Patent ID: 12233850

Throughout the drawings and the detailed description, the same reference numerals refer to the same elements. The drawings may not be to scale, and the relative size, proportions, and depiction of elements in the drawings may be exaggerated for clarity, illustration, and convenience.

DETAILED DESCRIPTION

This description provides a comprehensive understanding of the methods, apparatuses, and/or systems described. Modifications and equivalents of the methods, apparatuses, and/or systems described are apparent to one of ordinary skill in the art. Sequences of operations are exemplary, and may be changed as apparent to one of ordinary skill in the art, with the exception of operations necessarily occurring in a certain order. Descriptions of functions and constructions that are well known to one of ordinary skill in the art may be omitted.

Exemplary embodiments may have different forms, and are not limited to the examples described. However, the examples described are thorough and complete, and convey the full scope of the disclosure to one of ordinary skill in the art.

In this specification, “at least one of A and B” should be understood to mean “only A, only B, or both A and B.”

A controller100for a hybrid electric vehicle500according to an embodiment will now be described with reference toFIGS.1to6.

FIG.1shows the schematic configuration of the hybrid electric vehicle500including the controller100, which is an example of a controller for a hybrid electric vehicle. The hybrid electric vehicle500will be hereinafter simply referred to as the vehicle500.

Configuration of Vehicle

The vehicle500includes an engine10and a motor generator30as a power source. The vehicle500further includes a clutch20between the engine10and the motor generator30on a torque transmission path. Torque output from the engine10or the motor generator30is transmitted to driven wheels65through a transmission40and a differential60. Torque input to the transmission40from the power source is referred to as a system shaft torque.

The engine10includes fuel injection valves12, which inject fuel, and cylinders. The engine10further includes an intake passage13, which is connected to the cylinders, and an electronic throttle valve14, which regulates the amount of air flowing through the intake passage13. In the cylinders, air-fuel mixture containing the air drawn in from the intake passage13and the fuel injected from the fuel injection valves12is burned. Burning the air-fuel mixture produces exhaust gas that is discharged from the cylinders to an exhaust passage16. The exhaust passage16includes a catalyst17that purifies exhaust gas.

The engine10includes a crankshaft18. The crankshaft18is an output shaft of the engine10. The crankshaft18is rotated in a predetermined direction by the force obtained by burning the air-fuel mixture in the cylinders. That is, an engine torque Te, which is an output torque of the engine10, is output from the crankshaft18.

The clutch20is coupled to the crankshaft18of the engine10. In a state in which the clutch20is engaged, torque can be transmitted between the engine10and the motor generator30. In a state in which the clutch20is disengaged, torque cannot be transmitted between the engine10and the motor generator30.

In the present embodiment, the engagement of the clutch20includes complete engagement and slip engagement. The complete engagement produces a larger engagement force of the clutch20than the slip engagement. As the engagement force of the clutch20becomes larger, a torque capacity Tc of the clutch20becomes larger. Thus, when the clutch20is completely engaged, the efficiency of transmitting torque between the engine10and the motor generator30is relatively high. The slip engagement of the clutch20produces a smaller torque capacity Tc of the clutch20than the complete engagement of the clutch20. Thus, when the clutch20is slip-engaged, the efficiency of transmitting torque between the engine10and the motor generator30is relatively low although the torque is transmitted. That is, the clutch20may be slip-engaged to intentionally lower the efficiency of transmitting torque between the engine10and the motor generator30.

The clutch20is a hydraulically-driven clutch. In such a clutch20, as a clutch hydraulic pressure Pc, which is the hydraulic pressure supplied to the clutch20, becomes higher, the engagement force of the clutch20becomes larger. That is, adjusting the clutch hydraulic pressure Pc allows for slip engagement of the clutch20or complete engagement of the clutch20. Since the torque capacity Tc of the clutch20becomes larger as the clutch hydraulic pressure Pc becomes higher, the efficiency of transmitting torque between the engine10and the motor generator30becomes higher. That is, in a state in which the clutch20is engaged, adjusting the clutch hydraulic pressure Pc changes the torque capacity Tc and consequently adjusts the efficiency of transmitting torque of the clutch20.

The motor generator30includes a driving shaft31coupled to the clutch20. That is, when the motor generator30functions as an electric motor, the driving shaft31is rotated by the electric power supplied from a battery via an inverter. When the motor generator30functions as a power generator, regenerative electric power corresponding to the rotation of the driving shaft31is generated in the motor generator30so that the regenerative electric power is supplied to the battery via the inverter. The output torque of the motor generator30is referred to as a motor torque Tm. The engine torque Te includes torque input to the driving shaft31through the clutch20from the crankshaft18and the motor torque Tm. The sum of that torque and the motor torque Tm is referred to as a system shaft torque Tsys.

The transmission40includes a torque converter41and a transmission mechanism46. The torque converter41includes a pump impeller42, a turbine impeller43, and a lock-up clutch44. The pump impeller42is coupled to the driving shaft31of the motor generator30. The turbine impeller43is coupled to the transmission mechanism46. When the lock-up clutch44is disengaged, the hydraulic oil in the torque converter41causes torque to be transmitted from the pump impeller42to the turbine impeller43. When the lock-up clutch44is engaged, torque is directly transmitted from the pump impeller42to the turbine impeller43without relying on the hydraulic oil.

The transmission mechanism46is, for example, a multi-speed transmission mechanism. The transmission mechanism46includes an input shaft47, to which torque is input from the torque converter41, and an output shaft48, which outputs torque. The input shaft47is coupled to the turbine impeller43of the torque converter41. The transmission mechanism46decelerates the torque input from the input shaft47and then outputs the decelerated torque from the output shaft48to the differential60.

In the present embodiment, the vehicle500includes an electric pump80and a hydraulic control circuit90. The electric pump80pressurizes hydraulic oil and supplies the oil to the hydraulic control circuit90. The hydraulic control circuit90supplies the transmission mechanism46, the torque converter41, and the clutch20with the high-pressure hydraulic oil that has been supplied from the electric pump80. For example, the hydraulic control circuit90includes oil control valves. By controlling the oil control valves, the supplying and discharging of hydraulic oil to and from a target to be supplied with hydraulic oil is controlled, and the hydraulic pressure of hydraulic oil supplied to a supply target is controlled. That is, the hydraulic control circuit90is configured to adjust the clutch hydraulic pressure Pc.

Detection System of Vehicle

The detection system of the vehicle500includes sensors that output detection signals corresponding to detection results to the controller100. That is, the vehicle500includes a crank angle sensor111, an air flow meter112, an accelerator open degree sensor113, a motor angle sensor114, an input shaft sensor115, and an oil temperature sensor116. The crank angle sensor111outputs a detection signal corresponding to an engine rotation speed Ne, which is the rotation speed of the crankshaft18. The air flow meter112detects an intake air amount GA, which is the amount of air flowing through the intake passage13, and outputs a detection signal corresponding to the detection result. The accelerator open degree sensor113detects an accelerator open degree ACCP, which is the operation amount of the accelerator pedal, and outputs a detection signal corresponding to the detection result. The motor angle sensor114outputs a detection signal corresponding to a motor rotation speed Nm, which is the rotation speed of the driving shaft31of the motor generator30. The input shaft sensor115outputs a detection signal corresponding to an input shaft rotation speed Nat, which is the rotation speed of the input shaft47of the transmission mechanism46. The oil temperature sensor116detects an oil temperature TOIL, which is the temperature of hydraulic oil discharged out of the electric pump80, and outputs a detection signal corresponding to the detection result.

Controller

The controller100includes a CPU101, a ROM102, and a RAM103. The ROM102stores various control programs executed by the CPU101. The RAM103stores the results of calculation performed by the CPU101. The CPU101executes the control programs so as to control the engine10and the motor generator30. Further, the CPU101controls the electric pump80and the hydraulic control circuit90so as to control the clutch20and the transmission40. Thus, the CPU101corresponds to an execution device in the present embodiment.

The CPU101calculates the engine rotation speed Ne based on a detection signal Scr of the crank angle sensor111. The CPU101calculates an engine load factor KL based on the engine rotation speed Ne and the intake air amount GA.

The CPU101obtains a torque request value TsR, which is a request value of torque for the power source, based on the accelerator open degree ACCP. The torque request value TsR refers to a request value of torque input to the transmission40from the driving shaft31. For example, the CPU101sets the torque request value TsR to be larger as the accelerator open degree ACCP becomes larger. The CPU101controls the power source (i.e., the engine10and the motor generator30) based on the torque request value TsR.

Traveling modes of the vehicle500include an electric traveling mode and a hybrid traveling mode. Of the engine10and the motor generator30, the electric traveling mode causes only the motor generator30to output torque. Thus, when the electric traveling mode is selected, the CPU101controls the motor generator30based on the torque request value TsR. When the electric traveling mode is selected, the engine10is not operated and thus the CPU101causes the clutch20to be disengaged.

The hybrid traveling mode causes both the engine10and the motor generator30to output torque. When the engine10is operated, the CPU101controls the engine10and the motor generator30based on the torque request value TsR with the clutch20engaged. When the hybrid traveling mode is selected, the CPU101may intermittently stop the operation of the engine10. In this case, the CPU101controls the motor generator30based on the torque request value TsR with the clutch20disengaged.

When the operation of the engine10is stopped under a condition in which the hybrid traveling mode is selected, the CPU101may cause the engine10to start operating after the torque request value TsR is increased by, for example, an increase in the accelerator open degree ACCP. In this case, the CPU101engages the clutch20in addition to starting the engine10. In the present embodiment, when starting the engine10, the CPU101selects a first starting process or a second starting process and starts the engine10by executing the selected process.

The first starting process will now be described with reference toFIG.2.

In the first starting process, when the starting of the engine10is requested at time t11, the clutch20is engaged. In this case, the clutch20is slip-engaged. The CPU101controls the electric pump80and the hydraulic control circuit90so as to increase the clutch hydraulic pressure Pc, thereby increasing the engagement force of the clutch20. As the engagement force becomes larger, the torque capacity Tc of the clutch20becomes larger as shown in section (A) ofFIG.2. When the clutch20is slip-engaged, the motor torque Tm is input to the crankshaft18. This causes the motor generator30to crank the engine10. Thus, the engine rotation speed Ne becomes higher as shown in section (B) ofFIG.2. Then, the engine rotation speed Ne increases to the motor rotation speed Nm. This increases the clutch hydraulic pressure Pc and thus increases the torque capacity Tc of the clutch20. As a result, the clutch20is completely engaged.

The time at which the engine rotation speed Ne becomes substantially equal to the motor rotation speed Nm is referred to as a synchronization time of the clutch20. Combustion in the engine10is started at the synchronization time of the clutch20or at time t12, which is slightly later than the synchronization time. That is, combustion in the engine10is started after the clutch20is completely engaged.

The second starting process will now be described with reference toFIG.3.

In the second starting process, when the starting of the engine10is requested at time t21, the clutch20is engaged. In this case, the clutch20is slip-engaged. The CPU101controls the electric pump80and the hydraulic control circuit90so as to increase the clutch hydraulic pressure Pc, thereby increasing the engagement force of the clutch20. As the engagement force becomes larger, the torque capacity Tc of the clutch20becomes larger as shown in section (A) ofFIG.3. When the clutch20is slip-engaged, the motor torque Tm is input to the crankshaft18. This causes the motor generator30to crank the engine10. Thus, the engine rotation speed Ne becomes higher as shown in section (B) ofFIG.3.

The second starting process is different from the first starting process in that combustion in the engine10is started at time t22, which is before the engine rotation speed Ne reaches the motor rotation speed Nm. In the present embodiment, combustion in the engine10is started at a time when the crankshaft18is rotated once or at a time when the crankshaft18is rotated twice by cranking performed by the motor generator30.

Thus, subsequent to time t22, the engine rotation speed Ne is abruptly increased both by the cranking performed by the motor generator30and by an increase in the engine torque Te. Upon start of the engine10, the torque capacity Tc of the clutch20is adjusted before the engine rotation speed Ne reaches the motor rotation speed Nm. That is, the CPU101controls the hydraulic control circuit90so as to decrease the clutch hydraulic pressure Pc. As a result, the torque capacity Tc of the clutch20decreases from time t23. When the torque capacity Tc decreases, the torque transmitted to the driving shaft31through the clutch20from the crankshaft18becomes smaller. This lowers the torque transmission efficiency of the clutch20. Thus, during the period from when combustion is started in the engine10to when the engine rotation speed Ne reaches the motor rotation speed Nm, the torque capacity Tc of the clutch20is adjusted so as to adjust the engine torque Te transmitted to the driving shaft31. This limits an abrupt increase in the motor rotation speed Nm.

At time t24, when the engine rotation speed Ne becomes substantially equal to the motor rotation speed Nm, the CPU101controls the hydraulic control circuit90so as to increase the clutch hydraulic pressure Pc. As a result, the torque capacity Tc of the clutch20increases as shown in section (B) ofFIG.3. This causes the clutch20to be completely engaged and thus maximizes the torque transmission efficiency of the clutch20.

Processes Executed when Starting Engine

The processes executed by the CPU101when starting the engine10will now be described with reference toFIGS.4to6.

As shown inFIG.4, the CPU101executes a torque capacity estimation process M11and a turbine rotation speed estimation process M13. Further, the CPU101executes a first determination value candidate setting process M15, a second determination value candidate setting process M17, a setting process M19, and a provisional selection process M21. Furthermore, the CPU101executes an increase amount determination value setting process M23, a final determination process M25, and a starting process M27.

Torque Capacity Estimation Process

The torque capacity estimation process M11is a process that obtains an estimated torque capacity Tce, which is an estimated value of the torque capacity Tc of the clutch20. The estimated torque capacity Tce refers to the torque capacity Tc obtained at the synchronization time of the clutch20if the engine10is started with the second starting process. When starting the engine10with the second starting process, the CPU101adjusts a command value of the clutch hydraulic pressure Pc in a predefined manner. The manner of response of an actual value of the clutch hydraulic pressure Pc to the variations in the command value can be estimated to a certain extent from the motor rotation speed Nm, the system shaft torque Tsys, and the input shaft rotation speed Nat.

Accordingly, in the torque capacity estimation process M11, the CPU101obtains the estimated torque capacity Tce based on the motor rotation speed Nm, the system shaft torque Tsys, and the input shaft rotation speed Nat. For example, it is estimated that the clutch20synchronizes later as the motor rotation speed Nm becomes higher. Thus, as the motor rotation speed Nm becomes higher, the CPU101sets the estimated torque capacity Tce to be smaller. Further, for example, it is estimated that the clutch20synchronizes later as the system shaft torque Tsys becomes larger. Thus, as the system shaft torque Tsys becomes larger, the CPU101sets the estimated torque capacity Tce to be smaller. Furthermore, for example, it is estimated that the clutch20synchronizes later as the input shaft rotation speed Nat becomes higher. Thus, as the input shaft rotation speed Nat becomes higher, the CPU101sets the estimated torque capacity Tee to be smaller.

When the engine10is not operating, the clutch20is disengaged and thus the CPU101obtains the motor torque Tm as the system shaft torque Tsys.

Turbine Rotation Speed Estimation Process

The turbine rotation speed estimation process M13is a process that obtains an estimated turbine rotation speed Nte, which is an estimated value of the rotation speed of the turbine impeller43. The rotation speed of the turbine impeller43is referred to as the turbine rotation speed. The estimated turbine rotation speed Nte refers to the turbine rotation speed obtained at the synchronization time of the clutch20if the engine10is started with the second starting process. Since the turbine impeller43of the torque converter41is coupled to the input shaft47of the transmission mechanism46, the turbine rotation speed is substantially equal to the input shaft rotation speed Nat. That is, the estimated turbine rotation speed Nte is the estimated value of the input shaft rotation speed Nat.

In the turbine rotation speed estimation process M13, the CPU101obtains, as the estimated turbine rotation speed Nte, a value obtained by subtracting a deceleration correction value ΔNat from the input shaft rotation speed Nat. The deceleration correction value ΔNat is defined from the particulars of the driving system of the vehicle500.

First Determination Value Candidate Setting Process

The first determination value candidate setting process M15refers to a first map MAP1to obtain a first shaft torque determination value TsysTh1, which is one of the candidate values of a shaft torque determination value. The first map MAP1shows the relationship between the estimated turbine rotation speed Nte and the system shaft torque Tsys. In the first map MAP1, when the estimated turbine rotation speed Nte is less than a first reference rotation speed Nte1, the system shaft torque Tsys corresponding to the estimated turbine rotation speed Nte has a positive value. Specifically, when the estimated turbine rotation speed Nte is less than the first reference rotation speed Nte1, the system shaft torque Tsys corresponding to the estimated turbine rotation speed Nte becomes larger as the estimated turbine rotation speed Nte becomes lower. When the estimated turbine rotation speed Nte is greater than or equal to the first reference rotation speed Nte1, the system shaft torque Tsys corresponding to the estimated turbine rotation speed Nte has a negative value. Specifically, when the estimated turbine rotation speed Nte is greater than or equal to the first reference rotation speed Nte1, the absolute value of the system shaft torque Tsys corresponding to the estimated turbine rotation speed Nte becomes larger as the estimated turbine rotation speed Nte becomes higher.

In the first determination value candidate setting process M15, the CPU101refers to the first map MAP1to obtain the system shaft torque Tsys corresponding to the estimated turbine rotation speed Nte. Then, the CPU101sets, as the first shaft torque determination value TsysTh1, the system shaft torque Tsys obtained with reference to the first map MAP1.

As will be described in detail later, the first map MAP1is used when the estimated torque capacity Tce is less than a reference torque capacity Tcb. When the system shaft torque Tsys is greater than or equal to the first shaft torque determination value TsysTh1set with reference to the first map MAP1in a case in which the estimated torque capacity Tce is less than the reference torque capacity Tcb, the occurrence of vibration caused by starting the engine10is limited even if the engine10is started with the second starting process.

Second Determination Value Candidate Setting Process

The second determination value candidate setting process M17refers to a second map MAP2to obtain a second shaft torque determination value TsysTh2, which is one of the candidate values of the shaft torque determination value. The second map MAP2shows the relationship between the estimated turbine rotation speed Nte and the system shaft torque Tsys. In the second map MAP2, when the estimated turbine rotation speed Nte is less than a second reference rotation speed Nte2, the system shaft torque Tsys corresponding to the estimated turbine rotation speed Nte has a positive value. Specifically, when the estimated turbine rotation speed Nte is less than the second reference rotation speed Nte2, the system shaft torque Tsys corresponding to the estimated turbine rotation speed Nte becomes larger as the estimated turbine rotation speed Nte becomes lower. When the estimated turbine rotation speed Nte is greater than or equal to the second reference rotation speed Nte2, the system shaft torque Tsys corresponding to the estimated turbine rotation speed Nte has a negative value. Specifically, when the estimated turbine rotation speed Nte is greater than or equal to the second reference rotation speed Nte2, the absolute value of the system shaft torque Tsys corresponding to the estimated turbine rotation speed Nte becomes larger as the estimated turbine rotation speed Nte becomes higher. The value of the second reference rotation speed Nte2is set to be greater than that of the first reference rotation speed Nte1.

In the second determination value candidate setting process M17, the CPU101refers to the second map MAP2to obtain the system shaft torque Tsys corresponding to the estimated turbine rotation speed Nte. Then, the CPU101sets, as the second shaft torque determination value TsysTh2, the system shaft torque Tsys obtained with reference to the second map MAP2.

As will be described in detail later, the second map MAP2is used when the estimated torque capacity Tce is greater than or equal to the reference torque capacity Tcb. When the system shaft torque Tsys is greater than or equal to the second shaft torque determination value TsysTh2set with reference to the second map MAP2in a case in which the estimated torque capacity Tce is greater than or equal to the reference torque capacity Tcb, the occurrence of vibration caused by starting the engine10is limited even if the engine10is started with the second starting process.

The first shaft torque determination value TsysTh1is set by the first determination value candidate setting process M15. The second shaft torque determination value TsysTh2is set by the second determination value candidate setting process M17. The first shaft torque determination value TsysTh1and the second shaft torque determination value TsysTh2are both torques corresponding to the estimated turbine rotation speed Nte. In the present embodiment, the first map MAP1and the second map MAP2are created such that the second shaft torque determination value TsysTh2is greater than the first shaft torque determination value TsysTh1. The broken line in the graph illustrating the second map MAP2indicates the relationship between the estimated turbine rotation speed Nte and the system shaft torque Tsys in the first map MAP1.

Setting Process

The setting process M19is a process that sets one of the first shaft torque determination value TsysTh1and the second shaft torque determination value TsysTh2as a shaft torque determination value TsysTh. In the setting process M19, the CPU101sets the shaft torque determination value TsysTh based on the estimated torque capacity Tce. Specifically, when the estimated torque capacity Tce is less than the reference torque capacity Tcb, the CPU101sets the first shaft torque determination value TsysTh1as the shaft torque determination value TsysTh. When the estimated torque capacity Tce is greater than or equal to the reference torque capacity Tcb, the CPU101sets the second shaft torque determination value TsysTh2as the shaft torque determination value TsysTh. Thus, the shaft torque determination value TsysTh is set to be larger when the estimated torque capacity Tce is relatively large than when the estimated torque capacity Tce is relatively small.

Provisional Selection Process

The provisional selection process M21is a process that provisionally selects one of the first starting process and the second starting process based on the shaft torque determination value TsysTh and the system shaft torque Tsys. In the provisional selection process M21, when the system shaft torque Tsys is less than the shaft torque determination value TsysTh, the CPU101provisionally selects the first starting process. When the system shaft torque Tsys is greater than or equal to the shaft torque determination value TsysTh, the CPU101selects the second starting process.

Increase Amount Determination Value Setting Process

The increase amount determination value setting process M23is a process that sets an increase amount determination value ΔTsRTh, which will be described later. In the increase amount determination value setting process M23, the CPU101sets the increase amount determination value ΔTsRTh based on the estimated torque capacity Tce, the oil temperature TOIL, and a gear position Z that is selected by the transmission mechanism46. In the present embodiment, the CPU101sets, as the increase amount determination value ΔTsRTh, a value obtained by correcting a reference increase amount determination value ΔTsRThb based on the estimated torque capacity Tce, the oil temperature TOIL, and the gear position Z. The reference increase amount determination value ΔTsRThb is a reference value of the increase amount determination value ΔTsRTh.

The CPU101sets a first correction gain G1to a smaller value as the estimated torque capacity Tce becomes smaller. The CPU101sets a second correction gain G2to a smaller value as the oil temperature TOIL becomes higher. The CPU101sets a third correction gain G3to a smaller value as the gear position Z selected by the transmission mechanism46becomes higher. The correction gains G1, G2, G3are each set to a value greater than 0 and less than or equal to 1. The CPU101sets the increase amount determination value ΔTsRTh to a product of the reference increase amount determination value ΔTsRThb, the first correction gain G1, the second correction gain G2, and the third correction gain G3.

Final Determination Process

The final determination process M25is a process that finally determines the starting process of the engine10when the starting of the engine10is actually requested.

The final determination process M25will now be described with reference toFIG.5. The CPU101repeatedly executes the final determination process M25in a predetermined control cycle.

In step S11, the CPU101determines whether a start request for the engine10has been made. In a case in which the start request has not been made (S11: NO), the CPU101temporarily ends the final determination process M25. In a case in which the start request has been made (S11: YES), the CPU101advances the process to step S13. In step S13, the CPU101determines whether the first starting process was provisionally selected in the provisional selection process M21. In a case in which the first starting process was provisionally selected (S13: YES), the CPU101advances the process to step S15. In a case in which the second starting process was provisionally selected (S13: NO), the CPU101advances the process to step S19.

In step S15, the CPU101determines whether the motor torque Tm is excessive. In the present embodiment, the CPU101obtains a start-time motor torque maximum value, which is the maximum value of the motor torque Tm obtained when the engine10is started. More specifically, the CPU101uses the torque request value TsR, which is based on the accelerator open degree ACCP, to obtain an estimated value of the system shaft torque used when electric power is most needed to start the engine10. Subsequently, the CPU101obtains, as the start-time motor torque maximum value, the sum of the estimated value of the system shaft torque and a reaction torque of a cranking torque. When the motor generator30can output the start-time motor torque maximum value, the CPU101determines that the motor torque Tm is excessive. When the motor generator30cannot output the start-time motor torque maximum value, the CPU101determines that the motor torque Tm is not excessive. When determining that the motor torque Tm is excessive (S15: YES), the CPU101advances the process to step S21. When determining that the motor torque Tm is not excessive (S15: NO), the CPU101advances the process to step S17.

In step S17, the CPU101determines whether an increase amount ΔTsR of the torque request value TsR is greater than or equal to the increase amount determination value ΔTsRTh. When the starting of the engine10is requested under a condition in which the driver of the vehicle500is operating the accelerator pedal, the CPU101refers to an increase amount of the accelerator open degree ACCP to determine whether the increase amount ΔTsR of the torque request value is greater than or equal to the increase amount determination value ΔTsRTh. For example, the CPU101refers to an increase amount ΔACCP of the accelerator open degree ACCP in a predetermined period to determine whether the increase amount ΔTsR of the torque request value TsR is greater than or equal to the increase amount determination value ΔTsRTh.

As shown inFIG.6, the CPU101obtains a current value ACCP1of the accelerator open degree ACCP and a reference accelerator open degree ACCPb. The reference accelerator open degree ACCPb is an accelerator open degree ACCP at a time prior to the current time by a predetermined time TA. The predetermined time TA is the length of a time of the above predetermined period. The CPU101obtains, as the increase amount ΔACCP of the accelerator open degree in the predetermined period, a value obtained by subtracting the reference accelerator open degree ACCPb from the current value ACCP1of the accelerator open degree. When the increase amount ΔACCP of the accelerator open degree is greater than or equal to an open degree increase amount determination value ΔACCPth, the CPU101determines that the increase amount ΔTsR of the torque request value is greater than or equal to the increase amount determination value ΔTsRTh. When the increase amount ΔACCP of the accelerator open degree is less than the open degree increase amount determination value ΔACCPth, the CPU101determines that the increase amount ΔTsR of the torque request value is less than the increase amount determination value ΔTsRTh.

In the present embodiment, the increase amount determination value ΔTsRTh varies depending on the estimated torque capacity Tce, the oil temperature TOIL, and the gear position Z. Thus, as the increase amount determination value ΔTsRTh becomes larger, the open degree increase amount determination value ΔACCPth is set to be larger.

Referring back toFIG.5, when determining that the increase amount ΔTsR of the torque request value is greater than or equal to the increase amount determination value ΔTsRTh (S17: YES), the CPU101advances the process to step S19. When determining that the increase amount ΔTsR of the torque request value is less than the increase amount determination value ΔTsRTh (S17: NO), the CPU101advances the process to step S21.

In step S19, the CPU101determines the second starting process as a process that starts the engine10. Subsequently, the CPU101ends the final determination process M25.

In step S21, the CPU101determines the first starting process as a process that starts the engine10. Subsequently, the CPU101ends the final determination process M25.

Starting Process

The starting process M27is a process that starts the engine10. The CPU101starts the engine10with the starting process determined in the final determination process M25. When the starting process determined in the final determination process M25is the first starting process, the CPU101executes the first starting process as the starting process M27. When the starting process determined in the final determination process M25is the second starting process, the CPU101executes the second starting process as the starting process M27.

Operation and Advantage of Present Embodiment

In a case in which the operation of the engine10is not operating under the condition in which the hybrid traveling mode is selected, the starting of the engine10may be requested when the torque request value TsR is increased by the driver starting to operate the accelerator pedal. The controller100executes the first starting process or the second starting process as a process that starts the engine10.

To start the engine10with the first starting process, as described with reference toFIG.2, the engine rotation speed Ne is increased to the motor rotation speed Nm and then combustion in the engine10is started. Thus, variations in the motor rotation speed Nm resulting from the starting of the engine10are easily limited by the motor generator30or the clutch20. Starting the engine10with the first starting process limits an abrupt change in the motor rotation speed Nm resulting from an abrupt increase in the engine rotation speed Ne. This limits situations in which the vehicle500is vibrated due to the starting of the engine10. However, the combustion in the engine10is not started until the engine rotation speed Ne increases to the motor rotation speed Nm. Thus, the completion of the starting of the engine10is delayed.

To start the engine10with the second starting process, as described with reference toFIG.3, combustion in the engine10is started in a state in which the engine rotation speed Ne is less than the motor rotation speed Nm. Thus, variations in the motor rotation speed Nm resulting from the starting of the engine10are not easily limited by the motor generator30or the clutch20. As a result, the starting of the engine10easily vibrates the vehicle500. However, since the engine10is started before the engine rotation speed Ne reaches the motor rotation speed Nm, the starting of the engine10is completed at a relatively early time.

The reason that the vibration caused by starting the engine10is more likely to occur in the vehicle500when the second starting process is executed than when the first starting process is executed will now be described in detail. Immediately after combustion starts in the engine10(specifically, immediately after first combustion in the engine10), the variations in the engine torque Te and the torque capacity Tc of the clutch20tends to vary an increase rate of the engine rotation speed Ne. If the motor rotation speed Nm is sufficiently high, the variations in the increase rate of the engine rotation speed Ne converge and thus the synchronization time of the clutch20does not vary significantly. If the motor rotation speed Nm is relatively low, the variations in the increase rate of the engine rotation speed Ne does not easily converge and thus the synchronization time of the clutch20tends to vary. The vibration caused by starting the engine10can be reduced using the motor torque Tm. However, there is a response delay of detection of the crank angle sensor111and the motor angle sensor114and a response delay of the motor torque Tm. Thus, the synchronization time of the clutch20needs to be estimated based on the increase rate of the engine rotation speed Ne. In the first starting process, since combustion in the engine10is not performed prior to the synchronization time, the increase rate of the engine rotation speed Ne is relatively low and does not vary significantly. This allows the synchronization time of the clutch20to be estimated accurately. Accordingly, the occurrence of the vibration caused by starting the engine10is limited.

In the second starting process, since the increase rate of the engine rotation speed Ne varies, the synchronization time of the clutch20cannot be estimated accurately. Thus, the torque capacity Tc of the clutch20is temporarily lowered at time t23shown inFIG.3so as to limit the vibration caused by starting the engine10. Nevertheless, when the second starting process is executed with a relatively small motor torque Tm, the clutch20may synchronize at an earlier time than time t23, at which the torque capacity Tc starts to be lowered. In this case, since the torque capacity Tc is lowered later, the starting of the engine10produces vibration.

As the increase amount ΔTsR of the torque request value becomes larger, the acceleration of the vehicle500becomes larger. The occupant of the vehicle500is less likely to feel annoyed by the occurrence of vibration of the vehicle500when the acceleration of the vehicle500is relatively large than when the acceleration of the vehicle500is relatively small. Combustion in the engine10starts at a later time when the engine10is started with the first starting process than when the engine10is started with the second starting process. Thus, whereas the vibration caused by starting the engine10is less likely to increase in the first starting process, the vibration caused by starting the engine10is more likely to increase in the second starting process. In a case in which the increase amount ΔTsR of the torque request value is relatively large, it is desired that the starting of the engine10be completed at an earlier time to quickly increase the engine torque Te.

In the present embodiment, when the engine10is started in a case in which the increase amount ΔTsR of the torque request value is greater than or equal to the increase amount determination value ΔTsRTh, the second starting process is performed to start the engine10. This allows the starting of the engine10to be completed at an earlier time, and makes the occupant less likely to feel annoyed by the vibration of the vehicle500resulting from the starting of the engine10. When the engine10is started in a case in which the increase amount ΔTsR of the torque request value is less than the increase amount determination value ΔTsRTh, the first starting process is performed to start the engine10. In this case, although the completion of the starting of the engine10is delayed, the occurrence of the vibration of the vehicle500resulting from the starting of the engine10is limited.

Accordingly, the controller100makes the occupant less likely to feel annoyed when the engine10is started. while allowing the starting of the engine10to be completed at an earlier time.

The present embodiment further provides the following advantages.

(1) When the increase amount ΔTsR of the torque request value is greater than or equal to the increase amount determination value ΔTsRTh, the second starting process is executed. Thus, the starting of the engine10is completed at a relatively early time. That is, the system shaft torque Tsys becomes able to be increased by the engine torque Te at a relatively early time. This limits a response delay of an increase in the system shaft torque Tsys to the torque request value TsR. When the increase amount ΔTsR of the torque request value is less than the increase amount determination value ΔTsRTh, the increase rate of the system shaft torque Tsys does not have to be increased significantly. Thus, the first starting process is performed to start the engine10. As a result, when there is no request to suddenly accelerate the vehicle500, the occurrence of vibration caused by starting the engine10is limited. Accordingly, when the engine10is started, the occupant is less likely to feel annoyed.

(2) In the present embodiment, at a stage in which the starting of the engine10is not requested, the first or second starting process is provisionally selected as a process that starts the engine10. Specifically, when the system shaft torque Tsys is less than the shaft torque determination value TsysTh, the first starting process is provisionally selected. When the system shaft torque Tsys is greater than or equal to the shaft torque determination value TsysTh, the second starting process is provisionally selected.

When the system shaft torque Tsys is greater than or equal to the shaft torque determination value TsysTh, the motor rotation speed Nm is not easily varied by an abrupt increase in the engine rotation speed Ne. That is, the vibration caused by starting the engine10is less likely to occur in the vehicle500.

When the starting of the engine10is requested with the second starting process provisionally selected, the engine10is started with the second starting process even if the increase amount ΔTsR of the torque request value is less than the increase amount determination value ΔTsRTh. This allows the starting of the engine10to be completed at an earlier time while making the occupant less likely to feel annoyed when the engine10is started. Additionally, the second starting process can be executed more often.

In a case in which the increase amount ΔTsR of the torque request value is less than the increase amount determination value ΔTsRTh when the starting of the engine10is requested with the first starting process provisionally selected, the engine10is started with the first starting process. That is, in a case in which the system shaft torque Tsys is relatively small and the vehicle500is easily vibrated when the engine10is started, the first starting process is executed. Starting the engine10with the first starting process limits the occurrence of vibration of the vehicle500. Accordingly, the occupant is less likely to feel annoyed when the engine10is started.

(3) In a case in which the torque capacity Tc of the clutch20decreases if the second starting process is performed to start the engine10, variations in the engine torque Te are easily attenuated by the clutch20when the engine torque Te increases abruptly. That is, as the torque capacity Tc decreases if the second starting process is performed to start the engine10, the vibration caused by starting the engine10is less likely to occur in the vehicle500. Thus, in the present embodiment, the increase amount determination value ΔTsRTh is set to be smaller as the estimated torque capacity Tce, which is an estimated value of the torque capacity obtained if the engine10is started with the second starting process, becomes smaller. Thus, the second starting process is easily executed when it is estimated that the torque capacity Tc can be lowered by starting the engine10with the second starting process. That is, the present embodiment allows the second starting process to be executed more often while limiting situations in which the vehicle500is vibrated when the engine10is started.

(4) When the oil temperature TOIL is relatively high and thus the viscosity of hydraulic pressure is relatively low, the clutch hydraulic pressure Pc can be easily adjusted. That is, when an instruction is made to lower the clutch hydraulic pressure Pc, the clutch hydraulic pressure Pc starts to decrease quickly. When the oil temperature TOIL is relatively low and thus the viscosity of hydraulic pressure is relatively high, the clutch hydraulic pressure Pc cannot be easily adjusted. That is, when an instruction is made to lower the clutch hydraulic pressure Pc, the clutch hydraulic pressure Pc has a relatively low responsivity. For example, even if an instruction is made to lower the torque capacity Tc of the clutch20at time t23shown inFIG.3, the clutch hydraulic pressure Pc starts to decrease at a later time. This causes the engine rotation speed Ne to increase before the torque capacity Tc actually decreases. As a result, the starting of the engine10tends to cause vibration.

In the present embodiment, as the oil temperature TOIL becomes higher, the increase amount determination value ΔTsRTh is set to be smaller. Thus, when the oil temperature TOIL is relatively high and the responsivity of the clutch hydraulic pressure Pc is relatively high, the second starting process can be easily executed. That is, the present embodiment allows the second starting process to be executed more often while limiting situations in which the vehicle500is vibrated when the engine10is started.

(5) The vibration caused by starting the engine10is more likely to increase when the selected gear position Z of the transmission mechanism46is relatively high than when the selected gear position Z of the transmission mechanism46is relatively low. In the present embodiment, as the gear position Z selected by the transmission mechanism46becomes higher, the increase amount determination value ΔTsRTh is set to be smaller. This allows the second starting process to be executed more easily as the gear position Z becomes higher. That is, the present embodiment allows the second starting process to be executed more often while limiting situations in which the vehicle500is vibrated when the engine10is started.

Modifications

The above embodiment may be modified as follows. The above embodiment and the following modifications can be combined as long as the combined modifications remain technically consistent with each other.

The increase amount determination value ΔTsRTh does not have to be varied in correspondence with the gear position Z selected by the transmission mechanism46. In this case, the vehicle500does not have to include a transmission mechanism.

The increase amount determination value ΔTsRTh does not have to be varied in correspondence with the oil temperature TOIL. In this case, the clutch located between the engine10and the motor generator30may be a clutch that is electromagnetically driven.

The increase amount determination value ΔTsRTh does not have to be varied in correspondence with the estimated torque capacity Tce.

In the above embodiment, the increase amount determination value ΔTsRTh is varied based on the estimated torque capacity Tce, the gear position Z, and the oil temperature TOIL while the length of the predetermined period is fixed. Instead, for example, the increase amount determination value ΔTsRTh may be fixed while the length of the predetermined period may be varied in correspondence with at least one of the parameters: namely, the estimated torque capacity Tce, the gear position Z, and the oil temperature TOIL. For example, as the estimated torque capacity Tce becomes smaller, the length of the predetermined period may be longer. Further, for example, as the gear position Z becomes higher, the length of the predetermined period may be longer. Furthermore, for example, as the oil temperature TOIL becomes higher, the length of the predetermined period may be longer.

When the vehicle500functions to autonomously control the vehicle speed, there is a possibility that a controller different from the controller100requests the vehicle500to accelerate. Examples of the different controller include a controller that controls braking of the vehicle500and a controller that generates various commands related to self-driving. In this case, the controller100obtains the torque request value TsR based on the request or command from the different controller. Then, the controller100uses the increase amount ΔTsR of the torque request value at the request or command to determine whether to execute the first or second starting process.

In the above embodiment, when there is no request for starting the engine10, the provisional selection process M21is executed to provisionally select the first or second starting process as a process that starts the engine10. Instead, the provisional selection process M21does not have to be executed.

For example, when the starting of the engine10is requested, the determination of whether the system shaft torque Tsys is greater than or equal to the shaft torque determination value TsysTh and the determination of whether the increase amount ΔTsR of the torque request value is greater than or equal to the increase amount determination value ΔTsRTh may be made. When at least one of a condition in which the system shaft torque Tsys is greater than or equal to the shaft torque determination value TsysTh and a condition in which the increase amount ΔTsR of the torque request value is greater than or equal to the increase amount determination value ΔTsRTh is satisfied, the second starting process is preferably executed. When neither the condition in which the system shaft torque Tsys is greater than or equal to the shaft torque determination value TsysTh nor the condition in which the increase amount ΔTsR of the torque request value is greater than or equal to the increase amount determination value ΔTsRTh is satisfied, the first starting process is preferably executed.

Further, for example, when the starting of the engine10is requested, the determination of whether the increase amount ΔTsR of the torque request value is greater than or equal to the increase amount determination value ΔTsRTh may be made. Then, when the increase amount ΔTsR of the torque request value is greater than or equal to the increase amount determination value ΔTsRTh, the second starting process may be executed. When the increase amount ΔTsR of the torque request value is less than the increase amount determination value ΔTsRTh, the first starting process is executed. In this case, the process to be executed is determined from the first and second starting processes irrespective of how large the system shaft torque Tsys is.

In the final determination process M25shown inFIG.5, the determination of step S15may be omitted.

There may be multiple first maps MAP1that correspond to the motor rotation speed Nm. In this case, in the first determination value candidate setting process M15, the first map MAP1corresponding to the present motor rotation speed Nm is selected from the first maps MAP1. By referring to the selected first map MAP1, the system shaft torque Tsys corresponding to the estimated turbine rotation speed Nte is set as the first shaft torque determination value TsysTh1.

There may be multiple second maps MAP2that correspond to the motor rotation speed Nm. In this case, in the second determination value candidate setting process M17, the second map MAP2corresponding to the present motor rotation speed Nm is selected from the second maps MAP2. By referring to the selected second map MAP2, the system shaft torque Tsys corresponding to the estimated turbine rotation speed Nte is set as the second shaft torque determination value TsysTh2.

In the above embodiment, the electric pump80and the hydraulic control circuit90, which supply the transmission40with hydraulic oil, serve as a system of supplying the clutch20with hydraulic pressure. Instead, a device that supplies the clutch20with hydraulic pressure may be arranged separately from the electric pump80and the hydraulic control circuit90.

A transmission40that does not include the torque converter41may be used.

A continuously variable transmission mechanism may be used In this case, the increase amount determination value ΔTsRTh is set in correspondence with the gear ratio of the transmission mechanism.

The controller100does not have to include circuitry that includes a CPU and a ROM and that is configured to execute software processing. That is, the controller100may be modified as long as it has any one of the following configurations (a) to (c):

(a) The controller100includes one or more processors that execute various processes in accordance with a computer program. The processor includes a CPU and a memory, such as a RAM and ROM. The memory stores program codes or instructions configured to cause the CPU to execute the processes. The memory, or computer-readable medium, includes any type of medium that is accessible by general-purpose computers and dedicated computers.

(b) The controller100includes one or more dedicated hardware circuits that execute various processes. Examples of the dedicated hardware circuits include an application specific integrated circuit (ASIC) and a field programmable gate array (FPGA).

(c) The controller100includes a processor that executes part of various processes in accordance with a computer program and a dedicated hardware circuit that executes the remaining processes.

Various changes in form and details may be made to the examples above without departing from the spirit and scope of the claims and their equivalents. The examples are for the sake of description only, and not for purposes of limitation. Descriptions of features in each example are to be considered as being applicable to similar features or aspects in other examples. Suitable results may be achieved if sequences are performed in a different order, and/or if components in a described system, architecture, device, or circuit are combined differently, and/or replaced or supplemented by other components or their equivalents. The scope of the disclosure is not defined by the detailed description, but by the claims and their equivalents. All variations within the scope of the claims and their equivalents are included in the disclosure.