CN101741172B - Hybrid power system - Google Patents

Abstract

The invention relates to the field of parallel hybrid power automobiles, in particular to a hybrid power system of a parallel hybrid power automobile. The hybrid power system comprises an engine, a model clutch, a motor and a speed changer, wherein the model clutch comprises a flywheel and a clutch pressure plate used as a large inertia part and a clutch friction disc used as a small inertia part; the clutch friction disc used as the small inertia part is arranged at a crankshaft output end of the engine through a torsional vibration damper; the flywheel and the clutch pressure plate used as the large inertia part are arranged on an input shaft of the motor; and the input shaft of the motor is also provided with a bearing capable of bearing the axial force. By adopting the hybrid power system, the starting time and starting energy are greatly reduced when the engine is started, the impact is reduced, and the abrasion of the clutch is reduced.

Description

Hybrid power system

Technical field

The present invention relates to the parallel hybrid electric field, relate in particular to the hybrid power system and the mode switching method thereof of parallel hybrid electric.

Background technology

The scarcity of the energy and internal-combustion engines vehicle have promoted the development of hybrid power system to the gross pollution of atmosphere.In configuration aspects, hybrid power system is made up of two or more propulsion source, and these two kinds of propulsions source generally are driving engine and motor.Modal parallel connection type hybrid power system is between driving engine and change-speed box motor to be set, this motor both can be used as electrical motor and had been used for start the engine or powered vehicle, can be used as electrical generator again, under regenerative braking or driving power generation mode, provide electric energy for electrokinetic cell.Like this, by suitable control policy, hybrid power system can be given full play to the advantage of combustion engine and motor, when improving energy consumption and discharging significantly, obtains the same performance of internal-combustion engines vehicle drive system, has market-oriented prospect.

And, have two kinds of versions commonly used at present in the parallel hybrid electric field.One is the double-clutch mixed power system, and it is two for only there being the hybrid power system of regime clutch.The double-clutch mixed power system also is provided with the another one power-transfer clutch except being provided with the shift clutch between driving engine and motor between motor and change-speed box, under the situation of this power-transfer clutch combination, automobile is in hybrid mode; And in this disengaging of clutch, automobile can move with electric-only mode, and we claim that this power-transfer clutch is a regime clutch.As shown in Figure 1, driving engine 10 connects motor 12 via regime clutch 11, and motor 12 is connected to change-speed box 14 via shift clutch 13.The double-clutch mixed power system starts to walk with electric-only mode, uses motor to accelerate to a certain speed of a motor vehicle with one grade of powered vehicle of change-speed box, and slow then binding pattern power-transfer clutch directly is dragged to driving engine minimum startup rotating speed, carries out the oil spout igniting again; Perhaps the enriching injection process process when saving engine starting directly is dragged to idling with driving engine, can obviously reduce discharging, improves fuel economy.When the binding pattern power-transfer clutch, when reducing engine starting to the impact of car load, and to the demand of power of motor, the power that can cut off earlier between power system and the car load connects, and can realize by separating shift clutch for the double-clutch mixed power system.

The hybrid power system that regime clutch is only arranged is save shift clutch exactly between motor and change-speed box, motor directly links to each other with change-speed box, serves as shift clutch usefulness with regime clutch, or adopts no-clutch gearshift technology.In this hybrid power system, when the binding pattern power-transfer clutch, to the impact of car load, and, can pluck shelves by change-speed box and realize when reducing engine starting the demand of power of motor.

In above-mentioned two kinds of hybrid power systems, regime clutch generally adopts dry friction clutch, can certainly adopt wet friction clutch or magnetic clutch.For convenience, we are that example describes with the dry friction clutch.Regime clutch is divided into two parts, and a part is made up of the flywheel and the clutch driving disc of big inertia, and another part is the very little clutch disk of inertia.As shown in Figure 2, for the hybrid vehicle that adopts combustion engine, flywheel 21 is installed on the engine crankshaft mouth 23, engine crankshaft is provided with the thrust baring that is used for bearing the thrust that flywheel passes over, clutch driving disc 28 is installed on the flywheel 21, and clutch disk 29 is installed in by torsion vibration absorber 22 on the spline of motor input shaft 25, also is provided with release thrust bearing 26 on motor input shaft 25.So just formed, big inertia part all is linked to be integral body with engine crankshaft system, and little inertia part is connected with the motor input shaft.In engine starting process, motor will be done the rotation function that many merits are set up big inertia spare more, and this has caused too much energy dissipation on the one hand, has increased run up time; On the other hand, the big inertia resistance square owing to big inertia spare causes has increased the load and the impact of motor, has increased the sliding wear of regime clutch simultaneously, the life-span of having reduced power-transfer clutch; Moreover, during disengaging of clutch, engine off, the rotational kinetic energy of the not only rotational kinetic energy of engine crankshaft, and flywheel all will be fallen by the friction slow consumption of driving engine self.

Summary of the invention

For addressing the above problem, the present invention proposes a kind of new hybrid power system, big to overcome present hybrid vehicle startup energy consumption, run up time is long, defectives such as motor load and impact are big, and the service life of improving regime clutch, the energy consumption when reducing the regime clutch separation is improved hybrid vehicle traveling comfort, fuel economy and emission performance.

Described hybrid power system comprises driving engine, regime clutch, motor and change-speed box, described regime clutch comprises as the flywheel of big inertia part and clutch driving disc and as little inertia clutch portions friction disc, be installed on the crankshaft output end of driving engine by torsion vibration absorber as little inertia clutch portions friction disc, and on the input shaft that the flywheel of the big inertia part of conduct and clutch driving disc are installed to motor, on the input shaft of motor, also be provided with the bearing that bears axial force.

After adopting above-mentioned hybrid power system, when start the engine, will reduce run up time greatly and start energy, reduce impact simultaneously, reduce the wearing and tearing of power-transfer clutch.And big inertia parts such as flywheel have been installed to after the torsion vibration absorber, have reduced the preceding rotor inertia of torsion vibration absorber, have improved the damping effect of torsion vibration absorber, have further isolated the vibrations of driving engine effectively, thereby have improved the traveling comfort of car load.Moreover after the flywheel postposition, flywheel and rotor link together, because rotor itself has certain rotor inertia, can reduce the size of flywheel.

And such design has overcome the inertial thinking of existence of the prior art, has brought beneficial technical effects.Particularly, at first, the running of driving engine be unable to do without flywheel, on the engine crankshaft mouth flywheel is installed, and flywheel is the mounting means that all orthodox car driving engines are adopted as the driving disc spacing pressing of power-transfer clutch, is a kind of inertial thinking of the prior art.Secondly, in the prior art, when driving engine dispatches from the factory, all reserved on the crankshaft output end of driving engine and will adorn flywheel.But the contriver does not stick to such inertial thinking, finds behind in-depth study, for hybrid vehicle, under electric-only mode, does not need the work of driving engine, so driving engine can be thrown off flywheel fully; And when the needs engine operation, but be at hybrid mode or power generation mode, at this moment regime clutch is combination, i.e. flywheel and driving engine one.Thus, above-mentioned later-model hybrid power system has been proposed.

At above-mentioned hybrid power system, preferably, described clutch disk is connected on the spline of Coupling Shaft one end by torsion vibration absorber, and the other end of this Coupling Shaft is connected on the crankshaft output end of driving engine.

Perhaps, the crankshaft output end of described driving engine is provided with spline, and described clutch disk passes through the torsion vibration absorber direct mount to this spline.

Particularly, described flywheel is installed on the input shaft of described motor by key connection mode or bolt connecting mode.

From electric-only mode when hybrid mode is switched, reasonably set the speed of a motor vehicle when switching, can realize that zero electric energy start the engine to minimum startup rotating speed (as about 200rpm), can save the startup energy so more.

Speed of a motor vehicle when perhaps more rational setting is switched can drag driving engine to idling (as about 700rpm) by zero electric energy, thereby cancellation starts the enriching process, and then reduces discharging, improves fuel economy.

More preferably, from electric-only mode when hybrid mode is switched, incorporating transmission adds retaining, utilizes gearshift start the engine at interval, can save run up time more, improves dynamic property.

Further, rationally set the ratio between change-speed box one, the second gear transmitting ratio, can realize directly changing synchronously second gear, save synchronization time, reduce the wearing and tearing of synchro.

Description of drawings

Fig. 1 is the double-clutch mixed power system schematic;

Fig. 2 is the mounting means of regime clutch in the conventional hybrid power system;

Fig. 3 is the mounting means of regime clutch in the hybrid power system of the present invention;

Fig. 4 is the brace and connecting rod framework scheme drawing used when setting up engine starting process resistance model and the force analysis figure of piston;

Fig. 5 is the kinetic model of system used when setting up clutch model;

Fig. 6 is the comparison scheme drawing of the run up time of start the engine in run up time of start the engine in the conventional hybrid power system and the hybrid power system of the present invention;

Fig. 7 is the comparison scheme drawing of the startup energy of start the engine in the startup energy of start the engine in the conventional hybrid power system and the hybrid power system of the present invention.

The specific embodiment

As shown in Figure 3, in hybrid power system of the present invention, regime clutch is to install like this, be installed on the spline of Coupling Shaft 30 1 ends by torsion vibration absorber 32 as little inertia clutch portions friction disc 39, and the other end of this Coupling Shaft 30 connects engine crankshaft mouth 33, and the Coupling Shaft 30 of close engine crankshaft output shaft 33 1 sides of regime clutch is provided with release thrust bearing 36.At opposite side, clutch driving disc 38 is installed on the flywheel 31, just has been installed on the motor input shaft 35 as big inertia clutch portions platen 38 and flywheel 31 like this.Particularly, flywheel is in conjunction with the motor input shaft, or by bolted connection motor input shaft by the flat key on the self structure, spline.In order to bear axial force, motor input shaft 35 is provided with angular contact bearing 34, and thrust baring can certainly be set.

Principle of work of the present invention is as follows: during vehicle starting, and the clastotype power-transfer clutch, the change-speed box put in the first speed uses the motor-driven vehicle start.After accelerating to a certain speed of a motor vehicle, slowly the binding pattern power-transfer clutch directly is dragged to driving engine minimum startup rotating speed, carries out the oil spout igniting again; Perhaps the enriching injection process process when saving engine starting directly is dragged to idling with driving engine, can obviously reduce discharging, improves fuel economy.When the binding pattern power-transfer clutch, when reducing engine starting to the impact of car load, and to the demand of power of motor, the power that can cut off earlier between power system and the car load connects, can realize by separating shift clutch for the double-clutch mixed power system, can pluck shelves by change-speed box for the hybrid power system that regime clutch is only arranged and realize.

When from electric-only mode when hybrid mode is switched, motor outage separates shift clutch simultaneously or change-speed box is put neutral, this moment, motor speed was ω ₀Binding pattern power-transfer clutch then, when regime clutch principal and subordinate Moving plate (being clutch driving disc and clutch disk) synchronously after, the big inertia part of rotor and regime clutch directly is dragged to rotational speed omega with driving engine with the kinetic energy of storage ₁

ω ₀And ω ₁Between relational expression be

$\frac{1}{2}(I_e+I_{c1}){{\mathrm{\ω}}_1}^2+E_e+E_m+E_c=\frac{1}{2}(I_m+I_{c2})({{\mathrm{\ω}}_0}^2-{{\mathrm{\ω}}_1}^2)---\left(1\right)$

Can get after the arrangement

${\mathrm{\&omega;}}_0=\sqrt{\frac{(I_e+I_m+{\mathrm{<figure-callout\; id="1"\; label="I\; c"\; filenames="H2009102660221E00051.png"\; state="\{\{state\}\}">I</figure-callout>}}_c+I_{c2}){{\mathrm{\&omega;}}_1}^2+2(E_e+E_m+E_c)}{I_m+I_{c2}}}---\left(2\right)$

I in the formula _eThe rotor inertia of-engine crankshaft system;

I _mThe rotor inertia of-rotor;

I _C1The rotor inertia of the little inertia partial frictional of-regime clutch dish;

I _C2The rotor inertia of the big inertia part of-regime clutch (flywheel and platen);

E _eIn-the start-up course because the degradation of energy that engine interior friction and pressurized air produce, can be by test determination;

E _mIn-the start-up course because the degradation of energy of motor internal friction output, can be by test determination;

E _cThe degradation of energy that the regime clutch cunning is rubbed and produced in-the cohesive process.

Motor speed ω ₀And the relational expression between the speed of a motor vehicle is

$u_a=0.377\frac{r{\mathrm{\&omega;}}_0}{i_g{i}_0}---\left(3\right)$

U in the formula _a-automobile driving speed;

The r-radius of wheel;

i _g-transmission ratio;

i ₀-main reduction gear transmitting ratio.

Formula (2) substitution formula (3) can be got

$u_a=0.377\frac{r}{i_g{i}_0}\sqrt{\frac{(I_e+I_m+I_{\mathrm{<figure-callout\; id="1"\; label="c"\; filenames="H2009102660221E00051.png"\; state="\{\{state\}\}">c</figure-callout>}1}+I_{c2}){{\mathrm{\&omega;}}_1}^2+2(E_e+E_m+E_c)}{I_m+I_{c2}}}---\left(4\right)$

Driving engine is normally started, the rotational speed omega after driving engine drags ₁Must satisfy relational expression

ω ₁≥ω ₁’(5)

ω in the formula ₁The minimum startup rotating speed of '-driving engine.

Preferably, in order to reduce the discharging of driving engine, the enriching oil spout during the cancellation engine starting, the rotational speed omega after driving engine drags ₁Must satisfy relational expression

ω ₁≥ω ₁”(6)

ω in the formula ₁The idle speed value of "-driving engine.

With ω ₁=ω ₁' bring formula (4) into and can try to achieve u _a=u _a', to realize that promptly zero electric energy drags driving engine to minimum startup rotational speed omega ₁', start the speed of a motor vehicle and must satisfy relational expression

u _a≥u _a’；(7)

With ω ₁=ω ₁" bring formula (4) into and can try to achieve u _a=u _a", to realize that promptly zero electric energy drags driving engine to idling ω ₁", the speed of a motor vehicle must satisfy relational expression before starting

u _a≥u _a”。(8)

More than the design can only use under normal circumstances, promptly by the electric-only mode starting-up to speed to the speed of a motor vehicle more than or equal to u _a', and then switch to hybrid mode, can realize zero electric energy start the engine like this.Certainly zero power consumption also is comparatively speaking, be used for the rotation function of flywheel of start the engine also be before power consumption set up.When other situations, speed of a motor vehicle out of reach u during as switching _a', the rotation function that rotor adds flywheel and platen is not enough to driving engine is dragged to minimum startup rotational speed omega ₁', at this moment can make motor enter speed-regulating mode and force to satisfy formula (7).

When the binding pattern power-transfer clutch, when reducing engine starting to the impact of car load, and to the demand of power of motor, the power that can cut off earlier between power system and the car load connects, can realize by separating shift clutch for the double-clutch mixed power system, and for the hybrid power system that regime clutch is only arranged, can pluck shelves by change-speed box and realize.The double-clutch mixed power system adopts shift clutch and MT change-speed box, by manually shifting gears.By electric-only mode when hybrid mode is switched, can pluck shelves and cut off power system and be connected by separating shift clutch or change-speed box with the power of car load, more preferably, can incorporating transmission adding retaining utilizes gearshift to come start the engine at interval, when being electric-only mode, travel for one grade with change-speed box, accelerate to speed of a motor vehicle u _a, this moment, motor speed was ω ₀, motor outage then, change-speed box is plucked shelves, the binding pattern power-transfer clutch, start the engine, at this moment driving engine and rotating speed of motor are reduced to ω ₁More preferably, the proportionate relationship between the transmitting ratio of one grade of appropriate design change-speed box and second gear can make rotating speed behind the engine starting just equal the rotating speed of transmission output shaft, and at this moment change-speed box can not need synchro work and directly hang second gear.Realize directly changing synchronously second gear, the transmitting ratio of one grade of change-speed box and second gear must satisfy relational expression

$i_1=\frac{{\mathrm{\&omega;}}_0}{{\mathrm{\&omega;}}_1}{i}_2$ (9)

ω in the formula ₀-mode switch front motor rotating speed

ω ₁-mode switch rear engine rotating speed

i ₁One grade of transmitting ratio of-change-speed box;

i ₂-change-speed box second gear transmitting ratio.

Gearshift start the engine is at interval adopted in this design, has saved run up time, has improved dynamic property.And, realize directly changing synchronously second gear by the proportionate relationship between the transmitting ratio of one grade of appropriate design change-speed box and second gear, and also shortened the gearshift time relatively simultaneously, reduced the wearing and tearing of synchro.Yet, guarantee that the speed of a motor vehicle before the start the engine equals u _a, and utilize gearshift start the engine at interval, need chaufeur judgment and skilled maneuvering ability accurately.And for the hybrid power system that regime clutch is only arranged, it is just easier to implement.Only there is the hybrid power system of regime clutch to cancel shift clutch, and adopts the AMT change-speed box, come self shifter by gearshift controller control gearshift.Schedule and Starting Control strategy all are fixing in program in advance.Promptly stipulate to accelerate to speed of a motor vehicle u with one grade of starting of electric-only mode _a, promptly motor speed reaches ω ₀, the beginning mode switch, behind the engine starting, change-speed box directly changes second gear to be continued to travel with hybrid mode.

In order to verify the progress of embodiment of the present invention with respect to the conventional hybrid power system, let us adopts Matlab/simulink to set up realistic model, contrasts the influence of flywheel transposition front and back to engine starting by simulation result.We mainly set up engine starting process resistance model, regime clutch model and motor model.

1. engine starting process resistance model

Resisting moment in the engine starting process is mainly from three parts, a part is to affact the resisting moment that produces on the crankshaft crank by piston, connecting rod, the reciprocal inertia resistance that comprises the crank motion generation of parts such as piston, piston pin, wrist in end, the gas load that produces during Piston Compression gas, the cliding friction between piston bottom, piston ring and the cylinder and the friction drag that produces; Another part is because the sliding-frictional resistance square that the crankshaft-and-connecting-rod bearing produces.Third part is to be delivered to resisting moment on the bent axle by gear or timing belt, comprises that friction drag and engine accessory parts that valve system produces produce resistance.Because rotating speed was lower when driving engine had just begun to start, the resisting moment that valve system and appurtenances produce can be ignored.

1.1 affact resisting moment on the bent axle by piston rod

The reciprocal change speed linear motion of piston changes the rotation of bent axle into by piston crank mechanism, the structural representation of piston crank mechanism as shown in Figure 4, the motion of connecting rod is to swing the compound of relative motion with the transport motion of piston translation with around piston pin, for the ease of calculating, connecting rod is carried out the quality replacement, with discrete mass is to replace actual connecting rod, connecting rod quality is concentrated on 3 points (center, microcephaly hole, big draught animals center, centroid position), and think that these quality are that rigidity connecting rod by no quality couples together.Because the quality major part of connecting rod all concentrates on major part and little head part, the mass distribution of centroid position is very little to the result of calculation influence to two, therefore generally all adopts pair quality replacing systems.Think that promptly piston crank mechanism is the system of constrained particle that the rigidity connecting rod by no quality connects two lumped masses.

1.1.1 reciprocal inertia force

The speed v of piston and acceleration/accel j are respectively

$v=\mathrm{r\&omega;}\frac{\sin (\mathrm{\&alpha;}+\mathrm{\&beta;})}{\cos \mathrm{\&beta;}}---\left(10\right)$

$j=r{\mathrm{\&omega;}}^2[\frac{\cos (\mathrm{\&alpha;}+\mathrm{\&beta;})}{\cos \mathrm{\&beta;}}+\mathrm{\&lambda;}\frac{{\mathrm{<figure-callout\; id="2"\; label="cos"\; filenames="H2009102660221E00051.png,H2009102660221E00052.png"\; state="\{\{state\}\}">cos</figure-callout>}}^2\mathrm{\&alpha;}}{{\cos }^3\mathrm{\&beta;}}]---\left(11\right)$

ω in the formula-engine crankshaft rotational angular velocity;

$\mathrm{\&omega;}=\frac{\mathrm{d\&alpha;}}{\mathrm{dt}}$

α-crankshaft degree;

β-connecting rod and line of centers angle;

α, β satisfy relational expression

sinβ＝λsinα

λ-connecting rod ratio,

$\mathrm{\&lambda;}=\frac{r}{l}$

The r-crank radius,

The l-length of connecting rod.

So the reciprocal inertia resistance of piston is

F _j＝-(m _h+m _A)·j (12)

M in the formula _hThe total mass of-piston, piston pin, piston pin snap ring and piston ring;

m _AAfter-connecting rod replaces by two quality, concentrate on microcephaly's quality.

1.1.2 gas load

Pressurized air acts directly on piston head, promotes reciprocating motion of the pistons, and when piston was in compression with exhaust stroke, pressurized air was made negative work, becomes the resisting moment of driving engine.The Fg computing formula is

F _g＝(P _gas-P ₀)S _p (13)

P in the formula _GasPressure in the-cylinder;

P ₀-bar pressure;

S _pThe payload space of-piston head.

1.1.3 friction drag

Organism temperature during according to engine starting and lubricating oil flow regime, engine starting can be divided into cold start and hot start.Corresponding different starting process, the piston friction resistance is different.The piston friction resistance is by piston ring friction drag F _rWith piston bottom friction drag F _sConstitute.

1.1.3.1 piston friction resistance during cold start

In the process of engine cold starting, lubricating oil viscosity is big, flowing power is poor, needs a few minutes to tens minute ability to reach each friction means fully, in addition under low temperature condition, piston ring and cylinder, the gap is bigger between piston and the cylinder, can not form lubricant film.Therefore the lubricating status during engine cold starting is boundary lubrication, and coefficient of frictional resistance can be considered constant.

Friction force is between piston ring-cylinder liner

F _r＝μN ₁＝μ(P _gas+P ₀)S _r (14)

Piston bottom-cylinder sleeve friction force is

$F_s=\mathrm{\&mu;}{\mathrm{<figure-callout\; id="2"\; label="N"\; filenames="H2009102660221E00051.png,H2009102660221E00052.png"\; state="\{\{state\}\}">N</figure-callout>}}_2=\frac{(P_{\mathrm{gas}}+P_e)S_r(1-\mathrm{\&mu;}\tan \mathrm{\&beta;})}{\tan \mathrm{\&beta;}+1/\mathrm{\&mu;}}+\frac{((P_{\mathrm{gas}}-P_0)S_r+(m_h+m_A)(g+j))\tan \mathrm{\&beta;}}{\tan \mathrm{\&beta;}+1/\mathrm{\&mu;}}---\left(15\right)$

N in the formula ₁Pressure between-piston ring and cylinder sleeve;

N ₂Pressure between-piston bottom and cylinder sleeve;

Friction coefficient between μ-piston and the cylinder;

P _e-piston ring is to the elastic pressure of cylinder;

S _rThe area of contact of-piston ring and cylinder;

P ₀-bar pressure;

M _hThe quality of-piston and piston pin;

The past complex acceleration of j-piston;

The g-acceleration due to gravity.

1.1.3.2 piston friction resistance during hot start

During the engine thermal starting, organism temperature height, machine oil are also uncolled to get off, and the machine oil recoverable amount in each piston-ring slot is many; Gap between piston ring and cylinder sleeve is less in addition, and is better lubricated, is in the elasticity lubricating status.Friction force is between piston ring-cylinder liner

$F_r=a_{1}D({\mathrm{<figure-callout\; id="0"\; label="n"\; filenames="H2009102660221E00042.png,H2009102660221E00051.png"\; state="\{\{state\}\}">n</figure-callout>}}_0+0.4n_c)\sqrt{{\mathrm{\&eta;}}_v(P_e+P_{\mathrm{gas}})w}---\left(16\right)$

A in the formula ₁-piston ring shape coefficient;

η _vThe kinematic viscosity of-lubricating oil;

W-piston ring thickness;

The D-cylinder bore diameter;

n ₀-oil ring number;

n _c-compression ring number.

Piston bottom-cylinder sleeve friction force to the resistance of bent axle is

$F_s=a_2\mathrm{DM\&eta;}\frac{v}{h}---\left(17\right)$

The influence coefficient of a2 oil film thickness in the formula;

The h-oil film thickness;

The length of M-piston bottom.

1.1.4 piston force analysis

Utilization reaches the human relations principle to piston crank mechanism, and the stressed of piston analyzed, and as shown in Figure 4, piston stress balance equation is

N ₁＝(P _gas+P _e)S _r， (18)

F _Lsinβ+N ₁-N ₂＝0 (19)

F _Lcosβ+F _j+(m _h+m _A)g+F _g-F _r-F _s＝0，(20)

Simultaneous formula (18)-(20) are found the solution and can be got

$F_L=\frac{F_r+F_s-F_j-(m_h+m_A)g-F_g}{\cos \mathrm{\&beta;}}---\left(21\right)$

T in the formula _L-connecting rod is to the application force of piston pin.

So the resisting moment that the single cylinder connecting rod affacts on the bent axle is:

${\mathrm{<figure-callout\; id="1"\; label="T\; L"\; filenames="H2009102660221E00051.png"\; state="\{\{state\}\}">T</figure-callout>}}_L=[F_r+F_s-F_j-(m_h+m_A)g-F_g]\frac{\sin (\mathrm{\&alpha;}+\mathrm{\&beta;})}{\cos \mathrm{\&beta;}}r$

This hybrid vehicle adopts 4JB1 type diesel motor, and pattern is 4 cylinders, 4 strokes in upright arrangement.Phase angle in the driving engine between 4 cylinders differs 180 °.The resisting moment TL1 that the single cylinder connecting rod affacts on the bent axle is the function of crankshaft degree and crankshaft rotating speed ω, and (α, ω), then 4 cylinder rods affact resisting moment total on the bent axle and are to be designated as f

$T_L=\underset{0}{\overset{3}{\mathrm{\&Sigma;}}}f(\mathrm{\&alpha;}+i\frac{\mathrm{\&pi;}}{2},\mathrm{\&omega;})$

1.2 friction resistance moment by the plain bearing generation

In the process of engine cold starting, temperature is low, and lubricating oil viscosity is big, flowing power is poor, needs a few minutes to tens minute ability to reach each friction means fully, can't form lubricant film.Therefore the lubricating status of crankshaft-link rod bearing is boundary lubrication during engine cold starting, and coefficient of frictional resistance can be considered constant.The friction resistance moment of plain bearing is:

T _B＝∑μWR

μ-coefficient of sliding resistance in the formula;

The W-bearing load;

R-bearing sliding surface radius.

During the engine thermal starting, organism temperature height, machine oil are also uncolled to get off, and the machine oil recoverable amount in each bearing is many, better lubricated, is in the elasticity lubricating status.The friction resistance moment of plain bearing is:

$T_B=\mathrm{\&Sigma;}[-\frac{\mathrm{WC\&epsiv;}\sin \mathrm{\&phi;}}{2}-\frac{2{\mathrm{\&pi;}}^2\mathrm{SWC}}{{(1-{\mathrm{\&epsiv;}}^2)}^{1/2}}$

C-bearing radius clearance in the formula;

ε-eccentricity;

$\mathrm{\&epsiv;}=\frac{e}{C}$

The e-eccentric throw;

φ-attitude angle;

The S-rope is the Field number not;

$S=\frac{\mathrm{\&eta;N}}{W}\mathrm{LD}{\left(\frac{R}{C}\right)}^2;$

The N-rotating speed;

The L-bearing length.

1.3 the calculating of the total drag square of engine starting process

The total drag square that acts on the bent axle is:

T _z＝T _L+T _B (22)

2 clutch model

In the power-transfer clutch cohesive process, the kinetic model of system as shown in Figure 5.

At clutch driving case and the clutch plate kinetics equation before synchronously be

$(J_e+J_{c1})\frac{d{\mathrm{\&omega;}}_e}{d_t}=T_c-T_z$

$(J_m+J_{c2})\frac{d{\mathrm{\&omega;}}_m}{d_t}=T_m-T_c$

ω _e0＝0

ω _m0＝ω ₀

ω _e1＝ω _m1＝ω ₁

ω in the formula _e-engine speed;

ω _m-motor speed;

T _cThe friction torque of-clutch transmits;

T _zThe starting resistance square of-driving engine;

T _m-motor torque;

J _eThe rotor inertia of-driving engine;

J _mThe rotor inertia of-motor;

J _C1The rotor inertia of-power-transfer clutch A end;

J _C2The rotor inertia of-power-transfer clutch secondary part;

ω _E0The initial speed of-driving engine;

ω _M0The initial speed of-motor;

ω _E1, ω _M1Be the rotating speed after synchronous.

3 motor models

Motor adopts permagnetic synchronous motor (PMSM, permanent magnet synchronousmachine).This type motor volume is little, light weight, efficient height, flexible arrangement and control easily.When PMSM is carried out dynamic analysis, generally adopt Park to decompose, voltage in three phases, electric current, magnetic linkage are transformed to the d that rotates synchronously with rotor, two phasor1s in the q frame of axis.Dynamic differential equation through the permagnetic synchronous motor after the Park conversion is

$\left\{\begin{array}{c}\frac{d}{d_t}{i}_d=\frac{1}{L_d}{u}_d-\frac{R}{L_d}{i}_d+\frac{L_q}{L_d}\mathrm{p\&omega;}{i}_q\\ \frac{d}{d_t}{i}_q=\frac{1}{L_q}{u}_q-\frac{R}{L_q}{i}_q+\frac{L_d}{L_q}p{\mathrm{\&omega;}}_r{i}_d-\frac{\mathrm{\&lambda;p\&omega;}}{L_q}\\ T_m=1.5p[\mathrm{\&lambda;}{i}_q+(L_d-L_q)i_d{i}_q]\end{array}\right.$

L in the formula _q, L _d-q, d axle inductance (H);

R-stator winding resistance (Ω);

i _q, i _dThe stator current of-q, d axle (A);

u _q, u _dThe stator voltage of-q, d axle (V);

ω _r-rotor velocity (rads ^-1);

Coupling magnetic linkage (the W of λ-rotor permanent magnet on stator winding _b);

P-motor number of pole-pairs.

Usually often adopt rotor flux linkage orientation control (i at permagnetic synchronous motor _d=0), thus the torque relational expression can be reduced to

T _e＝1.5pλi _q (23)

By simulation calculation, obtain start the engine in different system run up time comparison scheme drawing (as shown in Figure 6) and start the comparison scheme drawing (as shown in Figure 7) of energy.In above-mentioned two figure, curve 1 be traditional hybrid power system simulation result, curve 2 is the simulation result of hybrid power system of the present invention.As can be seen from the figure, with respect to traditional hybrid power system, in hybrid power system of the present invention, shortened 44% run up time; Start energy and reduced 72%.

Claims (11)

1. hybrid power system, it comprises driving engine, regime clutch, motor and change-speed box, described regime clutch comprises as the flywheel of big inertia part and clutch driving disc and as little inertia clutch portions friction disc, it is characterized in that, be installed on the crankshaft output end of driving engine by torsion vibration absorber as little inertia clutch portions friction disc, and on the input shaft that the flywheel of the big inertia part of conduct and clutch driving disc are installed to motor, on the input shaft of motor, also be provided with the bearing that can bear axial force.

2. hybrid power system according to claim 1 is characterized in that described clutch disk is connected on the spline of Coupling Shaft one end by torsion vibration absorber, and the other end of this Coupling Shaft is connected on the crankshaft output end of driving engine.

3. hybrid power system according to claim 1 is characterized in that the crankshaft output end of described driving engine is provided with spline, and described clutch disk passes through the torsion vibration absorber direct mount to this spline.

4. according to any described hybrid power system in the claim 1 to 3, it is characterized in that described flywheel is installed on the input shaft of described motor by key connection mode or bolt connecting mode.

5. the mode switching method of a hybrid power system, this method is to any described hybrid power system implementation pattern switching controls of claim 1-4, it is characterized in that, at described hybrid power system is under the situation of double-clutch mixed power system, when from electric-only mode when hybrid mode is switched, the motor outage separates shift clutch simultaneously, and this moment, motor speed was ω ₀Binding pattern power-transfer clutch then, when the clutch driving disc of regime clutch and clutch disk synchronously after, the big inertia part of motor and regime clutch directly is dragged to driving engine minimum startup rotational speed omega with the kinetic energy of storage ₁, this moment, driving engine was all ω mutually with rotating speed of motor ₁ω ₀And ω ₁Between meet the following conditions and realize zero electric energy start the engine:

${\mathrm{\&omega;}}_0=\sqrt{\frac{(I_e+I_m+I_{c1}+I_{c2}){{\mathrm{\&omega;}}_1}^2+2(E_e+E_m+E_c)}{I_m+I_{c2}}}$

Wherein, I _eBe the rotor inertia of engine crankshaft system,

I _mBe the rotor inertia of rotor,

I _C1Be the rotor inertia of the little inertia partial frictional of regime clutch dish,

I _C2Be the flywheel of the big inertia part of regime clutch and the rotor inertia of clutch driving disc,

E _eFor in the start-up course because the degradation of energy that engine interior friction and pressurized air produce,

E _mFor in the start-up course because the degradation of energy of motor internal friction output,

E _cThe degradation of energy that rubs and produce for regime clutch cunning in the cohesive process.

6. the mode switching method of a hybrid power system, this method is to any described hybrid power system implementation pattern switching controls of claim 1-4, it is characterized in that, at described hybrid power system for only to have under the situation of regime clutch, when from electric-only mode when hybrid mode is switched, the motor outage, change-speed box is plucked shelves simultaneously, and this moment, motor speed was ω ₀Binding pattern power-transfer clutch then, when the clutch driving disc of regime clutch and clutch disk synchronously after, the big inertia part of motor and regime clutch directly is dragged to driving engine minimum startup rotational speed omega with the kinetic energy of storage ₁, this moment, driving engine was all ω mutually with rotating speed of motor ₁ω ₀And ω ₁Between meet the following conditions and realize zero electric energy start the engine:

${\mathrm{\&omega;}}_0=\sqrt{\frac{(I_e+I_m+I_{c1}+I_{c2}){{\mathrm{\&omega;}}_1}^2+2(E_e+E_m+E_c)}{I_m+I_{c2}}}$

Wherein, I _eBe the rotor inertia of engine crankshaft system,

I _mBe the rotor inertia of rotor,

I _C1Be the rotor inertia of the little inertia partial frictional of regime clutch dish,

I _C2Be the flywheel of the big inertia part of regime clutch and the rotor inertia of clutch driving disc,

E _eFor in the start-up course because the degradation of energy that engine interior friction and pressurized air produce,

E _mFor in the start-up course because the degradation of energy of motor internal friction output,

E _cThe degradation of energy that rubs and produce for regime clutch cunning in the cohesive process.

7. according to claim 5 or 6 described mode switching methods, it is characterized in that, work as ω ₁Be set at 〉=during the idle speed value of driving engine, the enriching oil spout in the time of can saving engine starting.

8. according to claim 5,6 or 7 described mode switching methods, it is characterized in that, utilize gearshift at interval start the engine promptly during electric-only mode, travel for one grade to save run up time with change-speed box, accelerate to speed of a motor vehicle u _a, this moment, motor speed was ω ₀, motor outage then, change-speed box is plucked shelves, the binding pattern power-transfer clutch, start the engine, this moment, driving engine and rotating speed of motor were reduced to ω ₁

9. mode switching method according to claim 8 is characterized in that, when the ratio between change-speed box one, the second gear transmitting ratio satisfies following the relation, can realize directly changing synchronously second gear:

$i_1=\frac{{\mathrm{\&omega;}}_0}{{\mathrm{\&omega;}}_1}{i}_2$

ω in the formula ₀Be mode switch front motor rotating speed

ω ₁Be mode switch rear engine rotating speed

i ₁Be one grade of transmitting ratio of change-speed box;

i ₂Be change-speed box second gear transmitting ratio.

10. hybrid vehicle, it comprises any described hybrid power system in the claim 1 to 4.

11. hybrid vehicle according to claim 10 is characterized in that, the hybrid power system of this hybrid vehicle adopts any described mode switching method in the claim 5 to 9.

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