JP2010188805A - Clutch controller - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a clutch controller of an electric vehicle capable of highly precisely estimating clutch torque capacity even when variation such as offset variation and gain variation occurs in a friction element of a clutch. <P>SOLUTION: The clutch controller of an electric vehicle includes: a motor generator MG; a first clutch CL1 for transmitting torque of the motor generator MG to an engine Eng; and an integrated controller 14 for controlling an engagement state of the first clutch CL1. The integrated controller 14 estimates clutch torque capacity based on motor torque when the first clutch CL1 is operated from a slip state to a fastening direction. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a clutch control device that detects a stroke and controls the engagement state of a dry clutch.

  Conventionally, in a vehicle, a dry clutch using a diaphragm spring provided in a driving force transmission path such as between a driving source and a transmission is known.

  Further, a clutch control device for fastening and releasing such a dry clutch using an actuator is known from Patent Document 1 and the like.

  A dry clutch using a diaphragm spring mounted on a conventional vehicle includes a clutch pedal that is mechanically disconnected from the clutch, and a clutch that connects and disconnects transmission of engine output to the transmission by operating the clutch. In addition to an actuator, the amount of depression by the driver of the clutch pedal is detected, and the drive of the actuator is controlled with the clutch engagement amount (pedal stroke amount) corresponding to the detected clutch depression amount as an upper limit.

JP 2004-308723 A

  However, the characteristics of the clutch torque capacity (clutch transmission torque) with respect to the clutch stroke change due to fluctuations due to wear of the friction elements of the clutch (offset fluctuations) and friction coefficient fluctuations (gain fluctuations). Therefore, as described above, in the control based on the stroke amount, the clutch torque capacity may not be estimated due to the influence of such fluctuation.

  The present invention has been made paying attention to the above-described problem, and provides a clutch control device for an electric vehicle that can estimate the clutch torque capacity with high accuracy even when a variation such as an offset variation or a gain variation occurs in the friction element of the clutch. For the purpose.

  In order to achieve the above object, in the clutch control device for an electric vehicle according to the present invention, the clutch control means estimates the clutch torque capacity based on the motor torque when the clutch is operated in the engagement direction from the slip state. .

  In the clutch control device according to the present invention, even when the motor torque is equal to the clutch torque capacity, the clutch torque is estimated from the motor torque, and even if a variation such as an offset variation or a gain variation occurs in the friction element of the clutch. It is possible to estimate the clutch torque capacity with high accuracy.

1 is an overall system diagram showing an FR hybrid vehicle (an example of a vehicle) by rear wheel drive to which the clutch control device of Embodiment 1 is applied. FIG. 3 is a configuration explanatory diagram illustrating a configuration of a first clutch CL1 that is a control target of the clutch control device according to the first embodiment. It is a Belleville spring model explaining reaction force characteristic of diaphragm spring 41 used for the 1st clutch CL1. It is a disk spring reaction force characteristic figure which shows the calculation result of the approximate expression of the disk spring model shown in FIG. It is a flowchart which shows the process performed in the integrated controller 14 of the clutch control apparatus of Example 1, and has shown the first half part of the process. It is a flowchart which shows the process performed in the integrated controller 14 of the clutch control apparatus of Example 1, and has shown the second half part of the process. It is a target drive torque characteristic figure which shows an example of the map used for calculating the target drive torque Td ^* in Example 1. FIG. FIG. 3 is a target charge / discharge amount characteristic diagram illustrating an example of a target charge / discharge amount characteristic (motor torque) with respect to a battery charge amount SOC in the first embodiment. 3 is a block diagram illustrating an outline of a configuration for performing learning processing in Embodiment 1. FIG. It is a command value characteristic figure showing the output mode of the 1st clutch torque capacity command value _{Tcl1_learning} at the time of learning in Example 1. Shows a map used from the final second clutch torque capacity command value T _cl2 ^* to compute the second clutch current command value I _cl2 ^* in Example 1, (a) is a clutch hydraulic pressure characteristic diagram for the clutch torque capacity FIG. 6B is a second clutch current command value characteristic diagram with respect to the clutch hydraulic pressure. It is a flowchart which shows the detail of the process which sets 2nd clutch control mode CL2MODE of step S5. (A) is a characteristic diagram showing the relationship between the second clutch input rotational speed target value and the clutch oil temperature, and (b) shows the relationship between the engine start distribution motor torque and the second clutch input rotational speed target value. FIG. FIG. 7 is a control block diagram illustrating a calculation process of a second clutch torque capacity command value for rotation speed control T _{cl2_FB_ON} in step S11. 6 is a flowchart illustrating a flow of a learning process of a first clutch stroke versus clutch torque capacity characteristic in the first embodiment. It is a block diagram of an engine speed control system showing the contents of the calculation process of a first clutch torque capacity command value for engine speed control T _{cl1_FB_ON} in step S22. It is a flowchart which shows the flow of the calculation process of the 1st clutch electric current command value which controls the hydraulic pressure of the 1st clutch CL1 in step S23. It is a map which shows the actual reaction force characteristic (spring constant Kp) which is a clutch torque capacity-clutch stroke characteristic used for calculation of the 1st clutch stroke target value in step S231. It is a control block diagram which shows the structure which calculates 1st clutch hydraulic pressure command value _Pcl1 ^* in Example 1. FIG. It is a time chart which shows the operation example at the time of normal operation | movement in a comparative example, and a friction element fluctuation | variation. It is a clutch torque capacity-clutch stroke characteristic view showing the relationship between the clutch torque capacity and the clutch stroke amount when the friction element of the first clutch CL1 is worn. It is a clutch torque capacity-clutch stroke characteristic view showing the relationship between the clutch torque capacity and the clutch stroke amount when the friction coefficient of the friction element of the first clutch CL1 varies. 6 is a time chart illustrating an operation example when correction is performed according to the first embodiment. 6 is a block diagram illustrating a configuration of a main part of Embodiment 2. FIG. 10 is a time chart illustrating an operation example when correction is performed according to the second embodiment.

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

  The clutch control device according to the embodiment of the present invention includes a motor (MG), a clutch (CL1) that transmits torque of the motor (MG) to the non-drive (Eng) side, and an engaged state of the clutch (CL1). A clutch control device for an electric vehicle including a clutch control means (14) for controlling the motor, wherein the clutch control means (14) operates the clutch (CL1) in a fastening direction from a slip state. A clutch control device for an electric vehicle characterized in that a clutch torque capacity is estimated based on torque.

  A clutch control apparatus according to Embodiment 1 of the best mode for carrying out the invention will be described with reference to FIGS.

First, the configuration will be described.
FIG. 1 is an overall system diagram illustrating a parallel hybrid vehicle (an example of a hybrid vehicle) to which the clutch control device according to the first embodiment is applied. Hereinafter, based on FIG. 1, the structure of a drive system and a control system is demonstrated.

  As shown in FIG. 1, the drive system of the parallel hybrid vehicle of the first embodiment includes an engine Eng, a first clutch CL1, a motor generator MG, a second clutch CL2, an automatic transmission AT, and a final gear FG. The left drive wheel LT and the right drive wheel RT are provided.

  The hybrid drive system of the first embodiment includes an electric vehicle travel mode (hereinafter referred to as “EV mode”), a hybrid vehicle travel mode (hereinafter referred to as “HEV mode”), and a semi-electric vehicle travel mode (hereinafter referred to as “EV mode”). ) And a driving torque control start mode (hereinafter referred to as “WSC mode”).

  The “EV mode” is a mode in which the first clutch CL1 is disengaged and the vehicle travels only with the power of the motor generator MG.

  The “HEV mode” is a mode in which the first clutch CL1 is engaged and the vehicle travels in any of the motor assist travel mode, travel power generation mode, and engine travel mode. The “quasi-EV mode” is a mode in which the first clutch CL1 is engaged but the engine Eng is turned off and the vehicle travels only with the power of the motor generator MG.

  “WSC mode” controls the motor generator MG at the time of P / N → D select start from “HEV mode” or D range start from “EV mode” or “HEV mode”. Then, the slip engagement state of the second clutch CL2 is maintained, and the clutch transmission torque passing through the second clutch CL2 starts while controlling the clutch torque capacity so that the required drive torque determined according to the vehicle state and the driver operation is achieved. Mode. “WSC” is an abbreviation for “Wet Start Clutch”.

  The engine Eng is capable of lean combustion, and the engine torque is controlled to coincide with the command value by controlling the intake air amount by the throttle actuator, the fuel injection amount by the injector, and the ignition timing by the spark plug.

  First clutch CL1 is interposed at a position between engine Eng and motor generator MG. As this first clutch CL1, a dry-type clutch that is normally engaged (normally closed) with an urging force of a diaphragm spring (urging means) 41 (see FIG. 2) is used, and between the engine Eng and the motor generator MG is engaged / halfway. Fasten / release. If the first clutch CL1 is in the fully engaged state, motor torque + engine torque is transmitted to the second clutch CL2, and if it is in the released state, only motor torque is transmitted to the second clutch CL2. The half-engagement / release control is performed by stroke control for the hydraulic actuator 50 shown in FIG.

Here, the structure of the first clutch CL1 will be briefly described with reference to FIG.
The first clutch CL1 includes a flywheel 43 coupled to an input shaft 42 on the engine side, a clutch disc 45 that is axially displaceable on the output shaft 44 on the motor generator MG side and restricted in movement in the rotational direction, And a clutch cover 46 that covers the clutch disk 45. When the pressure plate 47 presses the clutch disc 45 against the flywheel 43 by the urging force of the diaphragm spring 41, the input shaft 42 and the output shaft 44 are in a fastening state where torque can be transmitted.

  The first clutch CL1 is released by moving the piston 52 in the direction of the arrow ZL in the drawing by the hydraulic pressure output from the pressure control valve 51 of the hydraulic actuator 50. As a result, the pressure plate 47 moves in the direction of the arrow ZR, and the clutch disk 45 and the flywheel 43 are released from each other. The pressure control valve 51 is driven by a command signal from a clutch controller 16 described later.

As for the reaction force characteristics of the diaphragm spring (disc spring) 41, “Almen and Lathro approximate solution” shown in the following formula (aa) based on the disc spring model of FIG. 3 has been announced. FIG. 4 shows the calculation result of this approximate expression. From this calculation result, it can be seen that the inclination (spring constant) of the reaction force of the disc spring changes from positive to negative depending on the stroke.
P = (C ₁ CEh ⁴ / r ₂ ² ), C ₁
= [Δ / (1-ν ² ) h] [{(H / h) − (δ / h)} {(H / h) − (δ / 2h)} + 1]
... (aa)
Incidentally, P is the reaction force, C is a constant determined by the shape of the spring, E is Young's modulus, h is the disc spring thickness, r ₂ is the disc spring outside radius, [delta] stroke, [nu is the Poisson's ratio, H is the disc spring Free height.

  Returning to FIG. 1, the motor generator MG has an AC synchronous motor structure, and performs drive torque control and rotation speed control when starting and running, and also applies vehicle kinetic energy to the battery 9 by regenerative brake control during braking and deceleration. The collection is performed.

The second clutch CL2 is a normally open wet multi-plate clutch or wet multi-plate brake, and generates transmission torque (clutch torque capacity) in accordance with clutch hydraulic pressure (pressing force). The second clutch CL2 passes the torque output from the engine Eng and the motor generator MG (when the first clutch CL1 is engaged) to the left and right drive wheels LT and RT via the automatic transmission AT and the final gear FG. introduce.
As shown in FIG. 1, the second clutch CL2 is engaged at each gear position of the automatic transmission AT, in addition to setting an independent clutch at a position between the motor generator MG and the automatic transmission AT. A clutch or a brake used as a frictional engagement element may be used. Further, it may be set at a position between the automatic transmission AT and the left and right drive wheels LT, RT.

  The automatic transmission AT is a machine that obtains stepped gears, and includes a plurality of planetary gears. The clutch and the brake inside the transmission are engaged / released, and the speed is changed by changing the torque transmission path.

  As shown in FIG. 1, the control system of the parallel hybrid vehicle of the first embodiment includes a second clutch input rotational speed sensor 6 (= motor rotational speed sensor), a second clutch output rotational speed sensor 7, an inverter 8, Battery 9, accelerator sensor 10, engine speed sensor 11, clutch oil temperature sensor 12, stroke sensor 13, integrated controller 14, transmission controller 15, clutch controller 16, engine controller 17, and motor A controller 18, a battery controller 19, and a brake sensor 20 are provided.

  Inverter 8 performs DC / AC conversion and generates a drive current for motor generator MG. Battery 9 stores regenerative energy from motor generator MG via inverter 8.

The integrated controller 14 calculates the target drive torque Td ^* from the battery state, the accelerator opening, and the vehicle speed (a value synchronized with the transmission output speed). Based on the result, command values for the actuators (motor generator MG, engine Eng, first clutch CL1, second clutch CL2, automatic transmission AT) are calculated, and each controller 15, 16, 17, 18, 19 is processed. And send.

  The transmission controller 15 performs shift control so as to achieve the shift command from the integrated controller 14.

  The clutch controller 16 inputs sensor information from the second clutch input rotational speed sensor 6, the second clutch output rotational speed sensor 7, and the clutch oil temperature sensor 12, and the first clutch hydraulic pressure command value from the integrated controller 14 and the first clutch hydraulic pressure command value. The solenoid valve current is controlled so as to realize the clutch hydraulic pressure (current) command value with respect to the two-clutch hydraulic pressure command value.

  The engine controller 17 inputs sensor information from the engine speed sensor 11 and performs engine torque control so as to achieve an engine torque command value from the integrated controller 14.

  The motor controller 18 controls the motor generator MG so as to achieve the motor torque command value and the motor rotation speed command value from the integrated controller 14.

  The battery controller 19 manages the state of charge (SOC) of the battery 9 and transmits the information to the integrated controller 14.

  Next, the flow of processing executed in the integrated controller 14 of the first embodiment will be described with reference to the flowcharts shown in FIGS. Note that the processing contents shown in both figures are executed at a constant sampling frequency.

  In step S1, data indicating the vehicle state such as the battery charge amount SOC, the shift position of the automatic transmission AT, the input / output rotational speed of the second clutch CL2, and the vehicle speed Vsp are received, and the process proceeds to the next step S2.

In step S2, the accelerator opening Apo and the first clutch stroke measurement value _xscl1 of the first clutch CL1 are read, and the process proceeds to step S3.

In step S3, the target drive torque Td ^* is calculated from the accelerator opening Apo and the vehicle speed Vsp, and the process proceeds to step S4. Although details are omitted, the target drive torque Td ^* can be calculated based on, for example, a map as shown in FIG.

In step S4, the first clutch control mode flag fCL1 is determined and set based on the vehicle state such as the battery charge amount SOC, the target drive torque Td ^*, and the vehicle speed Vsp, and the process proceeds to step S5. The first clutch control mode flag fCL1 is a mode in which the first clutch CL1 is engaged (fCL1 = 1 and is set in the HEV mode and the WSC mode), and a mode in which the first clutch CL1 is released (fCL1 = 0. Yes, set in EV mode). Although detailed description of the setting of the first clutch control mode flag fCL1 is omitted here, for example, in a driving scene where the engine Eng is relatively inefficient such as starting at low acceleration, the EV mode driving is used. The first clutch CL1 is released (fCL1 = 0).

Further, the battery charge amount SOC is equal to or less than a preset charge amount set value SOCth1, or the target drive torque Td ^* is the maximum drive torque Td _max (maximum motor torque T _{m max} and target cranking torque T _crank when traveling in the EV mode). ^Since the EV mode traveling is difficult when the difference is equal to or greater than ^* , the first clutch CL1 is semi-engaged or engaged (fCL1 = 1) in order to travel in the HEV mode.
FIG. 8 shows an example of target charge / discharge amount characteristics (motor torque) with respect to the battery charge amount SOC. As described above, when the battery charge amount SOC is lower than the reference value, the target charge / discharge amount is set low and charged, and when the battery charge amount SOC is high, the target charge / discharge amount is set high and discharged. The

In step S5, the second clutch control mode CL2MODE is determined and set based on the vehicle state such as the battery charge amount SOC, the target drive torque Td ^* , the first clutch control mode flag fCL1, and the vehicle speed Vsp, and the process proceeds to step S6. The second clutch control mode CL2MODE determines whether the second clutch CL2 is controlled to be engaged, released, or slipped, and will be described in detail later.

In step S6, based on the control mode of each of the clutches CL1 and CL2 and the vehicle state, the share of the target drive torque Td ^* between the engine Eng and the motor generator MG is determined, and the process proceeds to step S7. That is, the basic engine torque command value _{Te_base} ^* corresponding to the drive torque distribution amount of the engine Eng is determined, and the basic motor torque command value _{Tm_base} ^* corresponding to the drive torque distribution amount of the motor generator MG is determined, step S7. Proceed to Although various torque distribution methods are conceivable, details thereof are omitted.

  In step S7, it is determined whether or not to execute slip rotation speed control (WSC) of the second clutch CL2. In this case, the second clutch control mode CL2MODE set in step S5 is the slip mode (CL2MODE = 2), and the actual slip rotational speed (second clutch input rotational speed−second clutch output rotational speed). If the absolute value is equal to or greater than the set value, the slip rotation speed control is turned on and the process proceeds to step S8. On the other hand, if the second clutch control mode CL2MODE is set to release (CL2MODE = 0) or engaged (CL2MODE = 1), the slip rotation speed control is turned OFF and the process proceeds to step S12.

In step S8, a basic second clutch torque capacity command value _{Tcl2_base} ^* is calculated, and the process proceeds to step S9. Here, the basic second clutch torque capacity command value _{Tcl2_base} ^* is, for example, the same value as the target drive torque Td ^* .

In step S9, the second clutch input rotational speed target value _ωcl2i ^* is calculated, and the process proceeds to step S10. Here, the second clutch input rotational speed target value ω _cl2i ^* includes the first clutch control mode flag fCL1, the basic second clutch torque capacity command value T _{cl2_base} ^* , the second clutch oil temperature Temp _cl2 , the battery charge amount SOC, and the second 2. Calculated from the measured clutch output rotational speed ω _o . Although detailed description of this calculation will be described later, this calculation is performed by the second clutch input rotation speed target value calculation means 201 shown in FIG.

In step S10, calculates the rotational speed control motor torque command value _{T M_FB_ON} as second clutch input rotational speed target value _ω cl2i ^* and the second clutch input rotational speed measurement value omega _Cl2i match, the process proceeds to step S11 . The calculation of the rotational speed control motor torque command value _{Tm_FB_ON} is executed by the motor torque command value calculation means 202 shown in FIG. 9, and various calculation methods can be considered. In the first embodiment, the following formula ( Based on 1), calculation by PI control is performed. In the first embodiment, this calculation is calculated using a recurrence formula obtained by discretization by Tustin approximation or the like.
T _m — _FB — _ON = {(K _pm S + K _lm ) / s} (ω _cl2i * −ω _cl2i ) (1)
In the above equation (1), K _pm is a motor control proportional gain, K _lm is a motor control integral gain, and s is a differential operator.

In step S11, the second clutch torque capacity command value _{Tcl2_FB_ON} for rotation speed control is calculated, and the process proceeds to step S14. The second clutch torque capacity command value _{Tcl2_FB_ON} for speed control is _obtained from the basic second clutch torque capacity command value _{Tcl2_base} ^* , the motor torque command value _{Tm_FB_ON} for engine speed control, and the engine torque command value. Details will be described later.

In step S12, internal state variables for calculating the above-described rotation speed control motor torque command value _{Tm_FB_ON} and rotation speed control second clutch torque capacity command value _{Tcl2_FB_ON} are initialized, and the process proceeds to step S13.

In step S13, the clutch torque capacity command value when the rotational speed control is not performed, that is, when the second clutch CL2 is engaged, released, and when the rotational speed control is performed from the engaged state (slip state). Each of T _{cl2_FB_OFF} is calculated, and the process proceeds to step S14.

Here, the clutch torque capacity command value _{Tcl2_FB_OFF} is _expressed by the following formulas (2), (3), (4), (5) when _engaged , when released, and when the rotational speed control is performed from the engaged state, respectively. )
(When concluded)
<T _{cl2_z1} ^* <Td ^* × K _safe >
T _{cl2_FB_OFF} = T _{cl2_z1} ^* + ΔT _cl2LU (2)
< _{Tcl2_z1} ^* ≧ Td ^* × K _safe >
T _{cl2_FB_OFF} = Td ^* × K _safe (3)
(When releasing)
T _{cl2_FB_OFF} = 0 (4)
(When the second clutch is engaged → slipped)
^{_{T cl2_FB_OFF = T cl2_Z1 * -ΔT cl2slp}} ··· (5)
However, in the above formulas (2) to (5), K _safe is the second clutch safety factor coefficient (> 1), ΔT _cl2LU is slip (or release) → torque capacity change rate at the time of engagement transition, and ΔT _cl2slp is , Torque capacity change rate at the time of transition from fastening to slip, T _{cl2_Z1} ^* is the last value of the final second torque command value.

In step S14, determines a final second clutch torque capacity command value _{T cl2} ^*, the process proceeds to step S15. In determining the final second clutch torque capacity command value T _cl2 ^* , when the slip rotation speed control is being performed, the following equation (6) is obtained. When the slip rotation speed control is stopped, the following expression (7 )
T _cl2 ^* = T _{cl2_FB_ON} (6)
T _cl2 ^* = T _{cl2_FB_OFF} (7)
In step S15, it is determined whether or not the engine is being started. If the difference between the second clutch input rotational speed measurement value _ωcl2i and the engine rotational speed measurement value _ωe is equal to or _smaller than the predetermined value, it is determined that the engine start operation has ended, and the process proceeds to step S16. Otherwise, the process proceeds to step S18. .

In step S16, an internal state variable for calculating the engine speed control first clutch torque capacity command value _{Tcl1_FB_OFF} is initialized (value is made zero), and the process proceeds to step S17.

In step S17, the engine speed control first clutch torque capacity command value _{Tcl1_FB_OFF} is calculated when the first clutch CL1 is engaged / disengaged, and the process proceeds to step S23. In calculating _{Tcl1_FB_OFF} , when the first clutch control mode flag fCL1 is in the engagement mode (= 1), the calculation is performed based on the following equation (8), and the first clutch control mode flag fCL1 is calculated. However, when it is in the open mode (= 0), it calculates based on the following formula (9).
T _{cl1_FB_OFF} = T _{cl1_max} (8)
T _{cl1_FB_OFF} = 0 (9)
T _{cl1_max} is the first clutch maximum torque capacity.

  In step S18, it is determined whether or not learning is to be performed based on the vehicle state and the driving request of the driver. Whether or not to perform this learning is determined by the stroke-to-torque capacity characteristic learning permission means 203 shown in FIG. 9, and the engine is being started (step S15) and the second clutch control mode CL2MODE is in the released state. (= 0 and there is no driver drive request) or immediately after starting the ignition switch (not shown), learning is allowed and the process proceeds to step S19. Otherwise, the process proceeds to step S21.

In step S19, the learning first clutch torque capacity command value _{Tcl1_learning} is calculated, and the process proceeds to step S20. The learning first clutch torque capacity command value T _{cl1_learning} at the time of starting the engine is set by the first clutch torque capacity command value means 205 shown in FIG. 9, and the learning first clutch torque capacity command value T _{cl1_learning} is shown in FIG. As shown, the cranking torque Tclk at the time of starting the engine accompanying the driving request of the driver is set to be discontinuously changed in two or more stages.

In step S20, the stroke-to-torque capacity characteristic of the first clutch CL1 is learned from the rotational speed control motor torque command value _{Tm_FB_ON} and the first clutch stroke measurement value _xscl1, and the process proceeds to step S23. The learning of the stroke-to-torque capacity characteristic is performed by the stroke-to-torque capacity characteristic learning means 204 shown in FIG. 9, and the detailed calculation method will be described later.

In step S21, the first clutch torque capacity basic value T _{cl1_base} at the time of engine start is calculated by the following equation (10), and then the process proceeds to step S22.
T _{cl1_base} = T _{cl1_ENG_ST} (10)
T _{cl1_ENG_ST} is a preset engine cranking torque.

In step S22, the engine speed control first clutch torque capacity command value _{Tcl1_FB_ON} is calculated, and the process proceeds to step S23. A detailed calculation method will be described later.

In step S23, the final first clutch torque capacity command value _Tcl1 ^* is determined based on the following conditions a), b) and c), and the process proceeds to step S24.
a) When the engine Eng is not started (ignited)
^{_{-T cl1 * = T cl1_FB_OFF ··· (}} 11)
b) If you are in learning ^{_{T cl1 * = T cl1_leaning ··· (}} 12)
b) If in the engine speed control ^{_{T cl1 * = T cl1_FB_ON ··· (}} 13)
In step S24, a second clutch current command value I _cl2 ^* to be output to a pressure control valve (not shown) that controls the hydraulic pressure applied to the second clutch CL2 is _calculated from the final second clutch torque capacity command value T _cl2 ^* , Proceed to step S25. The calculation of the second clutch current command value I _cl2 ^* is performed based on a map shown in FIG. 11 created based on characteristics acquired in advance. Thereby, even when the clutch torque capacity has a non-linear characteristic with respect to the hydraulic pressure or current, the control target can be regarded as linear, and thus the linear control theory as described above can be applied.

In step S25, the first clutch current command value _Icl1 ^* output to the pressure control valve 51 that controls the hydraulic pressure applied to the first clutch CL1 is calculated from the final first clutch torque capacity command value _Tcl1 ^* , and the process proceeds to step S26. . A detailed calculation method will be described later.

In step S26, a motor torque command value Tm ^* is determined, and the process proceeds to step S27. In determining the motor torque command value Tm ^* , it is determined based on the following formula (14) when the rotational speed control is being performed, and based on the following formula (15) when the rotational speed control is stopped. To decide.
Tm ^* = _{Tm_FB_ON} (14)
Tm ^* = _{Tm_base} (15)
At step S27, step S24, S25, the second clutch current command value obtained in S26 _{I cl2} ^*, first clutch current command value _{I cl1} ^*, the motor torque command value Tm ^*, and each controller 15, 16, 17, 18 and 19 are transmitted.

  Thus, the flow of processing executed in one sampling cycle in the integrated controller 14 is completed.

Next, details of each process described above will be described.
(Details of setting method of second clutch control mode CL2MODE)
Next, details of the setting method of the second clutch control mode CL2MODE in step S5 will be described. The second clutch control mode CL2MODE is set from the vehicle state such as the battery charge amount SOC, the target drive torque Td ^* , the first clutch control mode flag fCL1, and the vehicle speed Vsp. The details will be described below with reference to the flowchart shown in FIG.

  In S51, the first clutch control mode flag fCL1 is determined. If the first clutch control mode flag fCL1 is in the disengagement mode (engine stop), the process proceeds to step S52, and if it is in the engagement mode (engine start), the process proceeds to S55.

  In S52, it is determined whether or not the vehicle speed Vsp is zero (stop). If the vehicle speed Vsp is stopped, the process proceeds to step S53, and otherwise, the process proceeds to step S54.

  In S53, the second clutch control mode CL2MODE is set to the engagement mode (CL2MODE = 1), and one process is completed. In S54, the second clutch control mode CL2MODE is set to the slip mode (CL2MODE = 2), and one process is completed.

  In S55, it is determined whether or not the vehicle speed Vsp is higher than a preset value Vth1 (for example, the lowest vehicle speed at which the engine Eng can be started). If the vehicle speed Vsp is lower than the preset value Vth1, the process proceeds to step S56. If it is also higher, the process proceeds to step S58.

In step S56, the sign of the target drive torque Td ^* is determined. If the value is positive, the process proceeds to step S54. If the value is negative, the process proceeds to step S57.

  In step S57, the second clutch control mode CL2MODE is set to the release mode (CL2MODE = 0), and one process is completed.

  In step S58, it is determined whether or not the previous second clutch control mode CL2MODE is the engagement mode (CL2MODE = 1). If the engagement mode is the engagement mode, the process proceeds to step S53. Otherwise, the process proceeds to step S59.

In step S59, it is determined whether or not the engine speed measurement value _ωe and the second clutch slip rotation speed measurement value _ωcl2slp satisfy the following slip continuation conditions. If so, the process proceeds to step S54 to start or continue slipping. If the slip continuation condition is not satisfied, the process proceeds to step S53 to end the slip and shift to the fastening mode. Here, the case where the slip continuation condition is satisfied is a case where _ωe ≠ _ωcl2i (that is, the first clutch CL1 is released or slipped) or _ωcl2slp > _ωcl2slpth is satisfied. Note that ω _{cl2 slpth} is a slip rotation speed threshold value.

(Calculation method of second clutch input rotational speed target value _ωcl2i ^* )
Next, the details of the calculation method of the second clutch input rotation speed target value ω _cl2i ^* in step S9 will be described.

First, the second clutch slip rotation speed target value _{ωcl2_slp} ^* is calculated. This second clutch input rotational speed target value ω _cl2i ^* is calculated based on the following equation (16) when the traveling mode is the EV mode (fCL1 = 0), and when the engine is starting, the following equation: Calculate based on (17).
(In the EV mode (fCL1 = 0))
ω _{cl2_slp} ^* = f _{cl2_slp_cl1OP} (T _{cl2_base} , Temp _cl2 ) (16)
Here, f _{cl2_slp_cl1OP} () is a function having the basic second clutch torque capacity command value T _{cl2_base} ^* and the second clutch oil temperature Temp _cl2 as inputs. Specifically, it can be set based on the map shown in FIG. That is, when “the oil temperature is high” or “the clutch capacity command value is large”, it is possible to prevent the clutch oil temperature from rising by reducing the second clutch input rotation speed target value ω _cl2i ^* .
(When the engine is starting)
ω _{cl2_slp} ^* = f _{cl2_slp_cl1OP} (T _{cl2_base ′} Temp _cl2 )
+ F _{fcl2_Δωslp} (T _{Eng_staRT} ) (14)
Here, f _{fcl2_Δωslp} () is a function for calculating the amount of increase in the slip rotation speed of the second clutch CL2 at the time of engine start, and the engine start distribution motor torque T _{Eng_staRT} is input. Specifically, based on the map shown in FIG. 13B, when the engine start distribution motor torque T _{Eng_staRT} decreases, the second clutch input rotational speed target value ω _cl2i ^* is increased (the increase amount is increased). Set to. Thereby, even if the disturbance from the first clutch CL1 cannot be completely canceled and the rotational speed is reduced, it is possible to prevent sudden engagement, and as a result, it is possible to start the engine without causing fluctuations in acceleration.
When the slip control is continued even after the engine is started, the second clutch input rotational speed target value _ωcl2i ^* is the same as that during EV traveling (the increment is not added).

Next, based on the following equation (18), the second clutch input rotational speed target value ω _cl2i ^* is calculated from the second clutch slip rotational speed target value ω _{cl2_slp} ^* and the second clutch output rotational speed measured value ωo. To do.
_ωcl2i ^* = _{ωcl2_slp} ^* + ωo (18)
Finally, the above equation (18) second clutch input rotational speed target value calculated from _ω cl2i ^*, subjected to upper and lower limits, and the final second clutch input rotational speed target value _ω cl2i ^*. The upper and lower limit values are the upper and lower limit values of the engine speed.

(Calculation method of second clutch torque capacity command value T _{cl2_FB_ON} for rotation speed control)
Next, the details of the calculation method of the second clutch torque capacity command value T _{cl2_FB_ON} for rotation speed control in step S11 will be described.

FIG. 14 shows a control block diagram of a calculation method of the second clutch torque capacity command value T _{cl2_FB_ON} for rotational speed control. This control system is designed by a two-degree-of-freedom control method including feedforward (F / F) compensation and feedback (F / B) compensation. Various design methods can be considered for the F / B compensator, but this time, an example of PI control is shown as an example. Hereinafter, the calculation method will be described.

First, phase compensation is applied to the basic second clutch torque capacity command value T _{cl2_base} ^* based on the phase compensation filter G _FF (s) shown in the following equation (19), and the F / F second clutch torque capacity command value T _{cl2_FF} is _calculated . Calculate. The actual calculation is calculated using a recurrence formula obtained by discretization by Tustin approximation or the like.
T _{cl2_FF} / T _{cl2_base} ^* = G _FF (s) = (τ _cl2 · s + 1) / (τ _cl2ref · s + 1) (19)
However, τ _cl2 is the second clutch model time constant, and τ _cl2ref is the second clutch control reference response time constant.

Next, the second clutch torque capacity target value _{Tcl2_t} is calculated. Here, the second clutch torque capacity target value _{Tcl2_t} is calculated based on the following equation (20) in the EV mode (the first clutch CL1 is in the released state), and the HEV mode (the first clutch CL1 is engaged). In the case of (state), calculation is performed based on the following equation (21).
(In the EV mode (fCL1 = 0))
T _{cl2_t} = T _{cl2_base} ^* (20)
(In case of HEV mode (fCL1 = 1))
_{Tcl2_t} = _{Tcl2_base} ^* _{−Te_est} (21)
Note that the second clutch torque capacity target value T _{cl2_t} in the HEV mode means the capacity of the motor with respect to the torque capacity of the whole (engine and motor).

Further, _{Te_est} is an estimated engine torque value, and is calculated based on, for example, the following equation (22).
_{T e_est = (1 / τ e} s + 1) e -Les × T e_base * ··· (22)
Where τ _e is the engine first-order lag time constant, and Le is the engine dead time.

Next, the second clutch torque capacity reference value T _{cl2_ref} is calculated based on the following equation (23).
(T _{cl2_ref} / T _{cl2_t} ) = G _{cl2_REF} (s) = 1 / τ _{cl2_ref} · s + 1 (23)
Next, the F / B second clutch torque capacity command value T _{cl2_FB is calculated} from the second clutch torque capacity reference value T _{cl2_ref} and the above-described rotation speed control motor torque command value T _{m_FB_ON} based on the following equation (24). Is calculated.
T _{cl2_FB} =
{(K _Pcl2 s + K _Icc12 ) / s} × (T _{cl2 — ref} −T _{m — FB — ON} ) (24)
However, K _Pcl2 is a proportional gain for second clutch control, and K _Icc12 is an integral gain for two clutch control.

Furthermore, the torque capacity can be accurately controlled even when the input rotational speed is changed by considering the torque (inert torque) generated by the input rotational speed change as shown in the following equation (25).
T _{cl2_FB} = {(K _Pcl2 s + K _Icl2 ) / s} × (T _{cl2_ref} −T _{m_FB_ON} −T _{Icl2_est} ) (25)
Note that _{TIcl2_est} is an inertia torque estimated value, and is obtained, for example, by multiplying the input rotational speed change amount (differential value) by the moment of inertia around the input shaft.
Then, the F / F second clutch torque capacity command value T _{cl2_FF} and the F / B second clutch torque capacity command value T _{cl2_FB} are added to calculate a final second clutch torque capacity command value T _{cl2_FB_ON} for rotational speed control. To do.

(First clutch stroke vs. clutch torque capacity characteristic learning process)
Next, the learning process of the first clutch stroke versus clutch torque capacity characteristic in step S20 will be described. In carrying out this description, the configuration for performing this learning process will be described first with reference to the block diagram of FIG.

The learning process of the first clutch stroke-to-clutch torque capacity characteristic described above is performed by the stroke-to-torque capacity characteristic learning means 204. This learning process is started by a command from the stroke-to-torque capacity characteristic learning permission means 203 that performs the determinations in steps S15 and S18, and includes a rotational speed control motor generator torque command value Tm_FB_ON, an engine rotational speed measurement value ωe, a first clutch. The stroke measurement value x _sccl1 is made based on the first clutch stroke command value x _sccl1 ^* .

  The flow of the learning process of the first clutch stroke versus clutch torque capacity characteristic will be described below based on the flowchart of FIG. In the first embodiment, the learning process is performed only when the engine is started. However, the present invention is not limited to this, and the engine Eng is not required to be started from the vehicle state or the driver's drive request. It is also possible to learn by performing only cranking without ignition.

In step S201, the absolute value of the difference between the first clutch stroke command value _{x SCL1} ^* a first clutch stroke measurement value _{x SCL1} is, it is determined whether the threshold value _{x Scl1_th1} below a preset threshold value _{x Scl1_th1} If so, the process proceeds to step S202. Otherwise, the process proceeds to step S204.

In step S202, the rotational speed control motor torque command value _{Tm_FB_ON} and the first clutch stroke measurement value _xscl1 are stored, and the process proceeds to step S203.

In step S203, a torque capacity characteristic over the entire stroke of the first clutch CL1 is calculated from the stored values of the rotational speed control motor torque command value _{Tm_FB_ON} and the first clutch stroke measurement value _xscl1, and the process proceeds to step S204. In other words, the average value of the rotational speed control motor torque command value T _{m_FB_ON} and the first clutch stroke measurement value x _scl1 (or the first clutch ₎ (or the first clutch) for each period in which the first clutch stroke command value x _scl1 ^* is a constant value. The average value of the stroke command value _xscl1 ^* ) is calculated, and the result is linearly interpolated to obtain the torque capacity characteristic over the entire stroke.

In step S204, it is determined whether or not the learning is to be ended. If it is determined that the learning is to be ended, the process proceeds to step S205. Here, the learning end determination is made when the difference between the second clutch input rotation speed measurement value _ωcl2i and the engine rotation speed measurement value _{ωe is} equal to or less than a preset end determination threshold value _ωcl1slpth2 .
In step S205, according to the determination result in step S201, when the stroke-to-torque capacity characteristic is obtained in step S203, the stroke-to-torque capacity characteristic is updated.

( _Calculation of engine clutch speed control first clutch torque capacity command value _{Tcl1_FB_ON} )
Next, details of the calculation process of the engine speed control first clutch torque capacity command value _{Tcl1_FB_ON} in step S22 will be described.
FIG. 16 shows a block diagram of the engine speed control system. In the first embodiment, this engine rotation control system is designed by the two-degree-of-freedom control method, similarly to the second clutch torque capacity control system in step S11. Various design methods can be considered for the F / B compensator, but this time PI control is used as an example. Hereinafter, the calculation method will be described.

First, the engine speed target value _ωe ^* is _calculated from the first clutch torque capacity basic value T _{cl1_base} based on the following equation (25).
_ωe ^* / (T _{cl1_base} −T _{pump_loss} )
= G _{cl1_eng} (s) = (1 / Je) × (1 / s) (25)
Je is the moment of inertia of the engine Eng, and T _{pump_loss} is the pumping loss torque measured in advance.

Next, the engine speed reference value ωe_ref is calculated based on the following equation (26). Actually, it is calculated using a recurrence formula obtained by discretization by Tustin approximation or the like.
ω _{e_ref} / ω _e ^* = G _{cl1_ref} (s)
= Ω ² _{cl1_ref} / (s ² + 2ζ _{cl1_ref} ω _{cl1_ref} · s + ω ² _{cl1_ref} ) (26)
Ζ _{cl1_ref} is a first clutch reference response damping coefficient, and ω _{cl1_ref} is a first clutch reference response natural frequency.

Next, the F / B first clutch capacity command value T _{cl1_FB} is calculated from the engine speed _reference value ω _{e_ref} and the engine speed measured value ω _e based on the following equation (27).
_{T cl1_FB = [(K pcl1 s} + K Iccl1) / s] × (ω e_ref -ωe) ··· (27)
K _pc11 is a first clutch control proportional gain, and K _Icc11 is a first clutch control integral gain.
Then, the first clutch torque capacity basic value _{Tcl1_base} and the F / B first clutch capacity command value _{Tcl1_FB} are added to calculate the final engine speed control first clutch torque capacity command value _{Tcl1_FB_ON} .

(First clutch current command value _{I cl1} ^* calculation method)
Next, a calculation method of the first clutch current command value I _cl1 ^* output to the hydraulic control valve that controls the hydraulic pressure of the first clutch CL1 in step S23 will be described based on the flowchart shown in FIG.

In step S231, the final first clutch torque capacity command value _{T cl1} ^*, clutch torque capacity previously acquired - first calculates the clutch stroke command value _{x SCL1} ^* using a map shown in FIG. 18 created by the stroke characteristic, The process proceeds to step S232.

In step S232, the first clutch stroke command value _{x SCL1} ^*, calculates the first clutch oil pressure command value _{P cl1} ^* by a first clutch stroke measurement value _{x SCL1.}

In the first embodiment, the two-degree-of-freedom control method shown in FIG. 19 is adopted in the calculation of the first clutch hydraulic pressure command value P _cl1 ^* , as in S11.
In other words, the calculation of the first clutch hydraulic pressure command value P _cl1 ^* is performed by the hydraulic pressure command value calculation means 60 shown in FIG. 19, and this hydraulic pressure command value calculation means 60 calculates the F / F compensator 61. The reference response unit 62 and the F / B compensator 63 are provided.

First, in the F / F compensator 61, from the first clutch stroke command value x _scl1 ^* , a reference response transmission characteristic as shown in the following equation (28) and an inverse system of a control target transmission characteristic after hydraulic pressure correction to be described later. The F / F hydraulic pressure command value _{Pcl1_FF} is calculated using the phase compensation filter consisting of
P _{cl1_FF} / x _sccl1 ^* = G _{cl1_FF} (s)
= (Ms ² + Cs + K _{cl1_ref} ) / (s ² + 2ζ _{cl1_ref ωcl1_ref} s + ω ² _{cl1_ref} ) (28)
Where C is the first clutch mechanism viscosity coefficient, K _{cl1_ref} is the spring constant to be controlled after hydraulic pressure correction, ζ _{cl1_ref} is the first clutch reference response damping coefficient, ω _{cl1_ref} is the first clutch reference response natural frequency, and M is the clutch Mass.

Next, the norm response unit 62 calculates a stroke norm value x _{sccl1_ref} from the first clutch stroke command value x _scl1 ^* using a filter representing a norm response transmission characteristic as shown in the following equation (29).
x _{sccl1_ref} / x _sccl1 ^* = G _{cl1_ref} (s)
= Ω ² _{cl1_ref} / s2 + 2ζ _{cl1_ref} ω _{cl1_ref} s + ω ² _{cl1_ref} (29)
Next, at F / B compensator 63, the deviation _{x Scl1_err} stroke reference value _{x Scl1_ref} a first clutch stroke measurement value _{x SCL1,} calculates the F / B pressure command value _{P Cl1_FB} based on the following equation (30) To do.
P _{cl1_FB} / x _{sccl1_err} = G _{cl1_FB} (s)
= (K _{Pgain_cl1} · s + K _{Igain_cl1} + K _{Dgain_cl1} · s ² ) / s (30)
However, K _{Pgain_cl1} is a proportional gain, K _{Igain_cl1} is an integral gain, and K _{Dgain_cl1} is a differential gain.

Finally, by adding the F / B pressure command value _{P Cl1_FB} and F / F hydraulic pressure command value _{P Cl1_FF,} the first clutch oil pressure command value _{P cl1} ^*.

In step S233, it computes the final hydraulic pressure command value _{P Cl1_com} by correcting the first clutch oil pressure command value _{P cl1} ^*.

In step S234, the first clutch current command value _Icl1 ^* is calculated from the final hydraulic pressure command value _{Pcl1_com} using the map shown in FIG. 11 (b) created based on the previously acquired characteristics.
Further, it is performed by the hydraulic pressure command value correction unit 70. In FIG. 19, a control target part Gp (s) is a part corresponding to a model of the hydraulic actuator 50 and the first clutch CL1 to be controlled, and includes a hydraulic mechanism part 500 and a clutch mechanism part 600.

(Explanation of hydraulic pressure correction)
Next, the correction for obtaining the final hydraulic pressure command value _{Pcl1_com performed} in step S233 will be described in detail.
This correction includes a first clutch oil pressure estimate _{P Cl1_est} obtained based on diaphragm actual reaction force characteristic shown in FIG. 18, from the difference between the reaction force normative value _{P Cl1_ref} obtained based on the normative spring characteristics Kref, The hydraulic pressure correction value P _{cl1_hosei} is calculated.

Then, based on the _difference between the reaction force reference value P _{cl1_ref} estimated from the reference spring characteristic map based on the first clutch stroke measurement value x _scl1 and the first clutch hydraulic pressure estimated value P _{cl1_est} estimated from the actual spring characteristic map, The hydraulic pressure correction value P _{cl1_hosei} is calculated. In this calculation, the following equation (31) is used.
P _{cl1_hosei} = P _{cl1_ref} −P _{cl1_est}
= K _ref · x _sccl1 -f _xsccl1-P (x _sccl1 ) (31)
However, f _xscl1-P () is a function indicating the hydraulic pressure-stroke characteristic.

Further, a spring constant Kp approximated to the characteristic gradient shown in FIG. 18 may be obtained and calculated using the following equation (32).
P _{cl1_hosei} = P _{cl1_ref} −P _{cl1_est}
= K _ref · x _sccl1 -K _p · x _sccl1 (32)
It should be noted that a correction value for each stroke may be calculated in advance using the above equations (31) and (32), and a map may be used.

Then, from the above way hydraulic correction value is calculated by _{P Cl1_hosei} the first clutch oil pressure command value _{P cl1} ^*, it calculates the final hydraulic pressure command value _{P Cl1_com} based on the following equation (33).
^{_{P cl1_com = P cl1 * -P cl1_hosei}} ··· (33)
Therefore, in the region where the stroke amount of the first clutch CL1 is larger than xs1 having the inflection point, the spring characteristic of the diaphragm spring 41 is hydraulic as if it has the reference spring characteristic Kref intended by the designer. Is corrected.

Next, the operation of the first embodiment will be described.
(Learning correction)
In the first embodiment, when the engine is started, the first clutch CL1 is engaged and the second clutch CL2 is released, and the engine Eng is cranked by the driving torque of the motor generator MG.

  When this engine start is performed, the process proceeds to step S15 → S18 in the flowchart of FIG. 6, and since the second clutch CL2 is released in step S18, the second clutch CL2 is released. One clutch stroke versus torque capacity characteristic learning calculation is performed.

  Here, in describing the first clutch stroke versus torque capacity characteristic learning calculation according to the first embodiment, first, the operation of a comparative example in which the first clutch stroke versus torque capacity characteristic learning calculation is not performed will be described.

FIG. 20 shows the operation of the comparative example, and the stroke amount in the figure indicates the stroke amount of the first clutch CL1.
In the figure, when an engine start request is output at timing t01, engagement of first clutch CL1 is started at timing t02, and torque of motor generator MG is transmitted to engine Eng to perform cranking.
At this time, when the disengagement position of the first clutch CL1 is the clutch disengagement position St01, which is the original design position, the torque capacity of the first clutch CL1 rises with the characteristic indicated by the solid line hr1, and the engine speed is The engine ignition speed Ntn is reached at the timing of t03.

  However, in the dry first clutch CL1, the flywheel 43, the clutch disk 45, and the pressure plate 47 rub against each other, causing wear on these friction elements, or changing the wear coefficient due to thermal effects. There is a case.

When wear occurs in such a friction element or the friction coefficient fluctuates, the torque capacity with respect to the stroke amount fluctuates in the first clutch CL1. That is, FIG. 21 shows changes when wear occurs in the friction element, and as the wear progresses, the value of the torque capacity with respect to the stroke amount decreases as shown in the figure.
FIG. 22 shows a case where the friction coefficient (gain) of the friction element changes. When the friction coefficient increases, the torque capacity with respect to the stroke amount increases. Conversely, when the friction coefficient decreases, the torque capacity with respect to the stroke amount increases. Get smaller.

Therefore, in the comparative example, a case will be described in which the friction element as described above is worn and the torque capacity varies with the stroke amount.
When the clutch disengagement position in FIG. 20 changes from the initial clutch disengagement position St01 to the fluctuating clutch disengagement position St02 in FIG. Is executed, the clutch engagement start timing is delayed and becomes the timing of t02b.
Along with this, the rise timing of the engine speed is delayed, and the timing to reach the engine ignition speed is also greatly delayed at t03b.

In contrast to the comparative example, in the first embodiment, when the above-described wear occurs in the first clutch CL1 and the clutch release position changes to the position of St02, the stroke command value is corrected.
That is, when the engine is started, the first clutch stroke command value _xscl1 ^* and the first clutch stroke measurement value _xscl1 are read, and the absolute value of the deviation becomes equal to or less than a preset threshold value _{xscl1_th1} , and the motor torque and the clutch torque _{Over the} entire stroke of the first clutch CL1 from the motor torque command value for rotation speed control (= estimated clutch torque capacity value) _{Tm_FB_ON} and the first clutch stroke measurement value _xscl1. Calculate the torque capacity characteristics. In the first embodiment, the learning first clutch torque capacity command value T _{cl1_learning, which} is the final first clutch torque capacity command value T _cl1 ^* at this time, is given stepwise, and _thus is obtained for each value. The results are linearly interpolated to obtain the torque capacity characteristics over the entire stroke.

As a result, as shown in FIG. 23, the first clutch stroke command value _xscl1 ^* is corrected by the amount of variation in the stroke-to-torque capacity. As shown in the figure, the engagement start timing of the first clutch CL1 and the engine ignition rotation speed are corrected. The timing to reach Ntn is the same timing as in the case of the clutch release position St01 at the time of initial design.

In the first embodiment described above, the following effects can be obtained. A) The first clutch stroke command value _xscl1 ^* and the first clutch stroke measurement value _xscl1 are read, and the absolute value of the deviation is set in advance. By using the motor torque at the time when the threshold value x _{scl1_th1} or less is set as the estimated clutch torque value, it is possible to estimate the clutch torque capacity with high accuracy even when the friction element of the first clutch CL1 varies. is there.

b) When a variation occurs in the friction element of the first clutch CL1, it is possible to accurately learn the characteristic change due to the variation based on the relationship between the estimated clutch torque capacity and the actual clutch stroke amount. By updating the clutch torque capacity characteristic map based on the learning according to the fluctuation, the first clutch stroke command value _xscl1 ^* is corrected according to the fluctuation, and the same clutch torque capacity as when no fluctuation occurs is obtained. be able to.

c) The learning process is performed when it is determined that the driving force of the motor generator MG is not transmitted to the left and right driving wheels LT and RT. That is, in the first embodiment, the learning process is performed while the engine is being started and the second clutch control mode CL2MODE is in a released state (= 0 and there is no driver's drive request) or an ignition not shown. It was done immediately after startup when the switch was turned on.
Therefore, the clutch torque capacity can be estimated based on the motor torque in a state where the entire motor torque output from the motor generator MG is transmitted to the engine Eng via the first clutch CL1 without being transmitted to the drive wheel side. The clutch torque capacity can be estimated with higher accuracy.

d) During learning, the first clutch torque capacity command value T _{cl1_learning} during learning is given stepwise, and the results obtained for each value are linearly interpolated to obtain the torque capacity characteristics over the entire stroke. Therefore, learning can be performed with higher accuracy as compared with learning by giving one kind of torque.

e) The learning first clutch torque capacity command value _{Tcl1_learning} output during learning is set to a value smaller than the cranking torque Tclk. As a result, the rate of increase (angular acceleration) of the engine speed measurement value ωe becomes smaller than that during cranking, and a longer clutch torque estimation time can be secured, resulting in improved estimation accuracy. Further, since the estimation is performed at the time of non-driving request, the engine torque is not used for driving. Therefore, even if the engine start is delayed, the above effect can be obtained without causing insufficient acceleration.

  Next, a clutch control device according to a second embodiment of the present invention will be described. In addition, since Example 2 is a modification of Example 1, description is abbreviate | omitted about the point which a structure and effect | action common to Example 1, and only a different point is demonstrated.

The second embodiment includes a clutch torque capacity correction value calculating means 220 and an engine speed target value calculating means 221 shown in FIG.
The engine speed target value calculation means 221 calculates the engine speed target value _ωe ^* from the learning first clutch torque capacity command value T _{cl1_learning} . In the second embodiment, the learning first clutch torque capacity command value _{Tcl1_learning} gradually increases toward the cranking torque Tclk with the passage of time as shown by the inclined line in FIG.

The clutch torque capacity correction value calculating means 220 is configured to make the clutch torque measurement value ωe close to the engine speed target value ωe ^* based on the deviation between the engine speed measurement value ωe and the engine speed target value ωe ^*. A torque correction value is calculated and added to the final first clutch torque capacity command value T _cl1 ^* .

  FIG. 25 is a time chart showing an execution example of the correction. This example shows an example in which the friction coefficient is reduced by 30% in the first clutch CL1 while the clutch release position does not change. ing.

  In this case, the change in stroke amount and the cranking torque at the start of the engine are the change in stroke amount and the crank torque when the clutch torque capacity correction value calculation means 220 does not perform correction with respect to the change in the normal state shown by the solid line. As shown by the dotted line in the figure, the cranking torque is insufficient for the stroke amount and the cranking torque.

As a result, when the engine speed is normal when the engine speed reaches the engine ignition speed Ntn, as shown by the dotted line in the figure, the engine speed is normal with respect to the engine speed target value ωe ^* indicated by the two-dot chain line in the figure. The timing becomes t83 which is delayed from the timing t81.

As described above, when the engine speed measurement value ωe is separated from the engine speed target value ωe ^* indicated by the two-dot chain line as indicated by the dotted line, in the second embodiment, the clutch torque capacity correction value calculating means 220 is used. but both values .omega.e ^*, based on the deviation of .omega.e, two values .omega.e ^*, so .omega.e approaches is corrected to be added to the torque capacity command value. As a result of this correction, the stroke amount and the cranking torque become the values shown by the solid line in the figure, and the engine speed at the time of cranking also rises as shown by the solid line, and reaches the engine ignition speed Ntn. However, it approaches the normal time at the timing of t82.

As described above, the second embodiment is based on the deviation between the engine speed target value ωe ^* and the engine speed measured value ωe when the motor generator MG is rotated to cause the first clutch CL1 to slip. Thus, the clutch torque capacity is corrected in the direction in which both values approach each other.
Thereby, even if a change such as wear of the friction element or a change in the friction coefficient occurs in the first clutch CL1, a torque capacity similar to that in which no change occurs can be realized.

  As mentioned above, although the clutch control apparatus of this invention has been demonstrated based on Example 1, 2, it is not restricted to these Examples about a concrete structure, It concerns on each claim of a claim Design changes and additions are allowed without departing from the scope of the invention.

  For example, in the first and second embodiments, the example in which the clutch is applied to the first clutch CL1 has been described, but the clutch can also be applied to the second clutch CL2. Further, although the automatic transmission AT is interposed between the motor generator MG and the drive wheels (LT, RT), such a configuration may be adopted in which such a transmission is not interposed.

  In the first and second embodiments, the motor generator MG capable of regeneration is shown as the motor. However, the present invention is not limited to this, and a motor capable of only power running may be used.

Further, in the first embodiment, the example in which the first clutch torque capacity command value T _{cl1_learning} at the time of learning is output in two stages in a stepwise manner has been described, but two or more stages may be output. In the case of two stages, the minimum data necessary for linear interpolation can be obtained, and learning can be performed in a short time. Further, when the number of stages is three or more, the learning accuracy can be further improved.

  Although an example of application to an FR hybrid vehicle has been shown, it can also be applied to a front-wheel drive or four-wheel drive type hybrid vehicle. Further, the present invention can also be applied to an electric vehicle provided with only a motor in a drive source other than a hybrid vehicle. A manual transmission, a mechanical automatic transmission, or the like can also be applied as the transmission.

13 Stroke sensor (stroke detection means)
14 Integrated controller (clutch control means)
45 Clutch disc (friction element)
47 Pressure plate (friction element)
203 Stroke-to-torque capacity characteristic learning permission means (drive request determination means)
CL1 1st clutch (clutch)
CL2 Second clutch (connection / disconnection means)
Eng Engine LT Left drive wheel RT Right drive wheel MG Motor generator (motor)

Claims (5)

A motor,
A clutch that transmits the torque of the motor to the non-driving side;
Clutch control means for controlling the engagement state of the clutch;
A clutch control device for an electric vehicle comprising:
The clutch control device for an electric vehicle, wherein the clutch control means estimates a clutch torque capacity based on a motor torque when the clutch is operated in a fastening direction from a slip state. Stroke detecting means for detecting a stroke amount of the clutch;
The clutch control means has a clutch torque capacity characteristic map for the stroke amount of the clutch, and updates the clutch torque capacity characteristic map based on the relationship between the estimated clutch torque capacity and the detected clutch stroke amount. The clutch control device for an electric vehicle according to claim 1, wherein learning processing is performed. The motor includes driving wheels and an engine on the non-driving side,
The clutch is provided so as to be capable of connecting and disconnecting torque between the motor and the engine,
A connecting / disconnecting means capable of connecting / disconnecting torque transmission between the drive wheel and the motor,
Drive request determination means for determining whether the vehicle state is a drive request state for transmitting the motor torque to the drive wheels or a non-drive request state for not transmitting to the drive wheels;
3. The clutch control device for an electric vehicle according to claim 2, wherein the clutch control means executes the learning process when the drive request determination means determines that the non-drive request state.   The clutch control apparatus for an electric vehicle according to any one of claims 1 to 3, wherein the clutch torque is changed stepwise when the clutch torque is estimated.   The electric vehicle according to claim 3 or 4, wherein a clutch torque capacity command value at the time of estimating the clutch torque capacity is set to a torque capacity smaller than a cranking torque at the time of starting the engine. Clutch control device.

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