CN102770646B - The method of two-step supercharging is monitored with the fixed geometry turbine pressurized machine with Dynamic estimation device and the restriction of pre-turbine pressure - Google Patents

Abstract

The present invention relates to a kind of method of supercharging air of monitoring motor vehicle explosive motor (1), above-mentioned explosive motor is furnished with the twin turbocharged machine (6 of supercharging classification, 7), comprise: made it two turbines (10,12) rotated by the waste gas of described explosive motor (1), by described turbine (10,12) each two booster compressor (11 driven in,, and two high low pressure valve actuators (17,18) 13).Described method comprises the compression ratio (PR of compressor _c) control as about compression ratio setting value (PR _{c, cons}), and control the solution pressure ratio (PR of turbine (12) _i) to limit the pressure (P of turbine (12) upstream _{avt, t}), as the pressure (P of high-pressure turbine (12) upstream _{avt, t}) exceed threshold value (CONS _pavt) time perform described control.

Description

The method of two-step supercharging is monitored with the fixed geometry turbine pressurized machine with Dynamic estimation device and the restriction of pre-turbine pressure

Technical field

The present invention relates to the control to automotive internal combustion engines.

More specifically, the present invention relates to the air two-step supercharging of monitoring above-mentioned explosive motor.

A concrete advantageous application of the present invention relates to the supercharging of monitoring diesel engine, and described diesel engine, by turbocompressor supercharging, more specifically, is use the two turbocompressor structure of classification to carry out supercharging.

Background technique

Engine control refers to the technology regulating the performance of explosive motor by controlling all the sensors of explosive motor and actuator.

All control laws of motor and controling parameters be included in be called ECU or electronic control unit computer in.

Supercharged engine comprises turbocompressor, and described turbocompressor comprises the turbine that driven rotatably by waste gas and by this turbine drives and for increasing the compressor of air quantity entering cylinder.

For this reason, turbine is placed in the outlet port of gas exhaust manifold, and compressor is installed on the axle identical with turbine, and is placed in the upstream of intake manifold.

Turbocompressor is connected in series, with make low pressure compressor to high pressure compressor air supply high-pressure turbine to low-pressure turbine supply gas.

The power being supplied to high-pressure turbine and low-pressure turbine by waste gas regulates by installation escape cock or fin, and described escape cock or fin affect the flow velocity through the gas of turbine (or being supplied to the flow section of these gases).

Such turbocompressor is called as fixed geometry turbine compressor.

Along with the raising of supercharged engine performance, boost pressure level is corresponding improve also, and thus the load of turbocompressor will be more and more heavier.Therefore importantly, turbocompressor should be controlled as far as possible meticulously in case performance when it is degenerated and improves vehicle acceleration, especially strengthen the power of motor, namely improve the ability of its rotating speed fast.

Anti-pollution standard is more and more stricter, and the grain amount that motor (especially diesel engine) discharges must be fewer and feweri.Therefore, the discharge pipe line of motor is provided with particulate filter, in order to emissions reduction to the grain amount of environment.The utilization of this device adds exhaust back pressure.Because filter is filled with particle, therefore this back pressure is powerful increasingly.With regard to turbocompressor, this is reflected as expansion ratio and reduces, and is supplied to the reduction of the power of turbine along with waste gas, and along with the decline of engine performance.For reaching the performance of peer-level, expansion ratio need be kept by the pressure increasing turbine upstream.Usually above-mentioned increase is realized by closing escape cock or adjusting fin.

Usually based on the difference of resolving between pressure set-point and the pressure recorded, PID(ratio, integration, differential is adopted) pressure in engine intake manifold is adjusted to and is approximately pressure set points by regulator.

But this regulation scheme is difficult to perform, because this must make the pressure in manifold no matter can be adjusted to pressure set-point in steady operation conditions or under transient operating conditions.

Prior art has attempted to realize this goal.

To this, see file US 2003/0010019, two regulators of Cascade Arrangement can be which employs; Or file FR 2 829 530, advise the force value of the turbine upstream of turbocompressor to be adjusted to pressure set points in literary composition, this pressure set points is consistent with the maximum allowble pressure value of the turbine upstream of turbocompressor.

Also can reference paper WO 2,004,/00 99 84, file is proposed to adopt the position set point become with engine condition to monitor supercharging; Or file WO 20,04/,027 238, file proposes to regulate boost pressure or adjustment to be used for regulating the position of actuator of exhaust dynamics sequentially.

But no matter the prior art solution proposed all does not allow to control boost pressure accurately to monitor the pressure in engine intake manifold under steady operation conditions or transient operating conditions, and the pressure meanwhile limiting turbocompressor upstream protects motor and turbocompressor.

Summary of the invention

Therefore, object of the present invention is intended to reduce these drawbacks, and the method and apparatus being provided for the supercharging of monitoring supercharging type explosive motor is to realize following triple object, namely monitor the pressure of boost pressure under the boost pressure under transient operating conditions, monitoring steady operation conditions and restriction turbine upstream.

In the field of the control of two supercharging device, the applicant have developed a kind of double loop control methods simultaneously controlling two turbocompressor, described in No. 08 53686, the patent application FR that on June 4th, 2008 submits to.This system can provide remarkable performance, but needs discharge pressure sensor in the upstream of high-pressure turbine.Such sensor cost is installed high.The present invention proposes and save this sensor.

For this reason, when only having a turbocompressor, control methods advantageously have employed variable compressor pressure ratios to control this turbocompressor.In addition, when two turbocompressor, double loop just controls to change into control one or the other turbocompressor in preset time by the method, and combines with selecting the management unit of controlled turbocompressor.

Therefore, a first aspect of the present invention relates to a kind of method of supercharging of explosive motor of monitoring motor vehicle, above-mentioned explosive motor is equipped with the two turbocompressor of classification, the two turbocompressor of described classification comprises two turbines by the waste gas rotary actuation from this motor, two turbocharger compressor by each driving in above-mentioned turbine and two actuators for high pressure valve and low pressure valve, for the power regulating waste gas.

This method also comprises the setting value becoming to be roughly supercharger pressure ratio by the compression ratio adjustment of compressor, and regulates expansion ratio to limit the pressure of turbine upstream, and namely the pressure once turbine upstream carry out described adjustment more than a threshold value.

According to another characteristic of the invention, according to the force value of the turbine upstream of the force value in intake manifold and described turbocompressor and the signal produced for starting and stop the adjustment to expansion ratio of turbine according to first and second threshold value.

When the force value in intake manifold is more than or equal to first threshold, preferably stop the adjustment of the expansion ratio to turbine.

When the force value in gas exhaust manifold is less than Second Threshold, advantageously stop the adjustment of the compression ratio to compressor.

According to another feature of the present invention, realize the restriction of the pressure to turbine upstream by regulating loop, this regulating loop receive setting value and compressor pressure ratios estimated value as input and the control signal sent for the actuator of high pressure valve and low pressure valve as output.Can according to start and the change of stop signal value carrys out the switch gear of input, regulating and controlling loop setting, to make to show the estimated value of expansion ratio of turbine or the estimated value of the compression ratio of compressor on the one hand in the input of regulating loop, show arbitrary setting value on the other hand.

The setting value of the compression ratio of compressor can produce from figure, and the setting value of expansion ratio can produce from the ratio between the pressure in gas exhaust manifold and the pressure recorded in low-pressure turbine downstream or the estimated pressure in high-pressure turbine downstream.

The estimated pressure in high-pressure turbine downstream advantageously obtains from the dynamic model of low-pressure turbine compressor.

A second aspect of the present invention relates to a kind of device of supercharging of the explosive motor for monitoring motor vehicle, described explosive motor is equipped with the two turbocompressor of classification, and the two turbocompressor of described classification is provided with by two turbines of the waste gas rotary actuation from this motor and is provided with by two turbocharger compressor of each driving in above-mentioned turbine.

This device also comprises control unit, and the compression ratio adjustment of compressor can regulate expansion ratio to limit the force value of turbine upstream to being approximately supercharger pressure than setting value by it, and the pressure once turbine upstream exceedes threshold value and namely regulates.

According to another feature, use the figure of the predefined value of the actuator stored for high pressure valve and low pressure valve, for regulating the power of waste gas with the change of engine operating parameter, and also use the device carrying out default described actuator according to the numerical value taking from described figure.

Accompanying drawing explanation

From the following description also provided by reference to the accompanying drawings by non-limiting example, other objects of the present invention, feature and advantage will become apparent, wherein:

-Fig. 1 schematically shows the structure of the diesel internal combustion motor of vehicular engine, and it is equipped with supercharging monitoring device of the present invention;

-Fig. 2 shows the governing stage of circuit;

-Fig. 3 shows the Dynamic estimation device of the low-pressure turbine compressor based on mockup.

Embodiment

Fig. 1 schematically shows the general structure of the diesel internal combustion motor 1 of Motor Vehicle, and cool air intake manifold 2 and gas exhaust manifold 3.

As shown in the drawing, the loop 4 allowing cool air to enter motor 1 comprises air filter 5 substantially, and this air filter is supplied by the intake manifold 2 of low pressure first order turbocompressor 6 and high pressure second level turbocompressor 7 pairs of motors 1.

The present invention relates to gas exhaust manifold 3, this gas exhaust manifold reclaim burn the waste gas that causes and by turbocompressor 6,7 and particulate filter 8 by above-mentioned toxic emission to outside, described particulate filter is designed to reduce the particle (especially coal smoke) entering environment and measures.

Heat exchanger 9,9 ' can be placed in after each outlet of compressor, and compressor is equipped with pipeline 4 and supplies cool air to intake manifold 2.

Turbocompressor 6 substantially comprises by exhaust-driven turbine 10 and is arranged on and the compressor 11 in turbine 10 same axis, and this compressor is used for compressing the air that distributed by air filter 5 to increase the air quantity entered in the cylinder of motor 1.

Turbocompressor 7 substantially comprises by exhaust-driven turbine 12 and is arranged on and the compressor 13 in turbine 12 same axis, and this compressor is used for compressing the air that distributed by compressor 11 to increase the air quantity entered in the cylinder of motor 1.

In addition, motor 1 is also connected with an exhaust gas recirculation circuit 14, and this loop is used for some in above-mentioned waste gas to re-inject in intake manifold 2, to limit the amount of produced nitrogen oxides especially, avoids forming smog in the offgas simultaneously.

Loop 14 comprises the solenoid valve 15 for controlling EGR gas flow velocity substantially.

Motor 1 is relevant to waste gas circuit 16.

This loop 16 comprises the high-pressure discharge valve 17 being called as " bypass " valve and the low pressure drain valve 18 being commonly referred to as " exhaust pressure relief " valve substantially, to regulate the power being supplied to high-pressure turbine 12 and low-pressure turbine 11 by waste gas.

A principle of the present invention is exactly on the actuator by acting on corresponding high pressure valve 17 or low pressure valve 18, reaches each object only controlling a turbocompressor 6 or 7.

In addition, the electronic control unit ECU that reference character 20 represents is used for gathering the signal P carried by the suitable measuring transducer (not shown) arranged for this purpose _collwith signal P _{avt, t}, to measure the pressure laid respectively at high-pressure turbine 12 upstream in intake manifold 2.It acts on the component (as escape cock) of the power for regulating waste gas, so that by the pressure P of turbine 12 upstream of the force value in intake manifold 2 and turbocompressor 7 _{avt, t}be adjusted to and be approximately corresponding setting value CONS _pcolland CONS _pavt.

Unit ECU 20 also can monitor the operation of motor 1 in a per se known way.It specifically acts on solenoid valve 15 to regulate the gas flow of recirculation and to regulate the operating point of motor 1.

Current description relates to the pressure P of high-pressure turbine 12 upstream to turbocompressor 7 _{avt, t}restriction.Therefore, the basic device that this kind of restriction is achieved will be related to about the description of unit ECU 20 below.

As shown in Figure 1, described electronic control unit ECU 20 comprises regulon substantially, is used for limiting the pressure P of turbine 12 upstream of turbocompressor 1 _{avt, t}.

More specifically, central location 20 includes level 21, is used for regulating expansion ratio PR _t, it receives the expansion ratio PR estimated _{t, esti}with the compression ratio PR estimated _{c, esti}as input; The first order 22, is used for producing the first pressure threshold CONS corresponding with the maximum pressure value that intake manifold 2 allows _pcoll; And the second level 23, in order to produce the second corresponding with the maximum pressure value that exhaust manifold 3 allows, corresponding with the authorized pressure of turbine 12 upstream of high-pressure turbine compressor 7 pressure threshold CONS _pavt.

Central location 20 further comprises the third level 24,25, is used for the estimated value PR of the expansion ratio producing high-pressure turbine and low-pressure turbine respectively _{t, esti}; And the fourth stage 26,27, be used for the setting value PR of the expansion ratio producing high-pressure turbine and low-pressure turbine respectively _{t, cons}.

With reference to Fig. 2, only has the pressure P when turbine 12 upstream _{avt, t}be greater than Second Threshold CONS _pavttime, to the pressure P of turbine 12 upstream _{avt, t}restriction just work.In this case, by the third level 24,25 and the fourth stage 26, the 27 adjustment expansion ratio PR of control unit 20 _t.

The present invention relates to and be used for generation first pressure threshold CONSP _collthe first order 22, it should be noted, such as, this grade comprise have two input memory blocks, in advance by learning program obtain by one group of pressure threshold CONSP _collthe data formed are stored in wherein, and each pressure threshold all corresponds to engine operating condition and corresponding to fuel consumption level.

The present invention relates to and be used for producing Second Threshold CONS _pavtlevel 23, it comprises memory block equally, corresponding to the threshold value CONS of maximum pressure value _pavtstored in wherein, break down possibly in turbocompressor 6,7 when exceeding described threshold value.

This threshold value CONS _pavtpreferably by the setting value CONS corresponding with the setting value under transient operating conditions _2land the setting value CONS corresponding with the setting value under steady operation conditions _2psupplement.

As shown in Figure 2, expansion ratio governing stage comprises loop 25 substantially, and this loop comprises regulator 26 usually.

Circuit 25 receives the error signal E that carried by comparator 30 as input, and described comparator is by the setting value PR of expansion ratio _{t, cons}with the estimated value PR of expansion ratio _{t, esti}to compare or by the setting value PR of compression ratio _{c, cons}with the estimated value PR of compression ratio _{c, esti}compare.

Circuit 25 also comprises level 31, is used for starting and stopping expansion ratio PR in order to produce _tthe signal CPAVT of adjustment.Along with intake manifold 2 internal pressure P _collthe pressure P of turbine 12 upstream of value, turbocompressor 7 _{avt, t}change, and along with setting value CONS _colland CONS _pavtchange, signal CPAVT will be produced in logical circuit 32.

For this reason, the level 31 for generation of signal CPAVT comprises: the first comparator device 33, is used for comparing the pressure P recorded in intake manifold 2 _collvalue and respective settings value CONS _coll; With comparator device 34, be used for comparing the pressure value P recorded in gas exhaust manifold 3 _{avt, t}with respective threshold CONS _pavt, these results compared are provided to suitable logical circuit 32 to produce startup and stop signal CPAVT.

If pressure value P _{avt, t}be greater than corresponding threshold value CONS _pavt, signal CPAVT can enable switch 35,36, they to be set as the expansion ratio setting value PR of turbine 12 _{t, cons}and be set as expansion ratio estimated value PR _{t, esti}.By this way, comparator 30 is by expansion ratio estimated value PR _{t, esti}with expansion ratio setting value PR _{t, cons}compare.

Similarly, if pressure P _collvalue is greater than corresponding threshold value CONS _pcolltime, signal CPAVT can enable switch 35,36, they to be set as the compression ratio threshold value PR of compressor 13 _{c, cons}with and be set as compression ratio estimated value PR _{c, esti}.By this way, comparator 30 is by compression ratio estimated value PR _{c, esti}with compression ratio threshold value PR _{c, cons}compare.

In other words, as mentioned above, if the pressure value P that records of turbine 12 upstream _{avt, t}be greater than Second Threshold CONS _pavt, then to compression ratio PR _cadjustment will to stop and to expansion ratio PR _tadjustment will start, carry out limiting pressure P with this _{avt, t}.On the other hand, if the pressure P in manifold 2 _collbe more than or equal to threshold value CONS _coll, then to expansion ratio PR _tadjustment will to stop and to compression ratio PR _cadjustment will start.

The error signal E that comparator 30 is carried will be transferred into regulator 37, to regulate the expansion ratio PR of turbine 12 _tor the compression ratio PR of compressor 13 _c.

In addition, for improving the response time of regulating loop, the predefined value of low pressure (" bypass ") valve 17 and high pressure (" exhaust pressure relief ") valve 18 will be added into the output value of regulator 37.This predefined value is along with the change of engine speed N or fuel flow rate W is extracted from collection of illustrative plates C (cartographie C).

The collection of illustrative plates C that turbine 12 is preset is included in ECU 20, and the first estimated value of the adjustment of turbocompressor 7 can be obtained with the change of rotating speed N and flow velocity W, and therefore, it is possible to contribute to such adjustment.In addition, correct by the change along with particularly air pressure and temperature the numerical value taking from collection of illustrative plates C, just likely along with such as height or ambient temperature optimize the predefined value of turbine 12.It should be noted that this predefined value of turbine 12 turbocompressor 7 can be made to be in steady operation conditions under effective original state, this make it possible to good startup regulate enter transient operating conditions.

By a sum unit 38 to carrying out the output of self tuning regulator 37 and suing for peace from the output of collection of illustrative plates C, to determine the position of low pressure drain valve WG 18 and high-pressure discharge valve WG 17.

As shown in Figure 3, the Dynamic estimation device of low-pressure turbine compressor 6 performance based on mockup, and can estimate the pressure P of low-pressure turbine 10 upstream _{avt, t}with the pressure P in low pressure compressor 11 downstream _{aval, c}.

This dynamic estimation of low-pressure turbine compressor 6 can eliminate the risk that high-pressure turbine compressor exceeds the speed limit under transient operating conditions, and without the need to adding special sensor.

Dynamic estimation device can show following content as input: the air velocity W from compressor 11 recorded by flowmeter (not shown) _{avt, c}; The pressure value P of compressor 11 upstream _{avt, c}with temperature value T _{avt, c}; The air velocity W of low-pressure turbine 10 _{avt, t}; And the temperature value T of low-pressure turbine 10 upstream _{avt, t}.

Air velocity value W _{avt, c}and W _{avt, t}and pressure value P _{avt, c}and P _{avt, t}obtained by sensor (not shown).

The power that low pressure compressor 11 place is calculated is undertaken calculating by the following equation in square frame 40:

$P_c=W_{\mathrm{avt},c}{C}_p\frac{1}{{\mathrm{\η}}_c}{T}_{\mathrm{avt},c}({\mathrm{PR}}_{c,\mathrm{esti}}^{\frac{\mathrm{\γ}}{\mathrm{\γ}-1}}-1)---\left(1\right)$

For this reason, the flow velocity W of upstream of compressor is measured _{avt, c}with temperature T _{avt, c}.Cp is the thermal capacitance of fluid of flowing in turbocompressor 6 under constant voltage, and γ is the ratio between the thermal capacitance under this same fluid thermal capacitance at constant pressure and constant volume amass.

Compression ratio PR can be obtained from the static collection of illustrative plates C that turbocompressor MANUFACTURER provides _{c, esti}and efficiency eta _c.These magnitudes can be calculated with the change of the variable determined by following formula:

${\mathrm{PR}}_{C,\mathrm{esti}}=f_1(W_{\mathrm{avt},c}\frac{\sqrt{T_{\mathrm{avt},c}}}{P_{\mathrm{avt},c}},N_t\frac{1}{\sqrt{T_{\mathrm{avt},c}}})---\left(2\right)$

${\mathrm{\η}}_C=f_2(W_{\mathrm{avt},c}\frac{\sqrt{T_{\mathrm{avt},c}}}{P_{\mathrm{avt},c}},N_t\frac{1}{\sqrt{T_{\mathrm{avt},c}}})---\left(3\right)$

The pressure P of low pressure compressor 11 upstream _{avt, c}record.The rotating speed N of turbocompressor _tthered is provided by Dynamic estimation device, function f ₁and f ₂can obtain from the data being included in square frame 41 that turbocompressor MANUFACTURER provides.

Air velocity W _{avt, c}hot-wire transducer (not shown) by being such as arranged in air filter 5 outlet port is measured.Pressure P _{avt, c}measure by piezoelectric transducer (not shown).

The power P of live axle is supplied to by turbine 10 _tcalculate by the equation (4) in square frame 42:

$P_t=W_{\mathrm{avt},t}{C}_p{\mathrm{\η}}_t{T}_{\mathrm{avt},t}(1-{\left(\frac{1}{{\mathrm{PR}}_{c,\mathrm{esti}}}\right)}^{\frac{\mathrm{\γ}-1}{\mathrm{\γ}}})---\left(4\right)$

At this and the temperature T of unmeasured turbine 10 upstream _{avt, t}, and hypothesis is at this temperature T _{avt, t}, generator speed N _mand between load M, there is a kind of static dependencies relation:

T _avt，t=f ₁(M，N _m)(5)

Wherein, M is the fuel quantity injected, N _mfor generator speed.

In the mode similar to low pressure compressor 11, the flow velocity W of turbine 10 _{avt, t}, turbine 10 expansion ratio PR _{t, esti}and the rotating speed N of turbine 10 _tbetween also there is a kind of static relation.In the efficiency eta of turbine 10 _t, turbine 10 flow velocity W _{avt, t}and the rotating speed N of turbine 10 _tbetween also there is a kind of relation.

$W_{\mathrm{avt},t}\frac{\sqrt{T_{\mathrm{avt},t}}}{P_{\mathrm{avt},t}}=f_4({\mathrm{PR}}_{t,\mathrm{esti}},N_t\frac{1}{\sqrt{T_{\mathrm{avt},t}}})---\left(6\right)$

${\mathrm{\η}}_t=f_S(W_{\mathrm{avt},t}\frac{\sqrt{T_{\mathrm{avt},t}}}{P_{\mathrm{avt},t}},N_t\frac{1}{\sqrt{T_{\mathrm{avt},t}}})---\left(7\right)$

Function f ₃, 3/4 to be provided by MANUFACTURER, and to be included in square frame 43.

The flow velocity W of turbine 10 _{avt, t}estimate from the air velocity using low single order low pass filter (not shown) to record at the air inlet of motor 1.Just use this fact of low pressure estimator owing to only having when (" exhaust pressure relief ") valve 18 cuts out, therefore above-mentioned simplification operation is rational.

Therefore, the efficiency eta of turbine 10 _tjust can be determined by magnitude that is known or that estimate.

On the other hand, equation (4) needs the expansion ratio PR about low-pressure turbine 10 _{t, esti}information because this does not also record.For this reason, the pressure P recorded in low-pressure turbine 10 downstream should be adopted _dtBPand transform equation (6) to obtain following equation:

$W_{\mathrm{avt},t}=\frac{P_{\mathrm{dtBP}}{\mathrm{PR}}_{t,\mathrm{esti}}}{\sqrt{T_{\mathrm{avt},t}}}{f}_4({\mathrm{PR}}_{t,\mathrm{esti}},N_t\frac{1}{\sqrt{T_{\mathrm{avt},t}}})---\left(6^{,}\right)$

The new function f in square frame 43 can be considered _sform inverse function, obtain following equation:

$f_S({\mathrm{PR}}_{t,\mathrm{esti}},N_t\frac{1}{\sqrt{T_{\mathrm{avt},t}}})={\mathrm{PR}}_{t,\mathrm{esti}},f_4({\mathrm{PR}}_{t,\mathrm{esti}},N_t\frac{1}{\sqrt{T_{\mathrm{avt},t}}})---\left(8\right)$

According to the power P of the power P and low-pressure turbine 10 upstream that lay respectively at low pressure compressor 11 downstream _t, have employed following equation to determine the power at the axle place of low-pressure turbine compressor 6:

$J.N_t\frac{{\mathrm{dN}}_t}{\mathrm{dt}}=P_t-P_c---\left(9\right)$

Wherein:

J is the inertia of low-pressure turbine compressor 6, and

N _tit is the rotating speed of low-pressure turbine 10.

This carries out in estimator by means of the recurrence equation got according to the equation comprised in square frame 44 (10), and wherein, k is the deducible index representing the time:

$N_k=N_{k-1}+\left(\frac{P_t-P_c}{{J.N}_{k-1}}\right)---\left(10\right)$

So not only obtain the speed estimate value N of low-pressure turbine compressor 6 ^*, and obtain the compression ratio estimated value PR in compressor 11 _{c, esti}and the expansion ratio estimated value PR of turbine 10 _{t, esti}.According to the expansion ratio PR of turbine 10 _{t, esti}, the downstream pressure P of high-pressure turbine 12 can be released _atTTP.

By the Dynamic estimation device of low-pressure turbine compressor 6, the hypervelocity risk of high-pressure turbine compressor 7 under transient operating conditions can be avoided, and reduce the supercharging response time relative to given set point.

Setting value PR _{t, cons}record pressure P from turbine upstream _{avt, t}with the pressure value P in high-pressure turbine 12 downstream or low-pressure turbine 10 downstream _dtbetween ratio in produce.

In high-pressure regulation district, the setting value PR of expansion ratio _{t, cons}calculated by following equation:

${\mathrm{PR}}_{t,\mathrm{cons}}=\frac{{\mathrm{CONS}}_{\mathrm{Pavt}}}{P_{\mathrm{dtHP}}},$

Wherein:

P _dtHPthe estimated pressure in high-pressure turbine 12 downstream obtained from the dynamic model of low-pressure turbine compressor 6,

CONS _pavtthe pressure threshold of high-pressure turbine 12 upstream, the pressure P in itself and gas exhaust manifold 3 _collcorresponding.

At low pressure regulatory region, the setting value PR of expansion ratio _{t, cons}calculated by following equation:

${\mathrm{PR}}_{t,\mathrm{cons}}=\frac{{\mathrm{CONS}}_{\mathrm{Pavt}}}{P_{\mathrm{dtBP}}}$

Wherein:

P _dtBPbe low-pressure turbine 10 downstream record pressure,

CONS _pavtit is the pressure threshold of low-pressure turbine 10 upstream.

The estimated value PR of expansion ratio _{t, esti}calculated by following equation:

In high-pressure regulation district, the estimated value PR of expansion ratio _{t, esti}calculated by following equation:

${\mathrm{PR}}_{t,\mathrm{esti}}=\frac{P_{\mathrm{avt},t}}{P_{\mathrm{dtHP}}},$

Wherein:

P _{avt, t}be high-pressure turbine 12 upstream record pressure,

P _dtHPit is the estimated pressure in high-pressure turbine 12 downstream obtained from the dynamic model of low-pressure turbine compressor.

At low pressure regulatory region, the estimated value of expansion ratio is calculated by following equation:

${\mathrm{PR}}_{t,\mathrm{esti}}=\frac{P_{\mathrm{avt},t}}{P_{\mathrm{dtBP}}}$

Wherein:

P _{avt, t}be low-pressure turbine 10 upstream record pressure,

P _dtBPbe low-pressure turbine 10 downstream record pressure,

Due to the present invention described above, make to monitor the supercharging of explosive motor and the pressure limiting turbine upstream becomes possibility.

Claims (8)

1. the method for the supercharging air of the explosive motor (1) of a monitoring motor vehicle, this explosive motor is equipped with the two turbocompressor (6 of pressurized machine classification, 7), the two turbocompressor of this pressurized machine classification comprises: two turbines (10,12) driven in a rotative pattern by the waste gas from described explosive motor (1); Two turbocharger compressor (11,13) driven by each in these turbines (10,12); And for two actuators (17,18) of high pressure valve and low pressure valve, it is characterized in that, the method comprises the compression ratio PR of one of described two turbocharger compressor _cbe adjusted to and be about compression ratio setting value PR _{c, cons}, and regulate the expansion ratio PR of one of described two turbines (12) _tto limit the pressure value P of this turbine (12) upstream _{avt, t}, once this pressure value P of the turbine of high pressure (12) upstream _{avt, t}exceed Second Threshold CONS _pavtjust carry out described expansion ratio PR _tadjustment,

Wherein, according to the pressure value P in the intake manifold (2) of this explosive motor _collwith the pressure value P of this high-pressure turbine (12) upstream _{avt, t}and according to the first threshold CONS corresponding with the maximum pressure value that this intake manifold (2) allows _pcolland the described Second Threshold CONS corresponding with the authorized pressure of high-pressure turbine (12) upstream _pavtand produce the expansion ratio PR starting and stop for one of described two turbines (10,12) _tcarry out the signal CPAVT regulated, wherein, the pressure value P in this intake manifold (2) _collbe more than or equal to this first threshold CONS _pcolltime, stop the expansion ratio PR to one of described two turbines _tadjustment.

2. method according to claim 1, is characterized in that, when high-pressure turbine (12) upstream, pressure value P in the gas exhaust manifold (3) of this explosive motor _{avt, t}be greater than Second Threshold CONS _pavttime, stop the compression ratio PR to one of described two turbocharger compressor (11,13) _cadjustment.

3. method according to claim 1 and 2, is characterized in that: the pressure P being realized the upstream to one of described two turbines (10,12) by a regulating loop (25) _{avt, t}restriction, this regulating loop receives compression ratio setting value PR _{c, cons}with the compression ratio estimated value PR of one of described two turbocharger compressor _{c, esti}as input and the control signal WG sending the actuator (17,18) being used for high pressure valve and low pressure valve as output; And be arranged on multiple switch gears (35 of the input of this regulating loop (25), 36) controlled, so that according to startup and stop signal value CPAVT, show the expansion ratio estimated value PR of one of described two turbines on the one hand in the input of this regulating loop _{t, esti}or the compression ratio estimated value PR of one of described two turbocharger compressor _{c, esti}, display expansion ratio setting value PR on the other hand _{t, cons}or compression ratio setting value PR _{c, cons}in any one.

4. method according to claim 3, is characterized in that, this compression ratio setting value PR _{c, cons}produce from collection of illustrative plates C.

5. method according to claim 1 and 2, is characterized in that, at low pressure regulatory region, records pressure P from the pressure threshold of low-pressure turbine (10) upstream and this low-pressure turbine (10) downstream _dtBPbetween ratio in produce expansion ratio setting value PR _{t, cons}; In high-pressure regulation district, from the pressure threshold of high-pressure turbine (12) upstream and the estimated pressure P in this high-pressure turbine (12) downstream _dtHPbetween ratio in produce expansion ratio setting value PR _{t, cons}.

6. method according to claim 5, is characterized in that, the estimated pressure P in this high-pressure turbine (12) downstream _dtHPobtain from the dynamic model of low-pressure turbine compressor (6).

7. the device of the supercharging air of the explosive motor for monitoring motor vehicle (1), described explosive motor is equipped with the two turbocompressor (6 of pressurized machine classification, 7), the two turbocompressor of this pressurized machine classification is equipped with two turbines (10 driven in a rotative pattern by the waste gas from this explosive motor (1), 12) and by these turbines (10, 12) each two turbocharger compressor (11 driven in, 13), described device comprises control unit (20), it is characterized in that, this control unit (20) is by the compression ratio PR of one of described two turbocharger compressor _cbe adjusted to and be about compression ratio setting value PR _{c, cons}, and regulate the expansion ratio PR of one of described two turbines _tto limit the pressure value P of this turbine (12) upstream _{avt, t}, once this pressure value P of the turbine of high pressure (12) upstream _{avt, t}exceed Second Threshold CONS _pavtjust carry out described expansion ratio PR _tadjustment, wherein, according to the pressure value P in the intake manifold (2) of this explosive motor _collwith the pressure value P of this high-pressure turbine (12) upstream _{avt, t}and according to the first threshold CONS corresponding with the maximum pressure value that this intake manifold (2) allows _pcolland the described Second Threshold CONS corresponding with the authorized pressure of high-pressure turbine (12) upstream _pavtand produce the expansion ratio PR starting and stop for one of described two turbines (10,12) _tcarry out the signal CPAVT regulated, wherein, the pressure value P in this intake manifold (2) _collbe more than or equal to this first threshold CONS _pcolltime, stop the expansion ratio PR to one of described two turbines _tadjustment.

8. device according to claim 7, it is characterized in that, this device comprises collection of illustrative plates C, the actuator (17 for high pressure valve and low pressure valve is stored in this collection of illustrative plates C, 18) predefined value, to regulate the power of waste gas according to the operating parameter of this motor, and this device comprises for carrying out default described actuator (17 based on the numerical value extracted from this collection of illustrative plates C, 18) unit (37,38).