Transmission and power system

Abstract

This invention relates to the field of transmission technology, disclosing a transmission device and a power system. The transmission device includes: a first input shaft; a second input shaft; a third input shaft; a first output shaft, which is simultaneously driven by the first and second input shafts via a transmission assembly, and is also driven by the third input shaft; a planetary reduction unit, having a transmission adjustment assembly and a first planetary gear assembly and a second planetary gear assembly with transmission connection. The first planetary gear assembly has a power input part, and the second planetary gear assembly has a power output part. The power input part is driven by the first output shaft. The power input of the transmission device of this invention is combined with the planetary reduction unit through planetary power splitting to achieve power transmission. It offers a large number of selectable gears, effectively improving the gear utilization efficiency of the transmission device. The engine can continuously operate in the high-efficiency range, improving the efficiency of the power system, reducing fuel consumption, and also improving the working stability and reliability of the transmission device under heavy load conditions.

Description

Technical Field

[0001] This invention relates to the field of transmission technology, specifically to transmission devices and power systems. Background Technology

[0002] With the continuous development of new energy technologies, traditional work vehicles that rely on engines as their core power source are gradually moving towards electric and hybrid powertrains. Hybrid work vehicles, by integrating traditional fuel technology and electric technology, not only improve the vehicle's economy and environmental friendliness, but also enhance its adaptability and work efficiency under various working conditions.

[0003] Currently, existing hybrid vehicles typically use automatic transmissions adapted to low loads. These automatic transmissions have an engine power input shaft and an electric motor power input shaft. The power from the two input shafts is output after coupling through a series of transmission gears and planetary gear systems. Although this achieves a hybrid effect, this type of automatic transmission is a single-speed transmission and can only be used in low-load environments. However, hybrid work vehicles have larger loads and usually operate in complex road conditions, making this type of automatic transmission difficult to meet the usage requirements of hybrid work vehicles. Summary of the Invention

[0004] In view of this, the present invention provides a transmission device and a power system to solve the problem that the transmissions of existing hybrid systems are difficult to effectively meet the needs of hybrid work vehicles.

[0005] In a first aspect, the present invention provides a transmission device, comprising: a first input shaft adapted to be connected to an engine via a power clutch; a second input shaft adapted to be connected to a first power motor; a third input shaft adapted to be connected to a second power motor; a first output shaft, which is simultaneously driven and engaged with both the first input shaft and the second input shaft via a transmission assembly, and the first output shaft is driven and engaged with the third input shaft; the transmission assembly includes a planetary transmission section, a first clutch, and a second clutch, the planetary transmission section including a transmission sun gear, transmission planet gears, a transmission planet carrier, and a transmission ring gear, the first input shaft being detachably driven and engaged with the transmission ring gear via the first clutch, the transmission sun gear being driven and engaged with the second input shaft, the transmission planet carrier being driven and engaged with the first output shaft, and the second clutch being used to separately fix the transmission ring gear; a planetary reduction section having a transmission adjustment assembly and a first planetary gear assembly and a second planetary gear assembly connected in transmission, the first planetary gear assembly having a power input section, the second planetary gear assembly having a power output section, the power input section being driven and engaged with the first output shaft, the transmission adjustment assembly being adapted to adjust the transmission engagement state of the first planetary gear assembly and the second planetary gear assembly, and the planetary reduction section having a first transmission state, a second transmission state, and a third transmission state with gradually decreasing transmission ratios.

[0006] Beneficial effects: The power input to the transmission is combined with the planetary reduction gear through planetary power splitting to achieve power transmission. The planetary reduction gear can adjust the transmission state to achieve three gear ratios, enabling the transmission to achieve pure electric three-speed and hybrid three-speed transmission. Due to the large number of selectable gears, hybrid vehicles can flexibly select the required gear for power output according to their needs, effectively improving the gear utilization efficiency of the transmission. The power from the first and second input shafts is coupled through the planetary transmission and output through the transmission planetary carrier. Since the speed of the transmission planetary carrier is determined by the speeds of the first and second input shafts, when the vehicle operates in hybrid mode, the engine can operate at high efficiency. The power range drives the first input shaft to work continuously. The speed of the transmission planetary carrier can be adjusted by adjusting the power input at the second input shaft, which can effectively improve the efficiency of the power system and reduce fuel consumption. In addition, in this transmission method, since the planetary reduction unit is the main component for speed reduction and torque amplification, and the planetary reduction unit outputs a large torque, the power input at the first output shaft can meet the transmission requirements with a lower torque input. Therefore, the radial force on the first, second, and third input shafts during transmission can be effectively reduced, which can improve the working stability and reliability of the transmission under heavy load conditions. This effectively solves the problem that the transmission of the existing hybrid system cannot effectively meet the needs of hybrid vehicles.

[0007] In one optional embodiment, the transmission assembly further includes a first transmission shaft and a second transmission shaft. The first transmission shaft is rotatably sleeved outside the second input shaft. The first transmission shaft is in transmission engagement with the first input shaft and is also in transmission connection with the transmission gear ring. The second transmission shaft is in transmission connection with the transmission planetary carrier and is in transmission engagement with the first output shaft.

[0008] Beneficial effects: The first drive shaft can extend the transmission engagement position of the transmission gear ring along the axial direction, and the second drive shaft can extend the transmission engagement position of the transmission planetary carrier along the axial direction. After assembly, the overall structure is compact and reliable, which facilitates the transmission engagement between the planetary transmission unit and the corresponding components, while also occupying less space.

[0009] In one alternative embodiment, a first power gear is provided on a first output shaft, a second power gear is provided on a second transmission shaft, and a third power gear is provided on a third input shaft. The first power gear engages in transmission with both the second and third power gears.

[0010] Beneficial effects: By setting a first power gear on the first output shaft, the transmission requirements can be met, which can effectively reduce the number of transmission components and reduce the complexity of the device.

[0011] In one alternative embodiment, the second input shaft, the first drive shaft, and the third input shaft are coaxially arranged, with the second input shaft and the third input shaft located on opposite radial sides of the first output shaft.

[0012] Beneficial effect: This input shaft arrangement allows for a more balanced force distribution during the first output shaft transmission.

[0013] In one optional embodiment, a first mounting seat is provided on the outer peripheral surface of the first drive shaft, the outer hub of the first clutch is connected to the first mounting seat, and the inner hub is connected to the drive gear ring.

[0014] Beneficial effects: With this assembly method, the transmission gear ring only needs a simple connecting structure to connect with the inner hub of the transmission gear ring, which can effectively simplify the structural form of the transmission gear ring. In addition, the connection between the first mounting seat and the outer hub of the first clutch can also form a protective structure on the outside of the first clutch to prevent external components from interfering with the first clutch.

[0015] In one optional embodiment, the first planetary gear assembly includes a first sun gear, a first planet gear, a first planet carrier, and a first ring gear that are in transmission engagement; the second planetary gear assembly includes a second sun gear, a second planet gear, a second planet carrier, and a second ring gear that are in transmission engagement; the first planet carrier is in transmission engagement with the second ring gear; the first ring gear is in transmission engagement with the second sun gear; the first sun gear is a power input part and is connected to the first output shaft; and the second ring gear is a power output part.

[0016] Beneficial effects: The first planetary gear assembly and the second planetary gear assembly have simple and reliable structures. By cooperating with the two planetary gear assemblies, various transmission methods with different transmission ratios can be achieved.

[0017] In one optional embodiment, the planetary reducer further includes a second output shaft and a transmission sleeve. The first planet carrier is connected to the second ring gear via the second output shaft. The transmission sleeve is fitted outside the second output shaft. The first ring gear is connected to the second sun gear via the transmission sleeve. When the planetary reducer is in the first transmission state, the transmission adjustment component fixes the second planet carrier separately. When the planetary reducer is in the second transmission state, the transmission adjustment component fixes the first ring gear separately. When the planetary reducer is in the third transmission state, the planetary reducer fixes the first planet gear assembly as a whole for rotation.

[0018] Beneficial effects: The fit between the second output shaft and the transmission sleeve is simple and reliable. The two fit together by sleeve, resulting in a compact overall structure that occupies less space.

[0019] In one alternative embodiment, the transmission adjustment assembly includes a fixed frame, a third clutch, a fourth clutch, and a fifth clutch. The second planetary carrier is detachably connected to the fixed frame via the third clutch, the first gear ring is detachably connected to the fixed frame via the fourth clutch, and the first gear ring is detachably connected to the first output shaft via the fifth clutch.

[0020] Beneficial effects: The transmission adjustment component has a simple and reliable structure.

[0021] In one alternative implementation, the first clutch, the second clutch, the third clutch, the fourth clutch, and the fifth clutch are all wet clutches.

[0022] Beneficial effects: Wet clutches are more reliable and durable.

[0023] Secondly, the present invention also provides a power system comprising: the aforementioned transmission device; an engine connected to a first input shaft of the transmission device via a power clutch; a first power motor connected to a second input shaft of the transmission device; and a second power motor connected to a third input shaft of the transmission device. Attached Figure Description

[0024] To more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0025] Figure 1 This is a cross-sectional schematic diagram of a speed-changing device according to an embodiment of the present invention;

[0026] Figure 2 for Figure 1 An enlarged schematic diagram of point A of the speed change device shown;

[0027] Figure 3 for Figure 1 The diagram shows the transmission after the first output shaft of the speed change device is assembled with the planetary reduction gear.

[0028] Explanation of reference numerals in the attached figures:

[0029] 1. First input axis; 2. Second input axis;

[0030] 3. Third input shaft; 301. Third power gear;

[0031] 4. First output shaft; 401. First power gear; 402. Second mounting base;

[0032] 5. Transmission assembly; 501. First drive shaft; 5011. First mounting base; 502. Second drive shaft; 5021. Second power gear;

[0033] 6. Planetary transmission unit; 601. Transmission sun gear; 602. Transmission planet gears; 603. Transmission planet carrier; 604. Transmission ring gear;

[0034] 7. First clutch; 8. Second clutch;

[0035] 9. First planetary gear assembly; 901. First sun gear; 902. First planetary gear; 903. First planet carrier; 904. First gear ring;

[0036] 10. Second planetary gear assembly; 1001. Second sun gear; 1002. Second planetary gear; 1003. Second planetary carrier; 1004. Second gear ring;

[0037] 11. Second output shaft; 12. Transmission sleeve; 13. Fixing bracket; 14. Third clutch; 15. Fourth clutch; 16. Fifth clutch;

[0038] 17. Engine; 18. Power clutch; 19. First power motor; 20. Second power motor. Detailed Implementation

[0039] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0040] The following is combined with Figures 1 to 3 The following describes embodiments of the present invention.

[0041] According to an embodiment of the present invention, a transmission device is provided, comprising: a first input shaft 1, a second input shaft 2, a third input shaft 3, a first output shaft 4, and a planetary reduction gear. The first input shaft 1 is adapted to be connected to an engine 17 via a power clutch 18; the second input shaft 2 is adapted to be connected to a first power motor 19; the third input shaft 3 is adapted to be connected to a second power motor 20; the first output shaft 4 is simultaneously engaged with both the first input shaft 1 and the second input shaft 2 via a transmission assembly, and the first output shaft 4 is also engaged with the third input shaft 3. The transmission assembly includes a planetary transmission gear 6, a first clutch 7, and a second clutch 8. The planetary transmission gear 6 includes a transmission sun gear 601, transmission planet gears 602, a transmission planet carrier 603, and a transmission ring gear 6. 04. The first input shaft 1 is detachably connected to the transmission ring gear 604 via the first clutch 7. The transmission sun gear 601 is connected to the second input shaft 2. The transmission planetary carrier 603 is connected to the first output shaft 4. The second clutch 8 is used to fix the transmission ring gear 604 separately. The planetary reduction unit has a transmission adjustment component and a first planetary gear assembly 9 and a second planetary gear assembly 10 that are connected in transmission. The first planetary gear assembly 9 has a power input part, and the second planetary gear assembly 10 has a power output part. The power input part is connected to the first output shaft 4 in transmission. The transmission adjustment component is adapted to adjust the transmission engagement state of the first planetary gear assembly 9 and the second planetary gear assembly 10. The planetary reduction unit has a first transmission state, a second transmission state, and a third transmission state in which the transmission ratio gradually decreases.

[0042] The transmission device of this embodiment uses a planetary power splitting method to combine the input power with the planetary reduction unit to achieve power transmission. The planetary reduction unit can adjust the transmission state to achieve three gear ratios, so that the transmission device can achieve pure electric three-speed and hybrid three-speed transmission. Since there are many selectable gears, hybrid vehicles can flexibly select the required gear for power output according to their needs, which can effectively improve the gear utilization efficiency of the transmission device.

[0043] Specifically, the power from the first input shaft 1 and the second input shaft 2 is coupled through the planetary transmission unit 6 and output through the transmission planetary carrier 603. Since the rotational speed of the transmission planetary carrier 603 is determined by the rotational speed of the first input shaft 1 and the second input shaft 2, when the vehicle is operating in a hybrid state, the engine 17 can drive the first input shaft 1 to work continuously in the high-efficiency range. The rotational speed of the transmission planetary carrier 603 can be adjusted by adjusting the power input at the second input shaft 2, which can effectively improve the efficiency of the power system and reduce fuel consumption.

[0044] In addition, under this transmission method, since the planetary reduction unit is the main component for speed reduction and torque increase, and the planetary reduction unit has a large torque output, the power input of the first output shaft 4 can meet the transmission requirements with a lower torque input. Therefore, the radial force on the first input shaft 1, the second input shaft 2 and the third input shaft 3 during transmission can be effectively reduced, which can improve the working stability and reliability of the transmission device under heavy load conditions and effectively solve the problem that the transmission of the existing hybrid system is difficult to effectively meet the needs of hybrid operation vehicles.

[0045] Specifically, since the transmission device in this embodiment mainly uses a clutch to change the current transmission gear, compared with the sliding sleeve shifting in related technologies, the transmission device in this embodiment will not experience power interruption when shifting gears, and is also more wear-resistant and durable during long-term use.

[0046] In one possible implementation, the transmission assembly 5 further includes a first transmission shaft 501 and a second transmission shaft 502. The first transmission shaft 501 is rotatably sleeved on the outside of the second input shaft 2. The first transmission shaft 501 is in transmission engagement with the first input shaft 1 and is also in transmission connection with the transmission gear ring 604. The second transmission shaft 502 is in transmission connection with the transmission planetary carrier 603 and is in transmission engagement with the first output shaft 4. The first transmission shaft 501 can extend the transmission engagement position of the transmission gear ring 604 along the axial direction, and the second transmission shaft 502 can extend the transmission engagement position of the transmission planetary carrier 603 along the axial direction. After assembly, the overall structure is compact and reliable, which facilitates the transmission engagement of the planetary transmission unit 6 with the corresponding components, while also occupying less space.

[0047] It is understood that, as an alternative implementation, the transmission assembly 5 may not include the first transmission shaft 501 and the second transmission shaft 502. One end face of the transmission gear ring 604 may extend axially to form the required transmission mating sleeve. The transmission mating sleeve is provided with a transmission gear on its outside so that the transmission gear ring 604 can directly engage with the first transmission shaft 501. The transmission planetary carrier 603 may also extend axially to form the required transmission mating shaft. The outer circumferential surface of the transmission mating shaft is provided with a transmission gear so that the transmission planetary carrier 603 can directly engage with the first output shaft 4.

[0048] In one possible implementation, a first power gear 401 is mounted on the first output shaft 4, a second power gear 5021 is mounted on the second transmission shaft 502, and a third power gear 301 is mounted on the third input shaft 3. The first power gear 401 engages in transmission with both the second power gear 5021 and the third power gear 301. By using only one first power gear 401 on the first output shaft 4, the transmission requirements can be met, effectively reducing the number of transmission components and simplifying the device.

[0049] It is understood that, as an alternative implementation, two first power gears 401 can also be provided on the first input shaft 1, and the second power gear 5021 and the third power gear 301 can respectively drive and cooperate with the corresponding first power gear 401. In this arrangement, the transmission ratio of the first power gear 401 can also be changed by changing the transmission radius of the corresponding first power gear 401.

[0050] In one possible implementation, the second input shaft 2, the first transmission shaft 501, and the second transmission shaft 502 are coaxially arranged, and the second input shaft 2 and the third input shaft 3 are located on opposite radial sides of the first output shaft 4. This arrangement of input shafts can make the first output shaft 4 more balanced in terms of force during transmission.

[0051] It is understood that, as an alternative implementation, if required, the second input shaft 2, the first transmission shaft 501, and the second transmission shaft 502 can be configured such that two of them are coaxial, or all three are configured to be non-coaxial.

[0052] In one possible implementation, a first mounting seat 5011 is provided on the outer peripheral surface of the first drive shaft 501. The outer hub of the first clutch 7 is connected to the first mounting seat 5011, and the inner hub is connected to the drive gear ring 604. In this assembly method, the drive gear ring 604 only needs a simple connection structure to be connected to the inner hub of the drive gear ring 604, which can effectively simplify the structural form of the drive gear ring 604. In addition, the connection between the first mounting seat 5011 and the outer hub of the first clutch 7 can also form a protective structure on the outside of the first clutch 7 to prevent external components from interfering with the first clutch 7.

[0053] It is understood that, as an alternative implementation, the outer hub of the first clutch 7 may be connected to the transmission gear ring 604, and the inner hub may be connected to the first mounting base 5011.

[0054] Specifically, the first mounting base 5011 is an annular component sleeved on the outer circumferential surface of the first drive shaft 501. The first mounting base 5011 has an annular mounting groove on the side facing the drive gear ring 604. The first clutch 7 is disposed in the mounting groove. This type of first mounting base 5011 provides mounting space for the first clutch 7. During assembly, the first mounting base 5011 can be moved along with the drive shaft 5011.

[0055] In one possible implementation, the first planetary gear assembly 9 includes a first sun gear 901, a first planet gear 902, a first planet carrier 903, and a first ring gear 904 that are in a transmission engagement. The second planetary gear assembly 10 includes a second sun gear 1001, a second planet gear 1002, a second planet carrier 1003, and a second ring gear 1004 that are in a transmission engagement. The first planet carrier 903 is in a transmission engagement with the second ring gear 1004, and the first ring gear 904 is in a transmission engagement with the second sun gear 1001. The first sun gear 901 is a power input part and is connected to the first output shaft 4. The second ring gear 1004 is a power output part. The first planetary gear assembly 9 and the second planetary gear assembly 10 have simple and reliable structures. By cooperating with the two planetary gear assemblies, various transmission methods with different transmission ratios can be realized.

[0056] In one possible implementation, the planetary reducer further includes a second output shaft 11 and a transmission sleeve 12. The first planetary carrier 903 is connected to the second ring gear 1004 via the second output shaft 11. The transmission sleeve 12 is sleeved on the outside of the second output shaft 11. The first ring gear 904 is connected to the second sun gear 1001 via the transmission sleeve 12. When the planetary reducer is in the first transmission state, the transmission adjustment component fixes the second planetary carrier 1003 separately. When the planetary reducer is in the second transmission state, the transmission adjustment component fixes the first ring gear 904 separately. When the planetary reducer is in the third transmission state, the planetary reducer fixes the first planetary gear assembly 9 as a whole for rotation. The cooperation between the second output shaft 11 and the transmission sleeve 12 is simple and reliable. The two are engaged by sleeve, resulting in a compact overall structure and a small footprint.

[0057] Specifically, the fixing method for the planetary reduction section to fix the first planetary gear assembly 9 as a whole for rotation is not limited. It can be that the first output shaft 4 is fixedly connected to the first gear ring 904, the first output shaft 4 is fixedly connected to the first planet carrier 903, the first sun gear 901 is fixedly connected to the first planet carrier 903, or the first sun gear 901 is fixedly connected to the first gear ring 904. As long as the first sun gear 901, the first planet gear 902 and the first planet carrier 903 can rotate as a whole, it is acceptable.

[0058] In one possible implementation, the transmission adjustment assembly includes a fixed frame 13, a third clutch 14, a fourth clutch 15, and a fifth clutch 16. The second planetary carrier 1003 is detachably connected to the fixed frame 13 via the third clutch 14. The first gear ring 904 is detachably connected to the fixed frame 13 via the fourth clutch 15. The first gear ring 904 is detachably connected to the first output shaft 4 via the fifth clutch 16. The transmission adjustment assembly has a simple and reliable structure.

[0059] Among them, the third clutch 14 and the fourth clutch 15 are brakes, which play a braking role.

[0060] Specifically, in the first transmission state, the first output shaft 4 transmits power to the first sun gear 901. At this time, the third clutch 14 locks the second planetary carrier 1003. Part of the power of the first sun gear 901 is output through the first planetary carrier 903 driven by the first planetary gear 902. The first planetary carrier 903 is connected to the second output shaft 11 through a spline. The other part of the power of the first sun gear 901 is output through the first ring gear 904 driven by the first planetary gear 902. The first ring gear 904 drives the second sun gear 1001 to rotate through the transmission sleeve 12. The rotation of the second sun gear 1001 drives the second planetary gear 1002 to rotate, which in turn drives the second ring gear 1004 to rotate. The power of the second ring gear 1004 is coupled with the power on the second output shaft 11 and then output.

[0061] When in the second transmission state, the first output shaft 4 transmits power to the first sun gear 901. At this time, the fourth clutch 15 locks the first gear ring 904. All the power of the first sun gear 901 is output through the first planetary carrier 903 driven by the first planetary gear 902. The first planetary carrier 903 is connected to the second output shaft 11 through a spline.

[0062] When in the third transmission state, the first output shaft 4 transmits power to the first sun gear 901. At this time, the fifth clutch 16 fixes the first gear ring 904 to the first output shaft 4. At this time, the first planetary gear assembly 9 rotates as a whole. The power of the first sun gear 901 is directly output through the first planetary carrier 903. The first planetary carrier 903 is connected to the second output shaft 11 through a spline.

[0063] The fixing frame 13 can be a separate frame or the housing of the transmission device itself.

[0064] In addition, a second mounting seat 402 is provided on the outer peripheral surface of the first output shaft 4, the outer hub of the fifth clutch 16 is connected to the second mounting seat 402, and the inner hub of the fifth clutch 16 is connected to the first gear ring 904.

[0065] It is understood that, as an alternative implementation, the inner hub of the fifth clutch 16 can also be connected to the second mounting base 402, while the outer hub is connected to the first gear ring 904, which can be flexibly selected according to requirements.

[0066] Specifically, such as Figure 1 As shown, the second mounting base 402 is a separate component, which is connected to the outer peripheral surface of the first output shaft 4 through an assembly step.

[0067] In one possible implementation, the first clutch 7, the second clutch 8, the third clutch 14, the fourth clutch 15, and the fifth clutch 16 are all wet clutches, which are more reliable and durable.

[0068] The gear positions of the transmission device in this embodiment will be described in detail below:

[0069] Pure electric mode: such as Figure 1 As shown, when the power clutch 18 is disengaged, the engine 17 is not engaged in operation. At this time, the second clutch 8 fixes the transmission gear ring 604 separately. The power of the first power motor 19 is transmitted to the transmission sun gear 601 through the second input shaft 2. The transmission sun gear 601 drives the transmission planetary carrier 603 to rotate and transmits the power to the first output shaft 4 through the transmission planetary carrier 603. The second power motor 20 transmits the power to the first output shaft 4 through the third input shaft 3. It can be a single motor working or two motors working simultaneously.

[0070] Hybrid mode: such as Figure 1 As shown, this is the state where the engine 17 is engaged when the power clutch 18 is engaged. At this time, the second clutch 8 is disengaged. The engine 17 drives the transmission ring gear 604 to rotate through the first input shaft 1. The power of the first power motor 19 is transmitted to the transmission sun gear 601 through the second input shaft 2. The transmission sun gear 601 and the transmission ring gear 604 simultaneously drive the transmission planetary carrier 603 to rotate. The transmission planetary carrier 603 outputs a hybrid power from the engine 17 and the first power motor 19. The hybrid power is transmitted to the first output shaft 4 through the transmission planetary carrier 603. The second power motor 20 transmits power to the first output shaft 4 through the third input shaft 3.

[0071] When the first clutch 7, the second clutch 8, the third clutch 14, the fourth clutch 15, and the fifth clutch 16 are all disengaged, it is in neutral (N) gear.

[0072] like Figure 1As shown, when only the power clutch 18 and the third clutch 14 are engaged, the engine 17 drives the first transmission shaft 501 to rotate via the first input shaft 1. The first transmission shaft 501 drives the transmission ring gear 604 to rotate. The power of the first power motor 19 is transmitted to the transmission sun gear 601 via the second input shaft 2. The transmission sun gear 601 and the transmission ring gear 604 simultaneously drive the transmission planetary carrier 603 to rotate. The transmission planetary carrier 603 outputs the hybrid power of the engine 17 and the first power motor 19 and drives the second transmission shaft 502 to rotate. The hybrid power is transmitted to the second transmission shaft 502. The power of the second power motor 20 is transmitted to the third input shaft 3. The second transmission shaft 502 and the third input shaft 3 simultaneously drive the first output shaft 4 to rotate. The first output shaft 4 transmits power to the first sun gear 901. At this time, the third clutch 14 locks the second planetary carrier 1003. Part of the power from the first sun gear 901 is output through the first planetary carrier 903 driven by the first planetary gear 902. The first planetary carrier 903 is connected to the second output shaft 11 via a spline. The other part of the power from the first sun gear 901 is output through the first ring gear 904 driven by the first planetary gear 902. The first ring gear 904 drives the second sun gear 1001 to rotate through the transmission sleeve 12. The rotation of the second sun gear 1001 drives the second planetary gear 1002 to rotate, which in turn drives the second ring gear 1004 to rotate. The power of the second ring gear 1004 is coupled with the power on the second output shaft 11 and output. The above is the transmission process of the first gear.

[0073] The specific gear position is mainly controlled by the working status of various shifting components such as clutches. The working status of the shifting components for other gears is shown in Table 1 below:

[0074]

[0075] Table 1 Coupling methods of shifting components

[0076] It should be noted that, in the table above, the circled area indicates that the clutch is engaged, and the uncircled area indicates that the clutch is disengaged; in pure electric or hybrid mode, the gear ratios of gears one through six decrease sequentially; the pure electric and hybrid modes shown in the table above refer to the situation where the first power motor 19 and the second power motor 20 output power simultaneously, or it can be that only one of the motors outputs power.

[0077] According to an embodiment of the present invention, in another aspect, a power system is provided, comprising: the aforementioned transmission device, engine 17, first power motor 19, and second power motor 20, wherein engine 17 is connected to the first input shaft 1 of the transmission device via a power clutch 18; the first power motor 19 is connected to the second input shaft 2 of the transmission device; and the second power motor 20 is connected to the third input shaft 3 of the transmission device.

[0078] Although embodiments of the invention have been described in conjunction with the accompanying drawings, those skilled in the art can make various modifications and variations without departing from the spirit and scope of the invention, and such modifications and variations all fall within the scope defined by the appended claims.

Claims

1. A speed-changing device, characterized in that, include: The first input shaft (1) is adapted to be connected to the engine (17) via a power clutch (18); The second input shaft (2) is adapted to be connected to the first power motor (19); The third input shaft (3) is adapted to be connected to the second power motor (20); The first output shaft (4) is simultaneously driven by the first input shaft (1) and the second input shaft (2) through a transmission assembly, and the first output shaft (4) is driven by the third input shaft (3). The transmission assembly includes a planetary transmission unit (6), a first clutch (7), and a second clutch (8). The planetary transmission unit (6) includes a transmission sun gear (601), transmission planet gears (602), a transmission planet carrier (603), and a transmission ring gear (604) that are in transmission engagement. The first input shaft (1) is detachably connected to the transmission ring gear (604) through the first clutch (7). The transmission sun gear (601) is in transmission engagement with the second input shaft (2). The transmission planet carrier (603) is in transmission engagement with the first output shaft (4). The second clutch (8) is used to fix the transmission ring gear (604) separately. The planetary reduction unit has a first planetary gear assembly (9) and a second planetary gear assembly (10) with a transmission adjustment component and a transmission connection. The first planetary gear assembly (9) has a power input component, and the second planetary gear assembly (10) has a power output component. The power input component is transmissionally connected to the first output shaft (4). The transmission adjustment component is adapted to adjust the transmission engagement state of the first planetary gear assembly (9) and the second planetary gear assembly (10). The planetary reduction unit has a first transmission state, a second transmission state, and a third transmission state with a gradually decreasing transmission ratio.

2. The speed change device according to claim 1, characterized in that, The transmission assembly further includes a first transmission shaft (501) and a second transmission shaft (502). The first transmission shaft (501) is rotatably sleeved on the outside of the second input shaft (2). The first transmission shaft (501) is in transmission engagement with the first input shaft (1) and is in transmission connection with the transmission gear ring (604). The second transmission shaft (502) is in transmission connection with the transmission planetary carrier (603) and is in transmission engagement with the first output shaft (4).

3. The speed change device according to claim 2, characterized in that, A first power gear (401) is provided on the first output shaft (4), a second power gear (5021) is provided on the second transmission shaft (502), and a third power gear (301) is provided on the third input shaft (3). The first power gear (401) is simultaneously engaged with the second power gear (5021) and the third power gear (301).

4. The speed change device according to claim 2, characterized in that, The second input shaft (2), the first transmission shaft (501) and the second transmission shaft (502) are coaxially arranged, and the second input shaft (2) and the third input shaft (3) are located on opposite sides of the first output shaft (4) in a radial direction.

5. The speed change device according to claim 2, characterized in that, A first mounting seat (5011) is provided on the outer peripheral surface of the first drive shaft (501), the outer hub of the first clutch (7) is connected to the first mounting seat (5011), and the inner hub is connected to the drive gear ring (604).

6. The speed change device according to any one of claims 1 to 5, characterized in that, The first planetary gear assembly (9) includes a first sun gear (901), a first planet gear (902), a first planet carrier (903), and a first ring gear (904) that are in transmission engagement. The second planetary gear assembly (10) includes a second sun gear (1001), a second planet gear (1002), a second planet carrier (1003), and a second ring gear (1004) that are in transmission engagement. The first planet carrier (903) is in transmission engagement with the second ring gear (1004), and the first ring gear (904) is in transmission engagement with the second sun gear (1001). The first sun gear (901) is the power input part and is connected to the first output shaft (4). The second ring gear (1004) is the power output part.

7. The speed change device according to claim 6, characterized in that, The planetary reduction gear also includes a second output shaft (11) and a transmission sleeve (12). The first planet carrier (903) is connected to the second gear ring (1004) via the second output shaft (11). The transmission sleeve (12) is sleeved on the outside of the second output shaft (11). The first gear ring (904) is connected to the second sun gear (1001) via the transmission sleeve (12). When the planetary reduction unit is in the first transmission state, the transmission adjustment component fixes the second planetary carrier (1003) separately. When the planetary reduction unit is in the second transmission state, the transmission adjustment component fixes the first gear ring (904) separately. When the planetary reduction unit is in the third transmission state, the planetary reduction unit fixes the first planetary gear assembly (9) as a whole for rotation.

8. The speed change device according to claim 7, characterized in that, The transmission adjustment assembly includes a fixed frame (13), a third clutch (14), a fourth clutch (15), and a fifth clutch (16). The second planetary carrier (1003) is detachably connected to the fixed frame (13) via the third clutch (14). The first gear ring (904) is detachably connected to the fixed frame (13) via the fourth clutch (15). The first gear ring (904) is detachably connected to the first output shaft (4) via the fifth clutch (16).

9. The speed change device according to claim 8, characterized in that, The first clutch (7), the second clutch (8), the third clutch (14), the fourth clutch (15) and the fifth clutch (16) are all wet clutches.

10. A power system, characterized in that, include: The speed change device according to any one of claims 1 to 9; The engine (17) is connected to the first input shaft (1) of the transmission device via a power clutch (18); The first power motor (19) is connected to the second input shaft (2) of the speed change device; The second power motor (20) is connected to the third input shaft (3) of the speed change device.

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