CN101741172A - 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 severe contamination of atmosphere.In configuration aspects, hybrid power system is made up of two or more power source, and these two kinds of power sources generally are engine and motor.Modal parallel connection type hybrid power system is between engine and speed changer motor to be set, this motor both can be used as motor and had been used for ato unit or powered vehicle, can be used as generator again, under regenerative braking or driving power generation mode, provide electric energy for electrokinetic cell.Like this, by suitable control strategy, hybrid power system can be given full play to the advantage of internal 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 clutch except being provided with the shift clutch between engine and motor between motor and speed changer, under the situation of this clutch combination, automobile is in hybrid mode; And in this clutch separation, automobile can move with electric-only mode, and we claim that this clutch is a regime clutch.As shown in Figure 1, engine 10 connects motor 12 via regime clutch 11, and motor 12 is connected to speed changer 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 speed changer, and slow then binding pattern clutch directly is dragged to engine minimum startup rotating speed, carries out the oil spout igniting again; Perhaps the enriching injection process process when saving engine start directly is dragged to idling with engine, can obviously reduce discharging, improves fuel economy.When the binding pattern clutch, when reducing engine start to the impact of car load, and to the demand of power of motor, the power that can cut off earlier between dynamical 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 speed changer, motor directly links to each other with speed changer, serves as shift clutch usefulness with regime clutch, or adopts no-clutch gearshift technology.In this hybrid power system, when the binding pattern clutch, to the impact of car load, and, can pluck shelves by speed changer and realize when reducing engine start 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 electromagnetic 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 compressing 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 internal combustion engine, flywheel 21 is installed on the engine crankshaft output 23, engine crankshaft is provided with the thrust bearing that is used for bearing the thrust that flywheel passes over, clutch compressing 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 power shaft 25, also is provided with release bearing 26 on motor power 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 power 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 start-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 clutch; Moreover, during clutch separation, engine misses, 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 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, start-up time is long, defectives such as motor load and impact are big, and the useful life of improving regime clutch, the energy consumption when reducing the regime clutch separation is improved hybrid vehicle comfortableness, fuel economy and emission performance.

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

After adopting above-mentioned hybrid power system, when ato unit, will reduce start-up time greatly and start energy, reduce impact simultaneously, reduce the wearing and tearing of clutch.And big inertia parts such as flywheel have been installed to after the torsion vibration absorber, have reduced the preceding moment of inertia of torsion vibration absorber, have improved the damping effect of torsion vibration absorber, have further isolated the vibrations of engine effectively, thereby have improved the comfortableness of car load.Moreover after the flywheel postposition, flywheel and rotor link together, because rotor itself has certain moment of 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 engine be unable to do without flywheel, on the engine crankshaft output flywheel is installed, and flywheel is the mounting means that all orthodox car engines are adopted as the driving disc spacing pressing of clutch, is a kind of inertial thinking of the prior art.Secondly, in the prior art, when engine dispatches from the factory, all reserved on the crankshaft output end of engine and will adorn flywheel.But the inventor does not stick to such inertial thinking, finds after further investigation, for hybrid vehicle, under electric-only mode, does not need the work of engine, so 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 engine one.Thus, above-mentioned novel 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 engine.

Perhaps, the crankshaft output end of described engine is provided with spline, and described clutch disk directly is installed on this spline by torsion vibration absorber.

Particularly, described flywheel is installed on the power shaft of described motor by key connected 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 ato unit 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 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 ato unit at interval, can save start-up time more, improves dynamic property.

Further, rationally set the ratio between speed changer one, the second gear gearratio, can realize directly changing synchronously second gear, save lock in time, reduce the wearing and tearing of synchronizer.

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 dynamical 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 schematic diagram used when setting up engine start 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 schematic diagram of the start-up time of ato unit in start-up time of ato unit in the conventional hybrid dynamical system and the hybrid power system of the present invention;

Fig. 7 is the comparison schematic diagram of the startup energy of ato unit in the startup energy of ato unit in the conventional hybrid dynamical system and the hybrid power system of the present invention.

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 frictional disk 39, and the other end of this Coupling Shaft 30 connects engine crankshaft output 33, and the Coupling Shaft 30 of close engine crankshaft output shaft 33 1 sides of regime clutch is provided with release bearing 36.At opposite side, clutch compressing disc 38 is installed on the flywheel 31, just has been installed on the motor power shaft 35 as big inertia clutch portions platen 38 and flywheel 31 like this.Particularly, flywheel be by the flat key on the self structure, spline in conjunction with the motor power shaft, or connect the motor power shaft by bolt.In order to bear axial force, motor power shaft 35 is provided with angular contact bearing 34, and thrust bearing can certainly be set.

Operation principle of the present invention is as follows: during vehicle starting, and the clastotype clutch, speed changer puts in the first speed, and uses the motor-driven vehicle start.After accelerating to a certain speed of a motor vehicle, slowly the binding pattern clutch directly is dragged to engine minimum startup rotating speed, carries out the oil spout igniting again; Perhaps the enriching injection process process when saving engine start directly is dragged to idling with engine, can obviously reduce discharging, improves fuel economy.When the binding pattern clutch, when reducing engine start to the impact of car load, and to the demand of power of motor, the power that can cut off earlier between dynamical system and the car load connects, can realize by separating shift clutch for the double-clutch mixed power system, can pluck shelves by speed changer 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 speed changer is put neutral, this moment, motor speed was ω ₀Binding pattern clutch then, when regime clutch principal and subordinate Moving plate (being clutch compressing disc and clutch disk) synchronously after, the big inertia part of rotor and regime clutch directly is dragged to rotational speed omega with 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 moment of inertia of-engine crankshaft system;

I _mThe moment of inertia of-rotor;

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

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

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

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

E _cThe energy loss 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 reducing gear gearratio.

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

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

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

ω ₁≥ω ₁’(5)

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

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

ω ₁≥ω ₁”(6)

ω in the formula ₁The idle speed value of "-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 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 engine to idling ω ₁", the speed of a motor vehicle must satisfy relational expression before starting

u _a≥u _a”。(8)

More than design can only be used under normal circumstances, promptly accelerates to the speed of a motor vehicle more than or equal to u by the electric-only mode starting _a', and then switch to hybrid mode, can realize zero electric energy ato unit like this.Certainly zero power consumption also is comparatively speaking, be used for the rotation function of flywheel of ato unit also be before power consumption set up.When other situations, the speed of a motor vehicle does not reach u during as switching _a', the rotation function that rotor adds flywheel and platen is not enough to 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 clutch, when reducing engine start to the impact of car load, and to the demand of power of motor, the power that can cut off earlier between dynamical 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 speed changer and realize.The double-clutch mixed power system adopts shift clutch and MT speed changer, by manually shifting gears.By electric-only mode when hybrid mode is switched, can pluck shelves and cut off dynamical system and be connected by separating shift clutch or speed changer with the power of car load, more preferably, can incorporating transmission adding retaining utilizes gearshift to come ato unit at interval, when being electric-only mode, travel for one grade with speed changer, accelerate to speed of a motor vehicle u _a, this moment, motor speed was ω ₀, motor outage then, speed changer is plucked shelves, the binding pattern clutch, ato unit, at this moment engine and rotating speed of motor are reduced to ω ₁More preferably, the proportionate relationship between the gearratio of one grade of appropriate design speed changer and second gear can make rotating speed behind the engine start just equal the rotating speed of transmission output shaft, and at this moment speed changer can not need synchronizer work and directly hang second gear.Realize directly changing synchronously second gear, the gearratio of one grade of speed changer 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 gearratio of-speed changer;

i ₂-speed changer second gear gearratio.

Gearshift ato unit is at interval adopted in this design, has saved start-up time, has improved dynamic property.And, realize directly changing synchronously second gear by the proportionate relationship between the gearratio of one grade of appropriate design speed changer and second gear, and also shortened the gearshift time relatively simultaneously, reduced the wearing and tearing of synchronizer.Yet, guarantee that the speed of a motor vehicle before the ato unit equals u _a, and utilize gearshift ato unit at interval, need driver judgment and skilled maneuvering capability 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 speed changer, 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 start, speed changer 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 dynamical system, let us adopts Matlab/simulink to set up simulation model, contrasts the influence of flywheel transposition front and back to engine start by simulation result.We mainly set up engine starting process resistance model, regime clutch model and motor model.

1. engine start process resistance model

The moment of resistance in the engine starting process is mainly from three parts, a part is to affact the moment of resistance that produces on the crankshaft crank by piston, connecting rod, comprise the reciprocal inertia resistance of the reciprocating motion generation of parts such as piston, piston pin, small end of connecting rod, the gas load that produces during the piston Compressed Gas, the sliding friction between piston skirt, piston ring and the cylinder and the frictional resistance 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 the moment of resistance on the bent axle by gear or Timing Belt, comprises that frictional resistance and engine accessory parts that valve mechanism produces produce resistance.Because rotating speed was lower when engine had just begun to start, the moment of resistance that valve mechanism and appurtenances produce can be ignored.

1.1 affact the moment of resistance on the bent axle by piston rod

The reciprocal change speed linear motion of piston changes the rotation of bent axle into by toggle, the structural representation of toggle 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 toggle 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 j are respectively

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

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

ω in the formula-engine crankshaft rotational angular velocity;

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

α-crank angle;

β-connecting rod and center line angle;

α, β satisfy relational expression

sinβ＝λsinα

λ-connecting rod ratio,

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

The r-throw of crankshaft,

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 gross 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

Compressed air acts directly on top land, promotes reciprocating motion of the pistons, and when piston was in compression with instroke, compressed air was made negative work, becomes the moment of resistance of 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-atmospheric pressure;

S _pThe effective area of-top land.

1.1.3 frictional resistance

Organism temperature during according to engine start and the lubricating oil state that flows, engine start can be divided into cold start and hot exposure.Corresponding different starting process, the piston friction resistance is different.The piston friction resistance is by piston ring frictional resistance F _rWith piston skirt frictional resistance F _sConstitute.

1.1.3.1 piston friction resistance during cold start

In the process of engine cold starting, lubricating oil viscosity is big, mobile 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 lubricating oil film.Therefore the lubricating status during engine cold starting is boundary lubrication, and coefficient of frictional resistance can be considered constant.

Frictional force is between piston ring-cylinder liner

F _r＝μN ₁＝μ(P _gas+P ₀)S _r (14)

Piston skirt-cylinder sleeve frictional force is

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

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

N ₂Pressure between-piston skirt and cylinder sleeve;

Coefficient of friction between μ-piston and the cylinder;

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

S _rThe contact area of-piston ring and cylinder;

P ₀-atmospheric pressure;

M _hThe quality of-piston and piston pin;

The past complex acceleration of j-piston;

G-acceleration of gravity.

1.1.3.2 piston friction resistance during hot exposure

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 groove is many; Gap between piston ring and cylinder sleeve is less in addition, and is better lubricated, is in the elasticity lubricating status.Frictional force is between piston ring-cylinder liner

$F_r=a_{1}D({\mathrm{<figure-callout\; id="0"\; label="n"\; filenames="H2009102660221E00041.png,H2009102660221E00042.png"\; state="\{\{state\}\}">n</figure-callout>}}_0+0.4n_c)\sqrt{{\mathrm{\&eta;}}_v(P_e+P_{\mathrm{gas}})w}---\left(16\right)$

A in the formula ₁-piston ring form factor;

η _vThe kinematic viscosity of-lubricating oil;

W-piston ring thickness;

The D-cylinder bore;

n ₀-oil ring number;

n _c-compression ring number.

Piston skirt-cylinder sleeve frictional 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 skirt.

1.1.4 piston force analysis

Utilization reaches the human relations principle to toggle, 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 active force of piston pin.

So the moment of resistance 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 engine, and pattern is 4 cylinders, 4 strokes in upright arrangement.Phase angle in the engine between 4 cylinders differs 180 °.The moment of resistance TL1 that the single cylinder connecting rod affacts on the bent axle is the function of crank angle and speed of crankshaft ω, and (α, ω), then 4 cylinder rods affact the moment of resistance 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 frictional resistance moment by the sliding bearing generation

In the process of engine cold starting, temperature is low, and lubricating oil viscosity is big, mobile poor, needs a few minutes to tens minute ability to reach each friction means fully, can't form lubricating oil 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 frictional resistance moment of sliding bearing is:

T _B＝∑μWR

μ-coefficient of sliding friction 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 frictional resistance moment of sliding 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 resistance square of engine start process

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

T _z＝T _L+T _B (22)

2 clutch model

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

At clutch driving plate 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 that-clutch transmits;

T _zThe resistance of start square of-engine;

T _m-motor torque;

J _eThe moment of inertia of-engine;

J _mThe moment of inertia of-motor;

J _C1The moment of inertia of-clutch active part;

J _C2The moment of inertia of-clutch secondary part;

ω _E0The initial speed of-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 coordinate system.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 ato unit in different system start-up time comparison schematic diagram (as shown in Figure 6) and start the comparison schematic diagram (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% start-up time; Start energy and reduced 72%.

Claims (12)

1. hybrid power system, it comprises engine, regime clutch, motor and speed changer, described regime clutch comprises as the flywheel of big inertia part and clutch compressing disc and as little inertia clutch portions frictional disk, it is characterized in that, be installed on the crankshaft output end of engine by torsion vibration absorber as little inertia clutch portions frictional disk, and on the power shaft that the flywheel of the big inertia part of conduct and clutch compressing disc are installed to motor, on the power 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 engine.

3. hybrid power system according to claim 1 is characterized in that the crankshaft output end of described engine is provided with spline, and described clutch disk directly is installed on this spline by torsion vibration absorber.

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 power shaft of described motor by key connected mode or bolt connecting mode.

5. according to the mode switching method of any described hybrid power system in the claim 1 to 4, it is characterized in that, when from electric-only mode when hybrid mode is switched, first slowly binding pattern clutch, when engine is dragged to minimum startup rotating speed, engine oil spout ignition trigger.

6. according to the mode switching method of any described hybrid power system in the claim 1 to 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, separate shift clutch simultaneously, this moment, motor speed was ω ₀Binding pattern clutch then, when the clutch compressing disc of regime clutch and clutch disk synchronously after, the big inertia part of motor and regime clutch directly is dragged to engine minimum startup rotational speed omega with the kinetic energy of storage ₁, this moment, engine was all ω mutually with rotating speed of motor ₁ω ₀And ω ₁Between meet the following conditions and realize zero electric energy ato unit:

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

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

I _mBe the moment of inertia of rotor,

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

I _C2Be the moment of inertia of the big inertia part of regime clutch (flywheel and platen),

E _eFor in the start-up course because the energy loss that engine interior friction and compressed air produce,

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

E _cThe energy loss of rubbing and producing for regime clutch cunning in the cohesive process.

7. according to the mode switching method of any described hybrid power system in the claim 1 to 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, speed changer is plucked shelves simultaneously, and this moment, motor speed was ω ₀Binding pattern clutch then, when the clutch compressing disc of regime clutch and clutch disk synchronously after, the big inertia part of motor and regime clutch directly is dragged to engine minimum startup rotational speed omega with the kinetic energy of storage ₁, this moment, engine was all ω mutually with rotating speed of motor ₁ω ₀And ω ₁Between meet the following conditions and realize zero electric energy ato unit:

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

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

I _mBe the moment of inertia of rotor,

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

I _C2Be the moment of inertia of the big inertia part of regime clutch (flywheel and platen),

E _eFor in the start-up course because the energy loss that engine interior friction and compressed air produce,

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

E _cThe energy loss of rubbing and producing for regime clutch cunning in the cohesive process.

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

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

10. mode switching method according to claim 9 is characterized in that, when the ratio between speed changer one, the second gear gearratio 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 gearratio of speed changer;

i ₂Be speed changer second gear gearratio.

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

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

Images