• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The present invention makes public a hybrid system for a vehicle, it comprises an engine, a hybrid module and a transmission mechanism with double input shaft, the hybrid module comprises an electric motor, a planetary gear, a first clutch and a brake; the planetary gear includes at least three rotating shafts: an X1 shaft, an X2 shaft, an X3 shaft, the axes of the three shafts are on the same straight line, the rotational speed of the X2 shaft is between the rotational speed of the shaft X1 and the rotational speed of the shaft X3, the first clutch is disposed between any two of the three shafts; a motor power output shaft is connected to the X3 shaft or X1 shaft of the planetary gear and a second input shaft of the double input shaft transmission mechanism and the rotor of the electric motor is connected to the X1 shaft or X3 shaft, and the X2 shaft is connected to the first input shaft of the double input shaft transmission mechanism. This invention has high transmission efficiency, multiple speeds, introduced a three-axis planetary gear system with double degree of freedom, the speed differential between the motor and the electric motor drives the vehicle to start, the vehicle starts smoothly , with good speed change smoothness and low impact. Figure for the abstract: Fig. 1
    公开号:FR3101042A1
    申请号:FR2009512
    申请日:2020-09-18
    公开日:2021-03-26
    发明作者:Zhihui Duan
    申请人:Beijing New Energy Vehicle Technology Innovation Center Co Ltd；
    IPC主号:
    专利说明:

    [0001] The present invention relates to the technical field of hybrid vehicles, and more particularly to a hybrid system for a vehicle and a method for controlling the latter.
    [0002] Hybrid vehicles with two energy sources, motor and electric motor are known. Through the mutual cooperation between the two energy sources in driving the vehicle, it combines the advantages of traditional fuel vehicles and pure electric vehicles and becomes the best model to solve environmental and energy problems. It is the most industrialized and marketable power system among electric vehicles.
    [0003] Among the existing technologies, the propulsion system of hybrid vehicles largely adopts the hybrid transmission DCT (in English "Dual Clutch Transmission, DCT"), which consists of the addition of an engine in front of the double clutch of the DCT (Dual Clutch Transmission) and a clutch in front of the engine. DCT enables gear transmission, high efficiency, less energy loss caused by clutch drag resistance, less fossil fuel consumption; motor and electric motor driven in parallel, torque superposition and good power. DCT technology is mature, mass production is carried out, and the quality of parts and assembly is stable at low cost.
    [0004] However, there are the following shortcomings: 1. Double clutch control technology is complicated, risky and expensive. 2. The double clutch has a larger diameter and volume. After the engine is added, the axial length is greater and the arrangement in the engine compartment is difficult. 3. When the motor vehicle starts, it is difficult to control the sliding friction of the double clutch, and it is prone to squealing when shifting gears, switching of the two clutches may also cause noise. 4. Normally, it is limited by the axial length and the cost. There are 6 or 7 speeds; between low speeds, the gear ratio varies considerably and fuel consumption on urban roads is low.
    [0005] In order to solve the above problems, the aim of the present invention is to provide a hybrid system for vehicles with high transmission efficiency, multiple gear positions, compact structure and mature component technology, at the same time, the above-mentioned control method for the hybrid power system of a vehicle is disclosed, and a vehicle including the hybrid power system is also disclosed.
    [0006] In order to achieve the objective of the above invention, the present invention adopts the following technical solutions:
    [0007] A hybrid system for a vehicle comprising an engine, a hybrid module and a transmission mechanism with double input shaft, the hybrid module includes an electric motor, a planetary gear, a first clutch and a brake; in said system the planetary gear comprises at least three rotary shafts: a shaft X1, a shaft X2, a shaft X3, the axes of the three shafts are on the same straight line, in which the speed of rotation of the shaft X2 is between the speed of rotation of the shaft X1 and the speed of rotation of the shaft X3, wherein the first clutch is disposed between any two of the three shafts; wherein a power output shaft of the motor is connected to the shaft X3 or the shaft X1 of the planetary gear and to a second input shaft of the double input shaft transmission mechanism, and the rotor of the electric motor is connected to the shaft X1 or the shaft X3, and the shaft X2 is connected to a first input shaft of the double input shaft transmission mechanism; wherein the brake is mounted on the motor power output shaft; wherein the dual input shaft transmission mechanism comprises the first input shaft, the second input shaft, a plurality of pairs of front gears, at least one set of reverse gears and an output shaft, wherein the first input shaft is provided with drive gears assigned to odd speeds, while the second input shaft is provided with drive gears assigned to even speeds, in which the reverse drive pinions are arranged on the first shaft of the input or the second input shaft, in which the output shaft is arranged with the driven gears of each gear, and the driven gears of each gear engage with the corresponding driven gears; in which a pinion of each speed is connected to the shaft via a synchronizer.
    [0008] A hybrid system for a vehicle comprising an engine, a hybrid module and a double input shaft transmission mechanism, the hybrid module comprises an electric motor, a planetary gear, a first clutch and a brake; the planetary gear comprises at least three rotating shafts: an X1 shaft, an X2 shaft, an X3 shaft, the axes of the three shafts are on the same straight line, the rotational speed of the X2 shaft is between the rotational speed of the shaft X1 and the rotational speed of shaft X3; the first clutch is disposed between any two of the three shafts; a motor power output shaft is connected to the X3 shaft or X1 shaft of the planetary gear and a second input shaft of the double input shaft transmission mechanism, and the motor rotor electric is connected to the X1 shaft or X3 shaft, and the X2 shaft is connected to a first input shaft of the double input shaft transmission mechanism; the brake is mounted on the motor power output shaft; the dual input shaft transmission mechanism includes the first input shaft, the second input shaft, plural pairs of front gears, at least one set of reverse gears and one output shaft, the first shaft of The input is provided with drive gears assigned to odd speeds, while the second input shaft is provided with drive gears assigned to even speeds, a number of driven gears are arranged on the first output shaft, and a number of driven gears are also disposed on the second output shaft; the driven pinions are respectively connected to the shaft by means of respective synchronizers; each drive pinion engages with a driven pinion on the first and second output shafts.
    [0009] A hybrid system for a vehicle comprising an engine, a hybrid module and a double input shaft transmission mechanism, the hybrid module comprises an electric motor, a planetary gear, a first clutch and a brake; the planetary gear includes at least three rotating shafts: an X1 shaft, an X2 shaft, an X3 shaft, the axes of the three shafts are on the same straight line, the rotational speed of the X2 shaft is between the rotational speed of the shaft X1 and the rotational speed of the shaft X3; the first clutch is disposed between any two of the three shafts; the power output shaft of the motor is connected to the X3 shaft or X1 shaft of the planetary gear and a second input shaft of the double input shaft transmission mechanism, and the rotor of the electric motor is connected to the X1 shaft or X3 shaft, and the X2 shaft is connected to a first input shaft of the double input shaft transmission mechanism; the brake is mounted on the motor power output shaft;
    [0010] The dual input shaft transmission mechanism includes the first input shaft, the second input shaft, several pairs of front gears, at least one set of reverse gears and one output shaft, the front of the first input shaft is transmitted to the rear of the first input shaft by a two-stage gear; the rear of the first input shaft is provided with drive gears assigned to odd speeds, which are connected to the shaft by a corresponding synchronizer; the second input shaft is equipped with drive pinions assigned to even speeds, which are connected to the shaft by a corresponding synchronizer; the output shaft is equipped with a driven gear which is fixed on the shaft; each driven gear engages with two drive gears, one odd and one even, to form two gears.
    [0011] A hybrid system for a vehicle comprising an engine, a hybrid module and a double input shaft transmission mechanism, the hybrid module comprises an electric motor, a planetary gear, a first clutch and a brake; the planetary gear includes at least three rotating shafts: an X1 shaft, an X2 shaft, an X3 shaft, the axes of the three shafts are on the same straight line, the rotational speed of the X2 shaft is between the rotational speed of the shaft X1 and the rotational speed of the shaft X3; the first clutch is disposed between any two of the three shafts; the power output shaft of the motor is connected to the X3 shaft or X1 shaft of the planetary gear and a second input shaft of the double input shaft transmission mechanism, and the rotor of the electric motor is connected to the X1 shaft or X3 shaft, and the X2 shaft is connected to the first input shaft of the double input shaft transmission mechanism; the brake is mounted on the motor power output shaft; The dual input shaft transmission mechanism includes a first input shaft, a second input shaft, a plurality of pairs of front gears, at least one set of reverse gears and an output shaft, the front of the first input shaft is connected to the rear of the first input shaft by a first stage gear, and the front of the second input shaft is connected to the rear of the second input shaft by a gear of first floor; the rear of the first input shaft is provided with drive gears assigned to odd speeds, which are connected to the shaft by a corresponding synchronizer; the rear of the second input shaft is equipped with drive gears assigned to even speeds, which are connected to the shaft via a corresponding synchronizer; the output shaft is equipped with a gear driven gear, which is fixed on the shaft; each driven gear engages with two drive gears, one odd and one even, to form two gears.
    [0012] In addition, in its hybrid module, the planetary gear can include at least three rotating shafts, namely: a shaft of the sun gear S, a shaft of the planet carrier C, a shaft of the crown R, the axes of the three shafts are on the same straight line, the speed of rotation of the shaft of the planet carrier C is between that of the sun wheel S and that of the crown R, a first clutch is arranged between two of said three rotary shafts; the power output shaft of the motor is connected with the rotating shaft of the crown wheel R or the rotating shaft of the sun gear S of the planetary gear and the second input shaft of the double shaft transmission mechanism input, the rotor of the electric motor is connected to the rotating shaft of the sun gear S or to the crown shaft R of the planetary gear, the rotating shaft of the planetary carrier C is connected to the first shaft input of the double input shaft transmission mechanism.
    [0013] In addition, the brake in the hybrid module can be replaced with a second clutch, and the second clutch is mounted on the power output shaft of the engine.
    [0014] The present invention also provides a control method for a hybrid system of a vehicle, the operating mode may include a purely electric mode, a purely motor drive mode, a hybrid drive mode and a charging mode.
    [0015] In addition, in hybrid driving mode, the operating steps for changing gears are:
    [0016] I. from odd speed to adjacent even speed (1). before the gear change: the synchronizer is resting on the gear at odd speed, the first clutch is closed, the planetary gear is coupled, the motor and the electric motor drive the gear in parallel; (2). start the speed change: adjust the torque of the motor and the electric motor so that Tm = ρTen, the torque supported by the first clutch is reduced to zero, and the sum of the adjusted torque is equal to the sum of the torque before adjustment; Tm is the driving torque of the electric motor, ρ = S / R, R, S indicate the number of teeth of the crown and the sun gear respectively, Ten is the driving torque of the motor; (3). the release of the first clutch, differential drive of the motor and the electric motor; in the process, the torque of the electric motor and the motor is balanced around the planet carrier shaft, and the driving torque is equal to the torque before the gear change; (4). the electric motor adjusts the rotational speed of the sun wheel shaft, then drives the speed change of the crown shaft and the second input shaft, so that the second input shaft and the new one gears synchronize; the torque of the electric motor and the motor is balanced around the shaft of the planetary wheel, and the driving torque is equal to the torque before the gear change, the motor controls the torque while the electric motor controls the speed of rotation of the sun gear via the planetary gear, and controls the speed of the ring gear, so that the second input shaft and the pinion to be engaged at the even gear pinion rotate at the same speed and make it easier to change gears by the synchronizer; (5). the synchronizer hooks a new gear, in the process the torque remains the same; (6). the output torque of the electric motor is transferred to the power output shaft of the motor, the motor directly drives the second input shaft and the new gear, the torque of the electric motor becomes zero, the torque supported by the first shaft input and the gear of the original odd speed is zero, in the process, the torque of the electric motor is transferred to the motor, and the driving torque is equal to the torque before the speed change; (7). the synchronizer is removed from the original odd speed; (8). the first clutch is closed, the planetary gear is coupled, the motor and the electric motor drive the new speed in parallel; in the process, it is possible to adjust and balance the torque of the electric motor and the motor, the sum of the driving torque is equal to the torque before the gear change; II. from even speed to adjacent odd speed (1). before the speed change: the synchronizer is resting on the gear at even speed, the first clutch is closed, the planetary gear is coupled, the motor and the electric motor drive the speed in parallel; (2). start gear shifting: the output torque of the electric motor is transferred to the power output shaft of the motor, the motor directly drives the second input shaft and the original gear, the torque of the electric motor becomes zero and the clutch torque is zero, in the process, the torque of the electric motor is transferred to the motor, and the driving torque is equal to the torque before the gear change; (3). the first clutch is released, the three shafts of the planetary gear rotate at different rotational speeds, and the torque remains unchanged during this process; (4). the electric motor adjusts the rotational speed of the sun wheel shaft, then drives the speed change of the planet carrier shaft and the first input shaft, so that the first input shaft and the new gear synchronize; in this process, the driving torque acts directly on the second input shaft, driving the wheels by even gears, and the torque is equal to the torque before the gear change; (5). the synchronizer hooks a new gear, in the process the torque remains the same; (6). adjust the torque of the motor and the electric motor so that Tm = ρTen, and the sum of the adjusted torque is equal to the sum of the torque before the adjustment, so that the torque supported by the second input shaft and the gear original is reduced to zero; Tm is the driving torque of the electric motor, ρ = S / R, R, S indicates the number of the crown and the sun wheel respectively, Ten is the driving torque of the motor; (7). remove the original pair gear, the torque remains unchanged during this process; (8). the first clutch is closed, the planetary gear is coupled, the motor and electric motor drive in parallel the gear of the new speed; In the process, it is possible to adjust and balance the torque of the electric motor and the motor, the sum of the driving torque is equal to the torque before the gear change.
    [0017] In addition, the operating step of switching from a purely electric mode to a hybrid drive mode is as follows:
    [0018] (1). before shifting: the synchronizer is resting on the gear at odd speed, the first clutch is uncoupled, the motor power output shaft is locked by the brake, the electric motor drives the sun wheel, the first shaft d 'input and gear change gear via the planetary carrier; (2). start switching: the brake is released, the first clutch is closed and, which causes the three shafts of the gear system to rotate at the same rotational speed; (3). limiting the slip torque of the first clutch, and at the same time, the electric motor increases the torque to compensate for the loss of torque; (4). Once the engine power output shaft reaches firing speed, the engine fires up and begins to spin, the hybrid system goes into hybrid drive mode.
    [0019] The present invention also protects a vehicle comprising the hybrid system described above.
    [0020] Due to the adoption of the technical solution described above, the present invention has the following advantages:
    [0021] The hybrid system used in the vehicle and its control method have high transmission efficiency, many gears, compact structure, mature technology and reasonable design. The planetary gear system with three degrees of freedom and two degrees of freedom is introduced. The motor and the electric motor can drive the vehicle differently. Starting the vehicle no longer needs slipping. All gear shifting processes are controlled by the motor, such as input shaft and gear to achieve synchronization, directly suspended synchronizer, without clutch assist, fast motor response, high speed precision , good shifting, small impact; During the shifting process, the torque can be transferred between the motor and the motor, so that the driving torque remains unchanged, and the vehicle is driven smoothly throughout the shifting process. Cancel double clutch, lower cost; The planetary gear can be arranged inside the rotor of the motor, which can save space, shorten the length of the shaft, and further reduce the power consumption of the hydraulic system. Double input transmission gear and more, which will help reduce the fuel consumption of the vehicle, and the axial size is short; planetary gear system on the engine torsion, improve vehicle fuel consumption; differential drive of motor and electric motor, the acceleration process can be a continuous speed, to further reduce fuel consumption on city road; planetary gear system on the motor twist 2-3 times, the motor torque can be reduced by 25-50%, reducing motor costs; Realize pure electric drive, hybrid motor and motor drive, regenerative braking, cruise power generation, parking power generation and other functions.
    [0022] The is a structural schematic diagram of one of the embodiments of a hybrid system for a vehicle according to the present invention;
    [0023] The is a schematic diagram of the structure of the embodiment of the hybrid system for the vehicle according to the present invention;
    [0024] The is a schematic diagram of the structure of the planetary gear in Figures 1 and 2;
    [0025] The is a representation of the rotational speed lever of each shaft in the planetary gear on the ;
    [0026] The is a rotational speed lever diagram of three shafts in a general planetary gear;
    [0027] The is a torque diagram of each shaft in the planetary gear on the ;
    [0028] The is a lever diagram of the rotational speed of three shafts in a planetary gear as the engine speed ratio continuously changes under HEV conditions;
    [0029] The is a lever diagram of the rotational speed of three shafts in a planetary gear when the motor speed is controlled at zero speed under HEV conditions;
    [0030] The is a lever diagram of three shaft rotation speeds in the planetary gear of the present invention when the pure motor drive mode is a motor drive mode;
    [0031] The is a lever diagram of three shaft torques in the planetary gear of the present invention when the pure motor vehicle is driven;
    [0032] The is a lever diagram of three shaft rotation speeds in the planetary gear of the present invention during starting of the hybrid motor and motor vehicle;
    [0033] The is a lever diagram of three rotational shaft torques in the planetary gear of the present invention during starting of the engine-engine hybrid vehicle;
    [0034] The is a lever diagram of the rotational speed of three axes in the planetary gear of the present invention, which is transformed from an odd speed to an even speed of gears during the hybrid drive;
    [0035] The is a lever diagram of the rotational speed of three axes in the planetary gear of the present invention, which is transformed from an odd speed to an even speed of gears during the hybrid drive;
    [0036] The is a lever diagram of the three axes of rotation in the planetary gear of the present invention when converting an even speed to an odd speed in the hybrid drive;
    [0037] The is a lever diagram of the rotational speed of three axes in the planetary gear of the present invention when converting an even speed to an odd speed in the hybrid drive;
    [0038] The is a schematic diagram of the structure of one of the embodiments of a double input shaft transmission mechanism in a hybrid system of the present invention for a vehicle;
    [0039] The is a schematic diagram of the structure of the embodiment of the double input shaft transmission mechanism in the hybrid system of the present invention for the vehicle;
    [0040] The is a schematic diagram of the structure of the third embodiment of the hybrid system for the vehicle according to the present invention;
    [0041] Figure: 1-motor; 2-power output shaft; 3-brake; 4-first clutch 5-planetary gear; 6-electric motor; 7-rotor; 8-second clutch; 10-hybrid module 11-first input shaft; 12-second input shaft; 15- output shaft; 16-first output shaft; 17-second output shaft; 20-double input shaft transmission mechanism; S-sun wheel; C- satellite carrier; R- crown.
    [0042] The technical aspect of the present invention is described in more detail below in conjunction with the accompanying drawings and embodiments.
    [0043] As shown in the , the hybrid system for a vehicle comprises an engine 1, a hybrid module 10 and a transmission mechanism with double input shaft 20; the hybrid module 20 comprises an electric motor 6, a planetary gear 5, a first clutch 4 and a brake 3; the planetary gear 5 comprises at least three rotary shafts, the axes of the three shafts are on the same straight line. The three axes of rotation are the sun gear shaft S, the planet gear carrier shaft C, the ring gear shaft R. The power output shaft 2 of motor 1 is connected to the gear shaft. the crown R, and is connected to the second input shaft 12 of the transmission mechanism with double input shaft 20. The rotor 7 of the motor 6 is connected to the shaft of the sun gear S, the shaft of the carrier. satellite C is connected to the first input shaft 11 of the double input shaft transmission mechanism 20, and the first clutch 4 is disposed between any two of the three shafts of the sun gear S, the planet carrier C and the ring gear R, the planetary gear is used together with the rotating shaft. The brake 3 is mounted on the power output shaft 2 of the motor 1; the double input shaft transmission mechanism 20 comprises a first input shaft 11, a second input shaft 12, several pairs of front gears, at least one set of reverse gears GR and an output shaft 15 ; a set of inverted gears GR between the two gears with steering gear, the front gear is the gear G1, G2, G3, ....; a set of reverse gears GR is provided with a steering gear between the two gears; the first input shaft 11 is provided with drive gears assigned to odd speeds and reverse gears, and the second input shaft 12 is provided with drive gears assigned to even speeds, the driven gear of each gear is arranged on the output shaft 15, and the drive gear of the aforementioned gear engages with its corresponding driven gear. In each gear, a gear is connected to the shaft where the gear is located via the synchronizer; the synchronizer is supported on the gear, the gear and the connection of the corresponding shaft, the same speed of rotation; when the synchronizer is removed, the gear is separated from the corresponding shaft.
    [0044] As shown in the , the hybrid system for a vehicle comprises an engine 1, a hybrid module 10 and a transmission mechanism with double input shaft 20; the hybrid module 20 comprises an electric motor 6, a planetary gear 5, a first clutch 4 and a brake 3; the planetary gear 5 comprises at least three rotating shafts, the three rotating shafts are the sun gear shaft S, the planet carrier shaft C, the crown shaft R, the axes of the three shafts are on the same straight line. The power output shaft 2 of the motor 1 is connected to the shaft of the ring gear R, and connected to the second input shaft 12 of the double input shaft transmission mechanism 20. The rotor 7 of the electric motor 6 is connected to the shaft of the sun gear S. The planet carrier shaft C is connected to the first input shaft 11 of the double input shaft transmission mechanism 20. The first clutch 4 is disposed between any two Of the three shafts of the planetary gear, the planetary gear is used together with the rotating shaft. The brake 3 is mounted on the power output shaft 2 of the motor 1. The double input shaft transmission mechanism 20 comprises a first input shaft 11, a second input shaft 12, several pairs of. front gears, at least one set of reverse gears GR, a first output shaft 16 and a second output shaft 17. A set of reverse gears GR between the two gears with steering gear. The first input shaft 11 is provided with an odd speed drive gear DG1 / 3, DG5 / 7, the second input shaft is provided with an even speed drive gear DG2 / 4, DG6 / 8. The first output shaft 16 is arranged with driven gears DG1, DG5, DG2, DG6, each driven gear is connected to the shaft by respective synchronizers S1, S5, S2 and S6, respectively, and drive gear DG1 / 3 engages with driven gear DG1, DG3, drive gear DG5 / 7 engages with driven gear DG5, DG7, drive gear DG2 / 4 engages with driven gear DG2, DG4, drive gear DG6 / 8 engages with driven gear DG6, DG8. Each drive gear engages with two driven gears, thus reducing the occupation of axial space. The output gear of the first output shaft 16 and of the second output shaft 17 are engaged with the main reducer; each drive gear and two driven gears engage to form two gears, a total of four groups, eight speeds, the required number of small gears, along the axial arrangement of four rows of gears and two pairs of synchronizers, the axial size is compact; the speed ratio between the positions is also more reasonable, as shown in Table 1.
    [0045]
    [0046] As shown in Figures 1 and 2, the hybrid system for a vehicle whose brake function 3 is to lock the power output shaft 2 of the motor 1 during pure electric drive or regenerative braking for prevent it from rotating and give crown R an inverted torque. When the motor should be running, release the motor power output shaft so that it can rotate freely.
    [0047] In combination with the , the describes the kinematic relationship of each axis of rotation of the planetary gear on the and the .
    [0048] The axis of the sun gear S, the shaft of the planet carrier C and the shaft of the crown R have the following kinematic constraints:
    [0049] nR + p ns = (1 + ρ) nC
    [0050] ρ ＝ S / R
    [0051] Among them: nR, ns and nc respectively indicate the speed of the crown R, the sun wheel S and the planet carrier C; R and S respectively indicate the number of teeth of the crown R and the sun wheel S. This kinematic constraint can also be described intuitively by a lever diagram, as shown in the , a lever is placed horizontally, with three points above, followed by S, C, R, respectively representing the sun wheel S, the planet carrier C and the crown R; the distance between point S and point C is 1, and the distance between point C and point R is ρ ＝ S / R. A vector perpendicular to the lever is derived from each point, representing the rotational speed of the sun wheel S, the planet carrier C, the crown R, respectively, and the vertices of the three vectors are kept in a straight line. From the , it can be seen that the speed of the planet carrier C is always between the speed of the sun wheel S and the speed of the crown R; the connection between the shaft of the crown R and the shaft of the sun gear S is interchangeable and remains functional.
    [0052] As shown in the In general, a planetary gear has at least three shafts: the X1 shaft, X2 shaft and X3 shaft, respectively, on a single straight line. Kinematic constraints exist between the rotational speeds of the three shafts, which can be represented by a lever diagram: a lever is placed horizontally with three points X1, X2 and X3, representing the three shafts, respectively, and the distance between the points is determined by planetary parameters. From each point leads to a vector perpendicular to the lever, indicating the speed of the shaft, the three vector arrows pointing in a straight line. As can be seen on the , the speed of rotation of the shaft X2 is always between the speed of rotation of the shaft X1 and the speed of rotation of the shaft X3; the connection between shaft X1 and shaft X3 is interchangeable and remains functional.
    [0053] The power output shaft 2 of the motor 1 is connected with the rotation shaft X3 of the planetary gear and the second input shaft 12 of the double input shaft transmission mechanism 20, the rotor 7 of the motor electric 6 is connected to the shaft X1, the shaft X2 is connected to the first input shaft 11 of the double input shaft transmission 20, and the first clutch 4 is arranged between two rotation shafts of the gear planetary to lock the three planetary gear shafts, with the rotational speed.
    [0054] The torque is supported on the three shafts of the planetary gear, the sum of the torque on the sun gear shaft is Ts, the sum of the torque on the crown shaft is Tr, and the sum of the torque on the planetary gear shaft, as shown in the . When the first clutch is separated, there are the following relationships between the three torques:
    [0055] Ts = ρ Tr
    [0056] Tc = Ts + Tr
    [0057] The electric motor 6 is connected to the shaft of the sun gear S and acts on the drive torque Tm, Ts = Tm; the motor 1 is connected to the crown shaft R and to the second input shaft 12. The driving torque of the motor is Ten and the reaction torque of the second input shaft is T2, Tr = Ten-T2 ; the first input shaft 11 is connected to the rotation shaft of the planet carrier C, the reaction torque of the first input shaft is T1 = Tc; the reaction torque T1 is actually the reaction torque emitted by the planetary carrier to the first input shaft, with equal sizes and opposite directions. The reaction torque T2 is actually the reaction torque of the output torque of the ring gear R to the second input shaft, with equal sizes and opposite directions.
    [0058] Engine speed ratio: The ratio of the speed of the power output shaft 2 of the engine 1 to the speed of the gearbox output shaft is called the gear ratio. The hybrid power system of the present invention has fixed gears, and the speed ratios are respectively η1, η2, η3, ..., ηn, as long as each gear is engaged and the first clutch 4 is closed, the motor 1 of the power take-off shaft 2 can realize all these gears one by one.
    [0059] The particular situation is as follows: if it is an odd gear i, the speed ratio of the first input shaft 11 is equal to the speed ratio ηi of the gear; the planet carrier rotation shaft C is connected to the first input shaft 11, and the speed ratio is also equal to ηi; since the first clutch 4 is closed, the planetary gear 5 is coupled, and the three rotary shafts rotate at the same speed, and the speed ratio between the rotary shaft of the ring gear R and the power output shaft 2 of motor 1 is also equal to ηi. Likewise, if the synchronizer is fixed to an even pinion j, the speed ratio of the second input shaft 12 is equal to the speed speed ratio ηi; the rotation shaft of the ring gear R and the power output shaft 2 of the motor are connected to the second input shaft, the speed ratio is also equal to ηi; with the first clutch closed, planetary gear 5 is engaged and all three rotary shafts rotate at the same speed. The speed ratio between the rotational shaft of the sun gear S and the motor shaft is also equal to the gear speed ratio ηi.
    [0060] In addition to the n fixed gear positions described above, the hybrid system of the present invention can also provide a continuous gear ratio for the motor during acceleration, provided that the battery can provide the required electrical power, see it . The hybrid power system works as follows: the system is in first gear, the first clutch is disengaged, the engine and engine are differentially driven; the engine is kept at a certain speed, the engine speed constantly changes with the vehicle speed, the engine speed ratio to the first input shaft changes continuously, and the output shaft speed ratio changes continuously. As long as the number of odd speeds is maintained, the system can achieve continuous speed. Continuous transmission can improve the fuel consumption of the vehicle in urban road conditions. Likewise, by engaging other odd speeds, the system can also achieve a certain continuous speed range.
    [0061] With reference to the , in the case of differential drive, the hybrid system of the present invention can provide a gear ratio over a long period and is a quasi-fixed gear ratio. When engaging the first gear, with the motor near zero speed, the motor speed ratio is roughly equal to (1 + ρ) η1, which is greater than the speed ratio of the first gear, called 01 block for convenience. The motor can run near zero speed for a long time because when the motor speed is close to zero, the power consumption is low, and the battery pack can be powered for a long time. There is another reason: the motor speed may be above zero, which is an electrical condition, consuming battery power, or may also be below zero, which is a condition of power generation, charging the battery. In this way, the motor can run for long hours at a speed close to zero speed, essentially balancing the power of the battery. Therefore, the system obtains an additional speed / speed ratio with a total speed ratio n + 1, and the speed ratio range is also extended to (1 + ρ) times.
    [0062] The method of controlling a hybrid system for a vehicle according to the present invention comprises a purely electric mode, a purely motor drive mode, a hybrid drive mode and a charging mode.
    [0063] The method of controlling a hybrid system for a vehicle according to the present invention has operating conditions in purely electric mode (EV mode) as follows:
    [0064] 1. The hybrid system has engaged an odd gear, the gear ratio is ηi; the first clutch 4 is closed, the planetary gear rotates at different speeds; the brake 3 is applied to limit the power output shaft 2 of the rotary motor 1;
    [0065] 2. See the , the , the motor torque acting on the shaft of the sun gear S, so that it tends to rotate forwards; the sun wheel drives the rotation of the satellite, the satellite tends to drive the reverse rotation of the crown; the brake limits the inversion of the crown wheel, forcing the planet carrier C to turn positively;
    [0066] 3. The torque of the motor is Tm, the torque of the planet carrier shaft C is (1 + 1 / ρ) · Tm;
    [0067] 4. The speed of the motor is ns, the rotational speed of the planet carrier shaft C is ns / (1 + 1 / ρ), and the total driving speed ratio of the motor is (1 + 1 / ρ) · ηi.
    [0068] The hybrid vehicle system according to the present invention has the operating conditions of the hybrid drive mode (HEV mode) as follows:
    [0069] See it , the , when the hybrid engine and engine vehicles start,
    [0070] 1. Gear D of the hybrid system (forward gear), the suspended gearbox gear 1, the first clutch 4 is uncoupled; before starting, the wheel at zero speed, the first input shaft 11 and the planet carrier are also at zero speed, the engine rotation at idle, the electric motor reversing;
    [0071] 2. Starting: the motor increases the torque, the electric motor also increases the torque and increases the speed, drives the planetary carrier and the first input shaft to accelerate, and through the gearbox, drives the wheel to turn ;
    [0072] 3. At this time the motor and the electric motor differential drive, the speed ratio of the motor to the wheel can be continuous changes, optimize the engine conditions, reduce fuel consumption; the acceleration process is short, the battery power can be supported;
    [0073] 4. Vehicle acceleration, speed increase, planet carrier speed increase;
    [0074] 5. When the planet carrier speed reaches a certain speed, the first clutch is closed, the gear ratio of the motor to the wheel is fixed, in a fixed gear.
    [0075] In the method of controlling a hybrid system for a vehicle according to the present invention, under the conditions of the hybrid drive mode of the engine and the engine, the step of operating the fixed gear position is as follows:
    [0076] 1. The hybrid system has engaged an odd speed i, the first clutch is closed; the speed ratio between the first input shaft and the planet carrier is ηi; due to the closing of the first clutch, the three rotating shafts in the planetary gear rotate at the same speed, and the ratio of the crown wheel and the engine speed is equal to ηi; the motor and electric motor torque are respectively applied to the rotation shaft of the sun gear S and to the rotation shaft of the crown R and are superimposed via the planetary gear and transmitted to the wheel by the first shaft of input and transmission gear i;
    [0077] 2. Even speed j of the hybrid system, the first clutch is closed; the speed ratio of the second input shaft to the crown is ηj; due to the closing of the first clutch, the three rotating shafts in the planetary gear rotate at the same speed, and the ratio of the crown wheel and the engine speed is equal to ηi; the motor and electric motor torque are respectively applied to the rotation shaft of the sun gear S and to the rotation shaft of the crown R, superimposed via the planetary gear and transmitted to the wheel by the second input shaft and the gear j of the wheel.
    [0078] In the method of controlling a hybrid system for a vehicle according to the present invention, in hybrid driving mode, the operating steps for changing gear are:
    [0079] I. From odd speed to adjacent even speed, see , the :
    [0080] 1. before the speed change: the synchronizer is resting on the gear at odd speed i, the speed ratio of ηi; the first clutch is closed, the planetary gear is coupled, the motor and electric motor drive the gear in parallel, and the continuous horizontal line in the ;
    [0081] 2.start the gear change: adjust the torque of the motor and the electric motor so that Tm = ρTen, the torque supported by the first clutch is reduced to zero, and the sum of the adjusted torque is equal to the sum of the front torque adjustment; Tm is the driving torque of the electric motor, ρ = S / R, R, S respectively indicate the number of teeth of the crown and the sun wheel, ten is the driving torque of the motor;
    [0082] 3. release of first clutch, differential drive of motor and electric motor; in the process, the torque of the electric motor and the motor is balanced around the planet carrier shaft, and the driving torque is equal to the torque before the gear change;
    [0083] 4.The electric motor adjusts the rotational speed of the sun wheel shaft, then drives the gear shaft and second input shaft speed change, so that the second input shaft and the new gear synchronize; the torque of the electric motor and the motor are balanced around the shaft of the planetary wheel, and the driving torque is equal to the torque before the gear change, the motor controls the torque while the electric motor controls the speed of rotation of the sun wheel via the planetary gear, controls the speed of the ring gear, so that the second input shaft and the gear to be mounted even gear rotate at the same speed and facilitate the shifting of gears by the synchronizer, as shown by the dotted line on the . Due to the fast response and high precision of the motor speed control, the speed and smoothness of the synchronizer gear can be improved, and the shock of the gear can be reduced.
    [0084] 5.the synchronizer engages a new gear (even speed), the process torque remains unchanged, as shown in the ;
    [0085] 6.The motor output torque is transferred to the motor power output shaft, the motor directly drives the second input shaft and the new gear, the motor torque becomes zero, the first input shaft and the original odd gear, in the process, the motor torque is transferred to the motor, and the driving torque is equal to the torque before the gear change;
    [0086] 7. the synchronizer has removed the original odd speed;
    [0087] 8. the first clutch is closed, the planetary gear is coupled, the motor and the electric motor drive the new speed in parallel; in the process, it is possible to adjust and balance the torque of the electric motor and the motor, the sum of the driving torque is equal to the torque before the gear change, like the dotted line in the .
    [0088] II. From even speed to adjacent odd speed, see , the :
    [0089] 1. before the speed change: the synchronizer is resting on the gear at even speed j, the speed ratio ηj; the first clutch is closed and the planetary gear is coupled, the motor and electric motor drive the speed in parallel, as shown in the ;
    [0090] 2.start gear shifting: the motor output torque is transferred to the motor power output shaft, the motor directly drives the second input shaft and the original gear, the motor torque becomes zero and the clutch torque is zero, in the process, the engine torque is transferred to the engine, and the driving torque is equal to the torque before the gear change;
    [0091] 3. the first clutch is released, the three planetary gear shafts rotate at different speeds, and the torque remains unchanged during this process;
    [0092] 4.The electric motor adjusts the rotational speed of the sun gear shaft S, then drives the rotating shaft of the planet gear C and the first input shaft to adjust the speed, so that the first shaft d 'input is synchronized with the new gear, so that the gear synchronizer is easy to move, as shown in the dotted line; in this process, the motor torque acts directly on the second input shaft, and the wheels are driven by even gears, and the torque is equal to the torque before the gear change; Due to the fast response and high precision of motor speed control, it can improve the speed and smoothness of the synchronizer speed change compliance, reduce the shock of transmissions.
    [0093] 5.the synchronizer engages a new gear (odd speed), the process torque remains unchanged, as shown in the ;
    [0094] 6.Adjust the torque of the motor and the electric motor so that Tm = ρTen, and the sum of the adjusted torque is equal to the sum of the torque before the adjustment, so that the torque experienced by the second input shaft and l the original gear is reduced to zero; among them, Tm is the driving torque of the electric motor, ρ ＝ S / R, R, S indicates the number of teeth of the crown and the sun wheel S, respectively, Ten is the driving torque of the motor;
    [0095] 7. remove the original even speed, the process torque remains the same;
    [0096] 8. the first clutch is closed, the planetary gear is coupled, the motor and the electric motor drive the gear of the new speed in parallel; in the process, it is possible to adjust and balance the torque of the electric motor and the motor, the sum of the driving torque is equal to the torque before the gear change, see the dotted line of the .
    [0097] The method of controlling a hybrid system for a vehicle according to the present invention has the step of switching from a purely electric mode (EV condition) to a hybrid drive mode (HEV condition):
    [0098] 1.before shifting: the synchronizer is resting on the gear at odd speed i, the first clutch is uncoupled, the motor power output shaft is locked by the brake, the electric motor drives the sun wheel, the first input shaft and speed change gear via the planet carrier;
    [0099] 2. start switching: the brake is released, the first clutch is closed and, which causes the three shafts of the gear system to rotate at the same speed;
    [0100] 3. in order to avoid a greater impact, to limit the first friction torque of the clutch; at the same time, the motor should appropriately increase the torque to compensate for the loss of torque;
    [0101] 4.Once the engine power output shaft reaches ignition speed, the engine will ignite and start to run, the hybrid system will enter hybrid drive mode
    [0102] The method of controlling a hybrid system for a vehicle according to the present invention is converted from a hybrid drive mode (HEV condition) to a purely electric mode (EV condition):
    [0103] 1.before conversion, the system has engaged an odd-speed gear (or pinion), the synchronizer is resting on the odd-speed gear i, the first clutch is closed, the brake is released, the motor and the electric motor is driven in parallel; if the system is linked at an even speed, it must first be transformed into an odd speed;
    [0104] 2. start switching: the first clutch is released, allowing the motor shaft to slow down; the engine is off; the brake is applied, the speed of the motor power output shaft will be zero and locked;
    [0105] 3. the electric motor continues to drive the sun wheel, the system switches to purely electric mode (EV conditions).
    [0106] As shown on the , the hybrid system for a vehicle whose double input shaft transmission mechanism 20 comprises a first input shaft 11, a second input shaft 12, several pairs of front gears, at least one reverse gear GR and an output shaft 15. The first input shaft 11 is driven by a two-stage gear towards the first input shaft 11 ', the gear 11a is meshed with the gear 11b for the first transmission stage and the gear 11b is meshed with gear 11c for the second stage; the first input shaft 11 'is arranged with odd drive gears G1, G3, G5 and G7 connected to the shaft by the corresponding synchronizers S1, S3, S5 and S7; the second input shaft 12 is provided with drive gears of even speeds G2, G4, G6, G8 and is connected to the shaft by the corresponding synchronizers S2, S4, S6 and S8. The four driven gears with the gear positions on the output shaft 15 are fixed on the shaft, and the four driven gears are respectively engaged with G1 and G2, G3 and G4, G5 and G6, G7 and G8. Each driven gear is meshed with two active gears in a group to form two gears. A total of four groups, eight gears are required along the axial arrangement of four rows of gears and two pairs of synchronizer, which reduces the axial dimension. The speed ratio between gear changes is also more reasonable.
    [0107] As shown on the , the hybrid system for a vehicle whose double input shaft transmission mechanism 20 comprises a first input shaft 11, a second input shaft 12, several pairs of front gears, at least one reverse gear GR, and a output shaft 15. The first input shaft 11 is driven by a first stage gear to the first input shaft 11 'and the second input shaft 12 is driven by a first stage gear to the second shaft d 'entry 12'; the first input shaft 11 'is arranged with odd drive gears G1, G3, G5 and G7 connected to the shaft by the corresponding synchronizers S1, S3, S5 and S7; the second input shaft 12 'is provided with even speed drive gears G2, G4, G6, G8 and is connected to the shaft by the corresponding synchronizers S2, S4, S6 and S8. The four driven gears with the gear positions on the output shaft 15 are fixed on the shaft and the four driven gears are respectively engaged with G1 and G2, G3 and G4, G5 and G6, G7 and G8. Each driven gear is meshed with two active gears in a group to form two gears; a total of four groups, eight positions, the required number of gears, along the axial arrangement of four rows of gears and two pairs of synchronizer, reducing the axial dimension. The speed ratio between gear changes is also more reasonable.
    [0108] As shown on the , the hybrid system for the vehicle is provided with a second clutch 8 on the power output shaft 2 of the engine 1; the second clutch 8 replaces the brake 3 of the and some , the rest is unchanged. Pure electric drive: the second clutch 8 is disengaged to separate the power output shaft 2 from the engine of the hybrid power module 20; an odd gear is engaged; the first clutch 4 is closed to assemble the planetary gears, rotate at the same speed, and the output torque of the motor is driven by the planetary gear and the gear. When the motor and the electric motor are mixed mixed: the second clutch 8 is closed, and the power output shaft 2 of the motor is connected to the relevant rotary shaft of the planetary gear; all other functions and methods of implementation remain unchanged.
    [0109] The present invention also protects a vehicle comprising the hybrid system described above.
    [0110] The foregoing is only a preferred embodiment of the present invention, and not a limitation of the present invention, where changes and equivalent modifications within the scope of the patent application according to the present invention should be made without departing. of the spirit and scope of the present invention.
    权利要求:
    Claims (10)
    [0001]
    A hybrid system for a vehicle comprising an engine, a hybrid module and a transmission mechanism with double input shaft, the hybrid module includes an electric motor, a planetary gear, a first clutch and a brake; in said system the planetary gear comprises at least three rotary shafts: a shaft X1, a shaft X2, a shaft X3, the axes of the three shafts are on the same straight line, wherein the speed of rotation of the shaft X2 is between the speed of rotation of the shaft X1 and the speed of rotation of the shaft X3, wherein the first clutch is disposed between any two of the three shafts; wherein a power output shaft of the motor is connected to the shaft X3 or the shaft X1 of the planetary gear and to a second input shaft of the double input shaft transmission mechanism, and the rotor of the electric motor is connected to the shaft X1 or the shaft X3, and the shaft X2 is connected to a first input shaft of the double input shaft transmission mechanism; wherein the brake is mounted on the motor power output shaft; wherein the dual input shaft transmission mechanism comprises the first input shaft, the second input shaft, a plurality of pairs of front gears, at least one set of reverse gears and an output shaft, wherein the first input shaft is provided with drive gears assigned to odd speeds, while the second input shaft is provided with drive gears assigned to even speeds, in which the reverse drive gears are arranged on the first input shaft or the second input shaft, wherein the output shaft is arranged with the driven gears of each gear, and the driven gears of each gear engage with the corresponding driven gears; in which a pinion of each speed is connected to the shaft via a synchronizer.
    [0002]
    A hybrid system for a vehicle comprising an engine, a hybrid module and a transmission mechanism with double input shaft, the hybrid module includes an electric motor, a planetary gear, a first clutch and a brake; the planetary gear comprises at least three rotating shafts: an X1 shaft, an X2 shaft, an X3 shaft, the axes of the three shafts are on the same straight line, the rotational speed of the X2 shaft is between the rotational speed of the shaft X1 and the rotational speed of shaft X3; the first clutch is disposed between any two of the three shafts; a motor power output shaft is connected to the X3 shaft or X1 shaft of the planetary gear and a second input shaft of the double input shaft transmission mechanism, and the motor rotor electric is connected to the X1 shaft or X3 shaft, and the X2 shaft is connected to a first input shaft of the double input shaft transmission mechanism; the brake is mounted on the motor power output shaft; the double input shaft transmission mechanism includes the first input shaft, the second input shaft, a plurality of pairs of front gears, at least one set of reverse gears and an output shaft, the first input shaft is provided with drive gears assigned to odd speeds, while the second input shaft is provided with drive gears assigned to even speeds, a number of driven gears are provided on the first output shaft, and a number of driven gears are also provided on the second output shaft; the driven pinions are respectively connected to the shaft by means of respective synchronizers; each drive pinion engages with a driven pinion on the first and second output shafts.
    [0003]
    A hybrid system for a vehicle comprising an engine, a hybrid module and a transmission mechanism with double input shaft, the hybrid module includes an electric motor, a planetary gear, a first clutch and a brake; the planetary gear comprises at least three rotating shafts: an X1 shaft, an X2 shaft, an X3 shaft, the axes of the three shafts are on the same straight line, the speed of rotation of the shaft X2 is between the speed of rotation of the shaft X1 and the speed of rotation of the shaft X3; the first clutch is disposed between any two of the three shafts; the power output shaft of the motor is connected to the X3 shaft or X1 shaft of the planetary gear and a second input shaft of the double input shaft transmission mechanism, and the rotor of the electric motor is connected to the X1 shaft or X3 shaft, and the X2 shaft is connected to a first input shaft of the double input shaft transmission mechanism; the brake is mounted on the motor power output shaft; the double input shaft transmission mechanism includes the first input shaft, the second input shaft, a plurality of pairs of front gears, at least one set of reverse gears and an output shaft, the front of the first input shaft is transmitted to the rear of the first input shaft by a two-stage gear; the rear of the first input shaft is provided with drive pinions assigned to odd speeds, which are connected to the shaft by a corresponding synchronizer; the second input shaft is equipped with drive pinions assigned to even speeds, which are connected to the shaft by a corresponding synchronizer; the output shaft is equipped with a driven gear which is fixed on the shaft; each driven gear engages with two drive gears, one odd and one even, to form two gears.
    [0004]
    A hybrid system for a vehicle comprising an engine, a hybrid module and a transmission mechanism with double input shaft, the hybrid module includes an electric motor, a planetary gear, a first clutch and a brake; the planetary gear comprises at least three rotating shafts: an X1 shaft, an X2 shaft, an X3 shaft, the axes of the three shafts are on the same straight line, the speed of rotation of the shaft X2 is between the speed of rotation of the shaft X1 and the speed of rotation of the shaft X3; the first clutch is disposed between any two of the three shafts; the power output shaft of the motor is connected to the X3 shaft or X1 shaft of the planetary gear and a second input shaft of the double input shaft transmission mechanism, and the rotor of the electric motor is connected to the X1 shaft or X3 shaft, and the X2 shaft is connected to the first input shaft of the double input shaft transmission mechanism; the brake is mounted on the motor power output shaft; the dual input shaft transmission mechanism includes a first input shaft, a second input shaft, a plurality of pairs of front gears, at least one set of reverse gears and an output shaft, the front of the first input shaft is connected to the rear of the first input shaft by a first stage gear, and the front of the second input shaft is connected to the rear of the second input shaft by a first stage gear; the rear of the first input shaft is provided with drive pinions assigned to odd speeds, which are connected to the shaft by a corresponding synchronizer; the rear of the second input shaft is fitted with drive pinions assigned to even speeds, which are connected to the shaft via a corresponding synchronizer; the output shaft is equipped with a gear driven gear, which is fixed on the shaft; each driven gear engages with two drive gears, one odd and one even, to form two gears.
    [0005]
    Hybrid vehicle system according to one of claims 1, 2, 3 or 4, with in its hybrid module, the planetary gear comprises at least three rotary shafts, namely: a shaft of the sun gear S, a shaft of the door -satellite C, a shaft of the crown R, the axes of the three shafts are on the same straight line, the speed of rotation of the shaft of the planet carrier C is between that of the sun wheel S and that of the crown R , a first clutch is disposed between two of said three rotary shafts; the power output shaft of the motor is connected with the rotating shaft of the crown wheel R or the rotating shaft of the sun gear S of the planetary gear and the second input shaft of the double shaft transmission mechanism input, the rotor of the electric motor is connected to the rotating shaft of the sun gear S or to the crown shaft R of the planetary gear, the rotating shaft of the planetary carrier C is connected to the first shaft input of the double input shaft transmission mechanism.
    [0006]
    The hybrid system for vehicles according to one of claims 1, 2, 3, 4 or 5 is characterized in that the brake in the hybrid module is replaced by a second clutch and the second clutch is mounted on the output shaft of engine power.
    [0007]
    Method of controlling a hybrid system for a vehicle as described in one of claims 1 to 6, characterized in that the operating mode comprises a purely electric mode, a purely motor drive mode, a drive mode. hybrid drive and a charging mode.
    [0008]
    The method of controlling a hybrid system for a vehicle as described in claim 7, characterized in that in hybrid drive mode, the operating steps for changing gears are: I. from odd speed to adjacent even speed (1). before the gear change: the synchronizer is resting on the gear at odd speed, the first clutch is closed, the planetary gear is coupled, the motor and the electric motor drive the gear in parallel; (2). start the speed change: adjust the torque of the motor and the electric motor so that Tm = ρTen, the torque supported by the first clutch is reduced to zero, and the sum of the adjusted torque is equal to the sum of the torque before adjustment; Tm is the driving torque of the electric motor, ρ = S / R, R, S indicate the number of teeth of the crown and the sun gear respectively, Ten is the driving torque of the motor; (3). the release of the first clutch, differential drive of the motor and the electric motor; in the process, the torque of the electric motor and the motor is balanced around the planet carrier shaft, and the driving torque is equal to the torque before the gear change; (4). the electric motor adjusts the rotational speed of the sun wheel shaft, then drives the speed change of the crown shaft and the second input shaft, so that the second input shaft and the new one gears synchronize; the torque of the electric motor and the motor is balanced around the shaft of the planetary wheel, and the driving torque is equal to the torque before the gear change, the motor controls the torque while the electric motor controls the speed of rotation of the sun gear via the planetary gear, and controls the speed of the ring gear, so that the second input shaft and the pinion to be engaged at the even gear pinion rotate at the same speed and make it easier to change gears by the synchronizer; (5). the synchronizer hooks a new gear, in the process the torque remains the same; (6). the output torque of the electric motor is transferred to the power output shaft of the motor, the motor directly drives the second input shaft and the new gear, the torque of the electric motor becomes zero, the torque supported by the first shaft input and the gear of the original odd speed is zero, in the process, the torque of the electric motor is transferred to the motor, and the driving torque is equal to the torque before the speed change; (7). the synchronizer is removed from the original odd speed; (8). the first clutch is closed, the planetary gear is coupled, the motor and the electric motor drive the new speed in parallel; in the process, it is possible to adjust and balance the torque of the electric motor and the motor, the sum of the driving torque is equal to the torque before the gear change; II. from even speed to adjacent odd speed (1). before the speed change: the synchronizer is resting on the gear at even speed, the first clutch is closed, the planetary gear is coupled, the motor and the electric motor drive the speed in parallel; (2). start gear shifting: the output torque of the electric motor is transferred to the power output shaft of the motor, the motor directly drives the second input shaft and the original gear, the torque of the electric motor becomes zero and the clutch torque is zero, in the process, the torque of the electric motor is transferred to the motor, and the driving torque is equal to the torque before the gear change; (3). the first clutch is released, the three shafts of the planetary gear rotate at different rotational speeds, and the torque remains unchanged during this process; (4). the electric motor adjusts the rotational speed of the sun wheel shaft, then drives the speed change of the planet carrier shaft and the first input shaft, so that the first input shaft and the new gear synchronize; in this process, the driving torque acts directly on the second input shaft, driving the wheels by even gears, and the torque is equal to the torque before the gear change; (5). the synchronizer hooks a new gear, in the process the torque remains the same; (6). adjust the torque of the motor and the electric motor so that Tm = ρTen, and the sum of the adjusted torque is equal to the sum of the torque before the adjustment, so that the torque supported by the second input shaft and the gear original is reduced to zero; Tm is the driving torque of the electric motor, ρ = S / R, R, S indicates the number of the crown and the sun wheel respectively, Ten is the driving torque of the motor; (7). remove the original pair gear, the torque remains unchanged during this process; (8). the first clutch is closed, the planetary gear is coupled, the motor and electric motor drive in parallel the gear of the new speed; In the process, it is possible to adjust and balance the torque of the electric motor and the motor, the sum of the driving torque is equal to the torque before the gear change.
    [0009]
    The method of controlling a hybrid system for a vehicle according to claim 7, characterized in that the operating step of changing from a purely electric mode to a hybrid drive mode is as follows: (1). before shifting: the synchronizer is resting on the gear at odd speed, the first clutch is uncoupled, the motor power output shaft is locked by the brake, the electric motor drives the sun wheel, the first shaft d 'input and gear change gear via the planetary carrier; (2). start switching: the brake is released, the first clutch is closed and, which causes the three shafts of the gear system to rotate at the same rotational speed; (3). limiting the slip torque of the first clutch, and at the same time, the electric motor increases the torque to compensate for the loss of torque; (4). Once the engine power output shaft reaches firing speed, the engine fires up and begins to spin, the hybrid system goes into hybrid drive mode.
    [0010]
    Vehicle characterized in that it comprises a hybrid system according to one of claims 1 to 9.
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    同族专利:
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    KR100951967B1|2008-06-23|2010-04-08|현대 파워텍 주식회사|Power train for a hybrid electric vehicle with automated manual transmission|
    US8579751B2|2012-01-26|2013-11-12|GM Global Technology Operations LLC|Hybrid powertrain with layshaft transmission and electric torque converter and method of controlling same|
    US9108505B2|2013-05-28|2015-08-18|Ford Global Technologies, Llc|Powersplit powertrain for a hybrid electric vehicle|
    AT514979B1|2013-10-28|2016-03-15|Avl List Gmbh|Torque transmission device with a planetary gear device and method for operating such a torque transmission device|
    SE540692C2|2014-03-20|2018-10-09|Scania Cv Ab|A method for controlling a hybrid driver, vehicles with such a hybrid driver, computer programs for controlling such a hybrid driver, and a computer software product comprising program code|
    CN104842772B|2015-03-27|2016-04-13|比亚迪股份有限公司|Power drive system and there is its vehicle|
    CN106609815A|2016-08-01|2017-05-03|雷世庆|Plug-in multi-gears hybrid transmission|
    CN106864247B|2017-01-25|2019-02-22|段志辉|Hybrid power system for vehicle|
    CN109866604A|2017-12-05|2019-06-11|吉利汽车研究院（宁波）有限公司|A kind of double-motor hybrid assembly|
    US10569635B2|2018-01-25|2020-02-25|Zhihui Duan|Hybrid electric drive train of a motor vehicle|
    CN108501684B|2018-04-03|2020-08-14|段志辉|Automobile oil-electricity hybrid power gearbox|
    CN209008383U|2018-10-30|2019-06-21|广州汽车集团股份有限公司|Power dividing hybrid power coupled system and vehicle|
    CN110525191A|2019-09-20|2019-12-03|段志辉|Hybrid power system and its control method for vehicle|CN110525191A|2019-09-20|2019-12-03|段志辉|Hybrid power system and its control method for vehicle|
    CN112356651A|2020-11-23|2021-02-12|北京新能源汽车技术创新中心有限公司|Transmission, driving system and vehicle|
    CN113154029A|2021-05-12|2021-07-23|浙江吉利控股集团有限公司|Gear shifting control method and gear shifting control system of vehicle|
    法律状态:
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