CN103517840A

CN103517840A - Hybrid vehicle engine start control device

Info

Publication number: CN103517840A
Application number: CN201180070570.2A
Authority: CN
Inventors: 田川雅章; 伊藤芳辉; 斋藤正和; 大熊仁; 细江幸弘
Original assignee: Suzuki Motor Corp
Current assignee: Suzuki Motor Corp
Priority date: 2011-03-01
Filing date: 2011-03-01
Publication date: 2014-01-15
Anticipated expiration: 2031-03-01
Also published as: WO2012117517A1; CN103517840B; JPWO2012117517A1; JP5709093B2

Abstract

This hybrid vehicle engine start control device (1) is provided with a mechanism (39) for fixing an output shaft (3) of an engine (2) and driving and controlling the vehicle using output from the engine (2) and multiple motor generators (4, 5), wherein, when the engine (2) is started, after gradually decreasing the torque acting on the output shaft (3) of the engine (2), the engine torque is gradually changed until said engine torque is the torque necessary for cranking the engine (2). By this means, because step changes in torque are avoided when applying the torque necessary for starting the engine, sudden fluctuations in the driving force are suppressed and shocks during engine start are reduced.

Description

The engine start control device of motor vehicle driven by mixed power

Technical field

The present invention relates to the engine start control device of motor vehicle driven by mixed power, be particularly related to the power from a plurality of propulsions source is being synthesized and axle drive shaft carried out in the vehicle of input and output by Poewr transmission mechanism (differential gear train), the engine start control device of the motor vehicle driven by mixed power of propulsion source when control engine starts.

Background technology

In vehicle, have and the output from driving engine and a plurality of dynamotor (electrical motor) is driven to the motor vehicle driven by mixed power of controlling as drive source to vehicle.

In this motor vehicle driven by mixed power, (driving engine is only for rotating electrical generator series system, straight column mode), (driving engine and dynamotor configure parallel way side by side, and power is separately used to the mode driving: mode arranged side by side) drive the mode all undertaken by dynamotor:.

In addition, in motor vehicle driven by mixed power, except this series system, parallel way, also has alternate manner.

prior art document

patent documentation

Patent documentation 1: Unexamined Patent 9-170533 communique

Patent documentation 2: Unexamined Patent 10-325345 communique

Patent documentation 3: No. 3578451 communique of patent

Patent documentation 4: JP 2002-281607 communique

Patent documentation 5: JP 2010-95051 communique

Patent documentation 6: JP 2005-81931 communique

The motor vehicle driven by mixed power of patent documentation 1,2 is following modes: as the Poewr transmission mechanism of 3 shaft types, utilize 1 sun and planet gear (differential gear train with 3 rotating members) and as 2 dynamotor (the first dynamotors: MG1 of dynamotor, the second dynamotor: MG2) power of driving engine is divided into electrical generator and axle drive shaft, the driven by power that utilization is sent by electrical generator is located at the dynamotor of axle drive shaft, thus the power of driving engine is carried out to torque transfer.Thus, the operating point of driving engine (driving engine operating point) can be set as comprising and improve fuel efficiency by the point arbitrarily stopping.

In the motor vehicle driven by mixed power of patent documentation 3,4, in the Poewr transmission mechanism of 4 shaft types, to thering is each rotating member of the Poewr transmission mechanism (differential gear train) of 4 rotating members, be connected with the axle drive shaft as output link being connected with drive wheel with output shaft, the first dynamotor (MG1), second dynamotor (MG2) of driving engine, by the power coupling of the power of driving engine and the first dynamotor (MG1), the second dynamotor (MG2) and output to axle drive shaft.

The motor vehicle driven by mixed power of patent documentation 5,6 is provided with the stop mechanism of the revolution of the output shaft that utilizes brake-power control driving engine, the output shaft of energy stationary engine.

Summary of the invention

the problem that invention will solve

Yet, in the past, in above-mentioned patent documentation 1,2, although not as good as series system, in order to obtain the torque of enough axle drive shafts, need to there is the dynamotor of larger torque, and the handing-over amount of the electric power between electrical generator and electrical motor increases in low gear ratio region, therefore electric losses can become greatly, also has room for improvement.

In order to eliminate this problem, as above-mentioned patent documentation 3, in 4 disclosed motor vehicle driven by mixed powers, output shaft and axle drive shaft to the rotating member configuration driving engine of inner side in alignment chart, first dynamotor (MG1) of pusher side and second dynamotor (MG2) of drive shaft side are started in rotating member configuration to outside in alignment chart, the ratio that the first dynamotor (MG1) the power that can make thus to transmit from from driving engine to axle drive shaft and the second dynamotor (MG2) are born tails off, therefore can make the first dynamotor (MG1), the second dynamotor (MG2) miniaturization and improve the transmission efficiency of power.

In addition, following method has also been proposed: in the Poewr transmission mechanism of this 4 shaft types, further increase the 5th rotating member, be provided with the drg that the rotation of these rotating members is stopped.

In the Poewr transmission mechanism of 3 shaft types of recording at above-mentioned patent documentation 1, in the situation that being judged as start the engine, with the first dynamotor (MG1), drive driving engine, and control the propulsive effort of the second dynamotor (MG2) to produce in axle drive shaft with counteractings such as its antagonistic forces, the cogging of the axle drive shaft while suppressing engine starting thus.

And, in above-mentioned patent documentation 2, in the situation that being judged as start the engine, control the first dynamotor (MG1) so that the rotative speed of the first dynamotor (MG1) is target rotational speed, start the engine thus, and proofread and correct the cogging that the driving of the first dynamotor (MG1) brings, the cogging of the axle drive shaft while suppressing engine starting thus with the second dynamotor (MG2).

In addition, in the situation that the Poewr transmission mechanism of 3 shaft types, the torque of the second dynamotor (MG2) can not impact torque balance, therefore as long as outputed to the reaction force torque of axle drive shaft by driving engine and the first dynamotor (MG1) according to the torque calculation of the first dynamotor (MG1) of exporting for start the engine, control the torque of the second dynamotor (MG2) to offset this reaction force torque, the cogging that just can eliminate axle drive shaft makes engine starting.

Yet in the situation that the Poewr transmission mechanism of 4 shaft types, axle drive shaft and the second dynamotor (MG2) are independent axles, the torque of the second dynamotor (MG2) can not have influence on torque balance yet, therefore cannot use the control method of above-mentioned 3 shaft types.

In addition, the control of the Poewr transmission mechanism of 4 shaft types has following method.

By the output of driving engine, the first dynamotor (MG1), the power coupling of the second dynamotor (MG2) drives in the motor vehicle driven by mixed power of the axle drive shaft being connected with drive wheel, the value of the propulsive effort that the power auxiliary quantity that adds electric power is obtained is redefined for the maxim of target drive force, calculate and will speed up device operational ton and the speed of a motor vehicle as the target drive force of parameter, then according to this target drive force and the speed of a motor vehicle, obtain target drive power, and, charge condition based on battery (SOC) is obtained target and is discharged and recharged power, to adding that the value that target drive power obtains compares with starting the maximum output of function output, obtain less value as target engine power, according to target engine power, obtain target engine operating point, according to the difference of target drive power and target engine power, obtain the target power as the expected value of the input and output electric power of battery, according to the torque balance system and the control command value (motor torque command value) that comprises power balance formula computing the first dynamotor (MG1) and second dynamotor (MG2) of target power that comprise target engine torque.

Yet, in this method, although can suitably control the torque of 4 shaft types, do not mention the control relevant with engine starting, also have room for improvement.

And the scheme of the following stated has also been considered in the control of the engine starting of motor vehicle driven by mixed power.

By the output of driving engine, the first dynamotor (MG1), the power coupling of the second dynamotor (MG2) drives in the motor vehicle driven by mixed power of the axle drive shaft being connected with drive wheel, be configured to obtain and will speed up device operational ton and the speed of a motor vehicle as the target drive force of parameter, according to this target drive force and the speed of a motor vehicle, obtain target drive power, charge condition based on battery (SOC) is obtained target and is discharged and recharged power, using adding the value that target drive power obtains, as tentative target engine power, obtain, when making engine starting, target engine rotative speed while obtaining engine starting according to tentative target engine power and the speed of a motor vehicle, using the required torque of shaking of predefined driving engine as target engine torque, according to target engine rotative speed and target engine torque, calculate target engine power, according to the difference of the target drive power of calculating from target drive force and the speed of a motor vehicle and target engine power, obtain the target power as the expected value of the input and output electric power of battery, according to comprising the torque balance system of target engine torque and comprising power balance formula computing first dynamotor (MG1) of target power and the basic torque instruction value of the second dynamotor (MG2), and the first dynamotor (MG1) that the deviation of based target engine rotary speed and real engine rotative speed is calculated and the correction torque of the second dynamotor (MG2) add above-mentioned basic torque compensation value, and calculate target engine rotary acceleration according to target engine rotative speed, to adding the basic torque instruction value that feedback compensation torque obtains, add the driving engine to calculating according to target engine rotary acceleration, the first dynamotor (MG1), the first dynamotor (MG1) that the second dynamotor (MG2) inertia torque is separately proofreaied and correct, the inertia of the second dynamotor (MG2) is proofreaied and correct torque, as the first dynamotor (MG1), the final command torque value of the second dynamotor (MG2).

Yet, by this control, can suitably control the torque of 4 shaft types and make engine starting, but still having room for improvement.

In addition, in the motor vehicle driven by mixed power of recording at above-mentioned patent documentation 4, the output shaft of driving engine is arranged to free-wheel clutch so that driving engine is nonreversible, and at EV(elec. vehicle) while travelling, with free-wheel clutch, bear the reaction force torque of the second dynamotor (MG2) and travel.In this vehicle, when EV travels, with free-wheel clutch, bear the reaction force torque of the second dynamotor (MG2), and at HEV(hybrid power) while travelling, free-wheel clutch does not bear the reaction force torque of the second dynamotor (MG2), therefore in the moment that makes engine starting, the torque of the first dynamotor (MG1) and the second dynamotor (MG2) changes discontinuously, therefore there is following problem: likely the difference due to the responsibility of motor torque etc. causes propulsive effort to change discontinuously, to chaufeur, gives uncomfortable impact.

Therefore, the object of the present invention is to provide the sharply change that suppresses propulsive effort, the engine start control device of the motor vehicle driven by mixed power of the generation of the impact while reducing engine starting.

for the scheme of dealing with problems

The invention is characterized in, utilizing output from driving engine and a plurality of dynamotors to drive vehicle to control and possessing in the engine start control device of motor vehicle driven by mixed power of mechanism of the output shaft of fixing above-mentioned driving engine, in the situation that making above-mentioned engine starting, after the torque that makes to act on the output shaft of above-mentioned driving engine slowly reduces, make motor torque slowly change to the required torque of shaking of above-mentioned driving engine.

invention effect

The engine start control device of motor vehicle driven by mixed power of the present invention can suppress the sharply change of propulsive effort, the generation of the impact while reducing engine starting.

Accompanying drawing explanation

Fig. 1 is the system pie graph of the startup control setup of motor vehicle driven by mixed power.(embodiment)

Fig. 2 is the control block diagram of calculating target engine operating point.(embodiment)

Fig. 3 is the control block diagram of calculating motor torque command value.(embodiment)

Fig. 4 is the diagram of circuit of calculating target engine operating point.(embodiment)

Fig. 5 is the diagram of circuit of calculating motor torque command value.(embodiment)

Fig. 6 is the figure that the variation of each torque till engine rotary speed rises is shown.(embodiment)

Fig. 7 is the alignment chart at the time T a place of Fig. 6.(embodiment)

Fig. 8 is the alignment chart at the time T b place of Fig. 6.(embodiment)

Fig. 9 is the alignment chart at the time T c place of Fig. 6.(embodiment)

Figure 10 is the alignment chart at the time T d place of Fig. 6.(embodiment)

Figure 11 is the figure that target drive force retrieval mapping is shown.(embodiment)

Figure 12 illustrates the figure that target discharges and recharges power key.(embodiment)

Figure 13 is the figure that motor torque retrieval mapping while starting is shown.(embodiment)

Figure 14 is the figure that target operating point retrieval mapping is shown.(embodiment)

Figure 15 makes the alignment chart of the situation of vehicle variation at same driving engine operating point.(embodiment)

Figure 16 is the figure that each efficient state in equipower line is shown.(embodiment)

Figure 17 is the alignment chart that the each point (D, E, F) in equipower line is shown.(embodiment)

Figure 18 is the figure that the optimum line of engine efficiency and the optimum line of whole efficiency are shown.(embodiment)

Figure 19 is the alignment chart of low gear ratio state.(embodiment)

Figure 20 is the alignment chart of middle gear speed ratio state.(embodiment)

Figure 21 is the alignment chart of high gear ratio state.(embodiment)

Figure 22 is the alignment chart that the state of power cycle has occurred.(embodiment)

The specific embodiment

The present invention by avoiding stair-stepping torque to change to realize the sharply change that suppresses propulsive effort, the object of the generation of the impact while reducing engine starting when applying the required torque of engine starting.

embodiment

Fig. 1～Figure 22 illustrates embodiments of the invention.

In Fig. 1, the 1st, as the engine start control device of the motor vehicle driven by mixed power of elec. vehicle.

Engine start control device 1 possesses: as the output shaft 3 of driving engine (being designated as " ENG " on accompanying drawing) 2 of the drive source of output torque; The first dynamotor (being designated as " MG1 " on accompanying drawing) the 4 and second dynamotor (being designated as " MG2 " on accompanying drawing) 5 as a plurality of dynamotors (electrical motor); Axle drive shaft (being designated as " OUT " on accompanying drawing) 8 as the output link being connected with drive wheel 6 by output transmission mechanism 7; And the Poewr transmission mechanism (differential gear train) 9 connecting respectively with output shaft 3, the first dynamotor 4, the second dynamotor 5 and the axle drive shaft 8 of driving engine 2.A plurality of dynamotors comprise the first dynamotor (being designated as " MG1 " on accompanying drawing) the 4 and second dynamotor (being designated as " MG2 " on accompanying drawing) 5.

In driving engine 2 sides, possesses free-wheel clutch 10 at the output shaft 3 of driving engine 2 midway.This free-wheel clutch 10 can not reverse driving engine 2, in addition at EV(elec. vehicle) reaction force torque of bearing the second dynamotor 5 while travelling.

The first dynamotor 4 comprises the first rotor 11 and the first stator 12.The second dynamotor 5 comprises the second rotor 13 and the second stator 14.

In addition, engine start control device 1 possesses: the first inverter 15 that the work of the first dynamotor 4 is controlled, the second inverter 16 that the work of the second dynamotor 5 is controlled and the control unit (drive control part: ECU) 17 of getting in touch with the first inverter 15 and the second inverter 16.

The first inverter 15 is connected with the first stator 12 of the first dynamotor 4.The second inverter 16 is connected with the second stator 14 of the second dynamotor 5.

Each terminals for power supplies of the first inverter 15 and the second inverter 16 is connected with battery (driving high-voltage battery) 18.This battery 18 can carry out the exchange of electric power with the first dynamotor 4 and the second dynamotor 5.

In this engine start control device 1, utilize the output from driving engine 2 and the first dynamotor 4, the second dynamotor 5 to drive control to motor vehicle driven by mixed power.

Poewr transmission mechanism 9 is power input/output units of so-called 4 shaft types, dispose output shaft 3 and the axle drive shaft 8 of driving engine 2, in addition, dispose the first dynamotor 4 of driving engine 2 sides and the second dynamotor 5 of axle drive shaft 8 sides, the power coupling of the power of the power of driving engine 2, the first dynamotor 4 and the second dynamotor 5 is outputed to axle drive shaft 8, between driving engine 2, the first dynamotor 4, the second dynamotor 5 and axle drive shaft 8, carry out the handing-over of power.

That is to say, in Poewr transmission mechanism 9, using comprise driving engine 2, the first dynamotor 4, the second dynamotor 5 and as 4 key elements of the axle drive shaft 8 of output link as Fig. 7～Figure 10 be shown in alignment chart by the first dynamotor (MG1) 4, driving engine (ENG) 2, as the axle drive shaft (OUT) 8 of output link, the order of the second dynamotor (MG2) 5 connects to form gear mechanism.

The first sun and planet gear 19 that Poewr transmission mechanism 92 rotating members each other connect and the second sun and planet gear 20 are set up in parallel and form.

The first sun and planet gear 19 possesses: the first sun wheel 21, the first miniature gears 22 with these the first sun wheel 21 engagements, the first ring generating gear 23, the first tooth rest 24 connecting with the first miniature gears 22 that mesh with this first miniature gears 22 and the output gear 25 connecting with first ring generating gear 23.

The second sun and planet gear 20 possesses: the second sun wheel 26, the second miniature gears 27 with these the second sun wheel 26 engagements, the second Ring gear 28 meshing with this second miniature gears 27 and the second tooth rest 29 connecting with the second miniature gears 27.

In Poewr transmission mechanism 9, the first tooth rest 24 of the first sun and planet gear 19 connects with the output shaft 3 of driving engine 2.In addition, the second tooth rest 29 of the second sun and planet gear 20 and first ring generating gear 23 and the output gear 25 of the first sun and planet gear 19 connect.

For the first sun wheel 21, by the first motor output shaft 30, be connected with the first rotor 11 of the first dynamotor 4.The first tooth rest 24, the second sun wheel 26 are connected with to the output shaft 3 of driving engine 2.For first ring generating gear 23, the second tooth rest 29, by output gear 25 and output transmission mechanism 7, be connected with axle drive shaft 8.For the second Ring gear 28, by the second motor output shaft 31, be connected with the second rotor 13 of the second dynamotor 5.

The second dynamotor 5 can be directly connected to drive wheel 6 by the second motor output shaft 31, the second Ring gear 28, the second tooth rest 29, first ring generating gear 23, output gear 25, output transmission mechanism 7 and axle drive shaft 8, only with exporting and make Vehicle Driving Cycle separately.

That is to say, in Poewr transmission mechanism 9, the second sun wheel 26 of the first tooth rest 24 of the first sun and planet gear 19 and the second sun and planet gear 20 in conjunction with and be connected with the output shaft 3 of driving engine 2, the second tooth rest 29 of the first ring generating gear 23 of the first sun and planet gear 19 and the second sun and planet gear 20 in conjunction with and be connected with axle drive shaft 8, the first sun wheel 21 to the first sun and planet gear 19 is connected with the first dynamotor 4, the second Ring gear 28 to the second sun and planet gear 20 is connected with the second dynamotor 5, at driving engine 2, the first dynamotor 4, between the second dynamotor 5 and axle drive shaft 8, carry out the handing-over of power.

Will speed up accelerator operation amount detection unit 32, the speed of a motor vehicle detecting unit 33 that detects the speed of a motor vehicle, the battery charging state detecting unit 34 of the charge condition (SOC) that detects battery 18 that the amount of entering into of pedal detects as accelerator operation amount and the engine rotary speed detecting unit 35 that detects engine rotary speed gets in touch with control unit 17.

In addition, amount of air adjusting mechanism 36, fuel provide mechanism 37, ignition timing adjusting mechanism 38 to get in touch with control engine 2 with control unit 17.

In addition, as shown in Figure 1, also can in engine start control device 1, be configured to and possess stop mechanism 39 and replace free-wheel clutch 10 as the mechanism of the output shaft 3 of stationary engine 2.Thereby this stop mechanism 39 comprises the brake rotors 40He Cong both sides fixing with output shaft 3 one of driving engine 2 and will near the peripheral part of this brake rotors 40, clamp the brake shoe brake cheek 41 that output shaft 3 is braked.This brake shoe brake cheek 41 and control unit 17 contacts.

This stop mechanism 39 the torque that acts on the output shaft 3 of driving engine 2 be zero (0) (Nm) near time, according to the instruction from control unit 17, carry out opening operation.

And, torque detecting unit 42 contacts of control unit 17 and actual torque for detection of the first dynamotor 4 and the second dynamotor 5.This torque detecting unit 42 for example comprises the torque sensor of the torque of direct-detection the first dynamotor 4 and the second dynamotor 5.In addition, this torque detecting unit 42 also can wait with the following method: each coil to the first dynamotor 4 and the second dynamotor 5 arranges current sensor, according to power consumption, calculates torque.

As shown in Figure 1 and Figure 2, control unit 17 possesses: target drive force is calculated unit 17A, target drive power and calculated unit 17B, target and discharge and recharge power and calculate unit 17C, tentative target engine power and calculate unit 17D, target engine torque and calculate unit 17E, target engine rotative speed and calculate that unit 17F, target engine power calculate unit 17G, target power is calculated unit 17H and motor torque command value arithmetic element 17I.

Target drive force is calculated unit 17A based on calculating target drive force by the detected accelerator operation amount of accelerator operation amount detection unit 32 with by the detected speed of a motor vehicle of speed of a motor vehicle detecting unit 33.

Target drive power is calculated unit 17B based on by the detected accelerator operation amount of accelerator operation amount detection unit 32 with by the detected speed of a motor vehicle of speed of a motor vehicle detecting unit 33, that is to say, based on being calculated the target drive force that unit 17A calculates by target drive force and calculating target drive power by the detected speed of a motor vehicle of speed of a motor vehicle detecting unit 33.

Target discharges and recharges power and calculates unit 17C and discharge and recharge power based on calculating target by the charge condition of the detected battery 18 of battery charging state detecting unit 34.

Tentative target engine power is calculated unit 17D and is calculated target that unit 17C calculates and discharge and recharge power and calculate tentative target engine power based on being calculated target drive power that unit 17B calculates by target drive power and discharging and recharging power by target.

Target engine torque is calculated unit 17E in the situation that driving engine 2 is started, the target engine torque initial value of the torque value of calculating the output shaft 3 that acts on driving engine 2 when engine starting request occurs during as engine starting, calculate the required torque of shaking of driving engine 2, make target engine torque slowly change to the required torque of shaking of driving engine 2 from target engine torque initial value.

Unit 17F calculated by target engine rotative speed and target engine torque is calculated unit 17E contact, the target engine rotative speed while calculating engine starting.

Target engine power is calculated unit 17G according to being calculated target engine rotative speed that unit 17F calculates by target engine rotative speed and calculating by target engine torque the target engine torque that unit 17E calculates and calculate target engine power.

Target power calculate unit 17H using by target drive power, calculated target drive power that unit 17B calculates with the difference of being calculated the target engine power that unit 17G calculates by target engine power as target power.

Motor torque command value arithmetic element 17I utilizes and to comprise the torque balance system of target engine torque and to comprise that the power balance formula of target power calculates the command torque value of the first dynamotor, the second dynamotor.

And this engine start control device 1, in the situation that driving engine 2 is started, after the torque that makes to act on the output shaft 3 of driving engine 2 slowly reduces, makes motor torque slowly change to the required torque of shaking of driving engine 2.

In addition, in this engine start control device 1, in the situation that driving engine 2 is started, the first dynamotor 4 make torque be slowly changed to by be equivalent to finally to act on the torque of torque of output shaft 3 of driving engine 2 and driving engine 2 shake that required torque is added the torque that obtains and by its output, in addition, the required torque of driving of the second dynamotor 5 output motor vehicle driven by mixed powers.

In the present embodiment, mean during the startup of driving engine 2 while occurring from engine starting request till driving engine 2 while shaking during.

, in the present embodiment, by the output of driving engine 2, the first dynamotor 4, the power coupling of the second dynamotor 5 outputs to axle drive shaft 8 and possesses in the motor vehicle driven by mixed power of stop mechanism 39 with the output shaft 3 of energy stationary engine 2, when driving engine 2 is started, the initial value of the target engine torque of the torque settings of output shaft 3 that the time point at request start the engine is acted on to driving engine 2 when starting, target engine torque is slowly changed to and shake required torque, and calculate target engine power according to target engine rotative speed and target engine torque, according to the difference of the target drive power of calculating from accelerator operation amount and the speed of a motor vehicle and target engine power, obtain the target power as the expected value of the input and output electric power of battery 18, according to the torque balance system and power balance formula computing the first dynamotor 4 that comprises target power that comprise target engine torque, the command torque value of the second dynamotor 5.

In addition, in this motor vehicle driven by mixed power, when driving engine 2 is started, the initial value of the target engine torque of the torque settings of output shaft 3 that the time point at request start the engine is acted on to driving engine 2 when starting, the target engine torque that while being slowly changed to the startup according to Figure 13, target engine torque retrieval map retrieval goes out and calculate target engine power according to target engine rotative speed and target engine torque, according to the difference of the target drive power of calculating from accelerator operation amount and the speed of a motor vehicle and target engine power, obtain the target power as the expected value of the input and output electric power of battery 18, according to the torque balance system and power balance formula computing the first dynamotor that comprises target power that comprise target engine torque, the command torque value of the second dynamotor.

And, in this motor vehicle driven by mixed power, in the situation that by the output shaft 3 of stop mechanism 39 stationary engines 2, from acting on the torque of the output shaft 3 of driving engine 2, be that zero (0) is risen near (Nm) and made stop mechanism 39 carry out opening operation, the shaking of beginning driving engine 2.

Thus, in the motor vehicle driven by mixed power of output shaft 3 that can fix with 4 shaft types driving engine 2, from EV, travel while applying the required torque of the startup of driving engine 2, can when engine starting, make motor torque slowly change to avoid stair-stepping torque to change, suppress the sharply change of propulsive effort, the impact in the time of therefore engine starting can being reduced.

The computing to target engine operating point (target engine rotative speed, target engine torque) according to accelerator operation amount and the speed of a motor vehicle in flowchart text the present embodiment of control block diagram based on Fig. 2 and Fig. 4 below.

As shown in Figure 4, when the program of control unit 17 starts (step 101), first obtain the various signals (step 102) for controlling, according to the target drive force retrieval mapping shown in Figure 11, calculate and accelerator operation amount and the corresponding target drive force of the speed of a motor vehicle (step 103).In this case, in accelerator operation amount is the high speed of a motor vehicle region of zero (0), be set as negative value, to become the propulsive effort of the deceleration direction that is equivalent to Jake brake, on the other hand, in speed of a motor vehicle Di region, be made as on the occasion of, creeping, travel.

Then, target drive force and the speed of a motor vehicle are multiplied each other, set with target drive force and drive the required target drive power (step 104) of motor vehicle driven by mixed power.

And, for the charge condition of battery 18 (SOC) is controlled in common range of use, according to the target shown in Figure 12, charge and discharge electric weight key and calculate and discharge and recharge power (step 105) as target.In this case, in the situation that the charge condition of battery 18 (SOC) is low, make charge power become the overdischarge that prevents greatly battery 18, in the situation that the charge condition of battery 18 (SOC) is high, discharge power is become and prevent from greatly overcharging.For convenient, by discharge side be treated on the occasion of, charged side is treated to negative value.

According to target drive power and target, discharge and recharge the tentative target engine power (step 106) that power calculation driving engine 2 should be exported.The value that the tentative target engine power that this driving engine 2 should the be exported power that (in electric discharge in the situation that for deducting) charges to battery 18 in order the required power of the driving of motor vehicle driven by mixed power is added obtains.At this, charged side is treated to negative value, therefore from target drive power, deducting target discharges and recharges power, calculates tentative target engine power.

Then, judge whether master mode is hybrid power (HEV) pattern (step 107).

In the situation that this step 107 is "Yes", the target engine operating point (target engine rotative speed, target engine torque) (step 108) while calculating hybrid power (HEV) pattern.

In the situation that above-mentioned steps 107 is "No", judge whether the request (step 109) of engine starting.

In the situation that this step 109 is "No", the target engine operating point (target engine rotative speed, target engine torque) (step 110) while calculating elec. vehicle (EV) pattern.For example be made as target engine rotative speed=0(rpm), target engine torque=0(Nm) etc.

In the situation that above-mentioned steps 109 is "Yes", target engine rotative speed (step 111) during startup while calculating the startup of driving engine 2.During this startup, target engine rotative speed is according to the target engine operating point retrieval mapping shown in Figure 14, correspondingly calculate with tentative target engine power and the speed of a motor vehicle, or predefined value.

The initial value (step 112) of the target engine torque while then, setting engine starting.The initial value of this target engine torque is the current torque that free-wheel clutch 10 bears.

The current torque of bearing about this free-wheel clutch 10, by

The torque of the first dynamotor of the torque of the second dynamotor of current torque=K2 * reality-(k1+1) * reality

Calculate.

In addition, this step 112 only in the situation that never the Status Change of the request of engine starting be to have the state of the request of engine starting to carry out.

Then, according to the retrieval mapping of Figure 13, target engine torque (step 113) during startup while correspondingly calculating engine starting with real engine rotative speed.During the startup of this Figure 13, target engine torque retrieval mapping is the predefined value of engine friction torque during based on fuel cut-off in order to make driving engine 2 shake.In addition, at engine rotary speed, be 0(rpm) near time, consider coefficient of friction of rest and be set as ratio engine friction torque by the value of negative (-) side.

Then, carry out the restriction (step 114) of the rate of change of target engine torque.By carrying out like this restriction of the rate of change of target engine torque, make target engine torque from by above-mentioned steps 112, obtained engine starting time the initial value of target engine torque target engine torque while slowly changing to the startup of being obtained by above-mentioned steps 113.

After the processing of above-mentioned steps 108, after the processing of above-mentioned steps 110 or after the processing of above-mentioned steps 114, calculate target engine power (step 115), from above-mentioned target drive power, deduct above-mentioned target engine power, calculate target power (step 116).This target power target drive power than target engine in high-power situation for meaning the value of auxiliary power of the electric power of battery 18, on the other hand, in the situation that target engine power ratio target driving power is large, for meaning the value to the charging power of battery 18.

Then, program is returned to (step 117).

As shown in figure 14, in above-mentioned target engine operating point retrieval mapping, the line of the some gained selected by each power in equipower line, connecting overall efficiency is good is set as to target actuating wire, and whole efficiency is the efficiency of driving engine 2 to be added to the efficiency of the power-transmission system that comprises Poewr transmission mechanism 9, the first dynamotor 4 and the second dynamotor 5.And this target actuating wire is set by each speed of a motor vehicle.This setting value can experimentally be obtained, and also can obtain according to the efficiency calculation of driving engine 2, the first dynamotor 4, the second dynamotor 5.

In addition, target actuating wire is set as uprising and to high rotating speed side shifting along with the speed of a motor vehicle.

It is the reasons are as follows.

As shown in figure 15, in the situation that independently identical driving engine operating point is made as to target engine operating point with the speed of a motor vehicle, in the situation that the speed of a motor vehicle is low, the rotative speed of the first dynamotor 4 is for just, the first dynamotor 4 is electrical generator, and the second dynamotor 5 is electrical motor (state of the A of Figure 15).And, along with the speed of a motor vehicle raises, the rotative speed of the first dynamotor 4 approaches zero (0) (state of the B of Figure 15), when the speed of a motor vehicle raises again, the rotative speed of the first dynamotor 4 is for negative, when reaching this state, the first dynamotor 4 is as electrical motor work, and the second dynamotor 5 is as electrical generator work (state of the C of Figure 15).

In the low situation of the speed of a motor vehicle (state of the A of Figure 15 and the state of B), can not cause the circulation of power, so the target actuating wire of the target operating point speed of a motor vehicle=40km/h as shown in figure 14 approaches the good point of engine efficiency like that substantially.

But when in the high situation of the speed of a motor vehicle (state of Figure 15 C), the first dynamotor 4 is as electrical motor work, as electrical generator work, there is circulating of power in the second dynamotor 5, so the Efficiency Decreasing of power-transmission system.

Therefore, as shown in the some C of Figure 16, even if engine efficiency is good, the efficiency of power-transmission system also can reduce, and therefore can cause whole Efficiency Decreasing.

Therefore, in order to there is not circulating of power in high speed of a motor vehicle region, as shown in the some E of the alignment chart of Figure 17, as long as be that zero (0) is above although make the rotative speed of the first dynamotor 4, but the direction that driving engine operating point can raise to engine rotary speed like this moves, therefore as shown in the some E of Figure 16, even if the efficiency of power-transmission system is good, engine efficiency also can reduce greatly, therefore can cause whole Efficiency Decreasing.

Therefore, as shown in figure 16, the whole good point of engine efficiency is some D between the two, as long as this D just can be carried out to most effective running as target engine operating point.

In Figure 18, above-mentioned some C, some D, these 3 operating points of some E are illustrated in target operating point retrieval mapping.Known in this Figure 18, in the situation that the speed of a motor vehicle is high, the operating point of the driving engine operating point ratio engine efficiency optimization of whole efficiency optimum is to high rotating speed side shifting.

Below, the control block diagram based on Fig. 3 and the flowchart text of Fig. 5 are for exporting as the propulsive effort of target and making the computing that electric weight becomes the first dynamotor 4 of expected value and the target torque of the second dynamotor 5 that charges and discharge of battery 18.

As shown in Figure 5, when the program of control unit 17 starts (step 201), first according to the speed of a motor vehicle, calculate the rotative speed No of the axle drive shaft 8 of the first sun and planet gear 19, the second sun and planet gear 20, then, calculate the rotative speed Nmg2t(step 202 of rotative speed Nmg1t and second dynamotor 5 of the first dynamotor 4 in the situation that engine rotary speed is target engine rotative speed Net).This rotative speed Nmg1t and rotative speed Nmg2t utilize following (formula 1), (formula 2) to calculate.This arithmetic expression is obtained according to the relation of the rotative speed of the first sun and planet gear 19, the second sun and planet gear 20.

Nmg1t=(Net-No) * k1+Net ... (formula 1)

Nmg2t=(No-Net) * k2+No ... (formula 2)

At this, in above-mentioned (formula 1), (formula 2), as shown in Fig. 7～Figure 10,

K1: by the lever ratio between the first dynamotor (the MG1)-driving engine (ENG) being made as between driving engine (ENG)-axle drive shaft (OUT) in the situation of " 1 "

K2: by the lever ratio between axle drive shaft (OUT)-second dynamotor (MG2) being made as between driving engine (ENG)-axle drive shaft (OUT) in the situation of " 1 ".That is to say, this k1, k2 are the values being determined by the gear ratio of the first sun and planet gear 19, the second sun and planet gear 20.

Then, according to rotative speed Nmg1t, rotative speed Nmg2t, target power Pbatt, target engine torque Tet, calculate the basic torque Tmg1i(step 203 of the first dynamotor 4).This basic torque Tmg1i is calculated by following formula (3).

Tmg1i=(Pbatt * 60/2 π-Nmg2t * Tet/k2)/(Nmg1t+Nmg2t * (1+k1)/k2) ... (formula 3)

Should (formula 3) solve comprise expression shown below be input to the first sun and planet gear 19, the second sun and planet gear 20 torque balance (formula 4) and represent that the simultaneous equations of (formula 5) that the electric power that is sent or consumed by the first dynamotor 4 and the second dynamotor 5 equals the input and output electric power (Pbatt) of battery 18 derives.

Tet+(1+k1) * Tmg1i=k2 * Tmg2i ... (formula 4)

π/60+Nmg2t * Tmg2i * 2, Nmg1t * Tmg1i * 2 π/60=Pbatt ... (formula 5)

In addition, in torque balance system, as shown in above-mentioned (formula 4), the lever of the gear ratio of the Poewr transmission mechanism 9 mechanically connecting according to the work based on a plurality of dynamotors 4,5 and driving engine 2 is a plurality of dynamotors 4,5 of balance target torque and target engine torque separately recently.

Then according to basic torque Tmg1i and (formula 6) below target engine torque utilization, calculate the basic torque Tmg2i(step 204 of the second dynamotor 5).

Tmg2i=(Tet+(1+k1) * Tmg1i)/k2 ... (formula 6)

Should (formula 6) derive from above-mentioned formula (4).

Then, in order to make engine rotary speed approach target, the deviation of engine rotary speed and expected value is multiplied by the feedback gain of predefined regulation, calculates the feedback compensation torque Tmg2fb(step 205 of feedback compensation torque Tmg1fb and second dynamotor 5 of the first dynamotor 4).

Then, according to (formula 7) below engine rotary speed utilization, calculate target engine rotary acceleration (step 206).

Neta=(Net-Neto)/Tc ... (formula 7)

In this (formula 7),

Neta: target engine rotary acceleration

Net: target engine rotative speed

Neto: target engine rotative speed previous value

Tc: this program performance period.

Then, the inertia that (formula 8) below the utilization of target engine rotary acceleration, (formula 9) are calculated the first dynamotor 4 and the second dynamotor 5 according to this is proofreaied and correct torque (step 207).

Tmg1ine=(Img1 * (k1+1)) * 2 π/60 * Neta+Ie * (k2+1/k1+k2+1) * 2 π/60 * Neta ... (formula 8)

Tmg2ine=(Img2 * (k2)) * 2 π/60 * Neta+Ie * (k1/k1+k2+1) * 2 π/60 * Neta ... (formula 9)

In above-mentioned (formula 8), (formula 9),

Tmg1ine: the inertia of the first dynamotor is proofreaied and correct torque

Tmg2ine: the inertia of the second dynamotor is proofreaied and correct torque

Img1: the inertia of the first dynamotor

Img2: the inertia of the second dynamotor

Neta: target engine rotary acceleration

Ie: the inertia of driving engine

K2: by the lever ratio between axle drive shaft (OUT)-second dynamotor (MG2) being made as between driving engine (ENG)-axle drive shaft (OUT) in the situation of " 1 ".

Then, each feedback compensation torque Tmg1fb, Tmg2fb, each inertia are proofreaied and correct to torque Tmg1ine, Tmg2ine and add each basic torque Tmg1i, Tmg2i, calculate as the torque instruction value Tmg1 of the control command value of the first dynamotor 4 with as the torque instruction value Tmg2(step 208 of the control command value of the second dynamotor 5).

The torque instruction value Tmg1 of the first dynamotor 4 is calculated by Tmg1=Tmg1i+Tmg1fb+Tmg1ine.

The torque instruction value Tmg2 of the second dynamotor 5 is calculated by Tmg2=Tmg2i+Tmg2fb+Tmg2ine.

Then, utilize this torque instruction value Tmg1, Tmg2 calculating to drive control to the first dynamotor 4, the second dynamotor 5, can suppress thus the startup of driving engine 2 and impact and driving engine 2 is started, and can export as the propulsive effort of target and will discharging and recharging of battery 18 be made as to expected value.

Then, program is returned to (step 209).

Fig. 6 illustrates target engine torque, the target torque of the first dynamotor 4, the variation of the target torque of the second dynamotor 5 and real engine rotative speed till engine rotary speed rises.At this, the torque that outputs to axle drive shaft 8 is constant.

At the time T a place of Fig. 6, as shown in the alignment chart of Fig. 7, carry out EV and travel, free-wheel clutch 10 bears the reaction force torque of the second dynamotor 5 and travels.

At the time T b place of Fig. 6, as shown in the alignment chart of Fig. 8, be the timing of request start the engine.With this engine starting request while, the current torque that free-wheel clutch 10 bears is set to the initial value of target engine torque.Torque phase when the first dynamotor 4 going out according to the calculation of initial value of this target engine torque, the torque of the second dynamotor 5 are travelled with EV, than constant, does not have the point of discontinuity of torque.

At the time T c place of Fig. 6, as shown in the alignment chart of Fig. 9, be that initial value from target engine torque slowly changes to while starting target engine torque midway, target engine torque is zero (0) timing (Nm).At this regularly, for free-wheel clutch 10 does not bear reaction force torque, with the torque of the first dynamotor 4, bear the state of the reaction force torque of the second dynamotor 5.

At the time T d place of Fig. 6, as shown in the alignment chart of Figure 10, be that target engine torque is reduced to while starting near target engine torque, engine rotary speed starts the timing of rising.

Figure 19～Figure 22 illustrates the alignment chart under representational operating state.

At this, k1, k2 define as following.

k1＝ZR1/ZS1

k2＝ZS2/ZR2

At this,

ZS1: the number of teeth of the first sun wheel

ZR1: the number of teeth of first ring generating gear

ZS2: the number of teeth of the second sun wheel

ZR2: the number of teeth of the second Ring gear.

By the alignment chart of Figure 19～Figure 22, each operating state is described.

In addition, in the alignment chart of this Figure 19～Figure 22, rotative speed is that the hand of rotation of driving engine 2 is made as to positive dirction, and the torque of each axle input and output is that input and the direction of the equidirectional torque of torque phase of driving engine 2 are just defined as.Therefore, axle drive shaft torque is that positive situation is that the state that output will rearward drive the torque of vehicle (is deceleration while advancing, while retreating, be driving), on the other hand, axle drive shaft torque is that negative situation is the state (, for driving, being deceleration while retreating while advancing) that output will forwards drive the torque of vehicle.

At the first dynamotor 4 and the second dynamotor 5, generate electricity, power running in the situation that, the heating of the first inverter 15, the second inverter 16, the first dynamotor 4, the second dynamotor 5 can cause damage, therefore the efficiency in the situation that converting between electric energy and mechanical energy is not 100%, but supposes that free of losses describes for the purpose of simplifying the description.

The in the situation that of considering loss in reality, as long as control the electricity that goes out the amount of the energy losing due to loss for multiple.

(1), low gear ratio state (with reference to Figure 19)

This is to utilize driving engine 2 to travel, and the rotative speed of the second dynamotor 5 is the state of zero (0).Figure 19 illustrates alignment chart now.The rotative speed of the second dynamotor 5 is zero (0), therefore power consumption not.Therefore,, in the situation that not to the discharging and recharging of battery 18, do not need to generate electricity with the first dynamotor 4, therefore the torque instruction value Tmg1 of the first dynamotor 4 is zero (0).In addition, engine rotary speed is (1+k2)/k2 with the ratio of axle drive shaft rotative speed.

(2), middle gear speed ratio state (with reference to Figure 20)

This is to utilize driving engine 2 to travel, and the rotative speed of the first dynamotor 4 and the second dynamotor 5 is positive state.Figure 20 illustrates alignment chart now.In this case, in the situation that discharging and recharging battery 18 not, the first dynamotor 4 regeneration, make the second dynamotor 5 carry out power running (speed that transmission of power is kept in balance when wheel (drive wheel) accelerates or goes up a slope) with this regenerated electric power.

(3), high gear ratio state (with reference to Figure 21)

This is to utilize driving engine 2 to travel, and the rotative speed of the first dynamotor 4 is the state of zero (0).Figure 21 illustrates alignment chart now.The rotative speed of the first dynamotor 4 is zero (0), does not therefore regenerate.Therefore,, in the situation that not to the discharging and recharging of battery 18, do not carry out power running, the regeneration of the second dynamotor 5, the torque instruction value Tmg2 of the second dynamotor 5 is zero (0).In addition, engine rotary speed is k1/(1+k1 with the ratio of axle drive shaft rotative speed).

(4), there is the state (with reference to Figure 22) of power cycle

In the speed of a motor vehicle than the high gear ratio state of Figure 22 also under high state, the state that the first dynamotor 4 is reversion.Under this state, the first dynamotor 4 carries out power running, power consumption.Therefore, in the situation that not to the discharging and recharging of battery 18, the second dynamotor 5 is regenerated and is generated electricity.

Above, embodiments of the invention have been described, the formation of above-described embodiment have been applied to every claim and describe.

First, in the invention that claim 1 is recorded, in the situation that driving engine 2 is started, be, after the torque that acts on the output shaft 3 of driving engine 2 slowly reduces, to make motor torque slowly change to the required torque of shaking of driving engine 2.

Thus, can when applying the required torque of engine starting, avoid stair-stepping torque to change, therefore can suppress the sharply change of propulsive effort, the impact while reducing engine starting.

In the invention of recording in claim 2, a plurality of dynamotors comprise the first dynamotor 4 and the second dynamotor 5.Using comprise driving engine 2, the first dynamotor 4, the second dynamotor 5 and as 4 key elements of the axle drive shaft 8 of output link in alignment chart by the first dynamotor 4, driving engine 2, as the axle drive shaft 8 of output link, the order of the second dynamotor 5 connects to form the Poewr transmission mechanism 9 as gear mechanism.And, in the situation that driving engine 2 is started, the first dynamotor 4 make torque be slowly changed to by be equivalent to finally to act on the torque of torque of output shaft 3 of driving engine 2 and driving engine 2 shake that required torque is added the torque that obtains and by its output, in addition, the required torque of driving of the second dynamotor 5 output vehicles.

Thus, can export the required torque of travelling of vehicle and output engine and start required torque.

In the invention of recording in claim 3, control unit 17 possesses: target engine torque is calculated unit 17E, it is in the situation that starting driving engine 2, the target engine torque initial value of the torque value of output shaft 3 that output acts on driving engine 2 when engine starting request occurs during as engine starting, calculate the required torque of shaking of driving engine 2, make target engine torque slowly change to the required torque of shaking of driving engine 2 from target engine torque initial value; Target engine rotative speed is calculated unit 17F, target engine rotative speed when it calculates engine starting; Target engine power is calculated unit 17G, and it is according to being calculated target engine rotative speed that unit 17F calculates by this target engine rotative speed and calculating by target engine torque the target engine torque that unit 17E calculates and calculate target engine power; Target drive power is calculated unit 17B, and it is based on calculating target drive power by the detected accelerator operation amount of accelerator operation amount detection unit 32 with by the detected speed of a motor vehicle of speed of a motor vehicle detecting unit 33; Target power is calculated unit 17H, and it will be calculated target drive power that unit 17B calculates and be made as target power by the difference that target engine power is calculated the target engine power that unit 17G calculates by this target drive power; And motor torque command value arithmetic element 17I, its utilization comprises the torque balance system of target engine torque and comprises that the power balance formula of target power calculates the command torque value of the first dynamotor 4, the second dynamotor 5.

Thus, the first dynamotor 4 that target engine torque initial value during according to engine starting is calculated, the target torque of the second dynamotor 5 and calculate former target torque and compare constant, then make target torque slowly change, therefore can suppress the sharply change of propulsive effort, the impact while reducing engine starting.

In the invention of recording in claim 4, the mechanism of the output shaft 3 of stationary engine 2 is stop mechanisms 39.The torque that acts on the output shaft 3 of driving engine 2 be zero (0) (Nm) near time, stop mechanism 39 carries out opening operation.

Thus, can prevent the generation to the impact of vehicle.

description of reference numerals

1 engine start control device

2 driving engines (ENG)

4 first dynamotors (MG1)

5 second dynamotors (MG2)

6 drive wheels

8 axle drive shafts (OUT)

9 Poewr transmission mechanisms

15 first inverters

16 second inverters

17 control units

17A target drive force is calculated unit

17B target drive power is calculated unit

17C target discharges and recharges power and calculates unit

17D is tentative, and target engine power is calculated unit

17E target engine torque is calculated unit

17F target engine rotative speed is calculated unit

17G target engine power is calculated unit

17H target power is calculated unit

17I motor torque command value arithmetic element

18 batteries

32 accelerator operation amount detection units

33 speed of a motor vehicle detecting units

34 battery charging state detecting units

35 engine rotary speed detecting units

39 stop mechanisms

42 torque detecting units

Claims

1. an engine start control device for motor vehicle driven by mixed power, utilizes the output from driving engine and a plurality of dynamotors vehicle to be driven to the mechanism that controls and possess the output shaft of fixing above-mentioned driving engine, it is characterized in that,

In the situation that making above-mentioned engine starting, after the torque that makes to act on the output shaft of above-mentioned driving engine slowly reduces, make motor torque slowly change to the required torque of shaking of above-mentioned driving engine.

2. the engine start control device of motor vehicle driven by mixed power according to claim 1, is characterized in that,

Above-mentioned a plurality of dynamotor comprises the first dynamotor and the second dynamotor,

4 key elements that comprise above-mentioned driving engine, above-mentioned the first dynamotor, above-mentioned the second dynamotor and output link are connected to form gear mechanism by the order of above-mentioned the first dynamotor, above-mentioned driving engine, above-mentioned output link, above-mentioned the second dynamotor in alignment chart

In the situation that making above-mentioned engine starting,

Above-mentioned the first dynamotor is slowly changed to torque the torque of torque and the required torque of shaking of above-mentioned driving engine that are equivalent to finally to act on the output shaft of above-mentioned driving engine are added to the torque obtaining and are exported,

The required torque of driving of above-mentioned the second dynamotor output vehicle.

3. an engine start control device for motor vehicle driven by mixed power, utilizes the output from driving engine and a plurality of dynamotors vehicle to be driven to the mechanism that controls and possess the output shaft of fixing above-mentioned driving engine, it is characterized in that,

Be provided with the accelerator operation amount detection unit that detects accelerator operation amount,

Be provided with the speed of a motor vehicle detecting unit that detects the speed of a motor vehicle,

Be provided with control unit, it possesses:

Target engine torque is calculated unit, it is in the situation that making above-mentioned engine starting, the target engine torque initial value of the torque value of calculating the output shaft that acts on above-mentioned driving engine when engine starting request occurs during as engine starting, calculate the required torque of shaking of above-mentioned driving engine, make target engine torque slowly change to the required torque of shaking of above-mentioned driving engine from above-mentioned target engine torque initial value;

Target engine rotative speed is calculated unit, target engine rotative speed when it calculates engine starting;

Target engine power is calculated unit, and it is according to being calculated the target engine rotative speed of calculating unit and calculated by above-mentioned target engine torque the target engine torque of calculating unit and calculate target engine power by this target engine rotative speed;

Target drive power is calculated unit, and it is based on calculating target drive power by the detected accelerator operation amount of above-mentioned accelerator operation amount detection unit with by the detected speed of a motor vehicle of above-mentioned speed of a motor vehicle detecting unit;

Target power is calculated unit, and it is made as target power by calculated the target drive power of calculating unit and the difference of being calculated the target engine power of calculating unit by above-mentioned target engine power by this target drive power; And

Motor torque command value arithmetic element, its utilization comprises the torque balance system of target engine torque and comprises that the power balance formula of target power calculates the command torque value of above-mentioned a plurality of dynamotors.

4. according to the engine start control device of the motor vehicle driven by mixed power described in any one in claims 1 to 3, it is characterized in that,

The mechanism of the output shaft of fixing above-mentioned driving engine is stop mechanism,

In the time of near the torque that acts on the output shaft of above-mentioned driving engine is zero (Nm), above-mentioned stop mechanism carries out opening operation.