WO2015037588A1

WO2015037588A1 - Failure determination device for hybrid vehicles and failure determination method therefor

Info

Publication number: WO2015037588A1
Application number: PCT/JP2014/073825
Authority: WO
Inventors: 倫平天野; 創田坂
Original assignee: ジヤトコ株式会社; 日産自動車株式会社
Priority date: 2013-09-13
Filing date: 2014-09-09
Publication date: 2015-03-19
Also published as: JP6152422B2; JPWO2015037588A1

Abstract

An integrated controller determines whether or not the temperature of a second clutch has exceeded an upper limit temperature, on the basis of the difference in rotation speed in the second clutch, and, if a determination is made that the temperature of the second clutch exceeds the upper limit temperature, cuts drive force (high-temperature protection processing) such that the torque that is input to the second clutch from an engine and an MG is zero. In addition, the integrated controller determines second clutch engagement failure on the basis of the rotation speed difference in the second clutch and, while a second clutch engagement failure has been determined, does not cut drive force by using high-temperature protection processing.

Description

Hybrid vehicle failure determination device and failure determination method thereof

The present invention relates to a technique for determining a clutch engagement failure (MIN pressure failure) due to insufficient hydraulic pressure supplied to a clutch in a hybrid vehicle.

JP2010-155590A discloses a hybrid vehicle in which an engine and a motor are arranged in series, a first clutch is arranged between the engine and the motor, and a second clutch is arranged between the motor and the drive wheel.

In the hybrid vehicle having such a configuration, when the first clutch is released and the second clutch is engaged, the EV mode travels only with the motor. When the first clutch and the second clutch are engaged, the HEV travels with the engine and the motor. It becomes a mode.

Also, by starting WSC (Wet Start Clutch) control that slips the second clutch when starting or decelerating and stopping, smooth start and stop are realized without relying on a torque converter.

The failure determination as to whether or not a clutch engagement failure (MIN pressure failure) has occurred due to insufficient hydraulic pressure supplied to the clutch is determined if the engine blow-off is not suppressed by motor regeneration. This can be done based on the difference (difference between the rotational speed of the input side element and the rotational speed of the output side element). That is, if there is a rotational speed difference in the clutch when the select position such as D, R, etc. is operated to the travel position and the clutch is supposed to be engaged, it can be determined that a clutch engagement failure has occurred. .

On the other hand, the clutch temperature is estimated, and when it is determined that the estimated clutch temperature exceeds the upper limit, the driving force is cut to prevent the clutch temperature from rising further. The clutch temperature is estimated based on the engagement torque capacity of the clutch and the rotational speed difference in the clutch.

However, in the situation where these failure determination processing and high-temperature protection processing are performed simultaneously, interference between these two controls becomes a problem.

That is, in the situation where the clutch is poorly engaged, the clutch temperature is actually large because the clutch is released or substantially released and the clutch heat generation is small. There is a case where the driving force is cut by the high-temperature protection process because it is erroneously estimated to be high. If the driving force is cut, the rotational speed difference in the clutch is reduced, and the determination method based on the rotational speed difference cannot determine the engagement failure of the clutch.

The present invention has been made in view of such a technical problem, and prevents failure determination processing for determining clutch engagement failure from interfering with high-temperature protection processing so that failure determination processing is performed correctly. For the purpose.

According to an aspect of the present invention, the temperature of the clutch exceeds the upper limit temperature based on the engine and motor arranged in series, the clutch arranged between the motor and the drive wheel, and the rotational speed difference in the clutch. A high temperature protection unit that performs a driving force cut to zero the torque input to the clutch from the engine and the motor when it is determined that the temperature of the clutch exceeds the upper limit temperature. A failure determination apparatus for a hybrid vehicle, comprising: an engagement failure determination stage for determining an engagement failure of the clutch based on a rotational speed difference in the clutch; and the engagement failure determination unit determining an engagement failure of the clutch, There is provided a failure determination device including a control interference prevention unit that prevents the driving force from being cut by the high temperature protection unit.

According to another aspect of the present invention, an engine and a motor arranged in series, a clutch arranged between the motor and the drive wheel, and the temperature of the clutch based on a difference in rotational speed between the clutches is an upper limit temperature. When the temperature of the clutch is determined to exceed the upper limit temperature, a high-temperature protection unit that performs a driving force cut to zero torque input from the engine and the motor to the clutch; A failure determination method for a hybrid vehicle, comprising: determining a clutch engagement failure based on a rotational speed difference in the clutch; and determining the clutch engagement failure while performing the driving force cut by the high-temperature protection unit. A failure determination method is provided that is not performed.

According to these aspects, the clutch engagement failure is determined based on the rotational speed difference in the clutch, but the driving force is not cut by the high temperature protection of the clutch while the clutch engagement failure is determined. As a result, it is prevented that the rotational speed difference in the clutch is reduced due to the driving force cut and the clutch engagement failure cannot be determined (control interference is prevented), and the clutch engagement failure is correctly corrected based on the rotational speed difference in the clutch. Can be determined.

FIG. 1 is an overall configuration diagram of a hybrid vehicle to which a failure determination device according to an embodiment of the present invention is applied. FIG. 2 is an example of the mode switching map. FIG. 3 is a flowchart showing the contents of the failure determination process. FIG. 4 is a map for setting the torque-down amount. FIG. 5 is a flowchart showing the contents of the high temperature protection process.

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

FIG. 1 is an overall configuration diagram of a hybrid vehicle (hereinafter referred to as a vehicle) 100. The vehicle 100 includes an engine 1, a first clutch 2, a motor generator (hereinafter referred to as MG) 3, a first oil pump 4, a second oil pump 5, a second clutch 6, and a continuously variable transmission. (Hereinafter referred to as CVT) 7, drive wheel 8, and integrated controller 50.

Engine 1 is an internal combustion engine that uses gasoline, diesel, or the like as fuel, and the rotational speed, torque, and the like are controlled based on commands from integrated controller 50.

The first clutch 2 is a normally open hydraulic clutch interposed between the engine 1 and the MG 3. The first clutch 2 is engaged / released by the hydraulic pressure adjusted by the hydraulic control valve unit 71 using the discharge pressure of the first oil pump 4 or the second oil pump 5 as a source pressure based on a command from the integrated controller 50. Is controlled. For example, a dry multi-plate clutch is used as the first clutch 2.

MG3 is a synchronous rotating electric machine that is arranged in series with the engine 1, has a permanent magnet embedded in the rotor, and a stator coil wound around the stator. The MG 3 is controlled by applying a three-phase alternating current generated by the inverter 9 based on a command from the integrated controller 50. The MG 3 can operate as an electric motor that is rotationally driven by the supply of electric power from the battery 10. Further, when the rotor receives rotational energy from the engine 1 or the drive wheel 8, the MG 3 functions as a generator that generates electromotive force at both ends of the stator coil and can charge the battery 10.

The first oil pump 4 is a vane pump that operates when the rotation of the MG 3 is transmitted via the belt 4b. The first oil pump 4 sucks up the hydraulic oil stored in the oil pan 72 of the CVT 7 and supplies the hydraulic pressure to the hydraulic control valve unit 71.

The second oil pump 5 is an electric oil pump that operates by receiving power from the battery 10. The second oil pump 5 is driven when the amount of oil is insufficient with only the first oil pump 4 based on a command from the integrated controller 50, and is stored in the oil pan 72 of the CVT 7 in the same manner as the first oil pump 4. The hydraulic oil is sucked up and the hydraulic pressure is supplied to the hydraulic control valve unit 71.

The second clutch 6 is interposed between the MG 3, the CVT 7, and the drive wheel 8. The second clutch is controlled to be engaged and disengaged by the hydraulic pressure adjusted by the hydraulic control valve unit 71 using the discharge pressure of the first oil pump 4 or the second oil pump 5 as a source pressure based on a command from the integrated controller 50. Is done. As the second clutch 6, for example, a normally open wet multi-plate clutch is used.

The CVT 7 is arranged downstream of the MG 3 and can change the gear ratio steplessly according to the vehicle speed, the accelerator opening, and the like. The CVT 7 includes a primary pulley, a secondary pulley, and a belt that spans both pulleys. A primary pulley pressure and a secondary pulley pressure are generated by the hydraulic control valve unit 71 using the discharge pressure from the first oil pump 4 and the second oil pump 5 as a source pressure, and the movable pulley of the primary pulley and the movable pulley of the secondary pulley are generated by the pulley pressure. The gear ratio is changed steplessly by moving the shaft in the axial direction and changing the pulley contact radius of the belt.

A differential 12 is connected to an output shaft of the CVT 7 via a final reduction gear mechanism (not shown), and a drive wheel 8 is connected to the differential 12 via a drive shaft 13.

The integrated controller 50 includes a rotation speed sensor 51 that detects the rotation speed Ne of the engine 1, a rotation speed sensor 52 that detects an input rotation speed Nin of the CVT 7 (= output rotation speed of the second clutch 6), and an accelerator opening APO. Signals from an accelerator opening sensor 53 to be detected, an inhibitor switch 54 for detecting a select position of the CVT 7 (a state of a select lever or a select switch for switching forward, reverse, neutral and parking), a vehicle speed sensor 55 for detecting a vehicle speed VSP, and the like. Entered. The integrated controller 50 performs various controls on the engine 1, MG3 (inverter 9), and CVT 7 based on these input signals.

Specifically, the integrated controller 50 calculates a required driving force (driving force that realizes the acceleration required by the driver) based on the accelerator opening APO and the vehicle speed VSP, and the engine 1 is configured so that the required driving force is realized. And MG3 torque are controlled respectively.

Further, the integrated controller 50 sets the engagement torque capacity of the second clutch 6 capable of transmitting torque input from the engine 1 and the MG 3 as the target torque capacity Tc, and the engagement torque capacity of the second clutch 6 is set to the target torque capacity Tc. The hydraulic pressure supplied to the second clutch 6 from the hydraulic control valve unit 71 is controlled so that

Further, the integrated controller 50 calculates a target gear ratio based on the accelerator opening APO and the vehicle speed VSP, and controls the gear ratio of the CVT 7 so that the target gear ratio is realized.

Further, the integrated controller 50 switches between the EV mode and the HEV mode as the operation mode of the vehicle 100 with reference to the mode switching map shown in FIG.

EV mode is a mode in which the first clutch 2 is disengaged and only MG3 is used as a drive source. The EV mode is selected when the required driving force is low and the SOC of the battery 10 is sufficient.

The HEV mode is a mode in which the first clutch 2 is engaged and the engine 1 and the MG 3 are used as driving sources. The HEV mode is selected when the required driving force is high or when the SOC of the battery 10 is insufficient.

Note that the switching line from the EV mode to the HEV mode is set at a higher vehicle speed side and a larger accelerator opening than the switching line from the HEV mode to the EV mode so that the switching between the EV mode and the HEV mode is not hunting. The

Further, since the vehicle 100 is not provided with a torque converter, in the WSC region shown in FIG. 2 (the vehicle speed used when starting / decelerating and stopping is a low vehicle speed region of VSP1 or less, VSP1 is, for example, 10 km / h), the integrated controller 50 performs WSC control that starts and stops while slipping the second clutch 6.

Specifically, when the select position of the CVT 7 is switched from a non-travel position such as N or P to a travel position such as D or R and the vehicle 100 starts, the integrated controller 50 is supplied to the second clutch 6. The hydraulic pressure is gradually increased, and the second clutch 6 is gradually engaged while slipping. When the vehicle speed reaches VSP1, the integrated controller 50 completely engages the second clutch 6, and ends the WSC control.

Further, when the vehicle 100 is traveling with the select position of the CVT 7 being the traveling position, and the vehicle 100 is decelerated and the vehicle speed is reduced to VSP1, the integrated controller 50 gradually increases the hydraulic pressure supplied to the second clutch 6. The second clutch 6 is gradually released while slipping. When the vehicle 100 stops, the integrated controller 50 completely releases the second clutch 6 and ends the WSC control.

During WSC control, the integrated controller 50 controls the engine 1 and the MG 3 so that the rotational speed difference in the second clutch 6 becomes the target rotational speed difference.

By the way, when the hydraulic pressure supplied to the second clutch 6 is insufficient and the engagement failure of the second clutch 6 (MIN pressure failure) occurs, there is a possibility that the original line pressure has decreased, and the line pressure If it is lowered, there is a possibility that belt slip occurs in the CVT 7. For this reason, when the engagement failure of the 2nd clutch 6 arises, it is necessary to determine it immediately and to perform appropriate control, such as the torque reduction of the engine 1 and MG3. For this reason, the integrated controller 50 determines whether or not a fastening failure has occurred in the second clutch 6 during WSC control (failure determination processing).

Further, if the temperature of the second clutch 6 rises above the upper limit temperature, the durability of the second clutch 6 decreases, so the temperature of the second clutch 6 is estimated, and the estimated temperature of the second clutch 6 is the upper limit. When the temperature is exceeded, the driving force is cut so that the torque input from the engine 1 and the MG 3 to the second clutch 6 becomes zero, and the durability of the second clutch 6 is prevented from deteriorating due to heat generation (high temperature protection). processing).

FIG. 3 is a flowchart showing the content of the failure determination process of the second clutch 6 performed by the integrated controller 50.

Describing this, first, in S1, the integrated controller 50 determines whether a failure determination condition is satisfied. The failure judgment condition is that the CVT 7 select position is in a driving position such as D, R, etc., the accelerator opening is larger than 0, the operation mode is not being switched, the select position is not being changed, and a sensor failure has occurred. Is determined to have been established. If the failure determination condition is satisfied, the process proceeds to S2, and if not, the process ends.

In S2, the integrated controller 50 reads the accelerator opening APO, the vehicle speed VSP, the rotational speed Ne of the engine 1, the rotational speed Nm of MG3, and the input rotational speed Nin of CVT7. The accelerator opening APO, the vehicle speed VSP, the rotational speed Ne of the engine 1, and the input rotational speed Nin of the CVT 7 are values detected by sensors, and the rotational speed Nm of MG3 is a value calculated from a control signal of MG3. .

In S3, the integrated controller 50 calculates the actual torque Te of the engine 1 and the actual torque Tm of the MG3. The actual torque Te of the engine 1 can be calculated by referring to the torque map of the engine 1 based on the accelerator opening APO and the rotational speed Ne of the engine 1. The actual torque of MG3 can be calculated based on the electrical load (current value) of MG3.

In S4, the integrated controller 50 calculates the target torque capacity Tc of the second clutch 6. The target torque capacity Tc is an engagement torque capacity of the second clutch 6 capable of transmitting torque input from the engine 1 and MG3.

In S5, the integrated controller 50 determines whether or not the blow of the engine 1 when the second clutch 6 is poorly engaged can be suppressed by regeneration of the MG3. Whether the engine 1 can be blown or not depends on the actual torque of the engine 1 and the regenerative capacity of the MG 3. When the accelerator opening APO is smaller than the predetermined opening APOth, or the SOC of the battery 10 is a predetermined predetermined value. When it is smaller than SOCth, it is determined that the idling of engine 1 can be suppressed by regeneration of MG3.

If it is determined that regeneration of the MG 3 can suppress the air blow of the engine 1, the process proceeds to S6, and if it is determined that it cannot be suppressed, the process proceeds to S10.

In S6, the integrated controller 50 determines the absolute value of the deviation between the target torque capacity Tc of the second clutch 6 and the sum of the actual torque Te of the engine 1 and the actual torque Tm of MG3 (= actual input torque of CVT7) (hereinafter, “ Torque deviation ") is calculated, and it is determined whether this is greater than the first failure determination value δ1.

When the engagement failure occurs in the second clutch 6, regeneration is performed by MG3 so that the rotational speed difference in the second clutch 6 does not become larger than the target rotational speed difference, and the torque of MG3 becomes a negative value. Therefore, the torque input from the engine 1 and MG 3 to the second clutch 6 decreases, and the torque deviation increases.

Therefore, when the torque deviation is larger than the first failure determination value δ1, the integrated controller 50 determines that there is a possibility that the second clutch 6 is defectively engaged, and the process proceeds to S7. Otherwise, the process proceeds to S15.

In S7, the integrated controller 50 sets the failure determination flag to 1 and counts up the failure determination timer. The failure determination timer is a timer for measuring a time during which the torque deviation is larger than the first failure determination value δ1.

In S8, the integrated controller 50 determines whether the value of the failure determination timer is greater than the failure determination threshold value TFAIL. When the value of the failure determination timer is larger than the failure determination threshold value TFAIL, the process proceeds to S9, and the integrated controller 50 determines that the engagement failure has occurred in the second clutch 6.

If the value of the failure determination timer is smaller than the failure determination threshold value TFAIL, the process proceeds to S14, and it is determined that a so-called pseudo-D state is reached. The pseudo-D state is a state in which the second clutch 6 is not engaged due to the operation delay of the hydraulic control valve unit 71 even though the integrated position is recognized as the travel position because the select position is the travel position. is there. Since the torque deviation is likely to be resolved within a short time in the pseudo D state, it is possible to distinguish the pseudo D state from the engagement failure of the second clutch 6 by using the failure determination timer in this way. it can.

On the other hand, in S10, when it is determined in S5 that it is not possible to suppress the air blow of the engine 1 due to regeneration of MG3, the integrated controller 50 sets and sets the torque reduction amount with reference to the map shown in FIG. The torque of the engine 1 is reduced according to the amount of torque reduction. As a result, the temperature of the second clutch 6 is erroneously estimated to be high in the high temperature protection process described later, and the driving force is cut, so that the rotational speed difference in the second clutch 6 is reduced and the engagement failure of the second clutch can be determined. Prevent disappearance.

The torque-down amount is set when the rotational speed difference in the second clutch 6 calculated based on the rotational speed Nm of the MG 3 and the input rotational speed Nin of the CVT 7 is a predetermined value or more. The predetermined value is a lower limit value of the rotational speed difference that may cause the engagement failure of the second clutch 6. When the calculated rotational speed difference is less than the predetermined value, there is no defective engagement in the second clutch 6, and therefore, the torque reduction amount is set to 0 so that unnecessary torque reduction is not performed.

Further, the torque reduction amount when the rotational speed difference is equal to or larger than a predetermined value is set to a larger value as the rotational speed difference in the second clutch 6 becomes larger and as the required torque capacity of the second clutch 6 becomes larger. This is because, as these values increase, the temperature of the second clutch 6 estimated in the high temperature protection process increases and interference between the failure determination process and the high temperature protection process easily occurs. This is because in order to suppress an increase in the temperature of the two-clutch 6, it is necessary to increase the torque-down amount and reduce the engagement torque capacity.

In S11, the integrated controller 50 calculates the rotational speed difference in the second clutch 6 based on the rotational speed Nm of the MG 3 and the input rotational speed Nin of the CVT 7, and determines whether this is greater than the second failure determination value δ2. Since the temperature of the second clutch 6 estimated by the high-temperature protection process is lowered by reducing the torque of the engine 1 in S10, the driving force is not cut, and the second clutch 6 has a poor engagement. If it occurs, even if the torque of the engine 1 is reduced, the engine 1 is blown away. Therefore, it is possible to correctly determine the engagement failure of the second clutch 6 based on the rotational speed difference. If the rotational speed difference is larger than the second failure determination value δ2, the process proceeds to S12 on the assumption that there is a possibility that the second clutch 6 is defectively engaged, and if not, the process proceeds to S15.

The processing from S12 to S14 is the same as the processing from S7 to S9. The failure determination flag is set to 1 and the failure determination timer is counted up (S12). While the value of the failure determination timer is smaller than the failure determination threshold value TFAIL, the pseudo D state is determined (S13 → S14), and when the value of the failure determination timer becomes larger than the failure determination threshold value TFAIL, the second clutch 6 is determined that a fastening failure has occurred (S13 → S9).

On the other hand, if it is determined in S6 that the torque deviation is smaller than the first failure determination value δ1, and if it is determined in S11 that the rotational speed difference is smaller than the second failure determination value δ2, the process proceeds to S15. Then, the integrated controller 50 sets 0 to the failure determination flag.

In S16, the integrated controller 50 determines whether the return determination condition is satisfied. The return determination condition is determined to be satisfied when either of the following two conditions is satisfied.
Torque deviation <first return determination value Δ1, and rotational speed difference <second return determination value Δ2
・ Accelerator opening APO> 0 and rotational speed difference ≒ 0

If it is determined that the return determination condition is satisfied, the process proceeds to S17, and the return determination timer is counted up.

In S18, the integrated controller 50 determines whether the return determination timer has become larger than the return determination threshold value TSAFE. If it is determined that the return determination timer has become larger than the return determination threshold value TSAFE, the process proceeds to S19, and the integrated controller 50 resets the failure determination timer and the return determination timer, and determines that the second clutch 6 is normal. To do.

By the above failure determination processing, the engagement failure (MIN pressure failure) of the second clutch 6 is determined.

FIG. 5 is a flowchart showing the contents of the high temperature protection process of the second clutch 6 performed by the integrated controller 50.

To describe this, first, in S21, the integrated controller 50 multiplies the engagement torque capacity of the second clutch 6 by the rotational speed difference in the second clutch 6 to generate the heat generation rate of the second clutch 6 (the second clutch 6 in a minute time). Calorific value) at the same time. The target torque capacity Tc is used as the engagement torque capacity of the second clutch 6.

In S22, the integrated controller 50 time-integrates the heat generation rate of the second clutch 6 calculated in S21, calculates the heat generation amount of the second clutch 6, and estimates the temperature of the second clutch 6 based on this.

In S23, the integrated controller 50 determines whether the estimated temperature of the second clutch 6 exceeds the upper limit temperature. For example, the upper limit temperature is set to a temperature that is lower by a predetermined value than the temperature at which the durability of the second clutch 6 is reduced by heat. If it is determined that the temperature of the second clutch 6 exceeds the upper limit temperature, the process proceeds to S24.

In S24, the integrated controller 50 performs the fuel cut of the engine 1 and the energization stop of the MG 3 to zero the torque input to the second clutch 6 from the engine 1 and MG 3 (driving force cut).

During the WSC control, the failure determination process and the high-temperature protection process are performed simultaneously, and when the poor engagement of the second clutch 6 is determined based on the rotational speed difference, the temperature estimation value of the second clutch 6 becomes high and the driving is performed. If force cutting is performed, the rotational speed difference in the second clutch 6 is reduced, and it becomes impossible to determine the engagement failure of the second clutch 6. That is, interference occurs between the failure determination process and the high temperature protection process.

However, according to the failure determination process, the torque reduction of the engine 1 is performed while the failure of the engagement of the second clutch 6 is determined based on the rotational speed difference in the second clutch 6. (Target torque capacity Tc) decreases, and the temperature of the second clutch 6 estimated by the high temperature protection process decreases. As a result, the high-temperature protection treatment does not function substantially and the driving force is not cut. On the other hand, if the engagement failure occurs in the second clutch 6, the engine 1 is blown even if the torque of the engine 1 is reduced, and the rotational speed difference in the second clutch 6 becomes large. A fastening failure can be determined.

Therefore, according to the present embodiment, it is possible to correctly perform the failure determination process while preventing interference between the failure determination process and the high temperature protection process.

The embodiment of the present invention has been described above, but the above embodiment is merely a part of an application example of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. is not.

For example, in the high temperature protection process, the temperature of the second clutch 6 is specifically estimated, and it is determined whether or not the driving force cut is to be performed based on the estimated temperature of the second clutch 6, but is calculated in S21. If the heat generation rate or the heat generation amount calculated in S22 exceeds the upper limit value, it may be determined that the temperature of the second clutch 6 exceeds the upper limit temperature, and the driving force may be cut.

In the above embodiment, the torque of the engine 1 is reduced while the second clutch 6 is judged to be poorly engaged based on the rotational speed difference in the second clutch 6 so that the temperature of the second clutch 6 is not erroneously estimated to be high. However, the method for preventing the high temperature protection control from functioning is not limited to this.

For example, while the poor engagement of the second clutch 6 is determined based on the rotational speed difference in the second clutch 6, the estimated temperature of the second clutch 6 is fixed to a value lower than the upper limit temperature, or the estimated value of the second clutch 6 is estimated. Even if the temperature exceeds the upper limit temperature, the high temperature protection control may not be functioned, for example, by not performing the driving force cut.

In the above embodiment, the vehicle 100 includes the CVT 7 as a transmission. However, instead of the CVT 7, another type of transmission (step AT, toroidal CVT, 2 pedal MT, etc.) may be included.

This application claims priority based on Japanese Patent Application No. 2013-190338 filed on September 13, 2013 with the Japan Patent Office, the entire contents of which are incorporated herein by reference.

Claims

It is determined whether the temperature of the clutch exceeds an upper limit temperature based on a difference in rotational speed between the engine and motor arranged in series, a clutch arranged between the motor and the drive wheel, and a rotational speed difference in the clutch, and the temperature of the clutch And a high temperature protection means for performing a driving force cut to zero the torque input to the clutch from the engine and the motor when it is determined that the temperature exceeds the upper limit temperature. There,
An engagement failure determination means for determining an engagement failure of the clutch based on a rotational speed difference in the clutch;
Control interference prevention means for preventing the driving force cut by the high temperature protection means from being performed while the engagement failure determination means determines the engagement failure of the clutch;
A failure determination device comprising:
The failure determination device according to claim 1,
The control interference preventing means prevents the driving force from being cut by the high temperature protection means by performing torque reduction of the engine while the engagement failure determination means determines the engagement failure of the clutch.
Failure determination device.
It is determined whether the temperature of the clutch exceeds an upper limit temperature based on a difference in rotational speed between the engine and motor arranged in series, a clutch arranged between the motor and the drive wheel, and a rotational speed difference in the clutch, and the temperature of the clutch And a high-temperature protection means for performing a driving force cut to zero the torque input to the clutch from the engine and the motor when it is determined that the temperature exceeds the upper limit temperature. There,
Determine the engagement failure of the clutch based on the rotational speed difference in the clutch,
While determining the engagement failure of the clutch, do not perform the driving force cut by the high temperature protection means,
Failure determination method.