JP2006007968A - Hybrid vehicle drive transmission device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hybrid vehicle excellent in operating efficiency of a motor. <P>SOLUTION: In the hybrid vehicle provided with an engine 1, an engine driving shaft 10 for taking out driving force of the engine 1, the motor (MG)3 for imparting the driving force to the vehicle with electric power stored in a battery 18, a MG driving shaft 19 for taking out the driving force of the MG3, and a vehicle driving shaft 15 for transmitting the driving force to be transmitted from the engine driving shaft 10 and the MG driving shaft 19 to a driving wheel 5, a motor transmission 4 having stepped gear ratio for transmitting the driving force of the MG3 to the vehicle driving shaft 15, and a clutch 22 for interrupting transmission of the driving force from the MG3 is provided. The engine driving shaft 10 is provided with a forward gear 11, a reverse gear 12, and a clutch 13 to be selectively connected with or separated from the gears 11, 12. The vehicle driving shaft 15 is provided with a gear 16 connected with the gear 11, a gear 25 connected with the gear 12 through the MG transmission 4, and a clutch 26 to be connected with or separated from the gear 16. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a drive transmission device for a hybrid vehicle, and particularly, to perform a smooth shift.

  In recent years, hybrid vehicles (HEV) equipped with a combination of an engine and an electric motor (hereinafter referred to as MG) have been put into practical use because of demands for low pollution, cruising distance, and energy supply infrastructure.

Conventionally, an engine that assists the output of an engine with the output of an MG is disclosed in Patent Document 1.
JP 11-178112 A

  However, in the above invention, when the driving force from the engine is assisted by the MG, for example, the gear that transmits the driving force from the MG to the vehicle drive shaft is performed at a single gear ratio, and the MG is controlled according to the assist amount. The output fluctuates and the fluctuation range becomes large. Therefore, there is a problem that the MG may be operated in an output range where the efficiency of the MG is poor, and the MG cannot be operated with high efficiency.

  In addition, in order to use the driving force from the engine in reverse, it is necessary to provide a reverse gear. The present invention has been invented to solve such problems, and aims to operate the MG with high efficiency.

  In the present invention, an engine, an engine driving shaft that extracts the driving force of the engine, a motor that applies driving force to the vehicle by the electric power of the power storage device, a motor driving shaft that extracts the driving force of the motor, an engine driving shaft and a motor driving shaft In a hybrid vehicle having a vehicle drive shaft that transmits the driving force transmitted from the vehicle to the wheels, the vehicle has a stepped gear ratio that transmits the driving force of the motor to the vehicle driving shaft, and the vehicle is driven from the driving force of the motor. A motor transmission capable of interrupting transmission of driving force to the shaft; at least one forward transmission means for transmitting the rotation of the engine drive shaft when the vehicle is advanced; and an engine drive shaft when the vehicle is driven backward The reverse transmission means for transmitting the rotation of the engine, the engine drive shaft, and the forward transmission means or the reverse transmission means are selectively connected, separated, or not connected to any of the transmission means. Providing an engine drive shaft clutch sustainable in the neutral position. The vehicle drive shaft is connected to the forward transmission means to transmit at least one first transmission means for transmitting the rotation of the engine drive shaft and the motor drive shaft, and the reverse drive means is connected to the engine drive shaft via the motor transmission. Second transmission means for transmitting rotation of the motor drive shaft, and a first vehicle drive shaft clutch for connecting and separating the first transmission means and the vehicle drive shaft are provided.

  Also, an engine that applies driving force to the vehicle, an engine driving shaft that extracts the driving force of the engine, a motor that applies driving force to the vehicle by the electric power stored in the power storage device, a motor driving shaft that extracts the driving force of the motor, In a hybrid vehicle including an engine drive shaft and a vehicle drive shaft that transmits the driving force transmitted from the motor drive shaft to the wheels, the vehicle has a stepped gear ratio that transmits the driving force of the motor to the vehicle drive shaft, And a motor transmission capable of interrupting transmission of driving force between the motor drive shaft and the vehicle drive shaft, and at least one forward transmission means for transmitting the rotation of the engine drive shaft to the engine drive shaft when the vehicle is advanced, A counter shaft that is connected to the engine drive shaft and reverses the rotation direction of the engine drive shaft, and a third transmission hand that is connected to the motor transmission and transmits the rotation of the counter shaft. A counter clutch that connects and separates the counter shaft and the third transmission means, an inter-shaft clutch that connects and separates the engine drive shaft and the vehicle drive shaft, and a motor transmission. A plurality of driving force transmission means for transmitting rotation, and a second vehicle drive shaft clutch for connecting and separating the plurality of transmission means and the vehicle drive shaft. The third transmission means transmits the rotation of the engine drive shaft from the third transmission means to one of the plurality of transmission means via the motor transmission.

  According to the present invention, since the driving force transmitted from the motor to the vehicle drive shaft can be switched by the motor transmission, the efficiency of the motor can be increased, and the engine transmission 12 needs to have a separate forward / reverse switching mechanism. The hybrid vehicle can be reduced in size.

  The configuration of the first embodiment of the present invention will be described with reference to the block diagram of FIG.

  The hybrid vehicle of the present invention includes an engine 1 that is a prime mover such as an internal combustion engine, an engine transmission 2 that switches the output of the engine 1 according to the traveling state of the vehicle, an MG3 that is an electric motor and a generator, and an output of MG3. The MG transmission 4 is switched according to the traveling state. And the output by the engine 1 and MG3 is transmitted to the drive wheel 5, and a vehicle is drive | worked.

  The engine 1 is an internal combustion engine that generates an output for driving a vehicle by burning gasoline or the like, and is started by a starter / generator 6 (hereinafter, S / G) having functions of a starter and a generator. In addition, it can be started also by MG3 by connecting the clutch 26 mentioned later to the gearwheel 16. FIG. The driving force of the engine 1 is taken out by the engine shaft 7 and transmitted to the engine transmission 2 by the starting clutch 8 and the engine input shaft 9 of the engine transmission 2. The starting clutch 8 can be a friction clutch, a fluid clutch, an electromagnetic clutch, or the like.

  The engine transmission 2 changes the rotational speed and torque of the driving force of the engine 1 transmitted by the engine input shaft 9 and outputs the changed torque to the engine driving shaft 10. Here, the engine transmission 2 includes a belt-type continuously variable transmission, a toroidal-type continuously variable transmission, a transmission using planetary gears, an automatic clutch called automatic manual transmission (hereinafter referred to as automatic MT) and automatic transmission. Various transmissions such as a transmission combining a manual transmission to be performed can be used.

  The engine drive shaft 10 of the engine transmission 2 includes a gear 11 that is a forward transmission means used when the vehicle is moved forward, a gear 12 that is a reverse transmission means used when the vehicle is moved backward, and the engine drive shaft 10 and the gears. 11 or a clutch 13 that is an engine drive shaft clutch that connects and disconnects the gear 12 is disposed. By operating the clutch 13, the engine drive shaft 10 and the gear 11 or the gear 12 are connected, and the driving force of the engine 1 is transmitted to one of the gears 11 and 12 via the engine drive shaft 10. The gears 11 and 12 may use a traction drive. The clutch 13 is a meshing clutch (dog clutch), and is a clutch that selectively connects the meshing gear train (the gear 31 or the gear 32) and the engine drive shaft 10 selectively. The clutch 13 may be a multi-plate clutch, an electromagnetic clutch, a magnetic clutch, a bidirectional one-way clutch, or the like. This clutch configuration is also used for the clutch 22 and the clutch 26 described later. Note that the clutch 13 can be maintained at a neutral position where neither of the gears 11 and 12 is connected.

  The MG 3 generates a driving force that drives the vehicle with the electric power stored in the battery 18. Further, during regeneration, electric power is generated by torque transmitted from the drive wheel 5 or the engine drive shaft 10 via the MG transmission 4, and the battery 18 is charged by the electric power. An inverter 17 is provided between the battery 18 and the MG 3, and electric power is controlled by the inverter 17.

  The MG transmission 4 includes an MG drive shaft 19 that transmits the output of the MG 3, a gear 20 that is a motor drive force transmission unit disposed on the MG drive shaft 19, a gear 21, an MG drive shaft 19 and a gear 20, or a gear And a clutch 22 which is a motor drive shaft clutch to which the motor 21 is coupled. The MG drive shaft 19 is provided in parallel with the engine drive shaft 10, and the driving force of the MG drive shaft 19 is transmitted to the gear 21 or the gear 22 by connecting the gear 21 or the gear 22 and the MG drive shaft 19 by the clutch 22. To do. The gear 20 is engaged with a gear 16 described later, and the gear 21 is engaged with a gear 12 disposed on the engine drive shaft 10 and a gear 25 described later. That is, the gear 21 is provided between two gears, that is, a gear 12 disposed on the engine drive shaft 10 and a gear 25 disposed on the vehicle drive shaft 15, and meshes with the two gears 12 and 25. The clutch 22 can also be maintained in a neutral position where neither the gear 20 nor the gear 21 is connected.

  The vehicle drive shaft 15 is arranged in parallel with the engine drive shaft 10 and the MG drive shaft 19 and is constituted by a gear 25 that is a second transmission means that is always connected to the vehicle drive shaft 15 and a clutch 26 that is a first drive shaft clutch. A gear 16 that is a first transmission means to be connected and an output gear 24 that is always connected to the differential gear 23 are provided. The gear 25 meshes with the gear 21, whereby the driving force of the engine 1 is transmitted from the gear 12 to the gear 25 via the gear 21, and the driving force of the MG 3 is transmitted from the gear 21 to the gear 23. Further, the gear 16 meshes with the gear 11 and the gear 20, whereby the driving force of the engine 1 is transmitted from the gear 11 to the gear 16, and the output of the MG 3 is transmitted from the gear 20 to the gear 16. The driving force of the engine 1 or MG 3 transmitted by the gear 16 and the gear 25 is transmitted to the differential gear 23 by the output gear 24, and the vehicle travels by the driving wheel 5. The clutch 26 is necessary to prevent the vehicle drive shaft 15 from rotating during idle charging, which will be described later, and when the engine 1 is started by the MG 3. However, if these functions are not provided, the clutch 26 is omitted and the gear 16 is turned off. You may always connect with the vehicle drive shaft 15. FIG.

  With the above configuration, the driving force of the engine 1 or the MG 3 can be transmitted to the drive wheels 5 to drive the vehicle.

  Next, the gear switching operation when the hybrid vehicle of the present invention is traveling will be described.

  A case where the vehicle travels only with the driving force from the engine 1 when the vehicle moves forward (without assistance by the MG 3) will be described with reference to the block diagram of FIG. When the vehicle moves forward, the clutch 13 connects the engine drive shaft 10 and the gear 11, and the clutch 26 connects the vehicle drive shaft 15 and the gear 16. Since the gear 11 and the gear 16 are always meshed, the driving force from the engine 1 is transmitted to the vehicle drive shaft 15 to advance the vehicle. In FIG. 2, thick arrows indicate the flow of driving force (the same applies to the following drawings).

  Next, a case where driving force assist by MG3 is performed when the vehicle moves forward will be described. First, Low assist (Low gear) with a large assist torque by MG3 will be described with reference to FIG. In this case, the clutch 22 connects the MG driving force shaft 19 and the gear 20, and transmits the driving force from the MG 3 to the vehicle driving force shaft 15 via the gear 16. As a result, the gear 16 is rotated by the two gears of the gear 11 and the gear 20, and the driving force is transmitted to the vehicle driving force shaft 15. That is, the gear 16 is rotated by the driving force of the MG 3 in addition to the driving force of the engine 1, the driving force is transmitted to the vehicle driving force shaft 15, and the vehicle travels.

  Further, the high assist (high gear) in which the torque increase due to MG3 is small will be described with reference to FIG. In this case, the clutch 22 connects the MG driving force shaft 19 and the gear 21, and transmits the driving force from the MG 3 to the vehicle driving force shaft 15 through the gear 25. Thereby, the gear 16 and the gear 25 are rotated, and the driving force is transmitted to the vehicle driving force shaft 15. That is, the gear 16 is rotated by the driving force from the engine 1, the gear 25 is rotated by the driving force of the MG 3, the driving force is transmitted to the vehicle driving force shaft 15 by the two gears 16, 25, and the vehicle travels.

Here, the relationship between the gears 20, 21, 16, and 25 serving as the assist amount (driving force increase amount) for assisting the driving force by the engine 1 by the MG 3 will be described with reference to FIG. FIG. 5 is an arrow A view of the configuration diagram of FIG. The Low gear ratio R _L between the gear 16 and the gear 20 in the Low assist is

The high gear ratio _RH between the gear 25 and the gear 21 in the high assist is

It becomes. Thereby, the gear ratio of the assist amount for assisting the driving force of the engine 1 is
R _L > R _H formula (3)
If it becomes.

  The starting clutch 8 and the clutches 13, 22 and 26 include clutch actuators (not shown), and operate according to commands from a system controller (not shown) that controls the movement of the entire system of the vehicle by the operation of the driver. The engine 1, engine transmission 2, and MG3 are also controlled by the system controller.

  As described above, the hybrid vehicle of the present invention includes at least a two-stage transmission as the MG transmission 4.

  A case where the vehicle travels only with the driving force from the engine 1 when the vehicle is moving backward (without assistance by the MG 3) will be described with reference to the block diagram of FIG. When the vehicle is moving backward, the engine drive shaft 10 and the gear 12 are connected by the clutch 13. Further, the clutch 22 of the MG driving force shaft 19 is not connected to either the gear 20 or the gear 21 and is in a neutral position. Thereby, the rotation of the engine drive shaft 10 is transmitted to the vehicle drive shaft 15 by the gear 10, the gear 21, and the gear 25. At this time, the vehicle can be moved backward without changing the rotation direction of the engine drive shaft 10 by meshing one gear more than when moving forward, that is, by using the gear 21 as a counter gear. Note that the rotational direction of the MG driving force shaft 19 of the MG 3 is reverse to the rotational direction during forward travel during reverse travel.

  Next, the case where the driving force assist by the MG 3 is performed when the vehicle is moving backward will be described. First, Low assist (Low gear) in which the torque increase by MG3 is large will be described with reference to the block diagram of FIG. In this case, the clutch 22 connects the MG driving force shaft 19 and the gear 20, the clutch 26 connects the gear 16 to the vehicle driving force shaft 15, and the driving force from the MG 3 is transmitted to the vehicle driving force shaft via the gear 16. 15 is transmitted. That is, the gear 25 is rotated by the driving force from the engine 1, the gear 16 is rotated by the driving force from the MG 3, the driving force is transmitted to the vehicle driving force shaft 15 by the two gears 16, 25, and the vehicle travels. .

  Further, high assist (high gear) with a small assist torque by MG3 will be described with reference to the block diagram of FIG. In this case, the MG driving force shaft 19 and the gear 21 are connected by the clutch 22, the gear 21 is rotated by the gear 12 and the gear 25, and is transmitted to the vehicle driving force shaft 15. That is, in addition to the driving force from the engine 1, the gear 21 is rotated by the driving force of the MG 3, the driving force is transmitted to the vehicle drive shaft 15, and the vehicle travels.

Here, the relationship between the gears 10, 11, 16, 20, 21, 25 during reverse travel will be described with reference to FIG. 9 is a B view of the configuration diagram of FIG. In the reverse gear, the gear 21 meshes with the two gears, the gear 12 and the gear 25, and serves as a counter gear. Therefore, the gear 21 has no relation to the reverse gear ratio. Gear ratio R _R of the reverse gear stage gear,

It becomes. Further, the gear ratio R _F of the forward shift gear is:

It becomes. From formulas (4) and (5), the gear ratio used for forward and backward travel is almost the same.
R _F ≒ R _R formula (6)
If it becomes. As a result, the forward / reverse gear ratio can be made substantially the same, and the gear ratio can be changed.

Here, the relationship between the engine drive shaft 10, the MG drive shaft 19, the vehicle drive shaft 15, and the gears 10, 11, 16, 20, 21, 25 is summarized. The engine drive shaft 10, the MG drive shaft 19, and the vehicle drive shaft. 15, in order to secure the transmission path of the driving force, between the gears 10, 11, 16, 20, 21 and 25, between the engine drive shaft 10 and the vehicle drive shaft 15,
r1 + r6> r2 + r5 Formula (7)
Between the engine drive shaft 10 and the MG drive shaft 19,
r1 + r3 <r2 + r4 Formula (8)
Between the MG drive shaft 19 and the vehicle drive shaft 15,
r3 + r6 = r4 + r5 Formula (9)
It is necessary to satisfy the relationship.

In order to drive the vehicle with the engine 1 and the MG 3 in this embodiment, the expressions (3) and (6) to (9) must be satisfied.
r1> r2 Formula (10)
r3> r4 Formula (11)
r5> r6 Formula (12)
Satisfy this relationship. That is, the gear 11 and the gear 12 have a larger diameter in the gear 11, the gear 20 and the gear 21 have a larger diameter in the gear 21, and the gear 16 and the gear 25 have a larger diameter in the gear 16.

  Next, EV traveling in which the vehicle travels only with the driving force from MG3 will be described. First, LowEV traveling with a large torque will be described with reference to the block diagram of FIG. At this time, the clutch 22 connects the MG drive shaft 19 and the gear 20, and the clutch 26 connects the vehicle drive shaft 15 and the gear 16. As a result, the driving force of MG3 generated by the electric power stored in the battery 18 is transmitted to the vehicle drive shaft 15 by the low gear having a large torque increase, and the vehicle is driven. The clutch 13 is in a neutral position, and the gear 11 that always meshes with the gear 16 and rotates is separated from the engine drive shaft 10. The starting clutch 8 separates the engine shaft 7 and the engine input shaft 9.

  Next, HighEV traveling with a small torque will be described with reference to the block diagram of FIG. At this time, the clutch 22 connects the MG drive shaft 19 and the gear 21, and the clutch 26 connects the vehicle drive shaft 15 and the gear 16. As a result, the driving force of the MG 3 is transmitted to the vehicle drive shaft 15 by the high gear with a small increase in torque, and the vehicle is caused to travel. The clutch 13 is in a neutral position, and the gear 12 that always meshes with the gear 21 and rotates is separated from the engine drive shaft 10.

  In the state shown in FIGS. 10 and 11, the battery 18 can be charged during regeneration, and the vehicle drive shaft 15 can be moved from the vehicle drive shaft 15 by setting the clutch 13 to a neutral position during coasting such as during vehicle deceleration. The MG drive shaft 19 is rotated by the regenerative torque transmitted, the MG 3 generates electric power, and the battery 18 is charged. As a result, power is generated by the MG 3 separately from the engine drive shaft 10 and the battery 18 is charged, so that there is little friction loss due to the engine transmission 2 and the like, and efficient charging can be performed. Furthermore, since a Low gear and a High gear are provided, the rotation speed of the MG 3 can be selected. During regeneration, the arrows shown in FIGS. 10 and 11 are in the opposite direction.

  EV travel is used when the vehicle is started. When the vehicle is stopped, the MG drive shaft 19 and the gear 20 are connected in advance by the clutch 22 and the vehicle drive shaft 15 and the gear 16 are connected by the clutch 26 in preparation for the next start. And may be stopped in the Low EV traveling state.

  Next, charging (idle charging) of the battery 18 while the vehicle is stopped will be described with reference to FIG. When the vehicle 18 is stopped, the state of charge of the battery 18 is detected. When the battery 18 can be charged, that is, when the battery 18 is not fully charged, the engine drive shaft 10 and the gear 11 are connected by the clutch 13, and the clutch 22 The MG drive shaft 19 and the gear 20 are coupled by the rotation, the MG drive force shaft 19 is rotated by the drive force of the engine 1, and the MG 3 generates power. Then, the battery 18 is charged with the electric power generated by the MG 3 via the inverter 17. At this time, the clutch 26 is not connected to the gear 16, and the driving force of the engine 1 is not transmitted to the vehicle drive shaft 15.

  Next, a method of starting the engine 1 by the MG 3 when the S / G 6 is out of order or when the S / G 6 is not provided will be described with reference to the block diagram of FIG. In this case, the MG drive shaft 19 and the gear 20 are connected by the clutch 22, and the engine drive shaft 10 and the gear 11 are connected by the clutch 13. As a result, the driving force of the MG 3 is transmitted to the engine drive shaft 10, and the engine 1 is started via the engine transmission 2, the engine input shaft 9 and the engine shaft 7. As a result, even when the S / G 6 fails, the engine 1 can be started and the vehicle can run. Further, the vehicle can be driven without providing S / G6.

  Here, FIG. 14 shows a summary of the connected state of the starting clutch 8 and the clutches 13, 22, and 26 according to the traveling pattern of the present invention.

  FIG. 15 shows drive characteristics when this embodiment is used. According to FIG. 15, by providing the MG transmission 4 and assisting the driving force by the MG 3 in addition to the driving force of the engine 1, the vehicle driving force can be obtained even in the entire vehicle speed range, particularly when the vehicle speed is low. Can be increased, and the vehicle can travel more efficiently.

  The effect of 1st Embodiment of this invention is demonstrated.

  In this embodiment, since the increase (assist amount) of the driving force of the MG 3 can be changed by the MG transmission 4, the MG 3 can be operated with high efficiency, and the gear ratio can be reduced even when the amount of power stored in the battery 18 is small. By changing the above, it is possible to secure the assist torque by MG3. That is, the hybrid vehicle can be driven with high efficiency.

  Even when the vehicle is moving backward, the amount of assistance by the MG 3 can be changed, and the hybrid vehicle can be driven with high efficiency as in the case of moving forward.

  When a continuously variable transmission or automatic MT is used for the engine transmission 12, there is no need to provide a forward / reverse switching mechanism, and the hybrid vehicle can be reduced in size. Further, when an automatic transmission using a planetary gear is used, the layout of the planetary gear is restricted, but in this embodiment, the layout can be made free compared to the case where the planetary gear is used.

  During regenerative travel, the clutch 13 is neutral so that torque from the drive wheels 5 is not transmitted to the engine transmission 2 but only to the MG 3, so there is no friction loss in the engine transmission 2 and regeneration Efficiency can be increased. Furthermore, since the regenerative torque transmitted to the MG 3 by the MG transmission 4 can be changed, the regenerative efficiency can be further increased.

  Next, a second embodiment of the present invention will be described with reference to the block diagram of FIG. This embodiment is a hybrid vehicle in which a rear wheel drive vehicle and a powertrain system are vertically arranged. The configuration of this embodiment will be described with a focus on differences from the first embodiment.

  In this embodiment, the engine drive shaft 10 and the vehicle drive shaft 15 are disposed on the same axis, and the engine drive shaft 10 and the vehicle drive shaft 15 are directly connected and disconnected by the clutch 30. Further, a counter shaft 31 is provided, and the counter shaft 31 is provided in parallel with the engine drive shaft 10.

  The engine drive shaft 10 includes a gear 32 that is always connected to the engine drive shaft 10, and the gear 32 meshes with a gear 33 that is always connected to the counter shaft 31. Further, the engine drive shaft 10 is directly connected to and disconnected from the vehicle drive shaft 15 by the clutch 30 that is an inter-shaft clutch. At the time of connection, the driving force of the engine 1 is transmitted to the vehicle drive shaft 15 and the differential gear 23 to drive the vehicle.

  The counter shaft 31 includes a gear 34 that is third transmission means, and a clutch 35 that is a counter clutch that connects and disconnects the counter shaft 31 and the gear 34. The gear 34 meshes with a gear 36 disposed on the MG drive shaft 19 of MG3. As a result, the rotational direction of the engine drive shaft 12 is reversed and the driving force is transmitted.

  The MG drive shaft 19 includes a gear 36 and a gear 37 which are motor drive force transmission means, and a clutch 38 which connects and disconnects the MG drive shaft 19 and the gears 36 and 37. The gear 36 meshes with two gears, that is, a gear 34 and a gear 39 disposed on the vehicle drive shaft 15. As a result, the driving force of MG 3 is transmitted to the vehicle driving shaft 15, and the driving force of the engine driving shaft 12 is transmitted via the counter shaft 31. Further, the gear 37 meshes with a gear 40 disposed on the vehicle drive shaft 15. As a result, the driving force of MG 3 is transmitted to the vehicle drive shaft 15.

  The vehicle drive shaft 15 connects the gear 40 that is a drive transmission means that is always connected to the vehicle drive shaft 15, the gear 39 that is a drive transmission means that is connected to and disconnected from the vehicle drive shaft 15, and the vehicle drive shaft 15 and the gear 39. The clutch 41, which is the second vehicle drive shaft clutch to be disconnected, is provided. The clutch 30 is connected to and disconnected from the engine drive shaft 12. As a result, the driving force of the engine drive shaft 10 is transmitted to the vehicle drive shaft 15 by the clutch 30 when the vehicle moves forward, and is transmitted to the vehicle drive shaft 15 via the counter shaft 31 and the gears 34, 36, and 39 when moving backward. Further, the output of MG3 is transmitted to the vehicle drive shaft 15 via the gears 36 and 39 or the gears 37 and 40.

  The gear switching operation during traveling of the hybrid vehicle of the present invention will be described.

  When the vehicle travels only with the driving force of the engine 1, the engine drive shaft 10 and the vehicle drive shaft 15 are connected by the clutch 30 to travel the vehicle. At this time, the countershaft 31 and the gear 34 are separated by the clutch 35, and the clutch 38 is disposed at the neutral position.

  Next, a case where driving force assist by MG3 is performed when the vehicle moves forward will be described. First, in Low assist (Low gear) with a large assist torque by MG3, the clutch 38 connects the MG drive shaft 19 and the gear 36, and the clutch 39 connects the vehicle drive shaft 15 and the gear 39. As a result, the driving force from the engine 1 and the driving force from the MG 3 are transmitted to the vehicle driving shaft 15 to travel the vehicle.

  In the high assist (high gear) with a small assist torque by the MG 3, the MG drive shaft 19 and the gear 37 are connected by the clutch 38, and the vehicle drive shaft 15 and the gear 39 are disconnected by the clutch 41. As a result, the driving force from the engine 1 and the driving force from the MG 3 are transmitted to the vehicle driving shaft 15 to travel the vehicle.

  Note that the diameter of the gear 36 and the gear 37 is larger than the diameter of the gear 37, and the diameter of the gear 39 and the gear 40 is larger than the diameter of the gear 40. Thus, the gear 36 and the gear 39 constitute a Low gear, The gear 40 constitutes a high gear.

  Next, a description will be given of a case where the vehicle travels only by the driving force from the engine 1 when the vehicle moves backward. In this case, the engine drive shaft 10 and the vehicle drive shaft 15 are disconnected by the clutch 30, the counter shaft 31 and the gear 34 are connected by the clutch 35, and the vehicle drive shaft 15 and the gear 39 are connected by the clutch 41. As a result, the vehicle drive shaft 15 is rotated in the direction opposite to the forward direction without changing the rotation direction of the engine 1 to move the vehicle backward. The clutch 38 is in a neutral position.

  Next, a case where driving force assist by MG3 is performed when the vehicle moves forward will be described. First, in the low assist with a large assist amount by MG3, the clutch 38 connects the MG drive shaft 19 and the gear 38, transmits the driving force of the MG3 to the gear 38, and applies the gear 39 to the driving force from the engine 1, The vehicle is rotated by the driving force from MG3 and the vehicle is moved backward.

  In the high assist with a small assist amount by the MG 3, the MG drive shaft 19 and the gear 40 are connected by the clutch 38, and the driving force from the MG 3 is transmitted to the vehicle drive shaft 15 through the gear 40. That is, the gear 39 is rotated by the driving force of the engine 1, the gear 40 is rotated by the driving force of the MG 3, the driving force is transmitted to the vehicle drive shaft 15 by the two gears 39, 40, and the vehicle is moved backward.

  Next, EV traveling in which the vehicle travels only with the driving force from MG3 will be described. First, in low EV traveling with a large torque, the engine drive shaft 10 and the vehicle drive shaft 15 are disconnected by the clutch 30, the counter shaft 31 and the gear 34 are disconnected by the clutch 35, the MG drive shaft 19 and the gear 36 are connected by the clutch 38, The vehicle drive shaft 15 and the gear 39 are connected by the clutch 39. Thus, the vehicle is driven by the driving force of MG3.

  In high EV traveling with small torque, the engine drive shaft 10 and the vehicle drive shaft 15 are disconnected by the clutch 30, and the MG drive shaft 19 and the gear 37 are connected by the clutch 38. Thus, the vehicle is driven by the driving force of MG3.

  Next, charging (idle charging) of the battery 18 while the vehicle is stopped will be described with reference to FIG. When the vehicle 18 is stopped, the state of charge of the battery 18 is detected, and when the battery 18 can be charged, that is, when the battery 18 is not fully charged, the counter shaft 31 and the gear 34 are connected by the clutch 35, The MG drive shaft 19 and the gear 36 are connected, the MG drive force shaft 19 is rotated by the drive force of the engine 1, and power is generated by MG3. Then, the battery 18 is charged with the electric power generated by the MG 3 via the inverter 17. At this time, the engine drive shaft 10 and the vehicle drive shaft 15 are separated by the clutch 30, and the clutch 41 is in a neutral position, and the driving force of the engine 1 is not transmitted to the vehicle drive shaft 15.

  When S / G6 is out of order or S / G6 is not provided, it is the same as the connected state for charging battery 18 while the vehicle is stopped, and the engine can be started by the driving force of MG3.

  Here, FIG. 17 shows a summary of the connected state of the starting clutch 8 and the clutches 30, 35, 38, and 41 according to the traveling pattern of the present invention.

  The effect of 2nd Embodiment of this invention is demonstrated.

  In this embodiment as well, as in the first embodiment, the increase (assist amount) of the driving force of MG3 can be changed by MG transmission 4, so that MG3 can be operated with high efficiency, and the amount of power stored in battery 18 can be increased. Even when there is little, the assist torque by MG3 can be ensured by changing the gear ratio. That is, the hybrid vehicle can be driven with high efficiency.

  Even when the vehicle is moving backward, the amount of assistance by the MG 3 can be changed, and the hybrid vehicle can be driven with high efficiency as in the case of moving forward.

  When a continuously variable transmission or automatic MT is used for the engine transmission 12, there is no need to provide a forward / reverse switching mechanism, and the hybrid vehicle can be reduced in size. Further, when an automatic transmission using a planetary gear is used, the layout of the planetary gear is restricted, but in this embodiment, the layout can be made free compared to the case where the planetary gear is used.

  During regenerative travel, the engine drive shaft 10 and the vehicle drive shaft 15 are separated by the clutch 30, and the gear 34 and the counter shaft 31 are separated by the clutch 35, so that torque from the drive wheels 5 is not transmitted to the engine transmission 2, Since it is transmitted only to MG3, there is no friction loss in engine transmission 2, and the regeneration efficiency can be increased. Furthermore, since the regenerative torque transmitted to the MG 3 by the MG transmission 4 can be changed, the regenerative efficiency can be further increased.

  It goes without saying that the present invention is not limited to the above-described embodiments, and includes various modifications and improvements that can be made within the scope of the technical idea.

  The present invention can be used for a hybrid vehicle that is driven by an engine and an electric motor.

1 is a block diagram illustrating a configuration of a hybrid vehicle according to a first embodiment of the present invention. It is a figure which shows transmission of the driving force in case there is no assistance by MG3 at the time of advance of the hybrid vehicle of 1st Embodiment of this invention. It is a figure which shows transmission of the driving force in the case of Low assist by MG3 at the time of advance of the hybrid vehicle of 1st Embodiment of this invention. It is a figure which shows transmission of the driving force in the case of the High assist by MG3 at the time of advance of the hybrid vehicle of 1st Embodiment of this invention. It is the figure which looked at the gearwheel of FIG. 1 from arrow A. It is a figure which shows transmission of the driving force in case there is no assistance by MG3 at the time of reverse drive of the hybrid vehicle of 1st Embodiment of this invention. It is a figure which shows transmission of the driving force in the case of Low assist by MG3 at the time of reverse drive of the hybrid vehicle of 1st Embodiment of this invention. It is a figure which shows transmission of the driving force in the case of the High assist by MG3 at the time of reverse drive of the hybrid vehicle of 1st Embodiment of this invention. It is the figure which looked at the gearwheel of FIG. It is a figure which shows transmission of the driving force in the case of LowEV driving | running | working by MG3 of the hybrid vehicle of 1st Embodiment of this invention. It is a figure which shows transmission of the driving force in the case of LowEV driving | running | working by MG3 of the hybrid vehicle of 1st Embodiment of this invention. It is a figure which shows transmission of the driving force at the time of idle charge of this invention. It is a figure which shows transmission of the driving force at the time of starting the engine 1 by MG3 of this invention. It is the table | surface which put together the power switching of 1st Embodiment of this invention. It is a graph which shows the driving force characteristic of the hybrid vehicle of 1st Embodiment of this invention. It is a block diagram which shows the structure of the hybrid vehicle of 2nd Embodiment of this invention. It is the table | surface which put together the power switching of 2nd Embodiment of this invention.

Explanation of symbols

1 Engine 2 Engine transmission 3 Motor (MG)
4 MG transmission 10 engine drive shaft 11 gear (forward transmission means)
12 gear (reverse transmission means)
13 Clutch (Engine drive shaft clutch)
15 vehicle drive shaft 16 gear (first transmission means)
19 MG drive shaft (motor drive shaft)
20 gear (motor driving force transmission means)
21 Gear (Motor driving force transmission means)
22 Clutch (motor drive shaft clutch)
25 Gear (second transmission means)
30 Clutch (shaft clutch)
31 counter shaft 34 gear (third transmission means)
35 counter clutch 36 gear (drive transmission means)
37 Gear (drive transmission means)
41 Clutch (second vehicle drive shaft clutch)

Claims (7)

An engine that provides driving force to the vehicle;
An engine drive shaft for extracting the drive force of the engine;
A motor that gives driving force to the vehicle by the electric power stored in the power storage device;
A motor drive shaft for extracting the drive force of the motor;
In the hybrid vehicle comprising the engine drive shaft and a vehicle drive shaft that transmits the driving force transmitted from the motor drive shaft to the wheels,
A motor transmission having a stepped gear ratio for transmitting the driving force of the motor to the vehicle driving shaft and capable of interrupting driving force transmission between the motor driving shaft and the vehicle driving shaft;
At least one forward transmission means for transmitting the rotation of the engine drive shaft to the engine drive shaft when the vehicle is advanced;
Reverse transmission means for transmitting the rotation of the engine drive shaft when moving backward,
Providing the engine drive shaft and an engine drive shaft clutch capable of selectively connecting, separating, or maintaining a neutral position that is not connected to any of the transmission means;
At least one first transmission means connected to the forward transmission means for transmitting rotation of the engine drive shaft and the motor drive shaft to the vehicle drive shaft;
Second transmission means connected to the reverse transmission means via the motor transmission to transmit the rotation of the engine drive shaft and the motor drive shaft;
A hybrid vehicle, comprising: a first vehicle drive shaft clutch that connects and separates the first transmission means and the vehicle drive shaft. The motor transmission is installed on the motor drive shaft, and a plurality of motor drive force transmission means for transmitting rotation of the motor drive shaft;
A motor drive shaft clutch capable of selectively connecting, separating, or maintaining a neutral position that is not connected to any of the motor drive force transmission means, and the motor drive shaft and the plurality of motor drive force transmission means;
One of the motor driving force transmission means is always connected to the second transmission means and the reverse transmission means,
2. The hybrid vehicle according to claim 1, wherein the other motor driving force transmission means is always connected only to the first transmission means. The torque change amount of the engine driving force during forward and reverse movement of the vehicle between the engine drive shaft and the vehicle drive shaft is substantially the same,
The increase in torque of the driving force of the motor by the motor transmission is always connected to the second transmission means and the reverse transmission means rather than the motor driving force transmission means always connected only to the first transmission means. The hybrid vehicle according to claim 2, wherein a torque increase is smaller in the driving force transmission of the motor by the driving force transmission means.   The vehicle drive shaft clutch generates power with the motor by the driving force of the engine and charges the power to the charging device, and only when the engine is started, the first transmission means, the vehicle drive shaft, The hybrid vehicle according to any one of claims 1 to 3, wherein the vehicle is separated.   The hybrid vehicle according to any one of claims 1 to 4, wherein the engine drive shaft clutch is set to a neutral position when the vehicle is driven only by the driving force from the motor. An engine that provides driving force to the vehicle;
An engine drive shaft for extracting the drive force of the engine;
A motor that gives driving force to the vehicle by the electric power stored in the power storage device;
A motor drive shaft for extracting the drive force of the motor;
In the hybrid vehicle comprising the engine drive shaft and a vehicle drive shaft that transmits the driving force transmitted from the motor drive shaft to the wheels,
A motor transmission having a stepped gear ratio for transmitting the driving force of the motor to the vehicle drive shaft, and capable of interrupting transmission of the driving force between the motor drive shaft and the vehicle drive shaft;
At least one forward transmission means for transmitting the rotation of the engine drive shaft to the engine drive shaft when the vehicle is advanced;
A counter shaft connected to the engine drive shaft and reversing the rotation direction of the engine drive shaft;
A third transmission means connected to the motor transmission for transmitting rotation of the counter shaft;
A counter clutch for connecting and separating the counter shaft and the third transmission means;
An inter-shaft clutch for connecting and separating the engine drive shaft and the vehicle drive shaft;
A plurality of driving force transmission means connected to the motor transmission and transmitting the rotation of the motor transmission to the vehicle drive shaft;
A second vehicle drive shaft clutch for connecting and separating the plurality of transmission means and the vehicle drive shaft;
The hybrid vehicle, wherein the third transmission means transmits the rotation of the engine drive shaft from the third transmission means to one of the plurality of transmission means via the motor transmission.   2. The motor driving shaft and the vehicle driving shaft are connected by the motor driving force transmission means and the first transmission means with the largest increase in torque of the motor driving force when the vehicle is stopped. The hybrid vehicle according to any one of 6 to 6.

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