and the engine power is input through the planet carrier 41. When the first clutch unit 31 is engaged, the power input shaft 1 rotates to drive the first clutch unit 31 to rotate, and then drives the first input shaft 11, the sun gear 42, and the planet gear 44 to rotate, and the engine power is input to the planet carrier 41 connected to the planet gear 44 through the sun gear 42.

[0049] In some embodiments, the first clutch unit 31 includes a first driven disc, the second clutch unit 32 includes a second driven disc, the outer hub of the dual clutch 3 selectively engages or disengages with the first driven disc, and the outer hub of the dual clutch 3 selectively engages or disengages with the second driven disc. The dual clutch 3 is set as an integral structure, and the first driven disc engages with the outer hub of the dual clutch 3 or the second driven disc engages with the outer hub of the dual clutch 3, that is, the first clutch unit 31 and the second clutch unit 32 work alternately, so as to ensure that the power of the engine 20 is continuously transmitted to the wheels, and improve the smoothness and comfort of gear shifting. In addition, the integral dual clutch 3 can reduce the volume and weight of the clutch.

[0050] The dual clutch 3 with two driven discs is prior art and well known to those skilled in the art, so the specific structure and working principle of the dual clutch 3 are not described in detail here.

[0051] In this embodiment, the dual clutch 3 is preferably a dry dual clutch, and the hydraulic shifting system and the fork system are eliminated. The vehicle shifting is achieved by directly controlling the clutch, which can reduce redundant parts, reduce the volume and weight of the transmission, achieve a lightweight design of the transmission, and meet the layout of other components when the layout space of the whole vehicle is limited. For example, the transmission can be compressed to shorten the X-direction (body length direction) dimension of the transmission, and reduce the manufacturing cost of the transmission and the whole vehicle; in addition, the use of a dry dual clutch reduces the hydraulic pump, lubricating fluid, clutch cooling pipe and external cooling system, further meets the spatial structure layout and lightweight requirements of the vehicle, and reduces the manufacturing cost of the whole vehicle; in addition, the dry dual clutch has a high engagement efficiency and cooperates with the motor for stepless speed regulation, avoiding the disadvantage of low heat dissipation rate of the dual clutch 3 when the vehicle is driving in the city due to frequent shifting due to traffic lights, etc., improving the user's shifting experience, and the dry dual clutch is easy to repair and has a low maintenance cost.

[0052] In some embodiments, Figures 1 to 4 As shown, a planetary carrier output shaft 411 is provided on the planetary carrier 41, and the planetary carrier output shaft 411 is connected to the power output shaft 2 through a second transmission gear set. The second transmission gear set includes a second transmission gear 52 and a third transmission gear 53 that are meshed with each other. The second transmission gear 52 is installed on the planetary carrier output shaft 411, and the third transmission gear 53 is installed on the power output shaft 2. The third transmission gear 53 is meshed with the inner gear ring 431 of the double-sided gear ring.

[0053] One axial end of the planet carrier 41 is a power input end for inputting power, and the other axial end is a power output end for outputting power. The second clutch unit 32 can input the engine power to the planet carrier 41 through the second input shaft 12 connected to the axial end of the planet carrier 41, or the first clutch unit 31 can input the engine power to the sun gear 42 through the first input shaft 11 extending from the axial end of the planet carrier 41 into the planet carrier 41.

[0054] A planetary carrier output shaft 411 is arranged at the center of the other end of the planetary carrier 41 axial direction, and is connected to the power output shaft 2 through a second transmission gear set. The second transmission gear set can be used to change the speed ratio of the vehicle and output a greater torque to meet the torque requirements of the vehicle. The second transmission gear set has a second speed ratio i 2 (or the second transmission ratio), when the vehicle is in the 1st gear, the speed ratio of the power output shaft 2 is i 1 *i 2 When the vehicle switches to the 2nd gear, the speed ratio of the power output shaft 2 is i 2 .

[0055] In a specific implementation, multiple sets of second transmission gear sets can be provided according to the vehicle model, or an intermediate gear can be provided between the second transmission gear 52 and the third transmission gear 53, etc. The specific structure of the second transmission gear set is not specifically limited in the present invention.

[0056] In some embodiments, there are at least two planetary gears 44, and at least two planetary gears 44 are symmetrically arranged on the outer periphery of the sun gear 42. For example, in this embodiment, a planetary gear 44 is rotatably installed on the upper and lower side frames of the planetary carrier 41, and the inner and outer sides of the planetary gear 44 are respectively meshed with the sun gear 42 and the inner gear ring 431 of the double-sided gear ring. The planetary gear 44 can also be installed on the left and right sides of the planetary carrier 41, and respectively meshed with the left and right sides of the sun gear 42 and the left and right sides of the inner gear ring 431. The load can be shared by multiple planetary gears 44, and the radial force of the sun gear 42 and the gear ring 43 can be balanced by the planetary gear 44, thereby improving the bearing capacity of the planetary gear structure 4 and ensuring the smoothness of the transmission. The number of planetary gears 44 can be set according to the shape of the planetary carrier 41. For example, when the shape of the planetary carrier 41 is square, a planetary gear 44 can be set at each of the four corners of the planetary carrier 41.

[0057] A second embodiment of the present invention provides a hybrid drive system, including an engine 20 and a motor 30 , and the hybrid drive system also includes the above-mentioned hybrid-specific transmission.

[0058] Further, such as Figure 5 As shown, the hybrid drive system further includes a mechanical pump 40 , a liquid inlet pipeline 401 of the mechanical pump 40 is connected to a filter 501 in an oil pan 50 , and a liquid outlet pipeline 402 of the mechanical pump 40 is connected to an oil circuit of a hybrid-specific transmission.

[0059] The mechanical pump 40 can absorb the oil filtered by the filter 501 in the oil pan 50 to lubricate the hybrid transmission, or provide heat dissipation for the hybrid transmission, so as to fully utilize the oil in the oil pan 50, improve the economy of the vehicle, and meet the lubrication, heat dissipation and other needs of the transmission.

[0060] For example, the liquid outlet pipeline 402 of the mechanical pump 40 can be connected to the ring gear 43 to lubricate the ring gear 43, and the lubricating oil can flow to the planetary gear 44, the planetary carrier 41, and the sun gear 42 through the lubricating oil hole set on the ring gear 43, and then flow to the clutch through the power input shaft 1 or the planetary carrier 41, flow to the motor gear 301 through the planetary gear 44, and flow to the second transmission gear set and the power output shaft 2 through the planetary carrier output shaft 411, so as to achieve lubrication of the entire transmission. That is, when lubricating the transmission, only the mechanical pump 40 and the corresponding oil pipeline need to be added, which is low in cost. The oil circuit of the hybrid transmission can include a central oil channel set on the above-mentioned power input shaft 1, an oil cavity set on the surface of the gears such as the sun gear 42, etc.

[0061] Furthermore, the mechanical pump 40 is connected to the planetary carrier 41 or the ring gear 43 through a transmission mechanism. The mechanical pump 40 can be connected to the planetary carrier 41 through a transmission structure such as a sprocket or a pinion, and part of the power output by the planetary carrier 41 is provided to the mechanical pump 40. The mechanical pump 40 draws the oil in the oil pan 50 to provide lubrication and heat dissipation for the entire transmission. There is no need to set up an additional drive unit for the mechanical pump 40, and the power output by the engine 20 and the motor 30 can be fully utilized to achieve efficient use of power and reduce costs. In pure electric mode, the mechanical pump 40 can be connected to the ring gear 43 through a transmission mechanism, so that the power output by the motor is transmitted to the mechanical pump 40 after passing through the ring gear 43, and power is transmitted to the mechanical pump 40. In a specific implementation, an additional drive motor can be set as needed to provide power for the mechanical pump 40.

[0062] The hybrid drive system corresponds to the hybrid-specific transmission of the above-mentioned embodiment. Any optional items in the hybrid-specific transmission embodiment are also applicable to the embodiment of the hybrid drive system, which will not be described in detail here.

[0063] A third embodiment of the present invention provides a vehicle, comprising the above-mentioned hybrid drive system.

[0064] The vehicle corresponds to the hybrid drive system of the above-mentioned embodiment. Any optional items in the hybrid-specific transmission and hybrid drive system embodiments are also applicable to the vehicle embodiments and will not be described in detail here.

[0065] The above description is only a preferred embodiment of the utility model and an explanation of the technical principles used. Those skilled in the art should understand that the scope of disclosure involved in the utility model is not limited to the technical solution formed by a specific combination of the above technical features, but should also cover other technical solutions formed by any combination of the above technical features or their equivalent features without departing from the above disclosed concept. For example, the above features are replaced with the technical features with similar functions disclosed in the utility model (but not limited to) by each other to form a technical solution.

[0066] Although the subject matter has been described in language specific to structural features and / or methodological logical actions, it should be understood that the subject matter defined in the appended claims is not necessarily limited to the specific features or actions described above. On the contrary, the specific features and actions described above are merely example forms of implementing the claims.

Claims

1. A hybrid transmission, characterized in that: It includes a power input shaft, a power output shaft, a dual clutch and a planetary gear mechanism, the dual clutch is arranged between the engine and the planetary gear mechanism, the output end of the engine is connected to the dual clutch, the dual clutch includes a first clutch unit and a second clutch unit, the power input shaft includes a first input shaft and a second input shaft, the planetary gear mechanism includes a planet carrier, a sun gear and a ring gear, the first clutch unit is connected to the sun gear through the first input shaft, the second clutch unit is connected to the planet carrier through the second input shaft, the engine is engaged with or disengaged from the first input shaft through the first clutch unit, or the engine is engaged with or disengaged from the second input shaft through the second clutch unit, the ring gear is respectively meshed with the planetary gear on the planet carrier and the motor gear of the motor, and the power output shaft is connected to the planet carrier or the ring gear.

2. The hybrid transmission according to claim 1, characterized in that: The gear ring is a double-sided gear ring, which is arranged on the radial outside of the planetary carrier, the inner gear ring of the double-sided gear ring is meshed with the planetary gear, the outer gear ring of the double-sided gear ring is meshed with the motor gear, and the inner gear ring of the double-sided gear ring is connected to the power output shaft through a first transmission gear or a first transmission gear set.

3. The hybrid transmission according to claim 1, characterized in that: The first clutch unit and the second clutch unit are coaxially arranged, the second input shaft is a hollow shaft, and the second input shaft is sleeved outside the first input shaft.

4. The hybrid transmission according to claim 1, characterized in that: The first clutch unit includes a first driven plate, the second clutch unit includes a second driven plate, the outer hub of the dual clutch selectively engages with or disengages from the first driven plate, and the outer hub of the dual clutch selectively engages with or disengages from the second driven plate.

5. The hybrid transmission according to claim 2, characterized in that: The planetary carrier is provided with a planetary carrier output shaft, and the planetary carrier output shaft is connected to the power output shaft through a second transmission gear set. The second transmission gear set includes a second transmission gear and a third transmission gear that are meshed with each other. The second transmission gear is installed on the planetary carrier output shaft, and the third transmission gear is installed on the power output shaft. The third transmission gear is meshed with the inner gear ring of the double-sided gear ring.

6. The hybrid transmission according to claim 1, characterized in that: The dual clutch is a dry dual clutch.

7. A hybrid drive system, comprising an engine and a motor, characterized in that: It also includes a hybrid-specific transmission as described in any one of claims 1-6.

8. The hybrid drive system according to claim 7, characterized in that: It also includes a mechanical pump, wherein the liquid inlet pipeline of the mechanical pump is connected to the filter in the oil pan, and the liquid outlet pipeline of the mechanical pump is connected to the oil circuit of the hybrid transmission.

9. The hybrid drive system according to claim 8, characterized in that: The mechanical pump is connected to the planet carrier or the ring gear through a transmission mechanism.

10. A vehicle, characterized in that: Comprising the hybrid drive system as described in claim 8 or 9.

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