阅读说明：本技术 采用行星齿轮传动的dct动力装置 (DCT power device adopting planetary gear transmission ) 是由 彭飞 尹文杰 马连 罗瑞田 汪国建 唐祥华 严洪 张子川 于 2021-07-16 设计创作，主要内容包括：一种采用行星齿轮传动的DCT动力装置,发动机的曲轴与输入轴固定连接,实心传动轴、空心传动轴均通过行星齿轮机构与输入轴连接,该输入轴的一端与发动机的曲轴连接,另一端与行星齿轮机构的齿圈连接,第一输出轴、第二输出轴、空心传动轴均与差速器的半轴平行；实心传动轴通过第一离合器与行星齿轮机构连接,第一离合器的主动摩擦盘与行星齿轮机构的齿圈固定连接,第一离合器的从动摩擦盘周向固定在实心传动轴上；空心传动轴通过第二离合器与行星齿轮机构连接,第二离合器的主动摩擦盘与行星齿轮机构的齿圈固定连接,第二离合器的从动摩擦盘周向固定在空心传动轴上,且行星齿轮机构的行星架固定在该第二离合器的从动摩擦盘上。(A DCT power device adopting planetary gear transmission is characterized in that a crankshaft of an engine is fixedly connected with an input shaft, a solid transmission shaft and a hollow transmission shaft are connected with the input shaft through a planetary gear mechanism, one end of the input shaft is connected with the crankshaft of the engine, the other end of the input shaft is connected with a gear ring of the planetary gear mechanism, and a first output shaft, a second output shaft and the hollow transmission shaft are all parallel to a half shaft of a differential mechanism; the solid transmission shaft is connected with the planetary gear mechanism through a first clutch, a driving friction disc of the first clutch is fixedly connected with a gear ring of the planetary gear mechanism, and a driven friction disc of the first clutch is circumferentially fixed on the solid transmission shaft; the hollow transmission shaft is connected with the planetary gear mechanism through a second clutch, a driving friction disc of the second clutch is fixedly connected with a gear ring of the planetary gear mechanism, a driven friction disc of the second clutch is circumferentially fixed on the hollow transmission shaft, and a planet carrier of the planetary gear mechanism is fixed on the driven friction disc of the second clutch.)

1. A DCT power device adopting planetary gear transmission comprises an engine (1) and a differential (2), and is characterized in that a crankshaft of the engine (1) is fixedly connected with an input shaft (Z1), a solid transmission shaft (Z2) and a hollow transmission shaft (Z3) are connected with the input shaft (Z1) through a planetary gear mechanism, one end of the input shaft (Z1) is connected with the crankshaft of the engine (1), the other end of the input shaft is connected with a gear ring (X3) of the planetary gear mechanism, the input shaft (Z1) and the solid transmission shaft (Z2) are positioned on the same axial lead, the solid transmission shaft (Z2) passes through a hollow transmission shaft (Z3) to form a concentric shaft, and a first output shaft (Z4), a second output shaft (Z5) and the hollow transmission shaft (Z3) are all parallel to a half shaft of the differential (2);

the solid transmission shaft (Z2) is connected with the planetary gear mechanism through a first clutch (C1), a driving friction disc of the first clutch (C1) is fixedly connected with a gear ring (X3) of the planetary gear mechanism, and a driven friction disc of the first clutch (C1) is circumferentially fixed on the solid transmission shaft (Z2);

the hollow transmission shaft (Z3) is connected with the planetary gear mechanism through a second clutch (C2), a driving friction disc of the second clutch (C2) is fixedly connected with a gear ring (X3) of the planetary gear mechanism, a driven friction disc of the second clutch (C2) is circumferentially fixed on the hollow transmission shaft (Z3), and a planet carrier (X4) of the planetary gear mechanism is fixed on the driven friction disc of the second clutch (C2);

a sun wheel shaft (X5) of the planetary gear mechanism is sleeved on the hollow transmission shaft (Z3) in an empty way, one end of the sun wheel shaft (X5) is fixedly connected with the sun wheel (X1), the other end of the sun wheel shaft is fixedly connected with a driven friction disc of a brake (B1), and a driving friction disc of the brake (B1) is fixedly connected with the DCT power device box body;

a first driving gear (S1) and a second driving gear (S2) are circumferentially fixed on the hollow transmission shaft (Z3), and a third driving gear (S3) and a fourth driving gear (S4) are circumferentially fixed on the solid transmission shaft (Z2);

a first driven gear (G1), a second driven gear (G2), a third driven gear (G3) and a fourth driven gear (G4) are arranged on the first output shaft (Z4) in an empty sleeved mode, a first synchronizer (T1) is arranged between the first driven gear (G1) and the second driven gear (G2) and circumferentially fixed on the first output shaft (Z4), a second synchronizer (T2) is arranged between the third driven gear (G3) and the fourth driven gear (G4) and circumferentially fixed on the first output shaft (Z4), and a first driving reduction gear (L1) of the differential (2) is circumferentially fixed on the first output shaft (Z4);

a fifth driven gear (G5), a sixth driven gear (G6), a seventh driven gear (G7) and an eighth driven gear (G8) are sleeved on the second output shaft (Z5) in an empty manner, a third synchronizer (T3) is arranged between the fifth driven gear (G5) and the sixth driven gear (G6) and is circumferentially fixed on the second output shaft (Z5), a fourth synchronizer (T4) is arranged between the seventh driven gear (G7) and the eighth driven gear (G8) and is circumferentially fixed on the second output shaft (Z5), and a second driving reduction gear (L2) of the differential (2) is circumferentially fixed on the second output shaft (Z5);

the first driven gear (G1) and the fifth driven gear (G5) are respectively meshed with a first driving gear (S1), the second driven gear (G2) and the sixth driven gear (G6) are respectively meshed with a second driving gear (S2), the third driven gear (G3) and the seventh driven gear (G7) are respectively meshed with a third driving gear (S3), the fourth driven gear (G4) and the eighth driven gear (G8) are respectively meshed with a fourth driving gear (S4), and the first driving reduction gear (L1) and the second driving reduction gear (L2) of the differential (2) are respectively meshed with a driven reduction gear (L3) of the differential (2);

the reverse gear control device is characterized in that an idler wheel (G9) is arranged between the first driven gear (G1) and the first driving gear (S1), or between the second driven gear (G2) and the second driving gear (S2), or between the third driven gear (G3) and the third driving gear (S3), or between the fourth driven gear (G4) and the fourth driving gear (S4), or between the fifth driven gear (G5) and the first driving gear (S1), or between the sixth driven gear (G6) and the second driving gear (S2), or between the seventh driven gear (G7) and the third driving gear (S3), or between the eighth driven gear (G8) and the fourth driving gear (S4), and is used for reverse gear control.

Technical Field

The invention relates to the field of double-clutch transmissions, in particular to a DCT power device adopting planetary gear transmission.

Background

The concept of a dual clutch automatic transmission (DCT) has been in the sixty-seven decades since it was proposed to date. As early as 1939, the first patent of the K é force.a in germany filed a twin clutch transmission, which proposed a design concept that divides the manual transmission into two parts, one transmitting the odd gears and the other transmitting the even gears. And the power transmission of the gear shifting mechanism is connected with two input shafts through two clutches, the driven gears of adjacent gears are meshed with the gears of the two input shafts in a staggered manner, and the transmission ratio can be converted under the condition of not cutting off the power by matching the control of the two clutches, so that the gear shifting time is shortened, and the gear shifting quality is effectively improved.

The DCT generally includes two clutches, two input countershafts connected to the two clutches, and shift synchronizers respectively disposed on the two input shafts according to odd and even gears, and also includes an automatic shift control system, an electronic control system ECU, and corresponding gear sets. The DCT has the main characteristics that two sets of transmissions and two clutches are adopted, one transmission idles when in a working state, the two transmissions alternately enter a working state through the switching of the two clutches, the gear shifting can be completed under the condition of short power cut-off time, and the gear shifting process is very rapid. However, due to the space limitation of the arrangement of the whole front-wheel-drive economical passenger car, the number of common DCT gears is at most eight forward gears, and the common DCT gears are all realized by adopting multi-stage gear transmission, so that the size is large, the arrangement difficulty is high, the structural limitation conditions are many, and the platform requirement of the passenger car cannot be met.

Disclosure of Invention

The invention aims to solve the problems of low-gear speed ratio, low torque in a low-speed area, gear shifting impact and noise caused by frequent gear shifting and the like of the conventional DCT product, and provides a DCT power device adopting planetary gear transmission, which has ten forward gears with different gear speeds and two reverse gears with different gear speeds.

The purpose of the invention is realized by adopting the following scheme: a DCT power device adopting planetary gear transmission comprises an engine and a differential mechanism, wherein a crankshaft of the engine is fixedly connected with an input shaft, a solid transmission shaft and a hollow transmission shaft are connected with the input shaft through a planetary gear mechanism, one end of the input shaft is connected with the crankshaft of the engine, the other end of the input shaft is connected with a gear ring of the planetary gear mechanism, the input shaft and the solid transmission shaft are positioned on the same axial lead, the solid transmission shaft penetrates through the hollow transmission shaft to form a concentric shaft, and a first output shaft, a second output shaft and the hollow transmission shaft are all parallel to a half shaft of the differential mechanism;

the solid transmission shaft is connected with the planetary gear mechanism through a first clutch, a driving friction disc of the first clutch is fixedly connected with a gear ring of the planetary gear mechanism, and a driven friction disc of the first clutch is circumferentially fixed on the solid transmission shaft;

the hollow transmission shaft is connected with the planetary gear mechanism through a second clutch, a driving friction disc of the second clutch is fixedly connected with a gear ring of the planetary gear mechanism, a driven friction disc of the second clutch is circumferentially fixed on the hollow transmission shaft, and a planet carrier of the planetary gear mechanism is fixed on the driven friction disc of the second clutch;

a sun wheel shaft of the planetary gear mechanism is sleeved on the hollow transmission shaft in an empty way, one end of the sun wheel shaft is fixedly connected with a sun wheel, the other end of the sun wheel shaft is fixedly connected with a driven friction disc of a brake, and a driving friction disc of the brake is fixedly connected with the DCT power device box body;

a first driving gear and a second driving gear are circumferentially fixed on the hollow transmission shaft, and a third driving gear and a fourth driving gear are circumferentially fixed on the solid transmission shaft;

a first driven gear, a second driven gear, a third driven gear and a fourth driven gear are arranged on the first output shaft in a hollow manner, a first synchronizer is arranged between the first driven gear and the second driven gear and circumferentially fixed on the first output shaft, a second synchronizer is arranged between the third driven gear and the fourth driven gear and circumferentially fixed on the first output shaft, and a first driving reduction gear of the differential is circumferentially fixed on the first output shaft;

a fifth driven gear, a sixth driven gear, a seventh driven gear and an eighth driven gear are arranged on the second output shaft in a hollow manner, a third synchronizer is arranged between the fifth driven gear and the sixth driven gear and circumferentially fixed on the second output shaft, a fourth synchronizer is arranged between the seventh driven gear and the eighth driven gear and circumferentially fixed on the second output shaft, and a second driving reduction gear of the differential is circumferentially fixed on the second output shaft;

the first driven gear and the fifth driven gear are respectively meshed with the first driving gear, the second driven gear and the sixth driven gear are respectively meshed with the second driving gear, the third driven gear and the seventh driven gear are respectively meshed with the third driving gear, the fourth driven gear and the eighth driven gear are respectively meshed with the fourth driving gear, and the first driving reduction gear and the second driving reduction gear of the differential are respectively meshed with the driven reduction gear of the differential;

an idler wheel is arranged between the first driven gear and the first driving gear, or between the second driven gear and the second driving gear, or between the third driven gear and the third driving gear, or between the fourth driven gear and the fourth driving gear, or between the fifth driven gear and the first driving gear, or between the sixth driven gear and the second driving gear, or between the seventh driven gear and the third driving gear, or between the eighth driven gear and the fourth driving gear, and is used for reverse gear control.

By adopting the scheme, the crankshaft of the engine is fixedly connected with an input shaft, a solid transmission shaft and a hollow transmission shaft are connected with the input shaft through a planetary gear mechanism, one end of the input shaft is connected with the crankshaft of the engine, the other end of the input shaft is connected with a gear ring of the planetary gear mechanism, the input shaft and the solid transmission shaft are positioned on the same axial lead, the solid transmission shaft penetrates through the hollow transmission shaft to form a concentric shaft, and the first output shaft, the second output shaft and the hollow transmission shaft are all parallel to a half shaft of the differential mechanism;

the solid transmission shaft is connected with the planetary gear mechanism through a first clutch, a driving friction disc of the first clutch is fixedly connected with a gear ring of the planetary gear mechanism, and a driven friction disc of the first clutch is circumferentially fixed on the solid transmission shaft;

the hollow transmission shaft is connected with the planetary gear mechanism through a second clutch, a driving friction disc of the second clutch is fixedly connected with a gear ring of the planetary gear mechanism, a driven friction disc of the second clutch is circumferentially fixed on the hollow transmission shaft, and a planet carrier of the planetary gear mechanism is fixed on the driven friction disc of the second clutch;

a sun wheel shaft of the planetary gear mechanism is sleeved on the hollow transmission shaft in an empty way, one end of the sun wheel shaft is fixedly connected with a sun wheel, the other end of the sun wheel shaft is fixedly connected with a driven friction disc of a brake, and a driving friction disc of the brake is fixedly connected with the DCT power device box body;

a first driving gear and a second driving gear are circumferentially fixed on the hollow transmission shaft, and a third driving gear and a fourth driving gear are circumferentially fixed on the solid transmission shaft;

a first driven gear, a second driven gear, a third driven gear and a fourth driven gear are arranged on the first output shaft in a hollow manner, a first synchronizer is arranged between the first driven gear and the second driven gear and circumferentially fixed on the first output shaft, a second synchronizer is arranged between the third driven gear and the fourth driven gear and circumferentially fixed on the first output shaft, and a first driving reduction gear of the differential is circumferentially fixed on the first output shaft;

a fifth driven gear, a sixth driven gear, a seventh driven gear and an eighth driven gear are arranged on the second output shaft in a hollow manner, a third synchronizer is arranged between the fifth driven gear and the sixth driven gear and circumferentially fixed on the second output shaft, a fourth synchronizer is arranged between the seventh driven gear and the eighth driven gear and circumferentially fixed on the second output shaft, and a second driving reduction gear of the differential is circumferentially fixed on the second output shaft;

the first driven gear and the fifth driven gear are respectively meshed with the first driving gear, the second driven gear and the sixth driven gear are respectively meshed with the second driving gear, the third driven gear and the seventh driven gear are respectively meshed with the third driving gear, the fourth driven gear and the eighth driven gear are respectively meshed with the fourth driving gear, and the first driving reduction gear and the second driving reduction gear of the differential are respectively meshed with the driven reduction gear of the differential;

an idler wheel is arranged between the first driven gear and the first driving gear, or between the second driven gear and the second driving gear, or between the third driven gear and the third driving gear, or between the fourth driven gear and the fourth driving gear, or between the fifth driven gear and the first driving gear, or between the sixth driven gear and the second driving gear, or between the seventh driven gear and the third driving gear, or between the eighth driven gear and the fourth driving gear, and is used for reverse gear control.

The invention has the following advantages:

the invention has compact and simple structure, clear function of functional parts and low cost, and is beneficial to the integrated matching of a double-clutch automatic transmission system vehicle;

the technical scheme of the invention has good expansibility, can realize more reasonable modularization and platformization development, and can adapt to the requirements of more vehicle types;

the technical scheme of the invention adopts two clutches and one brake, so that the gears can be alternately shifted when being switched, the shifting frequency of the synchronizer is reduced, the service life is prolonged, and compared with two functional clutch components of the traditional double clutch, the switching time and the corresponding performance requirements are reduced on the basis of meeting the power response and the smoothness comfort;

the technical scheme of the invention adopts two clutches, one brake and a corresponding synchronous gear shifting mechanism, reduces the synchronous gear shifting times and the synchronous gear shifting continuous change times on the premise of ensuring the power response of the vehicle in the acceleration/deceleration process, and effectively optimizes the performance problems of gear shifting difficulty, gear shifting impact, gear shifting noise and the like of the traditional DCT structure.

The technical scheme of the invention adopts a planetary gear mechanism, two clutches and one brake structure, so that the number of synchronous gear shifting and gear pairs can be effectively reduced, more gear arrangements can be realized under the same requirement of the whole vehicle arrangement space, and the whole vehicle space arrangement and the improvement of the dynamic economic performance of a passenger vehicle are facilitated.

Drawings

FIG. 1 is a schematic structural view of the present invention;

fig. 2 is a gear distribution diagram of the present invention.

Detailed Description

As shown in fig. 1, a DCT power device using planetary gear transmission includes an engine 1, a differential 2, a crankshaft of the engine 1 is fixedly connected with an input shaft Z1, a solid transmission shaft Z2 and a hollow transmission shaft Z3 are both connected with the input shaft Z1 through a planetary gear mechanism, one end of the input shaft Z1 is connected with the crankshaft of the engine 1, the other end is connected with a gear ring X3 of the planetary gear mechanism, the input shaft Z1 and the solid transmission shaft Z2 are located on the same axial line, the solid transmission shaft Z2 passes through a hollow transmission shaft Z3 to form a concentric shaft, and a first output shaft Z4, a second output shaft Z5 and the hollow transmission shaft Z3 are all parallel to a half shaft of the differential 2; in the present embodiment, the first half shaft Z6 and the second half shaft Z7 of the differential 2 are both supported on the casing of the DCT power unit through bearings.

The solid transmission shaft Z2 is connected with the planetary gear mechanism through a first clutch C1, a driving friction disc of the first clutch C1 is fixedly connected with a gear ring X3 of the planetary gear mechanism, and a driven friction disc of the first clutch C1 is circumferentially fixed on the solid transmission shaft Z2;

the hollow transmission shaft Z3 is connected with the planetary gear mechanism through a second clutch C2, a driving friction disc of the second clutch C2 is fixedly connected with a gear ring X3 of the planetary gear mechanism, a driven friction disc of the second clutch C2 is circumferentially fixed on the hollow transmission shaft Z3, and a planet carrier X4 of the planetary gear mechanism is fixed on the driven friction disc of the second clutch C2;

in the embodiment, the input shaft Z1, the solid transmission shaft Z2, the hollow transmission shaft Z3, the first output shaft Z4 and the second output shaft Z5 are all supported on a box body of the DCT power unit through bearings.

A sun wheel shaft X5 of the planetary gear mechanism is sleeved on a hollow transmission shaft Z3 in a hollow mode, one end of the sun wheel shaft X5 is fixedly connected with a sun wheel X1, the other end of the sun wheel shaft X5 is fixedly connected with a driven friction disc of a brake B1, a driving friction disc of the brake B1 is fixedly connected with a DCT power device box, and the sun wheel shaft X5 and the hollow transmission shaft Z3 can be supported through a bearing to achieve sliding fit.

A first driving gear S1 and a second driving gear S2 are circumferentially fixed on the hollow transmission shaft Z3, and a third driving gear S3 and a fourth driving gear S4 are circumferentially fixed on the solid transmission shaft Z2;

a first driven gear G1, a second driven gear G2, a third driven gear G3 and a fourth driven gear G4 are arranged on the first output shaft Z4 in an empty manner, a first synchronizer T1 is arranged between the first driven gear G1 and the second driven gear G2 and circumferentially fixed on the first output shaft Z4, a second synchronizer T2 is arranged between the third driven gear G3 and the fourth driven gear G4 and circumferentially fixed on the first output shaft Z4, and a first driving reduction gear L1 of the differential 2 is circumferentially fixed on the first output shaft Z4;

a fifth driven gear G5, a sixth driven gear G6, a seventh driven gear G7 and an eighth driven gear G8 are arranged on the second output shaft Z5 in an empty manner, a third synchronizer T3 is arranged between the fifth driven gear G5 and the sixth driven gear G6 and circumferentially fixed on the second output shaft Z5, a fourth synchronizer T4 is arranged between the seventh driven gear G7 and the eighth driven gear G8 and circumferentially fixed on the second output shaft Z5, and a second driving reduction gear L2 of the differential 2 is circumferentially fixed on the second output shaft Z5;

the first driven gear G1 and the fifth driven gear G5 are respectively meshed with a first driving gear S1, the second driven gear G2 and the sixth driven gear G6 are respectively meshed with a second driving gear S2, the third driven gear G3 and the seventh driven gear G7 are respectively meshed with a third driving gear S3, the fourth driven gear G4 and the eighth driven gear G8 are respectively meshed with a fourth driving gear S4, and the first driving reduction gear L1 and the second driving reduction gear L2 of the differential 2 are respectively meshed with a driven reduction gear L3 of the differential 2;

an idler wheel G9 is arranged between the first driven gear G1 and the first driving gear S1, or between the second driven gear G2 and the second driving gear S2, or between the third driven gear G3 and the third driving gear S3, or between the fourth driven gear G4 and the fourth driving gear S4, or between the fifth driven gear G5 and the first driving gear S1, or between the sixth driven gear G6 and the second driving gear S2, or between the seventh driven gear G7 and the third driving gear S3, or between the eighth driven gear G8 and the fourth driving gear S4, and is used for reverse gear control.

In this embodiment, the idle gear G9 is disposed between the first driving gear S1 and the first driven gear G1, the gear arrangement of the DCT power plant using planetary gear transmission is as shown in fig. 2, and the DCT power plant has ten forward gears with different gear speeds and two reverse gears with different gear speeds, and the power transmission chain is operated as follows:

when the first clutch C1 is engaged, the power of the engine 1 is transmitted to the solid transmission shaft Z2 through the planetary gear mechanism with the speed ratio i of 1, and forms a power transmission chain with a plurality of speed ratio relationships with the third driving gear S3, the fourth driving gear S4, the third driven gear G3, the fourth driven gear G4, the seventh driven gear G7, the eighth driven gear G8, the second synchronizer T2 and the fourth synchronizer T4:

1) when the first clutch C1 is engaged, the second synchronizer T2 in combination with the third driven gear G3 realizes a three-speed power transmission chain;

2) when the first clutch C1 is engaged, the second synchronizer T2 in combination with the fourth driven gear G4 realizes a five-speed power transmission chain;

3) when the first clutch C1 is engaged, the second synchronizer T4 in combination with the seventh driven gear G7 realizes a seven-speed power transmission chain;

4) when the first clutch C1 is engaged, the second synchronizer T4 in combination with the eighth driven gear G8 realizes a nine-speed power transmission chain;

when the second clutch C2 is combined, the power of the engine 1 is transmitted to the hollow transmission shaft Z3 through a planetary gear mechanism with the speed ratio i being 1, and forms a power transmission chain with a plurality of speed ratio relations with the first driving gear S1, the second driving gear S2, the first driven gear G1, the second driven gear G2, the fifth driven gear G5, the sixth driven gear G6, the first synchronizer T1 and the third synchronizer T3 respectively;

1) when the first clutch C2 is engaged, the second synchronizer T3 is engaged with the fifth driven gear G5 to implement a two-gear power transmission chain;

2) when the first clutch C2 is engaged, the second synchronizer T3 in combination with the sixth driven gear G6 realizes a six-speed power transmission chain;

3) when the first clutch C2 is engaged, the second synchronizer T1 is engaged with the second driven gear G2 to implement a ten-speed power transmission chain;

4) when the first clutch C2 is engaged, the second synchronizer T1 in combination with the first driven gear G1 realizes a first reverse power transmission chain;

third, when the brake B1 is engaged, the speed ratio i of the planetary gear mechanism is as follows:

in the formula (I), the compound is shown in the specification,the number of teeth of the ring gear X3 of the planetary gear mechanism,the number of teeth of the sun gear X1 of the planetary gear mechanism;

the power of the engine 1 is transmitted to a hollow transmission shaft Z3 through a planetary gear mechanism with a speed ratio i, and forms a power transmission chain with a plurality of speed ratio relations with a first driving gear S1, a second driving gear S2, a first driven gear G1, a second driven gear G2, a fifth driven gear G5, a sixth driven gear G6, a first synchronizer T1 and a third synchronizer T3 respectively;

1) when the brake B1 is combined, the second synchronizer T3 is combined with the fifth driven gear G5 to realize a first-gear power transmission chain;

2) when the brake B1 is engaged, the second synchronizer T3 in combination with the sixth driven gear G6 realizes a four-speed power transmission chain;

3) when the brake B1 is combined, the second synchronizer T1 is combined with the second driven gear G2 to realize an eight-gear power transmission chain;

4) when the brake B1 is engaged, the second synchronizer T1 in combination with the first driven gear G1 effects a second reverse power transmission chain.