Patent Application
20230347864
The present disclosure relates to a method of controlling a hybrid vehicle provided with an engine and a motor as power sources, and a friction engagement element (clutch) which switches between transmission and interception of torque between the engine and the motor, and also relates to a control system therefor.
Conventionally, it is known that hybrid vehicles are provided with an engine (internal combustion engine), a motor (electric motor) provided downstream of the engine in a power transmission path to wheels, and a clutch (friction engagement element) provided between the engine and the motor so as to be connectable and disconnectable. This hybrid vehicle is able to switch between a first traveling mode in which the hybrid vehicle travels using torque of the motor without using torque of the engine (electric vehicle (EV) traveling mode), and a second traveling mode in which the hybrid vehicle travels at least using the engine torque (engine traveling mode or hybrid traveling mode). Particularly, this hybrid vehicle performs an engine startup control in which, when switching the traveling mode from the first traveling mode to the second traveling mode, in order to start the stopped engine, the clutch in a disengaged state is shifted to an engaged state, and the torque of the motor is transmitted to the engine via the clutch (in other words, the engine is cranked by the motor).
For example, JP2018-030507A discloses a technique relevant to such a hybrid vehicle. In detail, this technique suppresses a torque shock occurring in the vehicle accompanying an engagement of a clutch by gradually increasing the transmitting torque of the clutch until a rotational speed difference between an input shaft and an output shaft of the clutch becomes below a threshold, when switching the traveling mode from the first traveling mode (EV mode) to the second traveling mode (HV mode).
In such a hybrid vehicle, when switching the traveling mode from the first traveling mode to the second traveling mode (i.e., when starting the engine by the engine startup control), since the motor is used for traveling (propelling the vehicle), the motor rotational speed changes fundamentally according to a vehicle driver's demand, and the engine speed increases from 0 by the cranking with the motor and will eventually synchronize with the motor rotational speed. Thus, when the engine speed synchronizes the motor rotational speed, there may be a difference in torque between the engine and the motor. In this case, if it is in a state where the torque is fully and mutually transmittable between the engine and the motor (i.e., in a fully engaged state where the clutch transmits the entire torque), a comparatively large oscillation (hereinafter, referred to as “vehicle shock”) may occur according to the difference in the torque between the engine and the motor, and it may give a person on board uncomfortableness. On the other hand, if the clutch and the motor are controlled to give priority to the suppression of such a vehicle shock, the response of the engine startup is deteriorated.
The present disclosure is made in view of solving the problems of the conventional technique described above, and one purpose thereof is to provide a method of controlling a hybrid vehicle, in which, when an engine of the hybrid vehicle is started, by securely controlling a friction engagement element provided between the engine and a motor, a vehicle shock can be suppressed, while securing the response of the engine startup, and to provide a control system therefor.
In order to achieve the above-described purpose, the present disclosure provides a method of controlling a hybrid vehicle including an engine, a motor, and a friction engagement element provided between the engine and the motor so as to be engageable and disengageable, in which an engine startup control for starting the engine stopped is performed in order to switch a traveling mode from a traveling mode in which the hybrid vehicle travels using torque of the motor, without using torque of the engine, to a traveling mode in which the hybrid vehicle travels at least using the torque of the engine. The method includes raising an engine speed by cranking of the motor, while shifting the friction engagement element from a disengaged state to an engaged state, when the engine startup control is started, temporarily reducing an engaging torque of the friction engagement element, after the engine speed is raised by the cranking of the motor and before the engine speed coincides with a motor rotational speed, and raising the engaging torque to set the friction engagement element to a fully engaged state, after the temporarily reducing the engaging torque and the engine speed coincides with the motor rotational speed.
According to this configuration, when starting the engine in order to switch the traveling mode, the engaging torque of the friction engagement element is temporarily reduced, after the engine speed is raised by cranking with the motor and before the engine speed coincides with the motor rotational speed. Therefore, when the engine speed synchronizes with the motor rotational speed, a transmitting torque of the friction engagement element can be reduced. As a result, the difference in the torque between the engine and the motor can be compensated by the friction engagement element in a slip state where the transmitting torque is reduced. That is, it can be compensated as a slip torque of the friction engagement element, and the vehicle shock caused by the difference in the torque can be suppressed. Further, since such a reduction of the engaging torque of the friction engagement element is temporary, the response of engine startup can be secured. Therefore, according to this embodiment, when starting the engine in order to switch the traveling mode, the vehicle shock can be suppressed, while securing the response of the engine startup.
Note that the engaging torque of the friction engagement element is a torque which is applied to the friction engagement element, and is equivalent to a degree of engagement of the friction engagement element. Further, the transmitting torque of the friction engagement element is equivalent to a torque transmitted between the motor and the engine via the friction engagement element.
The temporarily reducing the engaging torque may include starting the temporary reduction of the engaging torque, when a difference between the engine speed and the motor rotational speed becomes below a given value.
According to this configuration, the vehicle shock caused by the difference in the torque during the rotation synchronization between the engine and the motor can be suppressed effectively.
The raising the engaging torque may include ending the temporary reduction of the engaging torque, and starting the raise of the engaging torque for setting the friction engagement element to the fully engaged state, when a state where a difference between the engine speed and the motor rotational speed is below a given value continues for a given period of time.
According to this configuration, the temporary reduction of the engaging torque can be ended appropriately at a timing when the difference in the torque between the engine and the motor becomes almost zero. Thus, it becomes possible to effectively achieve both the assurance of the response of the engine startup and the suppression of the vehicle shock.
The friction engagement element may operate according to hydraulic pressure applied. The raising the engine speed may include applying a first hydraulic pressure to the friction engagement element to fill up a hydraulic chamber of the friction engagement element with oil, and continuously applying a second hydraulic pressure lower than the first hydraulic pressure to the friction engagement element, after applying the first hydraulic pressure and before the temporarily reducing the engaging torque.
According to this configuration, by shifting the friction engagement element from the disengaged state to the engaged state, and transmitting the torque of the motor to the engine via the friction engagement element, the engine speed can be raised securely.
The raising the engine speed may include temporarily reducing the hydraulic pressure applied to the friction engagement element down to a third hydraulic pressure lower than the second hydraulic pressure, after applying the first hydraulic pressure and before applying the second hydraulic pressure, when there is no given acceleration demand from a vehicle driver during the engine startup control, and continuously applying the second hydraulic pressure to the friction engagement element without temporarily reducing the hydraulic pressure applied to the friction engagement element down to the third hydraulic pressure after applying the first hydraulic pressure and before the temporarily reducing the engaging torque, when there is the given acceleration demand from the driver during the engine startup control.
According to this configuration, when there is no given acceleration demand, the shock caused when the friction engagement element in the disengaged state starts to engage can be reduced, and when there is the given acceleration demand, a prompt startup of the engine can be secured.
In the temporarily reducing the engaging torque, the hydraulic pressure applied to the friction engagement element may be lower than the second hydraulic pressure and higher than the third hydraulic pressure.
According to this configuration, it becomes possible to effectively achieve both the assurance of the response of the engine startup and the suppression of the vehicle shock.
In another aspect, in order to achieve the above-described purpose, the present disclosure provides a control system for a hybrid vehicle, which includes an engine, a motor, a friction engagement element provided between the engine and the motor so as to be engageable and disengageable, and a control device which controls the engine, the motor, and the friction engagement element so that an engine startup control for starting the engine stopped is performed in order to switch a traveling mode from a traveling mode in which the hybrid vehicle travels using torque of the motor without using torque of the engine, to a traveling mode in which the hybrid vehicle travels at least using the torque of the engine. The control device is configured to raise an engine speed by cranking of the motor, while shifting the friction engagement element from a disengaged state to an engaged state, when the engine startup control is started, temporarily reduces an engaging torque of the friction engagement element, after the engine speed is raised by cranking of the motor and before the engine speed coincides with a motor rotational speed, and raises the engaging torque to set the friction engagement element to a fully engaged state, after temporarily reducing the engaging torque and the engine speed coincides with the motor rotational speed.
Also according to this configuration, when starting the engine in order to switch the traveling mode, the vehicle shock can be suppressed, while securing the response of the engine startup.
Hereinafter, a method of controlling a hybrid vehicle according to one embodiment of the present disclosure, and a control system therefor, will be described with reference to the accompanying drawings.
As illustrated in
An output shaft of the engine 2 and a rotational shaft of the motor 4 are coaxially coupled to each other by an axis AX1 via a first clutch CL1 which is connectable and disconnectable (engageable and disengageable). This first clutch CL1 switches between transmission and interception of the torque between the engine 2 and the motor 4. For example, the first clutch CL1 is comprised of a dry multiplate clutch or a wet multiplate clutch which controls continuously or stepwisely a clutch operating fluid flow rate and/or a clutch operating fluid pressure by a motor or a solenoid (not illustrated) and is able to change a transmitting torque capacity.
Here, referring to
The first clutch CL1 is able to change, by controlling the hydraulic pressure applied, between a released or disengaged state where the clutch piston 15c separates from the first clutch plate 15d, and an engaged state where the clutch piston 15c contacts the first clutch plate 15d. In the disengaged state of the first clutch CL1, the torque transmission between the engine 2 and the motor 4 is intercepted, and in the engaged state of the first clutch CL1, the torque is transmitted between the engine 2 and the motor 4. Although this engaged state is the state where the clutch piston 15c is in contact with the first clutch plate 15d as described above, this state includes a slip state where the first clutch plate 15d and the second clutch plate 15e slip (typically, a state where the first clutch plate 15d and the second clutch plate 15e separate from each other, and the torque is transmitted via oil therebetween), and a fully engaged state where the torque is fully transmitted between the first clutch plate 15d and the second clutch plate 15e (fundamentally, a state where the first clutch plate 15d and the second clutch plate 15e contact each other firmly). Note that such a first clutch CL1 is one example of a “friction engagement element” in the present disclosure.
Returning to
Further, the transmission 6 includes therein a second clutch CL2 which is connectable and disconnectable (engageable and disengageable), and the second clutch CL2 switches between transmission and interception of a torque between the upstream side of the transmission 6 (the engine 2 and the motor 4) and the downstream side of the transmission 6 (the wheel 12, etc.). For example, the second clutch CL2 is comprised of a dry multiplate clutch or a wet multiplate clutch which controls continuously or stepwisely the clutch operating fluid flow rate and/or the clutch operating fluid pressure by the motor and the solenoid (not illustrated) and is changeable of the transmitting torque capacity. Further, the second clutch CL2 is also able to switch a state between a released or disengaged state and an engaged state (a slip state or a fully engaged state) by controlling the hydraulic pressure applied.
Note that, in fact, the second clutch CL2 is comprised of a large number of clutches which are used to variously switch the gear stage of the transmission 6. Further, although in FIG. 1 only one planetary gear set is illustrated for simplification, the transmission 6 is actually provided with a plurality of planetary gear sets. For example, by selectively engaging the friction engagement elements, such as a plurality of clutches which are represented by the second clutch CL2, and a plurality of brakes (not illustrated), and switching the power transmission path passing through the planetary gear sets, a plurality of forward gear stages and one reverse gear stage can be realized.
A torque is inputted into the power transmission system 8 via an output axis AX3 of the transmission 6. The power transmission system 8 is comprised of a differential gear which distributes a driving force to a pair of left and right wheels 12, and a final gear.
A traveling mode of the hybrid vehicle 1 is changeable by switching engagement and release of the first clutch CL1. That is, the hybrid vehicle 1 has a first traveling mode in which the first clutch CL1 is set to the disengaged state and the travel hybrid vehicle 1 travels using the torque of the motor 4, without using the torque of the engine 2, and a second traveling mode in which the first clutch CL1 is set to the engaged state, and the hybrid vehicle 1 travels at least using the torque of the engine 2. The first traveling mode is a so-called electric vehicle (EV) traveling mode, and the second traveling mode includes an engine traveling mode in which the hybrid vehicle 1 travels only using the torque of the engine 2, and a hybrid traveling mode in which the hybrid vehicle 1 travels using the torques of both the engine 2 and the motor 4.
Next,
As illustrated in
The controller 20 is comprised of a computer provided with one or more processors 20a (typically, central processing units (CPUs)), and memory 20b, such as ROM and RAM, which stores various kinds of programs interpreted and executed by the processors (including a basic control program, such as an operating system (OS), and an application program which is booted on the OS and realizes a specific function), and various kinds of data. The controller 20 is an example of a “control device” in the present disclosure, and performs a “method of controlling a hybrid vehicle” in the present disclosure.
In detail, the controller 20 outputs a control signal mainly to the engine 2, the motor 4, the first clutch CL1, and the second clutch CL2 to control them based on the detection signals from the sensors SN1-SN4 described above. For example, the controller 20 performs a control for adjusting an ignition timing, a fuel injection timing, and a fuel injection amount of the engine 2, a control for adjusting the rotational speed and the torque of the motor 4, a control for switching states of the first and second clutches CL1 and CL2 (the disengaged state, the slip state, and the fully engaged state), etc. Actually, the controller 20 controls a spark plug, a fuel injection valve, and a throttle of the engine 2, controls the motor 4 via an inverter, and controls the first and second clutches CL1 and CL2 via a hydraulic control circuit (the motor, the solenoid 15f, etc.).
Next, the controls performed by the controller 20 in this embodiment are described. In this embodiment, in order to switch the traveling mode from the first traveling mode in which the hybrid vehicle 1 travels using the torque of the motor 4 without using the torque of the engine 2, to the second traveling mode in which the hybrid vehicle 1 travels at least using the torque of the engine 2, the controller 20 mainly performs an engine startup control for starting the stopped engine 2 by controlling the hydraulic pressure applied to the first clutch CL1 (hereinafter, referred to as “CL1 hydraulic pressure”) to shift the first clutch CL1 from the disengaged state to the engaged state, and controlling the motor 4 and the engine 2 to start the engine 2 by cranking with the motor 4. Note that the CL1 hydraulic pressure corresponds to a command value of the hydraulic pressure applied to the first clutch CL1 (indicated hydraulic pressure). In realizing the CL1 hydraulic pressure, the controller 20 controls the hydraulic control circuit (for example, the solenoid 15f) of the first clutch CL1.
First, referring to
At time t1, the controller 20 starts the engine startup control for starting the stopped engine 2 in order to switch the traveling mode from the first traveling mode to the second traveling mode. In detail, from the time t1, in order to fill up (precharge) the hydraulic chamber 15a of the first clutch CL1 with oil, the controller 20 sets the CL1 hydraulic pressure to a first hydraulic pressure P1 which is comparatively large (period T1). Next, after time t2, the controller 20 brings the clutch piston 15c which is separated from the clutch piston 15d in the first clutch CL1 into contact with the first clutch plate 15d, and it then raises the engine speed gradually by cranking with the motor 4 in a state where the first clutch plate 15d and the second clutch plate 15e slip. In detail, in order to reduce the shock caused when the clutch piston 15c contacts the first clutch plate 15d, the controller 20 first maintains the CL1 hydraulic pressure at a third hydraulic pressure P3 which is greatly reduced from the first hydraulic pressure P1 (period T2). Then, from time t3, the controller 20 waits for the engine speed to rise by cranking with the motor 4, while maintaining the CL1 hydraulic pressure at a second hydraulic pressure P2 larger than the third hydraulic pressure P3 (period T3).
Next, at time t4, the increased engine speed reaches the motor rotational speed, and the controller 20 slightly raises the CL1 hydraulic pressure so that the engine speed synchronizes with the motor rotational speed (in detail, so that the rotation synchronous state is stabilized) (period T4). Next, at time t5, the engine speed synchronizes with the motor rotational speed, and the controller 20 then further raises the CL1 hydraulic pressure to set the first clutch CL1 to the fully engaged state, and when the first clutch CL1 is set to the fully engaged state, it ends the raising of the CL1 hydraulic pressure and maintains the CL1 hydraulic pressure constant (period T5).
Here, when the engine speed synchronizes with the motor rotational speed as described above, there may be a difference in torque between the engine 2 and the motor 4. In this case, if it is in a state where the first clutch CL1 transmits the mutual torque of the engine 2 and the motor 4 nearly fully (the fully engaged state or the slip state close to the fully engaged state), a comparatively large oscillation occurs according to the difference in the torque between the engine 2 and the motor 4 (vehicle shock), and it may give a person on board uncomfortableness. On the other hand, if the first clutch CL1 and the motor 4 are controlled gently to give priority to suppression of such a vehicle shock, the response of the engine startup is deteriorated.
Therefore, in this embodiment, the first clutch CL1 is controlled so that, when starting the engine 2 for switching the traveling mode from the first traveling mode to the second traveling mode, both assurance of the response of the engine startup and the suppression of the vehicle shock are achieved. In detail, the controller 20 temporarily reduces the CL1 hydraulic pressure immediately before the engine speed which rose by cranking with the motor 4 coincides with the motor rotational speed, in order to reduce an engaging torque of the first clutch CL1 (a torque which is applied to the first clutch plate 15d and the second clutch plate 15e of the first clutch CL1, and is equivalent to a degree of engagement of the first clutch CL1). Therefore, when the engine speed synchronizes with the motor rotational speed, the transmitting torque of the first clutch CL1 (equivalent to the torque transmitted to the engine 2 from the motor 4 via the first clutch CL1) can be reduced temporarily. As a result, the difference in the torque between the engine 2 and the motor 4 can be compensated in the first clutch CL1 in the slip state where the transmitting torque is reduced, that is, it can be absorbed as a slip torque of the first clutch CL1 so that it becomes possible to suppress the vehicle shock. Further, since such a reduction of the engaging torque of the first clutch CL1 is temporary, the response of the engine startup can be secured.
Next, referring to
First, the case where there is no fast startup demand is described (see the graph G11). From the time t1 until immediately before the time t4 (periods T1, T2, and T3), the controller 20 performs a control similar to
Next, the controller 20 ends the temporary reduction of the CL1 hydraulic pressure at time t5a which is a given period of time after the time t5 at which the engine speed coincides with the motor rotational speed (in other words, at the time t5a at which a state in which the difference between the engine speed and the motor rotational speed is below the given value (a value near 0) has continued for the given period of time. The time t5a is equivalent to a timing at which the difference in the torque between the engine 2 and the motor 4 becomes almost zero. Then, after the time t5a, the controller 20 raises the CL1 hydraulic pressure in order to set the first clutch CL1 to the fully engaged state, and when the first clutch CL1 is set to the fully engaged state, it ends the raising of the CL1 hydraulic pressure and maintains the CL1 hydraulic pressure constant (period T5).
Next, the case where there is the fast startup demand is described (see the graph G12). Here, only the differences from the above-described case where there is no fast startup demand (see the graph G11) are described. When there is the fast startup demand, the controller 20 does not perform the temporary reduction of the CL1 hydraulic pressure down to the third hydraulic pressure P3 for reducing the shock caused when the clutch piston 15c contacts the first clutch plate 15d, such as the case where there is no fast startup demand, in the period T2 immediately after the period T1 during which the CL1 hydraulic pressure is set to the first hydraulic pressure P1 in order to fill up the hydraulic chamber 15a with oil. In detail, when there is the fast startup demand, in the period T2, the controller 20 sets the CL1 hydraulic pressure to the second hydraulic pressure P2 which is applied in the period T3 where it stands by for the raise of the engine speed (i.e., maintains the CL1 hydraulic pressure at the second hydraulic pressure P2 over the periods T2 and T3). Thus, it permits the shock caused when the clutch piston 15c contacts the first clutch plate 15d to some extent, and gives priority to the prompt startup of the engine 2.
Next, referring to
When the engine startup control is started, at Step S101, the controller 20 first acquires a variety of information. In detail, the controller 20 acquires the detection signals at least from the sensors SN1-SN4 described above.
Next, at Step S102, the controller 20 controls the first clutch CL1 in order to fill up the hydraulic chamber 15a of the first clutch CL1 with oil so that the CL1 hydraulic pressure is set to the comparatively large first hydraulic pressure P1 (precharge). Then, the controller 20 proceeds to Step S103 where it determines whether a given period of time passed after setting the CL1 hydraulic pressure to the first hydraulic pressure P1. This given period of time is defined in advance based on a period of time (obtained by an experiment, a simulation, or a given calculation formula) required for filling up the hydraulic chamber 15a of the first clutch CL1 with oil.
As a result of Step S103, if the given period of time passed (Step S103: Yes), the controller 20 proceeds to Step S104. On the other hand, if the given period of time has not yet passed (Step S103: No), the controller 20 returns to Step S102. In this case, the controller 20 maintains the CL1 hydraulic pressure at the first hydraulic pressure P1 by repeating Steps S102 and S103 until the given period of time passes.
Next, at Step S104, the controller 20 determines whether there is the fast startup demand of the engine 2. If the accelerator opening detected by the accelerator opening sensor SN3 is above the given value, or if the slope angle of the road surface detected by the slope sensor SN4 is above the given value, the controller 20 determines that there is the fast startup demand (Step S104: Yes), and proceeds to Step S105. On the other hand, if there is no such fast startup demand (Step S104: No), the controller 20 proceeds to Step S106.
If there is no fast startup demand (Step S104: No), the controller 20 controls the first clutch CL1 at Step S106 to set the CL1 hydraulic pressure to the third hydraulic pressure P3 which is greatly reduced from the first hydraulic pressure P1, in order to reduce the shock caused when the clutch piston 15c contacts the first clutch plate 15d. Then, the controller 20 proceeds to Step S107, where it determines whether a given period of time passed after the CL1 hydraulic pressure is set to the third hydraulic pressure P3. This given period of time is defined in advance based on a period of time (obtained by an experiment, a simulation, or a given calculation formula) after the hydraulic chamber 15a of the first clutch CL1 is filled up with oil until the clutch piston 15c contacts the first clutch plate 15d.
As a result of Step S107, if the given period of time passed (Step S107: Yes), the controller 20 proceeds to Step S105. On the other hand, if the given period of time has not yet passed (Step S107: No), the controller 20 returns to Step S106. In this case, the controller 20 maintains the CL1 hydraulic pressure at the third hydraulic pressure P3 by repeating Steps S106 and S107 until the given period of time passes.
On the other hand, when there is the fast startup demand (Step S104: Yes), in order to give priority to the prompt startup of the engine 2, the controller 20 controls the first clutch CL1 at Step S105 to set the CL1 hydraulic pressure to the second hydraulic pressure P2 larger than the third hydraulic pressure P3, without setting the CL1 hydraulic pressure to the third hydraulic pressure P3. Further, if there is no fast startup demand, the controller 20 controls the first clutch CL1 to change the CL1 hydraulic pressure to the second hydraulic pressure P2 from the third hydraulic pressure P3 after maintaining the CL1 hydraulic pressure at the third hydraulic pressure P3 for the given period of time (Step S107: Yes to Step S105).
Thus, when the CL1 hydraulic pressure is set to the second hydraulic pressure P2, the first clutch CL1 becomes in the state where the torque of the motor 4 can be transmitted to the engine 2 (in detail, the slip state). Here, the controller 20 controls the engine 2 and the motor 4 to raise the engine speed by cranking with the motor 4. In this way, the controller 20 waits for the engine speed to rise, while maintaining the CL1 hydraulic pressure at the second hydraulic pressure P2.
Next, the controller 20 proceeds to Step S108 after the above-described Step S105, where it determines whether the difference between the engine speed and the motor rotational speed (rotational speed difference) becomes below the given value. Here, the controller 20 determines a situation where the engine speed which rose by cranking with the motor 4 is about to reach the motor rotational speed. If the rotational speed difference becomes below the given value (Step S108: Yes), the controller 20 determines that the engine speed is about to reach the motor rotational speed, and proceeds to Step S109, where it controls the first clutch CL1 to temporarily reduce the CL1 hydraulic pressure down to the fourth hydraulic pressure P4. Thus, the vehicle shock caused by the difference in the torque during the rotation synchronization between the engine 2 and the motor 4 is suppressed. From such viewpoints, the given value for determining the rotational speed difference at Step S108 is defined in advance based on the timing before the engine speed reaches the motor rotational speed, at which the temporary reduction of the CL1 hydraulic pressure is to be started in order to securely suppress such a vehicle shock. Further, as for the fourth hydraulic pressure P4 to which the CL1 hydraulic pressure is temporarily reduced, the CL1 hydraulic pressure which does not deteriorate the response of engine startup while suppressing such a vehicle shock is applied. Fundamentally, the fourth hydraulic pressure P4 is set at least lower than the second hydraulic pressure P2 and higher than the third hydraulic pressure P3. The given value and the fourth hydraulic pressure P4 are defined based on an experiment, a simulation, a given calculation formula, etc.
On the other hand, if the rotational speed difference does not become below the given value (Step S108: No), the controller 20 returns to Step S105. In this case, the controller 20 maintains the CL1 hydraulic pressure at the second hydraulic pressure P2 by repeating Steps S105 and S108, until the rotational speed difference becomes below the given value.
Next, after the above-described Step S109, the controller 20 proceeds to Step S110, where it determines whether the state where the difference between the engine speed and the motor rotational speed (rotational speed difference) is below the given value (near 0) continues for the given period of time. Here, the controller 20 determines the situation where the difference in the torque between the engine 2 and the motor 4 becomes almost zero. Therefore, the given period of time used at Step S110 is defined in advance based on a period of time (obtained by an experiment, a simulation, or a given calculation formula) from when the engine speed almost coincides with the motor rotational speed until the difference in the torque between the engine 2 and the motor 4 is almost eliminated.
As a result of Step S110, if the state where the rotational speed difference is below the given value continued for the given period of time (Step S110: Yes), the controller 20 proceeds to Step S111. On the other hand, if the state where the rotational speed difference is below the given value has not yet continued for the given period of time (Step S110: No), the controller 20 returns to Step S109. In this case, the controller 20 maintains the CL1 hydraulic pressure at the fourth hydraulic pressure P4 until the state where the rotational speed difference is below the given value continues for the given period of time, by repeating Steps S109 and S110.
Next, at Step S111, in order to set the first clutch CL1 to the fully engaged state, the controller 20 ends the temporary reduction of the CL1 hydraulic pressure to the fourth hydraulic pressure P4 and controls the first clutch CL1 to gradually increase the CL1 hydraulic pressure. Then, when the CL1 hydraulic pressure reaches a final target hydraulic pressure corresponding to the fully engaged state of the first clutch CL1, the controller 20 proceeds to Step S112, where it ends the gradual increase of the CL1 hydraulic pressure and maintains the CL1 hydraulic pressure constant. Then, the controller 20 ends the engine startup control.
Next, operation and effects of the method of controlling the hybrid vehicle and the control system according to this embodiment of the present disclosure are described.
According to this embodiment, when starting the engine 2 in order to switch the traveling mode from the first traveling mode to the second traveling mode, the controller 20 temporarily reduces the hydraulic pressure applied to the first clutch CL1 so that the engaging torque of the first clutch CL1 is reduced, after the engine speed is raised by cranking with the motor 4 and before the engine speed coincides with the motor rotational speed. Therefore, when the engine speed synchronizes with the motor rotational speed, the transmitting torque of the first clutch CL1 can be reduced. As a result, the difference in the torque between the engine 2 and the motor 4 can be compensated by the first clutch CL1 in the slip state where the transmitting torque is reduced. That is, it can be compensated as the slip torque of the first clutch CL1, and the vehicle shock caused by the difference in the torque can be suppressed. Further, since such a reduction of the engaging torque of the first clutch CL1 is temporary, the response of engine startup can be secured. Therefore, according to this embodiment, when starting the engine 2 in order to switch the traveling mode from the first traveling mode to the second traveling mode, the vehicle shock can be suppressed, while securing the response of the engine startup.
According to this embodiment, since the controller 20 starts the temporary reduction of the engaging torque of the first clutch CL1 when the difference between the engine speed and the motor rotational speed becomes below the given value, it can effectively suppress the vehicle shock caused by the difference in the torque between the engine 2 and the motor 4 during the rotation synchronization.
According to this embodiment, the controller 20 ends the temporary reduction of the engaging torque of the first clutch CL1 when the state where the difference between the engine speed and the motor rotational speed is below the given value continues for the given period of time, and starts the raise of the engaging torque for setting the first clutch CL1 to the fully engaged state. Therefore, at the timing when the difference in the torque between the engine 2 and the motor 4 is eliminated, it can securely end the temporary reduction of the engaging torque, and it becomes possible to effectively achieve both the assurance of the response of the engine startup and the suppression of the vehicle shock.
Further, according to this embodiment, the controller 20 applies the first hydraulic pressure P1 to the first clutch CL1 during the engine startup control so that the hydraulic chamber 15a of the first clutch CL1 is filled up with oil, and then continues applying to the first clutch CL1 the second hydraulic pressure P2 lower than the first hydraulic pressure P1. Therefore, the first clutch CL1 in the disengaged state can be shifted to the engaged state, and the engine speed can be raised securely by cranking with the motor 4.
Further, according to this embodiment, when there is no fast startup demand of the engine 2, the controller 20 temporarily reduces the hydraulic pressure applied to the first clutch CL1 down to the third hydraulic pressure P3 lower than the second hydraulic pressure P2, after the first hydraulic pressure P1 is applied and before the second hydraulic pressure P2 is applied. Therefore, the shock which occurs when the first clutch CL1 in the disengaged state begins to engage can be reduced. On the other hand, when there is the fast startup demand of the engine 2, the controller 20 continues applying the second hydraulic pressure P2 to the first clutch CL1 after applying the first hydraulic pressure P1, without temporarily reducing the hydraulic pressure applied to the first clutch CL1 down to the third hydraulic pressure P3. Therefore, it can give priority to the prompt startup of the engine 2.
Further, according to this embodiment, the controller 20 sets the hydraulic pressure (fourth hydraulic pressure P4) applied to the first clutch CL1 in order to temporarily reduce the engaging torque of the first clutch CL1, to the pressure lower than the second hydraulic pressure P2 and higher than the third hydraulic pressure P3. Therefore, it becomes possible to effectively achieve both the assurance of the response of the engine startup and the suppression of the vehicle shock.
It should be understood that the embodiments herein are illustrative and not restrictive, since the scope of the invention is defined by the appended claims rather than by the description preceding them, and all changes that fall within metes and bounds of the claims, or equivalence of such metes and bounds thereof, are therefore intended to be embraced by the claims.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2022-074192 | Apr 2022 | JP | national |
