WO2015129692A1 - 4輪駆動車のクラッチ制御装置 - Google Patents
4輪駆動車のクラッチ制御装置 Download PDFInfo
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- WO2015129692A1 WO2015129692A1 PCT/JP2015/055247 JP2015055247W WO2015129692A1 WO 2015129692 A1 WO2015129692 A1 WO 2015129692A1 JP 2015055247 W JP2015055247 W JP 2015055247W WO 2015129692 A1 WO2015129692 A1 WO 2015129692A1
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- wheel drive
- wheel
- clutch
- drive mode
- vehicle
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- B60K23/08—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles
- B60K23/0808—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles for varying torque distribution between driven axles, e.g. by transfer clutch
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Definitions
- the present invention relates to a clutch control device for a four-wheel drive vehicle having a meshing clutch and a friction clutch in a driving force transmission system to auxiliary driving wheels.
- a front-wheel drive-based four-wheel drive vehicle having a meshing clutch and a friction clutch in a driving force transmission system to the rear wheels is known (for example, see Patent Document 1).
- the friction clutch when switching from the two-wheel drive mode to the four-wheel drive mode, the friction clutch is fastened, the drive source side of the meshing clutch is synchronized with the rear wheel side, and then the meshing clutch is fastened. Further, when switching from the four-wheel drive mode to the two-wheel drive mode, the mesh clutch is released after the friction clutch is released.
- An object of the present invention is to provide a clutch control device for a four-wheel drive vehicle.
- the present invention provides: As a clutch interposed between the drive source and the sub drive wheel, among the drive force transmission system to the sub drive wheel, the drive branch side transmission system path and the sub drive wheel side transmission system path across the differential Each has a meshing clutch and a friction clutch arranged separately, A clutch control unit that can be switched between a two-wheel drive mode in which only the main drive wheel is driven by controlling engagement and release of both clutches, and a four-wheel drive mode in which the main drive wheel and the sub drive wheel are driven,
- the two-wheel drive mode includes a disconnect two-wheel drive mode in which both clutches are released and a standby two-wheel drive mode in which the mesh clutch is engaged and the friction clutch is released, and the disconnect two-wheel drive mode
- the clutch control device for the four-wheel drive vehicle is switched to the standby two-wheel drive mode.
- the clutch control device for a four-wheel drive vehicle when the two-wheel drive mode is set to the standby two-wheel drive mode in which only the meshing clutch is engaged by setting the disconnect two-wheel drive mode in which both clutches are released.
- the two-wheel drive mode which is more advantageous for fuel consumption, can be achieved.
- the transition time is shortened when shifting to the four-wheel drive mode than when shifting from the disconnect two-wheel drive mode, It becomes possible to improve the stability of the driving force transmission state to the road surface.
- FIG. 6 is a map diagram showing a drive mode switching map according to a vehicle speed and an accelerator opening used in clutch control when “auto mode” in the first embodiment is selected.
- FIG. 3 is a drive mode transition diagram showing switching transition of drive modes (disconnect two-wheel drive mode, standby two-wheel drive mode, and connect four-wheel drive mode) by clutch control by the clutch control device of the first embodiment.
- FIG. 4 is a flowchart showing a flow of a clutch control process in an “auto mode” executed in the 4WD control unit of the clutch control device for a four-wheel drive vehicle according to the first embodiment.
- 3 is a time chart showing an example of operation during non-hill climbing by the clutch control device for a four-wheel drive vehicle of the first embodiment.
- 3 is a time chart showing an operation example during climbing by the clutch control device of the four-wheel drive vehicle of the first embodiment.
- FIG. 10 is a basic map diagram showing a drive mode switching map according to a vehicle speed and an accelerator opening used in clutch control when “auto mode” of the second embodiment is selected.
- FIG. 10 is a basic map diagram showing a drive mode switching map according to a vehicle speed and an accelerator opening used in clutch control when “auto mode” of the second embodiment is selected.
- FIG. 6 is a drive system configuration diagram showing a drive system configuration of a rear wheel drive base four-wheel drive vehicle to which a clutch control device of a third embodiment is applied.
- FIG. 10 is a map diagram showing another example of a drive mode switching map according to a vehicle speed and an accelerator opening used in clutch control when “auto mode” is selected.
- FIG. 1 shows a drive system configuration of a front-wheel drive-based four-wheel drive vehicle to which the clutch control device of the first embodiment is applied.
- the drive system configuration of the four-wheel drive vehicle will be described with reference to FIG.
- the front wheel drive system of the four-wheel drive vehicle includes a horizontally mounted engine 1 (drive source), a transmission 2, a front differential 3, a left front wheel drive shaft 4, and a right front wheel drive shaft 5. And a left front wheel 6 (main drive wheel) and a right front wheel 7 (main drive wheel). That is, the driving force that has passed through the horizontally mounted engine 1 and the transmission 2 is transmitted to the left and right front wheel drive shafts 4 and 5 via the front differential 3, and always drives the left and right front wheels 6 and 7 while allowing the differential.
- a horizontally mounted engine 1 drive source
- a transmission 2 a transmission 2
- a front differential 3 a left front wheel drive shaft 4
- a right front wheel 7 main drive wheel
- the rear wheel drive system of the four-wheel drive vehicle includes a dog clutch 8 (meshing clutch), a bevel gear 9, an output pinion 10, a rear wheel output shaft 11, and a propeller shaft 12. ing.
- 21 is a universal joint.
- the rotation of the propeller shaft 12 and the like between the dog clutch 8 and the electric coupling 16 is stopped, so that friction loss, oil agitation loss, etc. are suppressed, and fuel efficiency is improved. Is achieved.
- the dog clutch 8 is provided at a driving branch position from the left and right front wheels 6, 7 to the left and right rear wheels 19, 20, and a driving force transmission system to the left and right rear wheels 19, 20 is provided to the left and right front wheels 6, 7 by releasing the clutch. This is a meshing clutch that is disconnected from the driving force transmission system.
- the dog clutch 8 is disposed upstream of the bevel gear 9 and the output pinion 10 as a transfer mechanism provided at the drive branch position to the left and right rear wheels 19 and 20. 2 is connected to the differential case 3a of the front differential 3, and the output side engaging member 8b of the dog clutch 8 is connected to the bevel gear 9.
- the dog clutch 8, the bevel gear 9, the output pinion 10, and a part of the rear wheel output shaft 11 are built in a transfer case 23 fixed at a position adjacent to the front differential housing 22.
- the dog clutch 8 for example, one of a pair of meshing members 8a and 8b (see FIG. 2) is a fixed member, the other is a movable member, and a spring that biases in the fastening direction is provided between the two members.
- a screw groove that can be fitted to the solenoid pin on the outer periphery is used.
- the electric control coupling 16 is a friction clutch that is provided downstream of the dog clutch 8 and distributes a part of the driving force from the horizontally placed engine 1 to the left and right rear wheels 19 and 20 in accordance with the clutch engagement capacity.
- This electric control coupling 16 is disposed at the position of the left rear wheel drive shaft 17 from the bevel gear 9 and the output pinion 10 as a transfer mechanism to the left rear wheel 19 via the propeller shaft 12 and the rear differential 15.
- the input clutch plate of the electric control coupling 16 is connected to the left side gear of the rear differential 15, and the output clutch plate is connected to the left rear wheel drive shaft 17.
- the electric control coupling 16 is built in a coupling case 25 fixed at a position adjacent to the rear differential housing 24.
- the electric control coupling 16 for example, a multi-plate friction clutch in which a plurality of input and output plates are alternately arranged, a fixed cam piston (not shown) and a movable cam piston (not shown) having opposing cam surfaces are provided. ) And a cam member (not shown) interposed between opposing cam surfaces.
- the fastening of the electric control coupling 16 is performed by rotating a movable cam piston (not shown) in a predetermined fastening direction by an electric motor (electric control coupling actuator 49 shown in FIG. 2).
- a movable cam piston (not shown) strokes in the clutch fastening direction according to the rotation angle by the cam action that enlarges the piston interval, and the friction fastening force of the multi-plate friction clutch is increased.
- the electric coupling 16 is released by rotating a movable cam piston (not shown) by an electric motor (electric coupling actuator 49 shown in FIG. 2) in the direction opposite to the fastening direction.
- a movable cam piston (not shown) strokes in the clutch release direction according to the rotation angle by a cam action that reduces the piston interval, and reduces the frictional engagement force of the multi-plate friction clutch.
- FIG. 2 shows a control system configuration of a front-wheel drive-based four-wheel drive vehicle to which the clutch control device of the first embodiment is applied.
- the control system configuration of the four-wheel drive vehicle will be described with reference to FIG.
- the control system of the four-wheel drive vehicle includes an engine control module 31, a transmission control module 32, an ABS actuator control unit 33, and a 4WD control unit 34, as shown in FIG. Note that each control module and each control unit 31 to 34 is configured by an arithmetic processing unit such as a so-called computer.
- the engine control module 31 is a control device for the horizontal engine 1 and receives detection signals from an engine speed sensor 35, an accelerator opening sensor 36, and the like as a vehicle state detection device. From the engine control module 31, engine speed information and accelerator opening information (ACC information) are input to the 4WD control unit 34 via the CAN communication line 37.
- ACC information accelerator opening information
- the transmission control module 32 is a control device of the transmission 2 and receives detection signals from a transmission input rotational speed sensor 38, a transmission output rotational speed sensor 39, and the like as a vehicle state detection device.
- Gear ratio information (gear ratio information) is input from the transmission control module 32 to the 4WD control unit 34 via the CAN communication line 37.
- the ABS actuator control unit 33 is a control device of an ABS actuator that controls the brake fluid pressure of each wheel, and includes a yaw rate sensor 40, a lateral G sensor 41, a front / rear G sensor 42, a wheel speed sensor 43, Detection signals from 44, 45, 46, etc. are input. From the ABS actuator control unit 33, yaw rate information, lateral G information, front and rear G information, and wheel speed information of each wheel are input to the 4WD control unit 34 via the CAN communication line 37. In addition to the above information, steering angle information is input from the steering angle sensor 47 to the 4WD control unit 34 via the CAN communication line 37.
- the 4WD control unit (clutch control unit) 34 is an engagement / release control device for the dog clutch 8 and the electric coupling 16, and performs arithmetic processing based on various input information from each sensor as a vehicle state detection device. Then, a drive control command is output to the dog clutch actuator 48 (solenoid) and the electric coupling actuator 49 (electric motor).
- a drive mode selection switch 50 As input information sources other than the CAN communication line 37, a drive mode selection switch 50, a brake switch 51 for detecting presence or absence of a brake operation, a ring gear rotation speed sensor 52, a dog clutch stroke sensor 53, a motor rotation angle sensor 54, A shift position switch 55 is included.
- the drive mode selection switch 50 is a switch for the driver to switch between “2WD mode”, “lock mode”, and “auto mode”, which are switching modes between the 2WD state and the 4WD state.
- “2WD mode” the front wheel drive 2WD state in which the dog clutch 8 and the electric coupling 16 are released is maintained.
- the “lock mode” is selected, the complete 4WD state in which the dog clutch 8 and the electric control coupling 16 are engaged is maintained.
- “auto mode” the engagement / release of the dog clutch 8 and the electric coupling 16 is automatically controlled according to the vehicle state (vehicle speed VSP, accelerator opening ACC), and the two-drive state is automatically established. And 4WD state.
- the vehicle speed VSP is basically calculated from the wheel speeds of the left and right rear wheels 19 and 20 as auxiliary drive wheels.
- the ring gear rotation speed sensor 52 is a sensor for acquiring the output rotation speed information of the dog clutch 8, and by considering the rear side gear ratio and the front side gear ratio in the calculation for the ring gear rotation speed detection value, The output rotational speed of the dog clutch 8 is calculated. Note that the input rotation speed information of the dog clutch 8 is acquired by the average value of the left and right front wheel speeds.
- FIG. 4 shows switching transitions of drive modes (disconnect 2-wheel drive mode, standby 2-wheel drive mode, connect 4-wheel drive mode).
- the disconnect two-wheel drive mode is a mode of 2WD running (Disconnect) in which both the dog clutch 8 and the electric control coupling 16 are released, as shown in a frame C in FIG.
- the front wheel drive 2WD running (Disconnect) is basically maintained by transmitting the drive force only to the left and right front wheels 6 and 7.
- the drive slip amount or drive slip ratio
- the differential rotation control is performed to distribute the torque and suppress the drive slip.
- the electric coupling 16 is frictionally engaged, and then, when the rotation synchronization state is determined, the dog clutch 8 is engaged and engaged, and the driving force is distributed to the left and right rear wheels 19 and 20.
- the distribution of driving force to the left and right rear wheels 19 and 20 is adjusted by controlling the transmission torque of the electric control coupling 16.
- the standby two-wheel drive mode is a 2WD travel (Stand-by) mode in which the dog clutch 8 is engaged and the electric coupling 16 is released, as shown in a frame D in FIG. .
- the front wheel drive 2WD running (Stand-by) is basically maintained by transmitting the driving force only to the left and right front wheels 6 and 7.
- the drive slip amount (or drive slip ratio) exceeds a threshold value, a drive force is applied to the left and right rear wheels 19 and 20.
- Differential rotation control that distributes and suppresses drive slip is performed. In the differential rotation control in the standby two-wheel drive mode, only the frictional engagement of the electric coupling 16 is performed because the dog clutch 8 is engaged and engaged in advance. Therefore, the driving force can be distributed to the left and right rear wheels 19, 20 with good response.
- the connect four-wheel drive mode is a mode of 4WD running (Connect) in which the dog clutch 8 and the electric coupling 16 are both fastened, as shown in a frame E in FIG.
- this connected four-wheel drive mode basically, driving force distribution control is performed for the right and left front wheels 6 and 7 and the left and right rear wheels 19 and 20 so as to optimize driving force distribution according to the road surface condition.
- the fastening capacity of the electric control coupling 16 is increased. Control is performed to reduce the tight corner braking phenomenon.
- the switching transition speed (arrow F in FIG. 4) of 2WD traveling (Disconnect) ⁇ 2WD traveling (Stand-by) is increased, and the switching transition speed of 2WD traveling (Stand-by) ⁇ 2WD traveling (Disconnect) (FIG. 4).
- Arrow G) is delayed.
- the switching transition speed of 2WD traveling (Disconnect) ⁇ 4WD traveling (Connect) is increased, and the switching transition speed of 4WD traveling (Connect) ⁇ 2WD traveling (Disconnect) (arrow I in FIG. 4).
- the switching transition speed of 2WD traveling (Stand-by) ⁇ 4WD traveling (Connect) (arrow J in FIG. 4) and the switching transition speed of 4WD traveling (Connect) ⁇ 2WD traveling (Stand-by) (FIG. 4).
- the arrow K) shows the same high speed.
- FIG. 5 shows a flow of clutch control processing in the “auto mode” executed by the 4WD control unit 34.
- the switching between the disconnect two-wheel drive mode (2WD travel (Disconnect)), the standby two-wheel drive mode (2WD travel (Stand-by)), and the differential rotation control (4WD travel (Connect)) described above is detected by uphill detection. And based on the occurrence of differential rotation.
- a configuration for performing uphill detection will be described.
- This uphill detection can be performed, for example, by providing an inclination sensor that detects the inclination of the vehicle in the front-rear direction, but in the first embodiment, it is performed by the output of an existing in-vehicle sensor.
- An uphill detection unit (uphill sensor) 100 shown in FIG. 2 detects an uphill during running, and this uphill judgment during running is performed by executing one or more of the following processes a to c. . a. Based on the relationship between the vehicle speed, the vehicle longitudinal acceleration and the engine torque, it is determined that the vehicle is climbing when the actual vehicle speed is lower than a vehicle speed equivalent to a flat road obtained from the acceleration based on the engine torque by a predetermined value or more. b. Based on the relationship between the vehicle driving force and the shift speed and the vehicle speed, it is determined that the vehicle is going uphill when the actual vehicle speed is lower than a predetermined value with respect to the vehicle speed during flat road traveling based on the driving force and the shift speed. c.
- this uphill detection part 100 can also utilize the structure which detects an uphill road in the existing hill assist brake control apparatus.
- step S101 it is determined whether or not the climbing flag is currently set (uphill detection), and the process proceeds to step S102 with the non-climbing flag set, and to step S109 when the climbing flag is set.
- step S102 which proceeds when the non-hill climbing flag is set, the disconnect two-wheel drive mode is set based on the switching map of FIG. 3, and the subsequent step S103 and subsequent steps are executed to perform differential rotation control in the disconnect two-wheel drive mode. . That is, it is determined whether or not the differential rotation ⁇ V between the left and right front wheels 6 and 7 and the left and right rear wheels 19 and 20 exceeds the slip determination threshold value ⁇ Vlim (whether or not drive wheel slip has occurred).
- the synchronous processing in steps S104 to S107 is performed to set the connected four-wheel drive mode, and then the differential rotation control is performed. If no differential rotation ⁇ V exceeding the slip determination threshold ⁇ Vlim occurs in step S103, one process is terminated and the process returns to step S101.
- step S104 an engagement command output of the electric control coupling 16 is performed. Thereby, the driving force of the left and right rear wheels 19, 20 is transmitted to the bevel gear 9, and the rotation of the output side meshing member 8b of the dog clutch 8 is increased.
- step S105 a differential rotation ⁇ N between the input side meshing member 8a and the output side meshing member 8b of the dog clutch 8 is calculated, and in the next step S106, the differential rotation ⁇ N is in a synchronized state equal to or less than the synchronization determination threshold value ⁇ . It is determined whether or not.
- step S107 the dog clutch 8 will be fastened, it will be in a connected 4 wheel drive state, and it will progress to step S108.
- step S108 differential rotation control by fastening the electric control coupling 16 is executed.
- the differential rotation control is terminated when the differential rotation between the left and right front wheels 6 and 7 and the left and right rear wheels 19 and 20 is settled, and the process returns to step S101 to return to the two-wheel drive mode corresponding to the set state of the uphill flag.
- step S109 the process proceeds to the standby two-wheel drive mode in step S109, which proceeds when the climbing flag is set (when climbing is detected).
- This standby two-wheel drive mode is a two-wheel drive mode in which the dog clutch 8 is engaged as described above.
- the dog clutch 8 is synchronized and then engaged in the same manner as the processing in steps S104 to S107 during the differential rotation control from the disconnect two-wheel drive mode described above. In this case, the electric coupling 16 is released after the dog clutch 8 is engaged.
- the dog clutch 8 is fastened without synchronous operation when the vehicle stops or when climbing is detected immediately before the vehicle stops. At this time, if the engagement is not completed due to the tooth contact in the dog clutch 8, the engagement is performed by the biasing force of the spring when the differential rotation occurs at the start.
- step S110 it is determined whether or not a differential rotation ⁇ V (driving wheel slip) exceeding the slip determination threshold ⁇ Vlim has occurred between the left and right front wheels 6, 7 and the left and right rear wheels 19, 20.
- the process proceeds to step S108, and the driving slip is suppressed by the driving force distribution control to the left and right rear wheels 19, 20 by the engagement control of the electric control coupling 16.
- Perform differential rotation control In this case, since the dog clutch 8 is meshed and fastened in advance, it is only necessary to perform frictional fastening of the electric control coupling 16, and the driving force can be distributed to the left and right rear wheels 19 and 20 with good response. If no differential rotation ⁇ V (driving wheel slip) exceeding the slip determination threshold ⁇ Vlim occurs in step S110, one process is terminated and the process from the start is repeated.
- FIG. 6 shows an example of an operation during non-hill climbing, and shows an operation when drive wheel slip occurs on the left and right front wheels 6 and 7 when the accelerator pedal is stepped on at the time t1 to start.
- the engagement command output TETS for increasing the transmission torque of the electric coupling 16 is performed, the input / output side meshing members 8a and 8b of the dog clutch 8 are synchronized (S104 to S106), and then the dog clutch 8 is engaged. Control output is performed (S107).
- the vehicle enters the connected four-wheel drive mode, and thereafter, differential rotation control for controlling the transmission torque of the electric control coupling 16 is executed in accordance with the differential rotation ⁇ V (S108). Therefore, the fastening command output TETS to the electric control coupling 16 is increased according to the increase in the differential rotation ⁇ V.
- the driving force is distributed to the left and right rear wheels 19 and 20 by setting the connected four-wheel drive mode. As a result, the slip of the left and right front wheels 6 and 7 decreases, and after t3, the differential rotation ⁇ V decreases and the vehicle can be started smoothly.
- the engagement command output TETS to the electric control coupling 16 is decreased, and the differential rotation ⁇ V is decreased below a predetermined value (for example, the slip determination threshold ⁇ Vlim).
- the differential rotation control is terminated and the disconnect two-wheel drive mode is restored.
- the fastening command output TETS for the electric control coupling 16 is stopped and released, and the load from the left and right rear wheels 19, 20 on the propeller shaft 12 is eliminated.
- the dog clutch 8 is disengaged at time t5.
- the uphill flag is set, and the disconnect two-wheel drive mode is switched to the standby two-wheel drive mode (S101 ⁇ S109). That is, similar to the operation example shown in FIG. 6, the electric coupling 16 is engaged and the dog clutch 8 is synchronized, and then the dog clutch 8 is engaged (t12). 16 is released.
- the standby two-wheel drive mode is maintained.
- the wheel loads on the left and right front wheels 6, 7 which are the main drive wheels on the uphill road are reduced, and slip occurs simultaneously with the start.
- the differential rotation control is performed as the connected four-wheel drive mode (S110 ⁇ S108) in accordance with the front / rear differential rotation ⁇ V, since switching from the standby two-wheel drive mode is performed, only the electric coupling 16 is fastened. To switch to connected 4-wheel drive mode. Therefore, it is possible to suppress the slip of the left and right front wheels 6 and 7 immediately and to start stably.
- the clutch control device for a four-wheel drive vehicle of the first embodiment is Of the left and right front wheels 6, 7 and the left and right rear wheels 19, 20, one is a main drive wheel connected to the engine 1 as a drive source, and the other is a sub drive wheel connected to the drive source via a clutch, Of the driving force transmission systems to the left and right rear wheels 19 and 20 as the auxiliary driving wheels, the clutch is divided into a transmission system path on the driving branch side and a transmission system path on the auxiliary driving wheel side with the rear differential 15 interposed therebetween.
- a dog clutch 8 as a meshing clutch and an electric coupling 16 as a friction clutch The dog clutch 8 disconnects the driving force transmission system to the left and right rear wheels 19 and 20 by releasing the clutch from the driving force transmission system to the left and right front wheels 6 and 7, and the electric coupling 16 has a clutch fastening capacity. Accordingly, in a four-wheel drive vehicle that distributes a part of the driving force from the engine 1 to the left and right rear wheels 19 and 20, Engagement / release control of the dog clutch 8 and engagement / release of the electric coupling 16 according to the vehicle state detected by each sensor (35, 36, 38 to 47, 50 to 55) as a vehicle state detection device.
- a 4WD control unit 34 is provided as a unit,
- the vehicle state detection device includes an uphill detecting unit 100 as an uphill sensor that detects an uphill,
- the 4WD control unit 34 includes, as the two-wheel drive mode, a disconnect two-wheel drive mode in which the dog clutch 8 and the electric coupling 16 are released, and a standby two-wheel drive in which the dog clutch 8 is engaged and the electric coupling 16 is released.
- the standby two-wheel drive mode when an uphill is detected in the disconnect two-wheel drive mode, the standby two-wheel drive mode is switched. Accordingly, when the disc-connect two-wheel drive mode is controlled as the two-wheel drive mode, the drive system between the bevel gear 9 and the ring gear 14 of the rear wheel drive system is completely stopped, so that friction loss occurs. do not do. Therefore, fuel consumption deterioration can be suppressed, and the fuel consumption when used in the two-wheel drive mode while being a four-wheel drive vehicle can be made the same as that of a two-wheel drive vehicle.
- the standby two-wheel drive mode in which the dog clutch 8 is engaged is set when the uphill is detected. For this reason, the transition from the two-wheel drive mode to the four-wheel drive mode can be performed only by fastening the electric control coupling 16. Therefore, there is no need for the synchronous operation of the dog clutch 8 at the time of switching from the disconnected two-wheel drive mode to the four-wheel drive mode, and the transition from the two-wheel drive mode to the four-wheel drive mode is made in a short time. Is possible. Therefore, when controlling to the disconnected two-wheel drive mode, on an uphill road where drive wheel slip is likely to occur, switching to the four-wheel drive mode can be achieved in a short time by switching to the standby two-wheel drive mode, and driving stability Can be improved.
- the clutch control device for the four-wheel drive vehicle of the first embodiment is The 4WD control unit 34 as the clutch control unit controls the two-wheel drive mode when no differential rotation occurs between the main drive wheel and the sub drive wheel, and when the differential rotation occurs, Switching to the drive mode, and in the two-wheel drive mode, automatic switching control for controlling to the disconnect two-wheel drive mode is performed. Therefore, in the automatic switching control, the fuel economy can be improved as in 1) above by setting the disconnect two-wheel drive mode during the two-wheel drive mode.
- the two-wheel drive mode is switched to the disconnect two-wheel drive mode while switching to the standby two-wheel drive mode when the uphill is detected as described in 1) above. Switching to the drive mode can be performed in a short time. Therefore, in performing automatic switching control between the two-wheel drive mode and the four-wheel drive mode, it is possible to achieve both improvement in fuel efficiency and improvement in traveling performance when climbing.
- the clutch control device for a four-wheel drive vehicle of the first embodiment is The main driving wheels are the left and right front wheels 6, 7.
- the main driving wheels are the left and right front wheels 6 and 7
- the drive wheel slip in the two-wheel drive mode is more likely to occur during climbing than when the left and right rear wheels 19 and 20 are the main drive wheels, and the four-wheel drive mode.
- the driving stability improvement effect is remarkable.
- the clutch control device for the four-wheel drive vehicle of the first embodiment is
- the uphill detection unit 100 is characterized in that the uphill is determined based on detection of existing sensors such as vehicle speed, acceleration, and engine torque. Therefore, it is possible to reduce the manufacturing cost as compared with a sensor in which an uphill detection sensor such as an inclination sensor is additionally set.
- the clutch control device for the four-wheel drive vehicle of the first embodiment is The dog clutch 8 as the meshing clutch is disposed upstream of the output pinion 10 and the bevel gear 9 as a transfer mechanism provided at the driving branch position to the left and right rear wheels 19 and 20 as auxiliary driving wheels.
- An electric control coupling 16 as a friction clutch includes a bevel gear 9 as a transfer mechanism, an output pinion 10 and a left rear wheel drive shaft 17 from a propeller shaft 12 and a rear differential 15 to a left rear wheel 19 as an auxiliary drive wheel. It is characterized by being arranged at a position. For this reason, in the four-wheel drive vehicle based on the front wheel drive, when the disconnect two-wheel drive mode is selected, friction loss, oil agitation loss, and the like are effectively suppressed, and fuel efficiency can be improved.
- the clutch control device for a four-wheel drive vehicle of the embodiment differs from that of the first embodiment in mode switching characteristics during automatic control.
- the 4WD control unit 34 switches between the two-wheel drive mode and the four-wheel drive mode based on the drive mode switching map shown in FIG. That is, as shown in FIG. 8, the drive mode switching map includes a differential rotation control region (Disconnect) that is a control region for the disconnect two-wheel drive mode and a standby two-wheel according to the vehicle speed VSP and the accelerator opening ACC.
- the differential rotation control area (Stand-by) which is the control area for the drive mode
- the driving force distribution area (Connect) which is the control area for the connect four-wheel drive mode
- the differential rotation control region (Disconnect) which is a control region for the disconnect two-wheel drive mode, includes a vehicle speed axis line where the accelerator opening degree ACC is equal to or less than the set opening degree ACC0, and the accelerator opening degree ACC is zero. It is set to the area surrounded by the area dividing line B. In other words, since the accelerator opening ACC is equal to or less than the set opening ACC0, the frequency of occurrence of differential rotation between the left and right front wheels 6 and 7 and the left and right rear wheels 19 and 20 due to driving slip is extremely small, and slip occurs even when driving slip occurs. It is set in the low 4WD request area.
- the differential rotation control area (Stand-by), which is the control area for the standby two-wheel drive mode, is an area defined by the area division line A and the area division line B when the accelerator opening ACC exceeds the set opening ACC0. Is set. That is, although the accelerator opening ACC exceeds the set opening ACC0 but the vehicle speed VSP is in the high vehicle speed range, the 4WD requirement is low, but the differential rotation between the left and right front wheels 6 and 7 and the left and right rear wheels 19 and 20 is caused by driving slip. When this occurs, it is set in a region where there is a high possibility that the slip will increase rapidly.
- the driving force distribution area which is a control area for the connected four-wheel drive mode, is surrounded by an accelerator opening axis line where the vehicle speed VSP is zero, a vehicle speed axis line where the accelerator opening degree ACC is zero, and an area division line A. It is set to the area to be. That is, it is set in a region where the 4WD request is high, such as when the vehicle starts or when the vehicle speed VSP is low but the accelerator opening degree ACC is high and the load is high.
- disconnect when the disconnect two-wheel drive mode (Disconnect) is selected and the uphill flag is set, the disconnect two-wheel drive mode is canceled and the standby two-wheel drive mode is canceled. Switch to drive mode.
- the vehicle is switched to the standby two-wheel drive mode during climbing. Therefore, when slip occurs in the left and right front wheels 6 and 7, which are drive wheels, the vehicle can be instantaneously switched to the connected four-wheel drive mode to ensure running stability. Further, in the second embodiment, in the low-speed traveling region, the start acceleration performance and the start traveling stability can be ensured by controlling the connected four-wheel drive mode.
- the clutch control device of the third embodiment is applied to a four-wheel drive vehicle based on a rear wheel drive, and the arrangement relationship between the meshing clutch and the friction clutch sandwiching the differential is an arrangement relationship opposite to that of the first embodiment. It is.
- FIG. 9 shows a drive system configuration of a rear-wheel drive-based four-wheel drive vehicle to which the clutch control device is applied.
- the drive system configuration of the four-wheel drive vehicle will be described below with reference to FIG.
- the rear wheel drive system of the four-wheel drive vehicle includes a vertical engine 61 (drive source), a transmission 62, a rear propeller shaft 63, a rear differential 64, a left rear wheel drive shaft 65, and a right rear wheel drive.
- a shaft 66, a left rear wheel 67 (main drive wheel), and a right rear wheel 68 (main drive wheel) are provided. That is, the driving force that has passed through the vertical engine 61 and the transmission 62 is transmitted to the left and right rear wheel drive shafts 65 and 66 via the rear propeller shaft 63 and the rear differential 64, and allows the left and right rear wheels 67 while allowing the differential. , 68 are always driven.
- the front wheel drive system of the four-wheel drive vehicle includes an electric control coupling 70 (friction clutch), an input side sprocket 71, an output side sprocket 72, and a chain 73 in a transfer case 69. It is configured. Then, a front propeller shaft 74, a front differential 75, a left front wheel drive shaft 76, a right front wheel drive shaft 77, a left front wheel 78 (sub driving wheel), and a right front wheel 79 (sub driving wheel) connected to the output side sprocket 72. Drive wheel).
- the electric control coupling 70 is disposed in the transfer case 69 at a position upstream of the input side sprocket 71 (position on the main drive system side).
- the drive system rotation rotation of the front propeller shaft 74, etc.
- the electric coupling 70 stops, so that friction loss, oil agitation loss, etc. Suppressed and improved fuel efficiency.
- the dog clutch 8 is arranged on the transmission branch path on the driving branch side with the rear differential 15 interposed therebetween, and the auxiliary driving wheel side In this transmission system, the electric control coupling 16 is arranged separately. For this reason, when there is a fastening request for the dog clutch 8 in the released state, if the fastening control of the electric coupling 16 is performed, the left side gear of the rear differential 15 is restrained by the rotational speed of the left rear wheel 19.
- the rotational speeds of the left and right side gears are constrained, so that the rotational speed of the propeller shaft 12 coupled to the differential case can be reduced. , 20 average rotation speed (driven wheel rotation speed).
- the differential rotation ⁇ N of the dog clutch 8 that has decreased with the passage of time becomes a limit when the differential rotation becomes a certain differential rotation, and thereafter, the differential rotation ⁇ N of the dog clutch 8 increases.
- the differential rotation ⁇ N of the dog clutch 8 increases with the passage of time.
- the electric coupling 70 is arranged in the transmission system on the driving branch side with the front differential 75 interposed therebetween.
- the dog clutch 80 is arranged separately on the transmission system path on the auxiliary drive wheel side. For this reason, when there is an engagement request for the dog clutch 80 in the released state, if the engagement control of the electric coupling 70 is performed, the differential case of the front differential 75 is constrained by the rotational speed of the rear propeller shaft 63.
- the rotational speed of the right side gear (the right front wheel 79) and the differential case is constrained, so that the rotational speed of the left side gear becomes two rotational speeds. It will be decided by.
- the differential rotation ⁇ N expands in a reverse state. Since other operations are the same as those in the first embodiment, description thereof is omitted.
- the clutch control device for a four-wheel drive vehicle of Embodiment 3 is The electric coupling 70 as a friction clutch is located upstream of the transfer mechanism (input-side sprocket 71, output-side sprocket 72, chain 73) provided at the driving branch position to the left and right front wheels 78 and 79 as auxiliary driving wheels. Place and The dog clutch 80 as the meshing clutch is disposed at the position of the left front wheel drive shaft 76 from the transfer mechanism to the left front wheel 78 as the auxiliary drive wheel via the propeller shaft and the front differential 75.
- the clutch control device of the present invention is applied to a front-wheel drive-based four-wheel drive vehicle (4WD engine vehicle) equipped with an engine as a drive source.
- a front-wheel drive-based four-wheel drive vehicle (4WD engine vehicle) equipped with an engine as a drive source.
- the clutch control device of the present invention is applied to a rear wheel drive-based four-wheel drive vehicle (4WD engine vehicle) in which the main drive wheels are the left and right rear wheels.
- the present invention can be applied to a four-wheel drive vehicle with a rear wheel drive base in which the disposition relationship between the meshing clutch and the friction clutch is the relationship of the first embodiment.
- the present invention can be applied to a front-wheel drive base four-wheel drive vehicle in which the disposition relationship between the meshing clutch and the friction clutch is the relationship of the third embodiment.
- the two-wheel drive mode is divided into a disconnect two-wheel drive mode and a standby two-wheel drive mode.
- the two-wheel drive mode as shown in FIG. You may make it ensure more fuel-consumption as drive mode only.
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Abstract
Description
この4輪駆動車では、2輪駆動モードから4輪駆動モードへの切り替え時には、摩擦クラッチを締結し、噛み合いクラッチの駆動源側と後輪側とを同期させた後、噛み合いクラッチを締結する。また、4輪駆動モードから2輪駆動モードへの切り替え時には、摩擦クラッチを解放した後、噛み合いクラッチを解放する。
しかしながら、ディスコネクト2輪駆動モードから、4輪駆動モードへ移行する場合、噛み合いクラッチの同期が必要である。このため、噛み合いクラッチを締結させた2輪駆動モードから摩擦クラッチを締結させて4輪駆動モードに移行する場合よりも、4輪駆動モードに移行するのに時間を要する。
したがって、4輪駆動モードへの移行要求が高い登坂時に、4輪駆動モードへの移行に時間を要し、その間、路面への駆動力伝達状態が不安定になるおそれがあった。
駆動源と副駆動輪との間に介在されたクラッチとして、前記副駆動輪への駆動力伝達系のうち、デファレンシャルを挟んだ駆動分岐側の伝達系路と副駆動輪側の伝達系路にそれぞれ分けて配置される噛み合いクラッチと摩擦クラッチとを備え、
両クラッチの締結及び解放を制御して前記主駆動輪のみを駆動させる2輪駆動モードと、前記主駆動輪及び前記副駆動輪を駆動させる4輪駆動モードとに切替可能なクラッチコントロールユニットは、2輪駆動モードとして、両クラッチを解放したディスコネクト2輪駆動モードと、前記噛み合いクラッチを締結し前記摩擦クラッチを解放したスタンバイ2輪駆動モードと、を有し、かつ、前記ディスコネクト2輪駆動モード時に、登坂を検出した場合は、前記スタンバイ2輪駆動モードに切り替えることを特徴とする4輪駆動車のクラッチ制御装置とした。
一方、登坂検出時には、噛み合いクラッチを締結させたスタンバイ2輪駆動モードとすることにより、4輪駆動モードに移行する際に、ディスコネクト2輪駆動モードから移行する場合よりも移行時間を短縮し、路面への駆動力伝達状態の安定性向上を図ることが可能となる。
(実施の形態1)
まず、実施の形態1の構成を説明する。
実施の形態1における前輪駆動ベースの4輪駆動車(4輪駆動車の一例)のクラッチ制御装置の構成を、「4輪駆動車の駆動系構成」、「4輪駆動車の制御系構成」、「駆動モード切替構成」、「クラッチ制御構成」に分けて説明する。
図1は、実施の形態1のクラッチ制御装置が適用された前輪駆動ベースの4輪駆動車の駆動系構成を示す。以下、図1に基づき、4輪駆動車の駆動系構成を説明する。
また、図2に示すドグクラッチ8の入力側噛み合い部材8aは、フロントデファレンシャル3のデフケース3aに連結され、ドグクラッチ8の出力側噛み合い部材8bは、ベベルギア9に連結されている。
そして、電制カップリング16の入力側クラッチプレートは、リアデファレンシャル15の左サイドギアに連結され、出力側クラッチプレートは、左後輪ドライブシャフト17に連結されている。
図2は、実施の形態1のクラッチ制御装置が適用された前輪駆動ベースの4輪駆動車の制御系構成を示す。以下、図2に基づき、4輪駆動車の制御系構成を説明する。
「2WDモード」が選択されると、ドグクラッチ8と電制カップリング16とを解放した前輪駆動の2WD状態が維持される。
「ロックモード」が選択されると、ドグクラッチ8と電制カップリング16とを締結した完全4WD状態が維持される。
さらに、「オートモード」が選択されると、車両状態(車速VSP、アクセル開度ACC)に応じてドグクラッチ8と電制カップリング16の締結/解放が自動制御されて、自動的に2駆状態と4駆状態とに切り替えられる。なお、車速VSPは、本実施の形態1では、基本的には、副駆動輪としての左右後輪19,20の車輪速度から演算する。
「オートモード」選択時は、図3に示す駆動モード切替マップに基づいて車速VSPとアクセル開度ACCに応じて駆動モードを切り替えるが、本実施の形態1では、車速VSPとアクセル開度ACCの全域で、ディスコネクト差回転制御モードとしている。このディスコネクト差回転制御モードの詳細は、後述するが、通常はディスコネクト2輪駆動モードの2駆状態とし、左右前輪6,7と左右後輪19,20との間に差回転が生じると、4輪駆動モードに切り替える制御を実行する。
前記ディスコネクト2輪駆動モード(Disconnect)は、図4の枠線C内に示すように、ドグクラッチ8と電制カップリング16が共に解放された2WD走行(Disconnect)のモードである。このディスコネクト2輪駆動モードでは、基本的に左右前輪6,7にのみ駆動力を伝達しての前輪駆動の2WD走行(Disconnect)が維持される。
しかし、ディスコネクト2輪駆動モードでの2WD走行中に左右前輪6,7に駆動スリップが発生し、駆動スリップ量(又は駆動スリップ率)が閾値を超えると、左右後輪19,20に駆動力を配分して駆動スリップを抑える差回転制御が行われる。この差回転制御時には、まず、電制カップリング16を摩擦締結し、その後、回転同期状態が判定されるとドグクラッチ8を噛み合い締結し、左右後輪19,20に駆動力を配分する。なお、左右後輪19,20への駆動力配分は、電制カップリング16の伝達トルクを制御することにより調節する。
しかし、スタンバイ2輪駆動モードでの2WD走行中に左右前輪6,7に駆動スリップが発生し、駆動スリップ量(又は駆動スリップ率)が閾値を超えると、左右後輪19,20に駆動力を配分して駆動スリップを抑える差回転制御が行われる。このスタンバイ2輪駆動モードでの差回転制御では、予めドグクラッチ8が噛み合い締結されているため、電制カップリング16の摩擦締結のみを行う。したがって、応答良く左右後輪19,20に駆動力を配分することができる。
図5は、4WDコントロールユニット34にて実行される、「オートモード」時のクラッチ制御処理流れを示している。上述した前記ディスコネクト2輪駆動モード(2WD走行(Disconnect))と、スタンバイ2輪駆動モード(2WD走行(Stand-by))と、差回転制御(4WD走行(Connect))の切り替えは、登坂検出及び差回転の発生に基づいて行われる。
この図5のフローチャートの説明に先立ち、まず、登坂検出を行う構成について説明する。
a.車速と車両前後方向加速度とエンジントルクとの関係に基づいて、実車速が、エンジントルクに基づく加速度から求めた平坦路相当の車速よりも所定値以上低い場合に登坂と判定する。
b.車両の駆動力及び変速段と車速との関係により、駆動力及び変速段に基づく平坦路走行時の車速に対して、実車速が所定値以上低い場合に登坂と判定する。
c.走行駆動力から、勾配抵抗を除いた、各種抵抗(空気抵抗、路面抵抗など)を差し引いた値が、所定値よりも高い(勾配抵抗が発生している)場合に登坂と判定する。
また、この登坂検出部100は、既存のヒルアシストブレーキ制御装置において、登坂路を検出する構成を利用することもできる。
ステップS101では、現在、登坂フラグセット(登坂検出)であるか否か判定し、非登坂フラグセットでステップS102に進み、登坂フラグセット時はステップS109に進む。
すなわち、左右前輪6,7と左右後輪19,20との差回転ΔVが、スリップ判定閾値ΔVlimを超えたか否か(駆動輪スリップが生じたか否か)判定する。そして、スリップ判定閾値ΔVlimを超える差回転ΔVが生じた場合は、ステップS104~S107の同期処理を行ってコネクト4輪駆動モードとした上で、差回転制御を行う。なお、ステップS103においてスリップ判定閾値ΔVlimを超える差回転ΔVが生じない場合は、1回の処理を終了し、ステップS101に戻る。
続くステップS105では、ドグクラッチ8の入力側噛み合い部材8aと出力側噛み合い部材8bとの差回転ΔNを演算し、次のステップS106にて、この差回転ΔNが同期判定閾値α以下の同期状態となったか否か判定する。
なお、この差回転制御は、左右前輪6,7と左右後輪19,20との差回転が収まると終了し、ステップS101に戻り、登坂フラグのセット状態に応じた2輪駆動モードに戻す。
一方、停車時あるいは停車直前の登坂検出時には、ドグクラッチ8を、同期作動無しに締結させる。このとき、仮に、ドグクラッチ8において歯当たりにより締結が完了しない場合は、発進時に差回転が生じた時点で、スプリングの付勢力により締結される。
次に、本実施の形態1の作動を、図6、図7のタイムチャートに基づいて説明する。
図6は、非登坂時の動作の一例を示しており、t1の時点でアクセルペダルを踏み込んで発進する際に、左右前輪6,7に駆動輪スリップが生じた場合の動作を示している。
よって、差回転ΔVの上昇に応じて、電制カップリング16への締結指令出力TETSを上昇させる。そして、コネクト4輪駆動モードとすることにより、左右後輪19,20へ駆動力配分される。これにより、左右前輪6,7のスリップが低下して、t3の時点以降、差回転ΔVが低下し、車両を円滑に発進させることができる。
この場合、図示のように、t4の時点で、電制カップリング16に対する締結指令出力TETSを停止して解放し、プロペラシャフト12への左右後輪19,20からの負荷を無くした状態とした後、t5の時点で、ドグクラッチ8の締結を解除する。
このように、非登坂時(通常時)は、ディスコネクト2輪駆動モードに制御される。このディスコネクト2輪駆動モードでは、ドグクラッチ8及び電制カップリング16が解放された状態で左右前輪6,7のみを駆動させるため、後輪駆動系のべベルギア9からリングギア14の間が停止した状態となり、後輪側の駆動系のフリクションロスを低減できる。
この制御時には、登坂路で車両が停止し、この停止状態から発進する際の動作例を示している。
この動作例では、停止直前のt11の時点で、登坂路に差し掛かり、t13の時点で停車したのち、t14の時点で発進している。
そして、t14からの発進時に、登坂路で主駆動輪である左右前輪6,7は輪荷重が低下し、発進と同時にスリップが生じている。
この場合、前後の差回転ΔVに応じ、コネクト4輪駆動モードとして差回転制御を行う(S110→S108)が、スタンバイ2輪駆動モードからの切替であるため、電制カップリング16を締結するだけでコネクト4輪駆動モードに切り替えられる。したがって、即座に左右前輪6,7のスリップを抑えて、安定した発進が可能になる。加えて、コネクト4輪駆動モードに切り替えることにより、登坂路では、輪荷重が増加する左右後輪19,20を駆動させる。このため、後輪を主駆動輪としてスリップが生じた後、前輪を駆動させる場合よりも、4輪駆動モードに切り替えることによる安定性の向上効果が、早期に確実に得られる。
以下に、実施の形態1の4輪駆動車のクラッチ制御装置の効果を作用と共に列挙する。
1)実施の形態1の4輪駆動車のクラッチ制御装置は、
左右前輪6,7と左右後輪19,20のうち、一方を駆動源としてのエンジン1に接続される主駆動輪とし、他方を前記駆動源にクラッチを介して接続される副駆動輪とし、
前記クラッチとして、前記副駆動輪としての左右後輪19,20への駆動力伝達系のうち、リアデファレンシャル15を挟んだ駆動分岐側の伝達系路と副駆動輪側の伝達系路にそれぞれ分けて配置される噛み合いクラッチとしてのドグクラッチ8と摩擦クラッチとしての電制カップリング16とを備え、
前記ドグクラッチ8は、クラッチ解放により前記左右後輪19,20への駆動力伝達系を、前記左右前輪6,7への駆動力伝達系から切り離し、前記電制カップリング16は、クラッチ締結容量に応じて前記エンジン1からの駆動力の一部を前記左右後輪19,20へ配分する4輪駆動車において、
車両状態検出装置としての各センサ類(35,36,38~47、50~55)が検出する車両状態に応じて、前記ドグクラッチ8の締結/解放制御と前記電制カップリング16の締結/解放制御とを行って、前記左右前輪6,7のみを駆動させる2輪駆動モードと、前記左右前輪6,7及び前記左右後輪19,20を駆動させる4輪駆動モードとに切替可能なクラッチコントロールユニットとしての4WDコントロールユニット34を設け、
前記車両状態検出装置に登坂を検出する登坂センサとしての登坂検出部100を含み、
前記4WDコントロールユニット34は、前記2輪駆動モードとして、ドグクラッチ8及び電制カップリング16を解放したディスコネクト2輪駆動モードと、ドグクラッチ8を締結し電制カップリング16を解放したスタンバイ2輪駆動モードと、を有し、
かつ、前記ディスコネクト2輪駆動モード時に、登坂を検出した場合は、前記スタンバイ2輪駆動モードに切り替えることを特徴とする。
したがって、2輪駆動モードとしてディスクコネクト2輪駆動モードに制御した場合は、後輪駆動系のべベルギア9からリングギア14の間の駆動系が完全に停止した状態となるため、フリクションロスが発生しない。そのため、燃費悪化を抑制でき、4輪駆動車でありながら2輪駆動モードで使用しているときの燃費を2輪駆動車並みの燃費とすることができる。
しかも、上述のように、燃費に優れるディスコネクト2輪駆動モードに制御している場合でも、登坂検出時には、ドグクラッチ8を締結させたスタンバイ2輪駆動モードとする。このため、2輪駆動モードから4輪駆動モードへの移行を、電制カップリング16を締結させるだけで行うことができる。よって、ディスコネクト2輪駆動モードからの4輪駆動モードへの切替時のようなドグクラッチ8の同期作動が不要であり、その分、短時間に2輪駆動モードから4輪駆動モードへの移行を行うことが可能である。
したがって、ディスコネクト2輪駆動モードへの制御時に、駆動輪スリップが生じやすい登坂路では、スタンバイ2輪駆動モードに切り替えることにより、4輪駆動モードへの切替を短時間に可能として、走行安定性の向上を図ることができる。
前記クラッチコントロールユニットとしての4WDコントロールユニット34は、前記主駆動輪と前記副駆動輪とに差回転が生じていない場合は、前記2輪駆動モードに制御し、前記差回転が生じたら前記4輪駆動モードに切り替え、かつ、前記2輪駆動モードでは、前記ディスコネクト2輪駆動モードに制御する自動切替制御を実行することを特徴とする。
したがって、自動切替制御では、2輪駆動モード時に、ディスコネクト2輪駆動モードとすることにより、上記1)のように燃費の向上を図ることができる。
しかも、自動切替制御時に、2輪駆動モードでは、ディスコネクト2輪駆動モードに制御しながら、上記1)のように、登坂検出時にはスタンバイ2輪駆動モードに切り替えるため、差回転発生時の4輪駆動モードへの切り替えを短時間に行うことができる。
よって、2輪駆動モードと4輪駆動モードとの自動切替制御を行うにあたり、燃費性能の向上と、登坂時の走行性向上との両立が可能となる。
前記主駆動輪を、前記左右前輪6,7としたことを特徴とする。
主駆動輪を左右前輪6,7とした場合、左右後輪19,20を主駆動輪とした場合よりも、登坂時に、2輪駆動モードでの駆動輪スリップが生じやすいとともに、4輪駆動モードとした時の走行安定性向上効果が顕著である。
前記登坂検出部100は、車速と加速度とエンジントルクなどの既存のセンサの検出に基づいて、登坂を判定するようにしたことを特徴とする。
したがって、傾斜センサなどの登坂検出用のセンサを追加設定したものと比較して、製造コストの低減が可能となる。
噛み合いクラッチとしてのドグクラッチ8は、副駆動輪としての左右後輪19,20への駆動分岐位置に設けたトランスファ機構としてのベベルギア9、出力ピニオン10より上流位置に配置し、
摩擦クラッチとしての電制カップリング16は、トランスファ機構としてのベベルギア9、出力ピニオン10からプロペラシャフト12およびリアデファレンシャル15を経由した副駆動輪としての左後輪19への左後輪ドライブシャフト17の位置に配置したことを特徴とする。
このため、前輪駆動ベースの4輪駆動車において、ディスコネクト2輪駆動モードが選択されているとき、フリクション損失やオイル攪拌損失などが有効に抑えられ、燃費向上を達成することができる。
次に、他の実施の形態の4輪駆動車のクラッチ制御装置について説明する。
なお、他の実施の形態を説明するのにあたり、実施の形態1と共通する構成には実施の形態1と同じ符号を付して説明を省略し、実施の形態1との相違点のみ説明する。
実施の形態の4輪駆動車のクラッチ制御装置は、自動制御時のモード切替特性が実施の形態1と異なる。
この実施の形態2では、4WDコントロールユニット34は、図8に示す駆動モード切替マップに基づいて、2輪駆動モードと4輪駆動モードとに切り替える。すなわち、駆動モード切替マップは、図8に示すように、車速VSPとアクセル開度ACCに応じて、ディスコネクト2輪駆動モードへの制御領域である差回転制御領域(Disconnect)と、スタンバイ2輪駆動モードへの制御領域である差回転制御領域(Stand-by)と、コネクト4輪駆動モードへの制御領域である駆動力配分領域(Connect)と、を分けた設定としている。この3つの領域は、アクセル開度ゼロで設定車速VSP0の基点aから車速VSPの上昇に比例してアクセル開度ACCが上昇する領域区分線Aと、領域区分線Aとの交点bから高車速側に引いた設定開度ACC0で一定開度の領域区分線Bと、により分けている。
さらに、実施の形態2では、低速走行領域では、コネクト4輪駆動モードに制御することにより、発進加速性及び発進走行安定性を確保することができる。
実施の形態3のクラッチ制御装置は、後輪駆動ベースの4輪駆動車に適用し、デファレンシャルを挟んだ噛み合いクラッチと摩擦クラッチの配置関係を、実施の形態1とは逆の配置関係にした例である。
すなわち、電制カップリング70とドグクラッチ80を共に解放する2輪駆動モード(=ディスコネクト2輪駆動モード)を選択することが可能な駆動系構成としている。この電制カップリング70とドグクラッチ80を解放することにより、電制カップリング70より下流側の駆動系回転(フロントプロペラシャフト74等の回転)が停止することで、フリクション損失やオイル攪拌損失などが抑えられ、燃費向上が達成される。
実施の形態1では、副駆動輪である左右後輪19,20への駆動力伝達系のうち、リアデファレンシャル15を挟んだ駆動分岐側の伝達系路にドグクラッチ8を配置し、副駆動輪側の伝達系路に電制カップリング16にそれぞれ分けて配置した構成としている。
このため、解放状態のドグクラッチ8に対する締結要求があるとき、電制カップリング16の締結制御を行うと、リアデファレンシャル15の左側サイドギアが左後輪19の回転数により拘束される。
しかし、左右前輪6,7がスリップ状態のときは、時間の経過と共に減少していたドグクラッチ8の差回転ΔNが、ある差回転になると限界になり、その後、ドグクラッチ8の差回転ΔNは増加へ移行し、時間の経過と共にドグクラッチ8の差回転ΔNが拡大する。
このため、解放状態のドグクラッチ80に対する締結要求があるとき、電制カップリング70の締結制御を行うと、フロントデファレンシャル75のデフケースがリアプロペラシャフト63の回転数により拘束される。
この結果、左右後輪67,68が非スリップ状態のときは、ドグクラッチ80の差回転ΔNがΔN=0になる。
しかし、左右後輪67,68がスリップ状態のときは、時間の経過と共に減少していたドグクラッチ80の差回転ΔNが、ΔN=0(ゼロ)を跨いで逆転してしまい、その後、ドグクラッチ80の差回転ΔNは逆転した状態で拡大してゆくことになる。なお、他の作用は、実施の形態1と同様であるので、説明を省略する。
実施の形態3の4輪駆動車のクラッチ制御装置にあっては、下記の効果を得ることができる。
3-1) 実施の形態3の4輪駆動車のクラッチ制御装置は、
摩擦クラッチとしての電制カップリング70は、副駆動輪としての左右前輪78,79への駆動分岐位置に設けたトランスファ機構(入力側スプロケット71、出力側スプロケット72、チェーン73)よりも上流位置に配置し、
噛み合いクラッチとしてのドグクラッチ80は、トランスファ機構からプロペラシャフトおよびフロントデファレンシャル75を経由した副駆動輪としての左前輪78への左前輪ドライブシャフト76の位置に配置した。
このため、上記1)~4)の効果に加え、後輪駆動ベースの4輪駆動車において、「ディスコネクト2輪駆動モード」が選択されているとき、フリクション損失やオイル攪拌損失などが有効に抑えられ、燃費向上を達成することができる。
また、実施の形態2では、2輪駆動モードを、ディスコネクト2輪駆動モードと、スタンバイ2輪駆動モードとに分けたが、2輪駆動モードでは、図10に示すように、ディスコネクト2輪駆動モードのみとして、より燃費性を確保するようにしてもよい。
Claims (6)
- 左右前輪と左右後輪のうち、一方を駆動源に接続される主駆動輪とし、他方を前記駆動源にクラッチを介して接続される副駆動輪とし、
前記クラッチとして、前記副駆動輪への駆動力伝達系のうち、デファレンシャルを挟んだ駆動分岐側の伝達系路と副駆動輪側の伝達系路にそれぞれ分けて配置される噛み合いクラッチと摩擦クラッチとを備え、
前記噛み合いクラッチは、クラッチ解放により前記副駆動輪への駆動力伝達系を、前記主駆動輪への駆動力伝達系から切り離し、前記摩擦クラッチは、クラッチ締結容量に応じて前記駆動源からの駆動力の一部を前記副駆動輪へ配分する4輪駆動車において、
車両状態検出装置が検出する車両状態に応じて、前記噛み合いクラッチの締結/解放制御と前記摩擦クラッチの締結/解放制御とを行って、前記主駆動輪のみを駆動させる2輪駆動モードと、前記主駆動輪及び前記副駆動輪を駆動させる4輪駆動モードとに切替可能なクラッチコントロールユニットを設け、
前記車両状態検出装置は、登坂を検出する登坂センサを含み、
前記クラッチコントロールユニットは、前記2輪駆動モードとして、両クラッチを解放したディスコネクト2輪駆動モードと、前記噛み合いクラッチを締結し前記摩擦クラッチを解放したスタンバイ2輪駆動モードと、を有し、
かつ、前記ディスコネクト2輪駆動モード時に、登坂を検出した場合は、前記スタンバイ2輪駆動モードに切り替えることを特徴とする4輪駆動車のクラッチ制御装置。 - 請求項1に記載の4輪駆動車のクラッチ制御装置において、
前記クラッチコントロールユニットは、前記主駆動輪と前記副駆動輪とに差回転が生じていない場合は、前記2輪駆動モードに制御し、前記差回転が生じたら前記4輪駆動モードに切り替え、かつ、前記2輪駆動モードでは、前記ディスコネクト2輪駆動モードに制御する自動切替制御を実行することを特徴とする4輪駆動車のクラッチ制御装置。 - 請求項1または請求項2に記載の4輪駆動車のクラッチ制御装置において、
前記主駆動輪を、前記左右前輪としたことを特徴とする4輪駆動車のクラッチ制御装置。 - 請求項1~請求項3のいずれか1項に記載の4輪駆動車のクラッチ制御装置において、
前記登坂センサは、車速と車両前後方向加速度に基づいて登坂を検出することを特徴とする4輪駆動車のクラッチ制御装置。 - 請求項1~請求項4のいずれか一項に記載された4輪駆動車のクラッチ制御装置において、
前記噛み合いクラッチは、前記副駆動輪への駆動分岐位置に設けたトランスファ機構より上流位置に配置し、
前記摩擦クラッチは、前記トランスファ機構からプロペラシャフトおよびデファレンシャルを経由した前記副駆動輪へのドライブシャフトの位置に配置したことを特徴とする4輪駆動車のクラッチ制御装置。 - 請求項1~請求項4のいずれか一項に記載された4輪駆動車のクラッチ制御装置において、
前記摩擦クラッチは、前記副駆動輪への駆動分岐位置に設けたトランスファ機構より上流位置に配置し、
前記噛み合いクラッチは、前記トランスファ機構からプロペラシャフトおよびデファレンシャルを経由した前記副駆動輪へのドライブシャフトの位置に配置したことを特徴とする4輪駆動車のクラッチ制御装置。
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