CN220009446U - Hybrid power system and vehicle thereof - Google Patents
Hybrid power system and vehicle thereof Download PDFInfo
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- CN220009446U CN220009446U CN202321625850.1U CN202321625850U CN220009446U CN 220009446 U CN220009446 U CN 220009446U CN 202321625850 U CN202321625850 U CN 202321625850U CN 220009446 U CN220009446 U CN 220009446U
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- 230000007246 mechanism Effects 0.000 claims description 19
- 230000009977 dual effect Effects 0.000 claims 2
- 230000005540 biological transmission Effects 0.000 abstract description 11
- 230000008878 coupling Effects 0.000 abstract 1
- 238000010168 coupling process Methods 0.000 abstract 1
- 238000005859 coupling reaction Methods 0.000 abstract 1
- 238000000034 method Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 230000009471 action Effects 0.000 description 2
- 230000009194 climbing Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 238000010248 power generation Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 239000002243 precursor Substances 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
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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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- Arrangement Of Transmissions (AREA)
Abstract
The utility model relates to a hybrid power system and a vehicle thereof, comprising: an engine, an electric motor, a double planetary differential device, a coupling element and an output shaft. Wherein the engine has an engine output shaft; the motor is provided with a motor output shaft; the double-planetary differential device comprises a first input element, a second input element, a third input element and an output element; one end of a first clutch and one end of a second clutch of the connecting element are connected with an engine output shaft or a motor output shaft, the other end of the first clutch is connected with a first input element, the other end of the second clutch is connected with a second input element, and a third input element is connected with the motor output shaft or the engine output shaft; the output shaft is connected with the output element and transmits power to the wheels. The utility model can realize continuous variable driving, can realize multiple ECVT power mode transmission, can meet the output of medium-low speed and large torque, can realize medium-high speed driving, and can utilize the working high-efficiency areas of the engine and the motor to a greater extent, thereby improving the system efficiency.
Description
Technical Field
The utility model relates to the technical field of automobiles, in particular to a hybrid power system and a vehicle.
Background
At present, a hybrid power system in the industry generally adopts a fixed speed ratio to realize torque demands on different working conditions when realizing various modes, the speed ratio of the hybrid power system cannot be continuously adjustable, the fuel economy of an engine is poor, and the system efficiency is low.
Therefore, how to implement a hybrid system capable of continuously variable output is a problem to be solved by those skilled in the art.
Disclosure of Invention
In view of the above, the present utility model aims to provide a hybrid power system to solve the problems of the existing hybrid power system that the speed ratio cannot be continuously adjusted and the fuel economy is poor.
In order to achieve the above purpose, the utility model adopts the following technical scheme:
a hybrid system, comprising:
an engine having an engine output shaft;
a motor having a motor output shaft;
a double planetary differential device including a first input element, a second input element, a third input element, and an output element;
an engagement element including a first clutch and a second clutch, one end of the first clutch and one end of the second clutch being connected to the engine output shaft or the motor output shaft, the other end of the first clutch being connected to the first input element, the other end of the second clutch being connected to the second input element, the third input element being connected to the motor output shaft or the engine output shaft;
and the output shaft is connected with the output element and transmits power to wheels.
The utility model provides a hybrid power system, which adopts a double-planetary differential device, utilizes different action modes of an engine and a motor on the differential device, can realize continuous adjustable speed ratio, realizes transmission of multiple ECVT power modes, can meet the requirements of medium-low speed and large torque output, can realize medium-high speed driving, and can further utilize the working high-efficiency area of the engine and the motor to a greater extent so as to improve the system efficiency.
Preferably, the double planetary differential device includes a first sun gear, a first planet carrier, a first ring gear, a second sun gear, a second planet carrier, and a second ring gear, the first planet carrier and the second ring gear are connected to construct the third input element, the first sun gear is the second input element, the second sun gear is the first input element, and the first ring gear and the second planet carrier are connected to construct the output element.
Preferably, the outer hubs of the first clutch and the second clutch are connected with an output shaft of the motor, the inner hub of the first clutch is connected with the second sun gear, the inner hub of the second clutch is connected with the first sun gear, the output end of the engine is connected with a first planet carrier and a second gear ring, and the connecting piece of the first gear ring and the second planet carrier is in transmission connection with the output shaft.
Preferably, at least one output gear is fixedly arranged on the output shaft, and the output gear is respectively in transmission connection with the connecting piece of the first gear ring and the second planet carrier and the front axle differential mechanism.
In another preferred mode, the double planetary differential device includes a first sun gear, a first carrier, a first ring gear, a second sun gear, a second carrier, and a second ring gear, the first ring gear being the first input element, the second carrier being the second input element, the first sun gear and the second sun gear constructing the third input element, the first carrier and the second ring gear connecting to construct the output element.
Specifically, the outer hubs of the first clutch and the second clutch are connected with an output shaft of the engine, the inner hub of the first clutch is connected with the first gear ring, the inner hub of the second clutch is connected with the second planet carrier, the output end of the motor is connected with the first sun gear and the second sun gear, and the connecting piece of the first planet carrier and the second gear ring is in transmission connection with the output shaft.
Preferably, at least one output gear is fixedly arranged on the output shaft, and the output gear is respectively in transmission connection with the connecting piece of the first planet carrier and the second gear ring and the front axle differential mechanism.
Preferably, the output shaft is fixedly provided with at least one bevel gear and one spiral bevel gear, the bevel gear is in transmission connection with the output element, and the spiral bevel gear is in transmission connection with the front axle differential mechanism.
The utility model also provides a vehicle comprising the hybrid power system.
Drawings
The accompanying drawings, which are included to provide a further understanding of the utility model, illustrate and explain the utility model and are not to be construed as limiting the utility model. In the drawings:
FIG. 1 is a schematic diagram of a hybrid powertrain system according to the present disclosure;
fig. 2 is a schematic structural diagram of a second embodiment of a hybrid power system according to the present utility model.
Reference numerals illustrate:
1 Engine 11 Engine output shaft 2 Motor
21 motor output shaft 3 double planetary differential device 31 first sun gear
32 first planet carrier 33 first gear ring 34 second sun gear
35 second planet carrier 36 second ring gear 4 engagement element
41 first clutch 42 second clutch 5 output shaft
51 output gear 52 spiral bevel gear 6 front axle differential mechanism
Detailed Description
In addition, the embodiments of the present utility model and the features of the embodiments may be combined with each other without collision.
The present utility model will be described in detail below with reference to the accompanying drawings in conjunction with embodiments.
An embodiment of the present utility model provides a hybrid power system, as shown in fig. 1, including: an engine 1, an electric motor 2, a double planetary differential device 3, a joint element 4 and an output shaft 5, wherein the engine 1 is provided with an engine output shaft 11, the electric motor 2 is provided with an electric motor output shaft 21, and the double planetary differential device 3 comprises a first input element, a second input element, a third input element and an output element; the engagement element 4 includes a first clutch 41 and a second clutch 42, one end of the first clutch 41 and one end of the second clutch 42 are connected to the engine output shaft 11 or the motor output shaft 21, the other end of the first clutch 41 is connected to the first input element, the other end of the second clutch 42 is connected to the second input element, and the third input element is connected to the motor output shaft 21 or the engine output shaft 11; the output shaft 5 is connected to an output element, and transmits power to wheels.
The utility model provides a hybrid power system, which adopts a double-planetary differential device, and can realize continuous adjustable speed ratio and multiple power mode transmission by utilizing different action modes of an engine and a motor on the differential device, thereby utilizing the working high-efficiency areas of the engine and the motor to a greater extent and improving the system efficiency.
In particular, as shown in fig. 1, the double planetary differential device 3 includes a first sun gear 31, a first carrier 32, a first ring gear 33, a second sun gear 34, a second carrier 35, and a second ring gear 36, the first carrier 32 and the second ring gear 36 are connected to construct a third input element, the first sun gear 31 is a second input element, the second sun 34 is a first input element, and the first ring gear 33 and the second carrier 35 are connected to construct an output element.
Preferably, the outer hubs of the first clutch 41 and the second clutch 42 are connected to the output shaft 21 of the electric machine, the inner hub of the first clutch 41 is connected to the second sun gear 34, the inner hub of the second clutch 42 is connected to the first sun gear 31, the engine output shaft 11 is connected to the first planet carrier 32 and the second ring gear 36, and the connection of the first ring gear 33 and the second planet carrier 35 is in driving connection with the output shaft 5.
Preferably, at least one output gear 51 is fixedly arranged on the output shaft 5, and the output gear 51 is in driving connection with the connecting piece of the first gear ring 33 and the second planet carrier 32 and the front axle differential mechanism 6, respectively.
As in the first embodiment shown in fig. 1, the low-speed ECVT mode, the high-speed ECVT mode, the engine direct drive mode, and the strong hybrid mode can be realized in different operation modes of the first clutch 41 and the second clutch 42 with the engine and the 1 motor 2, specifically as follows:
1. low-speed ECVT mode:
the first clutch 41 is combined to connect the motor 2 and the second sun gear 34, the power of the motor 2 is input to the second sun gear 34 through the first clutch C1, the power of the engine 1 is input to the second gear ring 36, the power is coupled at the second planet carrier 35 and is transmitted to the front axle differential mechanism 6 through the output gear 51 and the output shaft 5, low-speed large-torque output is achieved, and the motor can be used for working conditions such as low-speed climbing or getting rid of poverty. In the ECVT process, the rotation speeds and the torques output by the engine 1 and the motor 2 can be matched and adjusted according to the whole vehicle requirement, so that continuous adjustable power output is realized.
2. High-speed ECVT mode:
the second clutch 42 is combined to connect the motor 2 and the first sun gear 31, the power of the motor 2 is input to the first sun gear 31 through the second clutch 42, the power of the engine 1 is input to the first planet carrier 32, the power is coupled at the first gear ring 33 and is transmitted to the front axle differential mechanism 6 through the output gear 51 and the output shaft 5, the middle and high speed output of the whole vehicle is realized, in the ECVT process, the rotating speeds and the torque of the engine 1 and the motor 2 can be matched and regulated according to the requirement of the whole vehicle, the power of the engine is distributed in two parts, one part is used for generating power of the motor 2, the power of the motor 2 can be controlled through the power generation of the motor controller, and the generated power can be stored in a battery or directly used for driving other motors; the other part is used for directly driving the vehicle, and power is output from the output gear. Thereby realizing continuously adjustable power output.
3. Engine direct drive mode:
the first clutch 41 and the second clutch 42 are both engaged to connect the second sun gear 34 and the first sun gear 31, and the double planetary differential device is rotated integrally. Engine 1 power is input to the first carrier 32 and the second ring gear 36. The double-planetary differential device integrally rotates, power is transmitted to the output gear 51 and the output shaft 5 to the front axle differential mechanism 6, and the direct driving function of the whole vehicle pure engine is realized.
4. Strong mixing mode
The first clutch 41 and the second clutch 42 are both engaged to connect the second sun gear 34 and the first sun gear 31, and the double planetary differential device is rotated integrally. The power of the engine 1 is input to the first carrier 32 and the second ring gear 36, and the power of the motor 2 is input to the first sun gear 31 and the second sun gear 34. The power of the engine 1 and the motor 2 is transmitted to the output gear 51 and the output shaft 5 is transmitted to the front axle differential mechanism 6 through the integral rotation of the double-planetary differential device, so that the strong hybrid power mode of the whole vehicle is realized.
Second embodiment as shown in fig. 2, the double planetary differential device 3 includes a first sun gear 31, a first carrier 32, a first ring gear 33, a second sun gear 34, a second carrier 35, and a second ring gear 36, the first ring gear 33 being a first input element, the second carrier 35 being a second input element, the first sun gear 31 and the second sun gear 34 constructing a third input element, the first carrier 32 and the second ring gear 36 being connected to construct an output element.
Specifically, the outer hubs of the first clutch 41 and the second clutch 42 are connected to the engine output shaft 11, the inner hub of the first clutch 41 is connected to the first ring gear 33, the inner hub of the second clutch 42 is connected to the second carrier 35, the motor output shaft 21 is connected to the first sun gear 31 and the second sun gear 34, and the connection member of the first carrier 32 and the second ring gear 36 is in driving connection with the output shaft 5.
Preferably, at least one output gear 51 is fixedly arranged on the output shaft 5, and the output gear 51 is in driving connection with the front axle differential mechanism 6 and the connecting piece of the first planet carrier 32 and the second gear ring 36 respectively.
In a more preferred embodiment, at least one bevel gear and one bevel gear 52 are fixedly arranged on the output shaft 5, the bevel gear is in transmission connection with the output element, and the bevel gear 52 is in transmission connection with the front axle differential mechanism 6. The bevel gear corresponds to the output gear 51 for receiving power from the output element and transmitting the power to the bevel gear, and further outputting the power to the wheels through the front axle differential mechanism 6. This embodiment is more suitable for a hybrid system with a longitudinal precursor.
As shown in the second embodiment of fig. 2, the low-speed ECVT mode, the high-speed ECVT mode, the engine direct drive mode, and the strong hybrid mode can be realized in different operation modes of the first clutch 41 and the second clutch 42 with the engine and the 1 motor 2, specifically as follows:
1. low speed ECVT mode
The first clutch 41 is combined to connect the engine 1 and the first gear ring 33, the power of the motor 2 is input to the first sun gear 31, the power of the engine 1 is input to the first gear ring 33, the power is coupled to the first planet carrier 32 and is transmitted to the front axle differential mechanism 6 through the output gear 51 and the output shaft 5, so that low-speed large-torque output is realized, and the engine can be used for working conditions such as low-speed climbing or getting rid of poverty. In the ECVT process, the rotation speeds and the torques output by the engine 1 and the motor 2 can be matched and adjusted according to the whole vehicle requirement, so that continuous adjustable power output is realized.
2. High speed ECVT mode
The second clutch 42 is combined and connects the engine 1 and the second planet carrier 35, the power of the motor 2 is input to the second sun gear 34, the power of the engine 1 is input to the second planet carrier 35, the power is coupled at the second gear ring 36 and is transmitted to the front axle differential mechanism 6 through the output gear 51 and the output shaft 5, the high-speed output of the whole vehicle is realized, in the ECVT process, the rotating speeds and the torques of the engine 1 and the motor 2 can be matched and adjusted according to the requirement of the whole vehicle, the power 1 of the engine is distributed in two parts, one part is used for generating power of the motor 2, the power generation control of the motor 2 can be performed through the motor controller, and the generated electric energy can be stored or directly used for driving other motors; the other part is used for directly driving the vehicle, and power is output from the output gear. Thereby realizing continuously adjustable power output.
3. Engine direct drive mode
The first clutch 41 and the second clutch 42 are both engaged to connect the first ring gear 33 and the second carrier 35, and the double planetary differential device is rotated integrally at this time. The engine 1 power is input to the first ring gear 33 and the second carrier 35. By the integral rotation of the double-planetary differential device, power is transmitted to the output gear 51 and the output shaft 5 to the front axle differential mechanism 6, so that the direct driving function of the whole vehicle pure engine is realized.
4. Strong mixing mode
The first clutch 41 and the second clutch 42 are both engaged to connect the first ring gear 33 and the second carrier 35, and the double planetary differential device is rotated integrally at this time. The power of the engine 1 is input to the first ring gear 33 and the second carrier 35, and the power of the motor 2 is input to the first sun gear 31 and the second sun gear 34. The power of the engine 1 and the motor 2 is transmitted to the output gear 51 and the output shaft 5 is transmitted to the front axle differential mechanism 6 through the integral rotation of the double-planetary differential device, so that the strong hybrid power mode of the whole vehicle is realized.
The utility model also provides a vehicle which comprises the hybrid power system, so that the vehicle can realize a low-speed ECVT mode, a high-speed ECVT mode, an engine direct drive mode and a strong mixing mode, and the requirements of various working conditions are met.
The foregoing description of the preferred embodiments of the utility model is not intended to be limiting, but rather is intended to cover all modifications, equivalents, alternatives, and improvements that fall within the spirit and scope of the utility model.
Claims (9)
1. A hybrid system, comprising:
an engine having an engine output shaft;
a motor having a motor output shaft;
a double planetary differential device including a first input element, a second input element, a third input element, and an output element;
an engagement element including a first clutch and a second clutch, one end of the first clutch and one end of the second clutch being connected to the engine output shaft or the motor output shaft, the other end of the first clutch being connected to the first input element, the other end of the second clutch being connected to the second input element, the third input element being connected to the motor output shaft or the engine output shaft;
and the output shaft is connected with the output element and transmits power to wheels.
2. A hybrid powertrain according to claim 1, wherein the dual planetary differential includes a first sun gear, a first carrier, a first ring gear, a second sun gear, a second carrier, and a second ring gear, the first carrier and the second ring gear being connected to form the third input member, the first sun gear being the second input member, the second sun gear being the first input member, the first ring gear and the second carrier being connected to form the output member.
3. A hybrid powertrain according to claim 2, wherein the outer hubs of the first and second clutches are connected to the output shaft of the electric machine, the inner hub of the first clutch is connected to the second sun gear, the inner hub of the second clutch is connected to the first sun gear, the output of the engine is connected to a first carrier and a second ring gear, and the connection of the first ring gear and the second carrier is in driving connection with the output shaft.
4. A hybrid system according to claim 3, wherein at least one output gear is fixedly arranged on the output shaft, said output gear being in driving connection with the connection piece of the first ring gear and the second carrier and the front axle differential mechanism, respectively.
5. A hybrid powertrain according to claim 1, wherein the dual planetary differential includes a first sun gear, a first carrier, a first ring gear, a second sun gear, a second carrier, and a second ring gear, the first ring gear being the first input element, the second carrier being the second input element, the first sun gear and the second sun gear constructing the third input element, the first carrier and the second ring gear connecting to construct the output element.
6. A hybrid powertrain according to claim 5, wherein the outer hubs of the first and second clutches are connected to the output shaft of the engine, the inner hub of the first clutch is connected to the first ring gear, the inner hub of the second clutch is connected to the second carrier, the output of the electric machine is connected to the first and second sun gears, and the connection of the first and second carrier to the output shaft is in driving connection.
7. A hybrid powertrain according to claim 6, wherein the output shaft is fixedly provided with at least one output gear in driving connection with the first and second ring gear connecting members and the front axle differential mechanism, respectively.
8. A hybrid powertrain according to claim 2 or claim 5, wherein the output shaft is fixedly provided with at least one bevel gear and a bevel gear, the bevel gear being in driving connection with the output member, the bevel gear being in driving connection with the front axle differential mechanism.
9. A vehicle comprising a hybrid system according to any one of claims 1-8.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202321625850.1U CN220009446U (en) | 2023-06-25 | 2023-06-25 | Hybrid power system and vehicle thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202321625850.1U CN220009446U (en) | 2023-06-25 | 2023-06-25 | Hybrid power system and vehicle thereof |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN220009446U true CN220009446U (en) | 2023-11-14 |
Family
ID=88679862
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202321625850.1U Active CN220009446U (en) | 2023-06-25 | 2023-06-25 | Hybrid power system and vehicle thereof |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN220009446U (en) |
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2023
- 2023-06-25 CN CN202321625850.1U patent/CN220009446U/en active Active
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