JP2016052210A - Vehicular drive apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vehicular drive apparatus with a recovery amount of regenerative energy of a motor improved.SOLUTION: A vehicular drive apparatus includes: a motor-generator 22; a transmission 23 for transmitting power of the motor-generator 22 to a drive wheel 72; and an ECU 100 for controlling the transmission 23. The ECU 100 performs, in the case of the motor-generator 22 performing regenerative braking: setting a gear stage of the transmission 23 at a gear stage determined on the basis of a gear-change diagram if torque of the motor-generator 22 does not exceed a given value; or changing a gear stage of the transmission 23 to a gear stage in a lower speed side than the gear stage determined on the basis of the speed-change diagram if the torque of the motor-generator 22 exceeds the given value.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a vehicle drive device, and more particularly to a vehicle drive device including an electric motor and a transmission.

  In Japanese Patent Laid-Open No. 9-9415, in a hybrid vehicle, the shift point is moved to the low speed side during braking, and the engine speed is reduced by reducing the overall engine speed to increase the regenerative power. It is disclosed.

Japanese Patent Laid-Open No. 9-9415

  In the technique disclosed in the above-mentioned document, the engine speed is lowered as a whole, but when the engine speed is lowered, the torque increases. Recoverable regenerative energy is limited by the magnitude of the motor torque. For this reason, there is a case where the regenerative energy cannot be obtained due to the limitation of the torque of the motor, and there is room for improvement.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a vehicle drive device with an improved amount of regenerative energy recovered from an electric motor.

  The present invention relates to a drive device for a vehicle, and includes an electric motor, a transmission that transmits power of the electric motor to drive wheels, and a control unit that controls the transmission. When the motor performs regenerative braking and the motor torque does not exceed a predetermined value, the control unit sets the gear stage of the transmission to a gear stage determined based on the shift diagram, and the motor torque is set to a predetermined value. Is exceeded, the gear stage of the transmission is changed to a gear stage on the lower speed side than the gear stage determined based on the shift diagram.

  By performing such control, when the torque of the motor during regeneration exceeds a predetermined value, the torque of the motor can be kept within a predetermined value by downshifting. As a result, the situation in which regenerative energy cannot be recovered due to the limitation of the torque of the electric motor can be reduced, and the fuel efficiency of the vehicle is improved.

  Preferably, the vehicle drive device further includes an internal combustion engine, and a clutch for engaging the rotation shaft of the internal combustion engine and the rotation shaft of the electric motor. The control unit controls the clutch to a non-engaged state when performing regenerative braking.

  According to the above configuration and control, particularly in a hybrid vehicle in which the torque capacity of the electric motor cannot be increased, the internal combustion engine can be disconnected to improve the vehicle fuel efficiency when regenerative braking is performed, and the regenerative power is limited by limiting the torque of the electric motor. The situation where energy cannot be recovered can be reduced.

It is a block diagram which shows the structure of the vehicle carrying the vehicle drive device which concerns on embodiment of this invention. FIG. 6 is a waveform diagram showing changes in motor torque and automatic transmission gear stage when the control according to the first embodiment is applied and when it is not applied. It is a flowchart for demonstrating the shift control in this Embodiment. 4 is a flowchart for illustrating a gear position determination process at the time of downshift in step S4 of FIG. 3 in the first embodiment. 4 is a waveform diagram for explaining energy that cannot be recovered in the first embodiment. FIG. It is a wave form diagram which showed the change of the gear stage of the motor torque and the case where the control of Embodiment 2 is applied and the case where it is not applied. FIG. 6 is a waveform diagram for explaining estimation of motor torque performed in the second embodiment. FIG. 10 is a flowchart for illustrating a gear position determination process at the time of downshift in step S4 of FIG. 3 in the second embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following description, the same parts are denoted by the same reference numerals. Their names and functions are also the same. Therefore, detailed description thereof will not be repeated.

[Embodiment 1]
FIG. 1 is a block diagram showing a configuration of a vehicle equipped with a vehicle drive device according to an embodiment of the present invention. Referring to FIG. 1, a vehicle 1 includes an engine 10, a K0 clutch 12, a motor generator 22 (hereinafter referred to as MG22), an automatic transmission 23, a torque converter 24, a hydraulic circuit 26, a PCU ( Power control unit) 40, battery 42, drive wheel 72, differential mechanism 70, and ECU (Electronic Control Unit) 100 are included.

  The crankshaft that is the output shaft of the engine 10 and the rotation shaft of the MG 22 are connected via the K0 clutch 12. The rotation shaft of MG 22 is connected to the input shaft of torque converter 24. The output shaft of the torque converter 24 is connected to the input shaft of the automatic transmission 23. The differential mechanism 70 is connected to the output shaft of the automatic transmission 23 and the drive wheels 72.

  MG22 is, for example, a three-phase AC rotating electric machine. The MG 22 is driven by electric power supplied from the battery 42 via the PCU 40. The MG 22 has a function as a motor that generates the driving force of the vehicle 1 and a function as a starter that starts the engine 10.

  The torque converter 24 includes a pump impeller 24a connected to the rotation shaft of the MG 22, a turbine impeller 24b connected to the input shaft of the automatic transmission 23, and a stator 24c provided between the pump impeller 24a and the turbine impeller 24b. including. The input shaft and output shaft of the torque converter 24 synchronize with each other when a lock-up clutch (not shown) is engaged, and release the synchronization when the lock-up clutch is released. .

  In the present embodiment, the automatic transmission 23 will be described as being a stepped automatic transmission that continuously changes a plurality of gear stages, for example. In the automatic transmission 23, a plurality of shift ranges are set. The plurality of shift ranges include, for example, a forward travel range (hereinafter referred to as D range), a reverse travel range (hereinafter referred to as R range), a parking range (hereinafter referred to as P range), and a neutral range. Range (hereinafter referred to as N range).

  For example, when the D range is selected as the shift range, in the automatic transmission 23, one of the range from the first speed to the upper limit gear stage (for example, sixth speed) is formed according to the driving state of the vehicle 1. Is done.

  The automatic transmission 23 includes a plurality of engagements such as a transmission unit including one or more planetary gear mechanisms, a brake that stops the rotation of the rotating elements of the planetary gear mechanism, and a clutch that synchronizes the rotation with other rotating elements. And a combination element.

  In the automatic transmission 23, when the gear stage is changed, any one of a plurality of engagement elements such as a brake and a clutch is released, or any engagement element is engaged. Or Thereby, the gear stage after the change is formed by changing the ratio (transmission ratio) between the input shaft and the output shaft of the transmission unit (automatic transmission 23).

  The engine 10 is an internal combustion engine such as a gasoline engine or a diesel engine. The crankshaft of engine 10 and the rotation shaft of MG 22 are connected via a K0 clutch 12.

  The K0 clutch 12 is engaged when the power is transmitted between the engine 10 and the MG 22 and is released when the power is interrupted between the engine 10 and the MG 22.

  The hydraulic circuit 26 supplies hydraulic oil to at least one of the K0 clutch 12 and the engagement element in the automatic transmission 23 based on a control signal from the ECU 100.

  The ECU 100 engages the K0 clutch 12 when the operation of the engine 10 is requested, for example, when the K0 clutch 12 is in a released state and the engine 10 is in a stopped state. Thereby, engine 10 and MG22 will be in a power transmission state. Therefore, the engine 10 can be operated by cranking the engine 10 by the MG 22 or by cranking the engine 10 by the rotation of the rotation shaft of the MG 22 when the vehicle 1 is coasting.

  When the engine 10 operates, the vehicle 1 travels using the power of the engine 10 or the power of the engine 10 in addition to the power of the engine 10. It is also possible to charge the battery 42 using the electric power generated by the MG 22 when the engine 10 is operated or when the vehicle 1 is coasting.

  On the other hand, for example, when the K0 clutch 12 is engaged and the engine 10 is in an operating state, the ECU 100 releases the K0 clutch 12 and requests the engine 10 when the engine 10 is requested to stop. The operation of is stopped.

  The ECU 100 requests the operation of the engine 10 or requests the engine 10 to be stopped according to the driving state of the vehicle 1. The ECU 100 calculates, for example, the power (required power) required for the vehicle 1 based on the depression amount of an accelerator pedal (not shown) and the speed of the vehicle 1, and when the required power exceeds a threshold value, the engine 10 May be requested, or the engine 10 may be requested to stop when the requested power is below the threshold value.

  Although not particularly limited, the ECU 100 preferably controls the K0 clutch 12 to be in a disengaged state when performing regenerative braking. Then, no loss due to the friction of the engine 10 occurs, so that the regenerative energy to be recovered can be increased.

  The vehicle 1 shown in FIG. 1 is a hybrid vehicle (hereinafter referred to as 1M-HV) equipped with a single motor generator. However, the hybrid vehicle mainly includes a motor generator that works as an electric motor that drives drive wheels, and mainly generates power. There is also a type (hereinafter referred to as 2M-HV) equipped with two motor generators that function as a machine.

  1M-HV of FIG. 1 has the structure which added K0 clutch 12 and MG22 between the engine of the vehicle which does not mount a motor, and a torque converter. If an attempt is made to mount a drive device on a vehicle without making major changes to the engine, automatic transmission, and torque converter of a conventional vehicle that is not a hybrid vehicle, the MG22 should be made as thin and compact as possible because of the limited mounting space of the vehicle. It is preferable. A small motor cannot handle a large torque because the number of windings of the stator coil is small. For this reason, a 1M-HV motor generator often has a smaller capacity than a 2M-HV motor generator. Small capacity motors are more limited in torque during regeneration than large capacity motors. Therefore, there may be a case where the regenerative energy cannot be effectively recovered during braking.

  FIG. 2 is a waveform diagram showing changes in the motor torque and the gear stage of the automatic transmission when the control of the first embodiment is applied and not applied. Referring to FIG. 2, motor torque and vehicle speed waveforms are shown superimposed, and the regeneration request ON / OFF and change in gear stage are shown below.

  The maximum torque that can be regenerated over the motor torque waveform is indicated by a broken line. Here, since the negative value of the motor torque is the regenerative torque, the motor cannot regenerate torque below the maximum torque.

  At times t1 to t2 and t3 to t6, the regeneration request is ON according to the user's operation of the brake pedal. At times t1 to t5, the vehicle speed gradually decreases from 80 km / h to 0. At this time, as shown by the solid line, if the gear stage is downshifted from the sixth speed to the first speed, the motor torque jumps below the maximum regenerative torque at times t3 to t4. Therefore, in practice, when the control of the present embodiment is not applied, the regenerative braking force of the motor among the total braking forces is limited so that the torque does not jump out below the maximum regenerative torque. It is necessary to increase the brake distribution. Increasing the friction brake distribution loses energy as heat.

  On the other hand, if the shift line is determined so as to shift down early and the downshift is executed so that the regenerative torque is limited as a whole, a downshift occurs even when regeneration is possible, so that when re-acceleration is requested Slack occurs and the driving comfort of the driver is inferior.

  Therefore, in the present embodiment, when motor generator 22 performs regenerative braking, ECU 100 determines that when torque of motor generator 22 does not exceed a predetermined value (threshold value corresponding to the maximum regenerative torque), The gear of the automatic transmission 23 is set to a gear determined based on the shift diagram, and when the torque of the motor generator 22 exceeds a predetermined value, the gear of the automatic transmission 23 is determined based on the shift diagram. Change to a lower gear position than the gear position. Specifically, at time t3 to t4 in FIG. 2, the downshift is performed earlier than usual as indicated by the broken line only when the motor torque approaches the maximum regenerative torque. As a result, the motor torque does not jump below the maximum regenerative torque as shown by the broken line, so that the recovered regenerative energy is increased and the fuel efficiency is improved.

  FIG. 3 is a flowchart for explaining the shift control in the present embodiment. The processing of this flowchart is called and executed from a predetermined main routine every predetermined time or every time a predetermined condition occurs.

  Referring to FIG. 3, in step S1, the gear stage is determined from the shift diagram. The shift diagram is generally used when determining the gear stage, and an upshift line and a downshift line are described on a plane having the accelerator opening as the vertical axis and the vehicle speed as the horizontal axis.

  Subsequently, in step S2, it is determined whether or not the regeneration is requested. For example, if the brake pedal is depressed (ON state), it is determined that the regeneration is being requested. When the automatic brake is activated, it may be determined that the regeneration is requested when the travel control device generates a brake activation request.

  If it is determined in step S2 that the regeneration is not requested (NO in S2), the gear determined based on the shift diagram in step S1 is applied to the automatic transmission as it is, and control is returned to the main routine.

  On the other hand, if it is determined in step S2 that the regeneration is requested (YES in S2), the process proceeds to step S3. In step S3, it is determined whether or not the magnitude of motor torque (| Tm |) is larger than the magnitude of regenerative maximum torque (| Tmmax |).

  If | Tm | is equal to or smaller than | Tmmax | in step S3 (NO in S3), the gear determined based on the shift diagram in step S1 is applied to the automatic transmission as it is, and control is performed. Returned to the main routine.

  In step S3, if | Tm | is greater than | Tmmax | (YES in S3), the process proceeds to step S4. In step S4, a downshift is further performed as compared with the gear stage determined in the shift diagram in step S1. This gear stage determination process will be described later with reference to FIG. When the gear stage is determined in step S4, the control is returned to the main routine.

  FIG. 4 is a flowchart for illustrating the gear position determination process at the time of downshift in step S4 of FIG. 3 in the first embodiment. Referring to FIG. 4, first, in step S1, propeller shaft torque Tp is acquired. Specifically, the propeller shaft torque Tp is calculated by calculating back the command value of the motor torque Tm generated in the ECU 100 using the current gear ratio of the automatic transmission 23.

Subsequently, in step S20, motor torques Tm (1) to Tm (6) when the gears are changed to the first to sixth gears are calculated by the following equations.
Tm (1) = Tp / (1st gear ratio)
Tm (2) = Tp / (2nd gear ratio)
Tm (3) = Tp / (3rd gear ratio)
Tm (4) = Tp / (4-speed gear ratio)
Tm (5) = Tp / (5-speed gear ratio)
Tm (6) = Tp / (6-speed gear ratio)
In step S30, the temporary gear stage n is determined from the shift line used during normal traveling.

  In step S40, it is determined whether or not there is a regeneration request. Since the regeneration request is the same as S2 in FIG. 3, the description thereof will not be repeated here.

  If there is no regeneration request in step S40, the process proceeds to step S80, and the temporary gear stage n is set as the post-shift gear stage as it is. In step S90, control is returned to the flowchart of FIG.

  On the other hand, if there is a regeneration request in step S40, the process proceeds to step S50. In step S50, it is determined whether or not the magnitude | Tm (n) | of the temporary gear stage n is smaller than the magnitude | Tmmax | of the maximum regenerative torque.

  If | Tm (n) | <| Tmmax | is not satisfied in step S50, there is energy that cannot be recovered by the motor generator 22 as it is, and therefore the process proceeds to step S60 and the temporary gear stage n is increased by one stage. Downshift. Then, the process of step S50 is executed again.

  In step S50, when temporary gear stage n is downshifted until | Tm (n) | <| Tmmax | is satisfied, in step S70, temporary gear stage n is determined as the post-shift gear stage. In step S90, control is returned to the flowchart of FIG.

  By doing so, an early downshift occurs at times t3 to t4 in FIG. 2, so that the motor torque does not exceed the maximum regenerative torque (the maximum regenerative in FIG. 2). The automatic transmission is controlled so that the waveform does not protrude below the torque. Therefore, the energy that can be regenerated increases, and the fuel efficiency of the vehicle is improved.

[Embodiment 2]
In the processing of the first embodiment, the shift diagram is not uniformly changed so that a downshift is likely to occur, but only when there is a regeneration request, the torque is considered and the shift stage determined by the shift diagram is used. And further downshifted. However, it can be considered that the shift cannot catch up with the change in torque and the kinetic energy of the vehicle cannot be recovered as regenerative energy.

  FIG. 5 is a waveform diagram for explaining energy that cannot be recovered in the first embodiment. As in FIG. 2, the motor torque and vehicle speed waveforms are also shown in FIG. 5, and the regeneration request ON / OFF and gear stage changes are shown below. The maximum possible torque is indicated by a broken line.

  At time t11 in FIG. 5, the regeneration request changes from OFF to ON in accordance with the user's operation of the brake pedal. A case where the normal downshift is performed is indicated by a solid line waveform, and a case where the downshift of the first embodiment is performed is indicated by a broken line waveform.

  At time t12, since the magnitude of the motor torque has become larger than the magnitude of the maximum regenerative torque, a downshift has occurred from the sixth speed to the third speed. For this reason, the portion of the broken line waveform protruding below the maximum regenerative torque is smaller than the solid line waveform of the motor torque.

  However, since the downshift timing is late, before and after the start of the shift at time t12, there is a small portion protruding below the maximum regenerative torque even in the broken line waveform. In the second embodiment, by predicting a change in torque, the protruding portion of the broken line is eliminated, and the regenerative energy is increased. In the second embodiment, the configuration of the vehicle in FIG. 1 and the basic process in FIG. 3 are also applied in common. Hereinafter, the differences between the second embodiment and the first embodiment will be described.

  FIG. 6 is a waveform diagram showing changes in the motor torque and the gear position of the automatic transmission when the control of the second embodiment is applied and when it is not applied. As in FIG. 2, the motor torque and vehicle speed waveforms are also shown in FIG. 6 and the regeneration request ON / OFF and the change in gear stage are shown below. The maximum torque is shown with a broken line.

  At time t21 in FIG. 6, the regeneration request changes from OFF to ON in accordance with the user's operation of the brake pedal. A case where a normal downshift is performed is indicated by a solid line waveform, and a case where the downshift of the second embodiment is performed is indicated by a broken line waveform.

  At time t22, the predicted motor torque is larger than the maximum regenerative torque, so a downshift occurs from the sixth speed to the third speed. For this reason, compared with the waveform of the solid line of the motor torque, in the waveform of the broken line, there is no portion protruding below the maximum regenerative torque. Compared with the waveform of FIG. 5, the shift start timing of the waveform of FIG.

  For this reason, when comparing the motor torque indicated by the broken line, in FIG. 5, there remains a portion where the motor torque protrudes below the maximum regenerative torque, but in FIG. 6, this protrusion disappears.

  FIG. 7 is a waveform diagram for explaining the estimation of the motor torque performed in the second embodiment. At time t31 in FIG. 7, the regeneration request changes from OFF to ON in accordance with the user's operation of the brake pedal. Thereafter, at t32, t33, t34, and t35, the vehicle speed and the motor torque are measured or calculated for each control cycle of the ECU 100, and the control of the first embodiment is executed.

  Here, in the second embodiment, in addition to the control of the first embodiment, a process of estimating the next value at t35 from the previous value at t33 and the current value at t34 is performed when calculating the motor torque. Then, when the magnitude of the next value exceeds the magnitude of the maximum regenerative torque, the control for starting the downshift is executed. Thus, an early downshift is possible.

The estimation of the motor torque is not particularly limited, but it may be calculated that there is an estimated value in the extension of the straight line connecting the previous value and the current value, assuming that the torque change is linear. Specifically, since an increase from the previous value may be added to the current value, when the previous value is T (k−1), the current value is T (k), and the next value is T (k + 1), The next value can be easily estimated.
T (k + 1) = T (k) + (T (k-1) -T (k))
FIG. 8 is a flowchart for explaining the gear position determination process at the time of downshift in step S4 of FIG. 3 in the second embodiment. The process of the flowchart of FIG. 8 is different from the first embodiment in that steps S41, S42, and S43 are added to the process of the flowchart of FIG. Since the processing of other steps has been described with reference to FIG. 4, the description thereof will not be repeated below.

In the second embodiment, when it is determined in step S40 that there is a regeneration request, the process of step S41 is executed. In step S41, the next value of motor torque Tm (k + 1) is estimated from the previous value of motor torque Tm (k-1) and the current value of motor torque Tm (k-1). The estimation is not particularly limited, but can be estimated by the following equation as described in FIG.
T (k + 1) = T (k) + (T (k-1) -T (k))
Subsequently, in step S42, the condition that the magnitude of the motor torque | T (k + 1) | of the next value exceeds the magnitude of the maximum regenerative torque | Tmmax | and the vehicle speed is equal to or higher than the threshold value Vt ( It is determined whether or not (jump speed change condition) is satisfied. In step S42, when the jump gear change condition is satisfied (YES in S42), the process of step S50 is executed after the process of step S43 is executed. In step S43, a process of further downshifting the temporary gear stage determined based on the shift diagram in step S30 by two stages is executed. On the other hand, if it is determined in step S42 that the jump gear change condition is not satisfied (NO in S42), the process proceeds to step S50.

  In steps S50, S60, and S70, the temporary gear stage n is downshifted until the magnitude of the temporary gear stage motor torque | Tm (n) | falls below the magnitude of the maximum regenerative torque | Tmmax |. After the process is performed, a process for changing the temporary gear stage n to the post-shift gear stage is performed.

  As described above, in the second embodiment, the addition of the processes of S41 to S43 starts the downshift earlier than in the first embodiment, so the recovery rate of regenerative energy is improved.

  The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

  1 Vehicle, 10 Engine, 12 K0 Clutch, 22 Motor Generator, 23 Automatic Transmission, 24 Torque Converter, 24a Pump Impeller, 24b Turbine Impeller, 24c Stator, 26 Hydraulic Circuit, 40 PCU, 42 Battery, 70 Differential Mechanism, 72 Drive wheel, 100 ECU.

Claims (1)

An electric motor,
A transmission for transmitting the power of the electric motor to drive wheels;
A control unit for controlling the transmission,
When the electric motor performs regenerative braking and the torque of the electric motor does not exceed a predetermined value, the control unit sets the gear stage of the transmission to a gear stage determined based on a shift diagram, and When the torque of the vehicle exceeds a predetermined value, the vehicle drive device changes the gear stage of the transmission to a gear stage on the lower speed side than the gear stage determined based on the shift diagram.

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