CN220682135U - Hybrid power speed change device of medium and heavy vehicle - Google Patents
Hybrid power speed change device of medium and heavy vehicle Download PDFInfo
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- CN220682135U CN220682135U CN202322296676.7U CN202322296676U CN220682135U CN 220682135 U CN220682135 U CN 220682135U CN 202322296676 U CN202322296676 U CN 202322296676U CN 220682135 U CN220682135 U CN 220682135U
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- 230000007246 mechanism Effects 0.000 claims abstract description 64
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
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Abstract
The utility model provides a hybrid power speed change device of a medium-heavy vehicle, comprising: the device comprises an input shaft, an intermediate shaft and an output shaft; a first motor; a second motor; a third motor; a power splitting mechanism; a planetary transmission mechanism; the input shaft is connected with the engine, the power splitting mechanism is connected with the planetary speed change mechanism through the intermediate shaft, and the planetary speed change mechanism is connected with wheels through the output shaft to transmit power to drive the vehicle; the power splitting mechanism comprises a first planetary row and a second planetary row, a first gear ring is fixedly connected with the second gear ring, a first planet carrier is fixedly connected with a second sun gear and is connected with an input shaft, the first sun gear is connected with a first motor, the second planet carrier is connected with an intermediate shaft, and a third motor is connected with the intermediate shaft; the planetary transmission mechanism comprises a third planetary row and a fourth planetary row. By combining a hybrid module having continuously variable transmission characteristics with a planetary transmission module, a hybrid transmission device having a relatively simple structure and capable of realizing power shifting is obtained.
Description
[ technical field ]
The utility model relates to the technical field of vehicle driving, in particular to a hybrid power speed change device of a medium-heavy vehicle.
[ background Art ]
The existing medium and heavy truck adopts a P2 hybrid power system, a driving motor is arranged between an engine and a gearbox, the driving motor is positioned behind a main clutch and is connected with an input shaft of the gearbox, and the gearbox adopts at least 10 or 12 forward gears of manual or AMT gearboxes. Such gearboxes are difficult to achieve power uninterrupted gear shifting and have limited oil saving effects.
Accordingly, it is also desirable to provide a hybrid transmission that is capable of power-uninterrupted shifting and has a simple structure, particularly suitable for use in medium-and heavy-duty vehicles.
[ summary of the utility model ]
In order to overcome the problems in the prior art, the utility model provides the hybrid power transmission device of the medium-heavy vehicle, which has a simple structure and can realize power shift.
The utility model provides a hybrid power speed change device for medium and heavy vehicles, which comprises:
the device comprises an input shaft, an intermediate shaft and an output shaft; one end of the input shaft is connected with an engine, the other end of the input shaft is connected with a power splitting mechanism, the power splitting mechanism is connected with a planetary speed change mechanism through the intermediate shaft, and the planetary speed change mechanism is connected with wheels through the output shaft to transmit power to drive a vehicle;
the power splitting mechanism comprises a first planet row and a second planet row, wherein the first planet row comprises a first sun gear, a first planet carrier and a first gear ring, the second planet row comprises a second sun gear, a second planet carrier and a second gear ring, the first gear ring is fixedly connected with the second gear ring, the first planet carrier is fixedly connected with the second sun gear and is connected with the input shaft, the first sun gear is connected with the first motor, the second planet carrier is connected with the intermediate shaft, and the second motor is connected with the intermediate shaft;
the planetary transmission mechanism comprises a third planetary row and a fourth planetary row, wherein the third planetary row comprises a third sun gear, a third planet carrier and a third gear ring, and the fourth planetary row comprises a fourth sun gear, a fourth planet carrier and a fourth gear ring.
Preferably, the planetary transmission mechanism further includes a first brake, a second brake, a first clutch, and a second clutch.
Preferably, the third sun gear is fixedly connected with the fourth sun gear, the third planet carrier is fixedly connected with the fourth gear ring, the fourth planet carrier is connected with the output shaft, the third gear ring is connected with the frame through the first brake, the fourth gear ring is connected with the frame through the second brake, the intermediate shaft is connected with the third sun gear through the first clutch, and the intermediate shaft is further connected with the third planet carrier through the second clutch.
Preferably, the planetary transmission mechanism further includes a one-way clutch, and the intermediate shaft is connected to the third sun gear through the one-way clutch.
Preferably, the first brake is disengaged, the first clutch is closed, the second brake is closed, the second clutch is disengaged, and the planetary transmission mechanism achieves 1 st gear;
the first brake is closed, the first clutch is closed, the second brake is separated, the second clutch is separated, and the planetary speed change mechanism realizes 2 gears;
the first brake is separated, the first clutch is closed, the second brake is separated, the second clutch is closed, and the planetary speed change mechanism realizes 3 gears; and
the first brake is closed, the first clutch is separated, the second brake is separated, the second clutch is closed, and the planetary transmission mechanism realizes 4 gears.
Preferably, the motor further comprises a third motor, and the third motor is connected with the intermediate shaft.
Preferably, the first, second and third transmission gear sets are further included.
Preferably, the first motor, the second motor, and the third motor are offset within a peripheral space of the input shaft; the first motor is connected with the first sun gear through a first transmission gear set; the second motor and the third motor are connected with the intermediate shaft through a second transmission gear set and a third transmission gear set respectively.
Preferably, the first, second and third drive gear sets are fixed axis gear sets.
Compared with the prior art, the hybrid power speed change device combines the hybrid power module with the stepless speed change characteristic with the planetary speed change module, and utilizes the larger stepless speed change characteristic of the hybrid power module, so that the gear of the planetary speed change module is reduced, and the hybrid power speed change device which has a simpler structure and can realize power gear change is obtained.
[ description of the drawings ]
FIG. 1 is a schematic structural view of a hybrid transmission for a medium-heavy vehicle according to an embodiment of the present utility model;
FIG. 2 is a power flow schematic diagram of the planetary transmission mechanism of the hybrid transmission of the medium and heavy vehicle of the embodiment of FIG. 1 in gear 1;
FIG. 3 is a power flow schematic diagram of the planetary transmission mechanism of the hybrid transmission of the medium and heavy vehicle of the embodiment of FIG. 1 in 2 gear;
FIG. 4 is a power flow schematic of the planetary transmission mechanism of the hybrid transmission of the medium and heavy vehicle of the embodiment of FIG. 1 in 3-speed;
fig. 5 is a power flow schematic diagram of the planetary transmission mechanism of the hybrid transmission of the medium-heavy vehicle of the embodiment of fig. 1 in 4 th gear.
Detailed description of the preferred embodiments
For the purpose of making the technical solutions and advantages of the present utility model more apparent, the present utility model will be described in further detail below with reference to the accompanying drawings and examples. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the utility model.
As shown in fig. 1, a hybrid transmission for a medium and heavy vehicle includes: an input shaft 11, an intermediate shaft 12, and an output shaft 13; a first motor 2; a second motor 31; a third motor 32; a power splitting mechanism 6; a planetary transmission mechanism 7; one end of an input shaft 11 is connected with an engine 4, the other end of the input shaft 11 is connected with a power splitting mechanism 6, the power splitting mechanism 6 is connected with a planetary speed change mechanism 7 through an intermediate shaft 12, and the planetary speed change mechanism 7 is connected with wheels 8 through an output shaft 13 to transmit power to drive the vehicle;
the power splitting mechanism 6 comprises a first planetary row 61 and a second planetary row 62, the first planetary row 61 comprises a first sun gear 611, a first planet carrier 612 and a first gear ring 613, the second planetary row 62 comprises a second sun gear 621, a second planet carrier 622 and a second gear ring 623, the first gear ring 613 is fixedly connected with the second gear ring 623, the first planet carrier 612 is fixedly connected with the second sun gear 621 and is connected with the input shaft 11, the first sun gear 611 is connected with the first motor 2, the second planet carrier 622 is connected with the intermediate shaft 12, and the second motor 31 and the third motor 32 are respectively connected with the intermediate shaft 12;
the planetary transmission mechanism 7 includes a third planetary row 71 and a fourth planetary row 72, the third planetary row 71 including a third sun gear 711, a third carrier 712, and a third ring gear 713, and the fourth planetary row 72 including a fourth sun gear 721, a fourth carrier 722, and a fourth ring gear 723.
A power splitting mechanism 6, a first motor 2, a second motor 31 and a third motor 32 with stepless speed regulation characteristics; the formed hybrid power module is combined with the planetary speed change mechanism 7, and the gear position of the planetary speed change mechanism 7 is reduced by utilizing the larger stepless speed change characteristic of the hybrid power module, so that the hybrid power speed change device which has a simpler structure and can realize power gear change is obtained.
The first planetary gear set 61 and the second planetary gear set 62 constitute a power split mechanism 6 for splitting the engine power input from the first planetary gear set 612 into two paths, i.e., one path of power is output by the first sun gear 611 to drive the first motor 2 to generate electricity, and the other path of power is output by the second planetary gear set 622 to drive the vehicle. From the kinematic equations of the first planetary row 61 and the second planetary row 62, the following equations (1) and (2) of kinematics and dynamics can be obtained after analysis:
T m1 :T out :T in ＝k 2 :k 1 (1+k 2 ):(k 1 +k 2 +k 1 k 2 ) (2)
in the formula: n is n m1 、n out 、n in 、T m1 、T out 、T in 、k 1 、k 2 The first motor 2 speed, the output speed, the input speed, the first motor 2 torque, the output torque, the input torque, the structural characteristic parameters of the first planetary gear set 61 and the structural characteristic parameters of the second planetary gear set 62 are respectively, wherein the input end is the first planetary gear set 612 connected with the input shaft 11, and the output end is the second planetary gear set 622 connected with the intermediate shaft 12.
The second motor 31 and the second motor 31 are respectively connected with the intermediate shaft 12 to apply torque to the intermediate shaft 12 to provide an appropriate torque to satisfy that the hybrid module including the engine 4 has an appropriate output characteristic, which is then shifted through the speed change of the planetary transmission mechanism 7 to obtain an output characteristic required for satisfying the medium-heavy vehicle.
Preferably, the planetary transmission mechanism 7 further includes a first brake 73, a second brake 74, a first clutch 75, and a second clutch 76. By means of a plurality of shift elements, a plurality of forward gears can be achieved, which cooperate with the hybrid module to provide the desired driving characteristics.
Preferably, the third sun gear 711 is fixedly connected to the fourth sun gear 721, the third planet carrier 712 is fixedly connected to the fourth ring gear 723, the fourth planet carrier 722 is fixedly connected to the output shaft 13, the third ring gear 713 is connected to the frame 78 via the first brake 73, the fourth ring gear 723 is connected to the frame 78 via the second brake 74, the intermediate shaft 12 is connected to the third sun gear 711 via the first clutch 75, and the intermediate shaft 12 is also connected to the third planet carrier 712 via the second clutch 76.
Preferably, the planetary gear mechanism 7 further includes a one-way clutch 77, and the intermediate shaft 12 is connected to a third sun gear 711 through the one-way clutch 77. The one-way clutch 77 can be used to fix or decouple the intermediate shaft 12 to the third sun gear 711, and in the case of the 1 and 2 gears of the planetary gear, the intermediate shaft 12 is fixed to the third sun gear 711, and the first clutch 75 together takes up the input torque. The intermediate shaft 12 is decoupled from the third sun gear 711 in rotation when gear 4 of the planetary transmission is engaged.
FIG. 2 is a power flow schematic diagram of the planetary transmission mechanism of the hybrid transmission of the medium and heavy vehicle of the embodiment of FIG. 1 in gear 1; FIG. 3 is a power flow schematic diagram of the planetary transmission mechanism of the hybrid transmission of the medium and heavy vehicle of the embodiment of FIG. 1 in 2 gear; FIG. 4 is a power flow schematic of the planetary transmission mechanism of the hybrid transmission of the medium and heavy vehicle of the embodiment of FIG. 1 in 3-speed; fig. 5 is a power flow schematic diagram of the planetary transmission mechanism of the hybrid transmission of the medium-heavy vehicle of the embodiment of fig. 1 in 4 th gear.
As shown in fig. 2, the first brake 73 is disengaged, the first clutch 75 is closed, the second brake 74 is closed, the second clutch 76 is disengaged, and the planetary transmission mechanism 7 achieves 1 st gear, the speed ratio of which is shown in formula (3):
1+k 4 (3)
as shown in fig. 3, the first brake 73 is closed, the first clutch 75 is closed, the second brake 74 is disengaged, the second clutch 76 is disengaged, and the planetary transmission mechanism 7 achieves 2 nd gear, the speed ratio of which is shown in formula (4):
as shown in fig. 4, the first brake 73 is disengaged, the first clutch 75 is closed, the second brake 74 is disengaged, the second clutch 76 is closed, and the planetary transmission mechanism 7 achieves 3 speed, the speed ratio of which is shown in formula (5):
1(5)
as shown in fig. 5, the first brake 73 is closed, the first clutch 75 is disengaged, the second brake 74 is disengaged, the second clutch 76 is closed, and the planetary transmission mechanism 7 achieves 4 th gear, the speed ratio of which is shown in formula (6):
wherein k is 3 、k 4 The structural characteristic parameter of the third planetary row 71 and the structural characteristic parameter of the fourth planetary row 72, respectively. Furthermore, the first brake 73 is closed, i.e. the third ring gear 713 is connected to the frame 78, the rotational speed of which is zero; the second brake 74 is closed, i.e. the fourth ring gear 723 is connected to the frame 78 at a speed of zero; the first clutch 75 is closed, and the intermediate shaft 12 and the third sun gear 711 are connected and integrally rotated; the second clutch 76 is closed, and the intermediate shaft 12 is connected to the third carrier 712 to rotate integrally therewith.
Preferably, a third motor 32 is also included, the third motor 32 being connected to the intermediate shaft 12. When the structure is limited or there is no motor with a large output torque, a plurality of motors may be employed together to provide the torque applied to the intermediate shaft 12.
Preferably, the first motor 2, the second motor 31 and the third motor 32 are biased in the peripheral space of the input shaft 11; the first motor 2 is connected with the first sun gear 611 through the first transmission gear set 51; the second and third electric machines 31 and 32 are connected to the intermediate shaft 12 via a second and third drive gear set 52 and 53, respectively.
Preferably, the first, second and third drive gear sets 51, 52 and 53 are dead axle gear sets. Because the three motors are all offset from the input shaft 11, a coaxial planetary gear set is not required, and a fixed shaft transmission gear set with a simpler structure can be adopted. The first transmission gear set 51 plays a role in accelerating the first motor 2, namely, one path of power split by the power splitting mechanism 6 of the engine 4 is accelerated and then drives the first motor 2 to generate power. The second and third transmission gear sets 52 and 53 serve to decelerate the second and third motors 31 and 32, that is, to decelerate the power of the second and third motors 31 and 32 and output the decelerated power to the intermediate shaft 12.
The hybrid power transmission device of the medium-heavy vehicle of the embodiment of the utility model comprises: the device comprises an input shaft, an intermediate shaft and an output shaft; a first motor; a second motor; a power splitting mechanism; a planetary transmission mechanism; the input shaft is connected with an engine, the power splitting mechanism is connected with the planetary speed change mechanism through the intermediate shaft, and the planetary speed change mechanism is connected with wheels through the output shaft to transmit power to drive a vehicle; the power splitting mechanism comprises a first planet row and a second planet row, wherein the first planet row comprises a first sun gear, a first planet carrier and a first gear ring, the second planet row comprises a second sun gear, a second planet carrier and a second gear ring, the first gear ring is fixedly connected with the second gear ring, the first planet carrier is fixedly connected with the second sun gear and is connected with the input shaft, the first sun gear is connected with the first motor, the second planet carrier is connected with the intermediate shaft, and the second motor is connected with the intermediate shaft; the planetary transmission mechanism comprises a third planetary row and a fourth planetary row, wherein the third planetary row comprises a third sun gear, a third planet carrier and a third gear ring, and the fourth planetary row comprises a fourth sun gear, a fourth planet carrier and a fourth gear ring. The hybrid power module with the stepless speed regulation characteristic is combined with the planetary speed change module, and the larger stepless speed change characteristic of the hybrid power module is utilized, so that the gear of the planetary speed change module is reduced, and the hybrid power speed change device which has a simpler structure and can realize power gear shifting is obtained.
The embodiments of the present utility model described above do not limit the scope of the present utility model. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present utility model should be included in the scope of the present utility model as set forth in the appended claims.
Claims (9)
1. A hybrid transmission for a medium and heavy vehicle, comprising:
the device comprises a first motor, a second motor, an input shaft, an intermediate shaft and an output shaft; one end of the input shaft is connected with an engine, the other end of the input shaft is connected with a power splitting mechanism, the power splitting mechanism is connected with a planetary speed change mechanism through the intermediate shaft, and the planetary speed change mechanism is connected with wheels through the output shaft to transmit power to drive a vehicle;
the power splitting mechanism comprises a first planet row and a second planet row, the first planet row comprises a first sun gear, a first planet carrier and a first gear ring, the second planet row comprises a second sun gear, a second planet carrier and a second gear ring, the first gear ring is fixedly connected with the second gear ring, the first planet carrier is fixedly connected with the second sun gear and is connected with the input shaft, the first sun gear is connected with the first motor, the second planet carrier is connected with the intermediate shaft, and the second motor is connected with the intermediate shaft;
the planetary transmission mechanism includes a third planetary row including a third sun gear, a third carrier, and a third ring gear, and a fourth planetary row including a fourth sun gear, a fourth carrier, and a fourth ring gear.
2. The hybrid transmission of a medium and heavy vehicle of claim 1, wherein the planetary transmission further comprises a first brake, a second brake, a first clutch, and a second clutch.
3. The hybrid transmission of a medium and heavy vehicle according to claim 2, wherein the third sun gear is fixedly connected to the fourth sun gear, the third planet carrier is fixedly connected to the fourth ring gear, the fourth planet carrier is connected to the output shaft, the third ring gear is connected to a frame via the first brake, the fourth ring gear is connected to the frame via the second brake, the intermediate shaft is connected to the third sun gear via the first clutch, and the intermediate shaft is further connected to the third planet carrier via the second clutch.
4. The hybrid transmission of a medium and heavy vehicle according to claim 3, further comprising a one-way clutch, wherein the intermediate shaft is connected to the third sun gear through the one-way clutch.
5. The hybrid transmission of a medium and heavy vehicle according to any one of claims 3 or 4, characterized in that;
the first brake is separated, the first clutch is closed, the second brake is closed, the second clutch is separated, and the planetary speed change mechanism realizes 1 gear;
the first brake is closed, the first clutch is closed, the second brake is separated, the second clutch is separated, and the planetary speed change mechanism realizes 2 gears;
the first brake is separated, the first clutch is closed, the second brake is separated, the second clutch is closed, and the planetary speed change mechanism realizes 3 gears; and
the first brake is closed, the first clutch is separated, the second brake is separated, the second clutch is closed, and the planetary transmission mechanism realizes 4 gears.
6. The hybrid transmission of a medium and heavy vehicle of claim 1, further comprising a third electric machine coupled to the intermediate shaft.
7. The hybrid transmission of a medium and heavy vehicle of claim 6, further comprising a first drive gear set, a second drive gear set, and a third drive gear set.
8. The hybrid transmission of a medium and heavy vehicle of claim 7, wherein the first motor, the second motor, and the third motor are offset within a peripheral space of the input shaft; the first motor is connected with the first sun gear through a first transmission gear set; the second motor and the third motor are connected with the intermediate shaft through a second transmission gear set and a third transmission gear set respectively.
9. The hybrid transmission of a medium and heavy vehicle of claim 8, wherein the first, second and third drive gear sets are fixed-axis gear sets.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202322296676.7U CN220682135U (en) | 2023-08-25 | 2023-08-25 | Hybrid power speed change device of medium and heavy vehicle |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202322296676.7U CN220682135U (en) | 2023-08-25 | 2023-08-25 | Hybrid power speed change device of medium and heavy vehicle |
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| CN220682135U true CN220682135U (en) | 2024-03-29 |
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| CN202322296676.7U Active CN220682135U (en) | 2023-08-25 | 2023-08-25 | Hybrid power speed change device of medium and heavy vehicle |
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2023
- 2023-08-25 CN CN202322296676.7U patent/CN220682135U/en active Active
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