CN101726378A - Device and method for measuring mechanical loss power of turbocharger - Google Patents

Abstract

The invention relates to a device and a method for measuring mechanical loss power of a turbocharger. The basic principle of the invention is that: the turbocharger is operated at a certain speed; when an external gas source supply is cut off, namely external energy is stopped inputting, the turbocharger is in a freely decelerating process from an initial speed to a rotating speed of zero; in the process, through measuring loss for overcoming the frictional resistance of a radial floating bearing, an axial thrust bearing (a ball bearing turbocharger has no thrust bearing) and a sealing ring friction pair, and pneumatic loss and turbine pneumatic loss caused by continuing compressing air by a gas compressor, and subtracting the pneumatic loss measured by the latter two parts from the measured loss of the frictional resistance, the real mechanical loss power of the turbocharger is obtained. The device and the method for measuring the mechanical loss power of the turbocharger provided by the invention can measure more accurately and conveniently.

Description

A kind of measurement mechanism of mechanical loss power of turbocharger and method

Technical field

The present invention relates to a kind of mechanical loss power proving installation and method, relate in particular to a kind of mechanical loss power of turbocharger measurement mechanism and method.

Background technology

Turbosupercharger now has been widely used in various mobile and stationary engines such as vehicle, boats and ships, engineering and agricultural machinery, power station, and the efficient that how to improve turbosupercharger is the common problems of paying close attention to of people.The efficient of turbosupercharger is by turbine efficiency, compressor efficiency, the decision of mechanical efficiency three parts.Under present scientific and technological level, the amplitude that further improves turbine and compressor efficiency is limited, and difficulty is very big.Comparatively speaking, mechanical efficiency also has bigger room for promotion, can reduce mechanical loss as using high-performance hybrid ceramic ball bearing, air bearing, electromagnetic bearing etc., improves mechanical efficiency.For the floating bearing turbosupercharger, its mechanical loss is made up of radial floating bearing, axial thrust bearing, three friction losses of sealing ring friction pair.For ball bearing turbine supercharger, its mechanical loss is made up of angular contact ball bearing and two friction losses of sealing ring friction pair.These lose the bearing of turbosupercharger-rotor-support-foundation system friction horsepower just, and its size has determined the mechanical efficiency of supercharger, and therefore, accurately measuring bearing-rotor-support-foundation system friction horsepower is the prerequisite that obtains accurate supercharger mechanical efficiency.

Measuring the relatively more direct method of turbosupercharger friction power loss is to measure the rotating speed and the suffered moment of friction of Rotor-Bearing System of rotor simultaneously.But because the rotor diameter of axle of turbosupercharger is less, rotating speed is very high, measures very difficulty of moment of friction or power exactly.

Round-about way is the import and export flow and the oil temperature of measurement axis bearing lubrication oil.Suppose that the heat that friction power loss produced in the bearing all taken away by lubricating oil, then just can determine the friction power loss of bearing according to flow rate of lubricating oil and temperature rise, as national automobile industry standard " QC/T 591-1999 diesel engine of vehicle turbocharger test method " regulation by measuring the mechanical loss power that lubricating oil inlet and outlet pressure, temperature, flow obtain supercharger.But for the bearing body of turbocharger lubricating oil cooling, it not only dispels the heat to air by heat interchange, heat radiation, and its armature spindle is also accepted, and turbine conducts heat, the while dispels the heat to compressor impeller; In addition, for turbosupercharger water-cooled footstep body, bearing and the mechanical friction of sealing ring friction pair are given birth to heat conduction and taken away for a part of heat of bearing body water that is cooled, and is therefore, very inaccurate with the measuring method of the friction power loss of the just definite bearing of temperature rise according to flow rate of lubricating oil.

At above-mentioned, domesticly there is a kind of equipment of measuring turbocharger friction power approx at present: measuring test table for turbocharger friction power, the patent No. 200510114348.4.Wherein said testing table is that this is inaccurate according to hypothesis " when turbocharger rotor was not subjected to other external moment loading, the suffered moment of friction of rotor was the sole cause that causes its rotation speed change ".After this method was not considered to stop air feed, compressor impeller, turbine drop to the slow-speed of revolution process from high rotating speed was still working, and promptly pneumatic plant is at pressurized air, and turbine then is subjected to the resistance of air.Therefore the friction horsepower measured of patent 200510114348.4 is not real mechanical loss power, but has comprised the loss that pneumatic plant institute's work and turbine overcome resistance.In addition, this testing table is not considered turbosupercharger in the acceleration, deceleration process, and the direction of axial force all changes with size, and differs bigger with steady state condition, causes mechanical loss power size, direction all changing.In a word, it is inaccurate utilizing described measurement device mechanical loss power.

At present, also there be not a kind of measurement mechanism and method of measuring mechanical loss power of turbocharger more accurately.

Summary of the invention

The objective of the invention is to overcome the deficiency that above-mentioned prior art exists, a kind of measurement mechanical loss power of turbocharger measurement mechanism and method more accurately are provided.The ultimate principle of measuring method of the present invention: the turbosupercharger that under certain rotating speed, turns round, source of the gas supply outside cutting off, when promptly stopping the external energy input, one of turbosupercharger experience is in the free moderating process of zero (static) from the initial speed to the rotating speed, in this process, overcome the radial floating bearing by measurement, axial thrust bearing (the ball bearing supercharger does not have thrust bearing), the fricting resistance loss of sealing ring friction pair and pneumatic plant continue aerodynamic loss and the turbine pneumatic loss that pressurized air causes, and deduct the back aerodynamic loss that records of two parts with the fricting resistance loss that measures, obtain the true mechanical loss power of turbosupercharger.

The objective of the invention is to be achieved through the following technical solutions.

The measurement mechanism of a kind of mechanical loss power of turbocharger of the present invention as shown in Figure 1, comprising: outer source of the gas, data acquisition process and control system, sensor, heating system, lubricating system, automatic temperature control system; This measurement mechanism is in use measured the mechanical loss power of peripherals turbosupercharger.

Described outer source of the gas links to each other with heating system, and its major function provides the gases at high pressure that the turbine that drives described turbosupercharger reaches higher rotation speed.

Described heating system is connected with the peripherals turbosupercharger, and its effect provides the combustion gas to the certain energy of turbosupercharger, makes the duty of turbosupercharger meet turbosupercharger and is installed in actual working state on the engine.Heating system can be a combustion system, but is not limited to combustion system.

Described peripherals turbosupercharger comprises turbine, pneumatic plant, bearing body, turbine exhaust pipe, aerostatic press draft tube, aerostatic press gas outlet.

Described lubricating system is connected with the bearing body of described peripherals turbosupercharger, and its effect is to provide circulating lubricating oil for turbosupercharger.

Described automatic temperature control system is connected with described lubricating system, and its effect is to regulate lubricating oil temperature automatically, it is remained under the working temperature, the repeatability of warranty test and accuracy; Its principle of work is: when the lubricating system temperature value of reaching a high temperature, the open cold radiator cooler reduces the lubricating system temperature automatically; When the lubricating system temperature is lower than low-temperature values, open heating arrangement automatically, improve the lubricating system temperature.Preferable, high temperature values is 90 degrees centigrade, low-temperature values is 40 degrees centigrade.

Described sensor comprises gas pressure sensor, liquid-pressure pick-up, gas temperature sensor, fluid temperature sensor, liquid mass flow meter, speed probe, comprises the sensor but is not limited thereto.Described sensor is positioned on the interface channel of the inside of outer source of the gas, outer source of the gas and heating system, heating system inside, lubricating system inside, on turbine exhaust tube wall, aerostatic press air inlet tube wall, the aerostatic press exhaust wall, be used to monitor temperature, pressure, liquid quality flow and the rotating speed etc. of gas or liquid, and give data acquisition process and control system the data transfer that obtains.

Described data acquisition process and control system are to adopt the specific implementation of the measuring method of described mechanical loss power of turbocharger.Data acquisition process and control system obtain data from each sensor, and handle, and obtain the mechanical loss power of measured turbosupercharger.

Concrete operations step based on a kind of mechanical loss power of turbocharger measuring method of said apparatus is as follows:

Step 1, turbosupercharger to be measured is connected to the mechanical loss power of turbocharger measurement mechanism that the present invention proposes;

The measurement mechanism of step 2, startup mechanical loss power of turbocharger makes turbosupercharger to be measured reach working speed.

Every data in step 3, the acquisition test process, the concrete operations step is as follows:

The 1. step: reach data under the working speed situation by described each sensor acquisition turbosupercharger, and with the data transmission of each sensor acquisition to data acquisition process and control system.

The 2. step: cut off source of the gas,, gather and the record turbosupercharger is reduced to static every data during this period of time by working speed once more by described each sensor, and with the data transmission of each sensor acquisition to data acquisition process and control system.

The aerodynamic loss of step 4, acquisition turbosupercharger

Data acquisition process and control system are used the data that obtain in step 3, according to the data of the turbosupercharger that collects under working speed and the aerodynamic loss of associated hot mechanics formula acquisition supercharger.Its concrete grammar is as follows:

The 1. step: the aerodynamic loss sum that obtains turbocharger air compressor.

When air flowed in turbo-charger blower impeller, main aerodynamic loss had with the lower part:

A. the corner loss of air in passage.Comprise that inducer loss (uses W _I1Expression) and the impeller radial blade loss of airflow direction when axially changing into radially (used W _I2Expression), calculate by formula 1 and formula 2 respectively.

$W_{I1}={\mathrm{\ξ}}_1\frac{{\mathrm{\ω}}_1^2}{2}---\left(1\right)$

${\mathrm{<figure-callout\; id="2"\; label="W\; I"\; filenames="H2009102372775E0000021.png"\; state="\{\{state\}\}">W</figure-callout>}}_I={\mathrm{\&xi;}}_2\frac{{\mathrm{<figure-callout\; id="2"\; label="c\; r"\; filenames="H2009102372775E0000021.png"\; state="\{\{state\}\}">c</figure-callout>}}_r^2}{2}---\left(2\right)$

Wherein: ω ₁Be impeller inlet place relative velocity, c _R2Be the radial component of impeller outlet place absolute velocity, ξ ₁And ξ ₂Be loss coefficient.

B. the friction loss of air-flow in impeller passage.Comprise that eddy current loss (uses W _I3Expression), calculate by formula 3.

$W_{I3}={\mathrm{\&xi;}}_3\frac{{\mathrm{<figure-callout\; id="2"\; label="c\; r"\; filenames="H2009102372775E0000021.png"\; state="\{\{state\}\}">c</figure-callout>}}_r^2}{2}---\left(3\right)$

Wherein: ξ ₃Be loss coefficient.

C. air loss and the disk friction loss of air-flow between impeller and housing.

Owing to have the gap between the blade of rotation and the housing, just have air loss inevitably.This being lost between impeller and the compressor casing shows as undercurrent and air blast circulation; Between the impeller wheel back of the body and back of the body dish, show as air blast circulation.This partial loss merged in the disk friction loss calculate.

Disk friction loss (is used W _IdExpression), calculate by formula 4.

$W_{\mathrm{Id}}=\mathrm{\&alpha;}{\mathrm{<figure-callout\; id="2"\; label="u"\; filenames="H2009102372775E0000021.png"\; state="\{\{state\}\}">u</figure-callout>}}_2^2---\left(4\right)$

Wherein, α is a loss coefficient, u ₂Be the impeller outlet convected velocity.

D. the loss in the compressor casing (is used W _I4Expression), calculate by formula 5.

$W_{I4}={\mathrm{\&xi;}}_4\frac{{c_4}^2}{2}---\left(5\right)$

Wherein, ξ ₄Be volute loss coefficient, c ₄Be diffusion gas outlet absolute velocity.

Based on more than, turbocharger air compressor aerodynamic loss sum (is used W _IExpression) can calculate by formula 6:

W _I＝W _I1+W _I2+W _Id+W _I4 (6)

The 2. step: obtain the aerodynamic loss in the turbocharger turbine, mainly comprise with the lower part:

A. the energy loss in the nozzle ring (is used Δ W ₁Expression), calculate by formula 7.

Wherein:

Expression nozzle ring velocity coefficient;

B. the loss in the impeller (is used Δ W _iExpression), calculate by formula 8.

$\mathrm{\&Delta;}{W}_i=(\frac{1}{{\mathrm{\&psi;}}^2}-1)\frac{{\mathrm{\&omega;}}_2^2}{2}\&times;{10}^{-3}---\left(8\right)$

Wherein: ψ represents impeller medium velocity coefficient, ω ₂Be the impeller outlet relative velocity;

C. leaving loss (is used Δ W _OutExpression), calculate by formula 9.

$\mathrm{\&Delta;}{W}_{\mathrm{out}}=\frac{{\mathrm{<figure-callout\; id="2"\; label="c"\; filenames="H2009102372775E0000021.png"\; state="\{\{state\}\}">c</figure-callout>}}_2^2}{2}\&times;{10}^{-3}---\left(9\right)$

D. impeller friction and ventilation loss (are used Δ W _RdExpression).Because the flow losses of air-flow in turbine box have been included in the ventilation loss, so calculate by formula 10.

$\mathrm{\&Delta;}{W}_{\mathrm{rd}}=\frac{75\&times;\mathrm{\&beta;}\&times;{10}^{-6}\&times;{\mathrm{\&rho;}}_{1m}{u}_1^3{D}_1^2}{M_{\mathrm{Td}}\&times;{10}^3}\&times;9.806---\left(10\right)$

Wherein, β represents the shape coefficient of hub disk; ρ _1mAverage density around the expression impeller; u ₁Rim velocity for impeller inlet; D ₁Expression impeller inlet diameter; W _TdAdiabatic expansion merit before the expression impeller.

E. air loss (is used Δ W _LeExpression), calculate by formula 11.

ΔW _le＝0.005W _Td； (11)

Based on more than, to the turbosupercharger of nozzle ring is arranged, turbine loss sum (W represents with Δ) is:

ΔW＝ΔW ₁+ΔW _i+ΔW _out+ΔW _rd+ΔW _le (12)

To there not being the turbosupercharger of nozzle ring, turbine loss sum Δ W is:

ΔW＝ΔW _i+ΔW _out+ΔW _rd+ΔW _le (13)

Step 5, acquisition turbosupercharger are reduced to this stage pneumatic plant power consumption of 0 rotating speed by working speed

Data acquisition process and control system are used the data that obtain in step 3, obtain turbosupercharger and be reduced to this stage pneumatic plant power consumption of 0 rotating speed by working speed.

After cutting off source of the gas, the pneumatic plant flow is reduced to zero by steady state flow, and the compressor impeller power that acting consumes to air adopts the mean value of compressor power under working speed in this process, calculates by formula (14):

$N_C=\frac{G_C{c}_{p_0}{T}_{C1}^{*}({{\mathrm{\&pi;}}_C}^{\frac{\mathrm{\&kappa;}-1}{\mathrm{\&kappa;}}}-1)}{2{\mathrm{\&eta;}}_C}---\left(14\right)$

Wherein:

Expression pressurization by compressed air specific heat,

T _C1 ^*Expression compressor air inlet machine stagnation temperature; π _CThe expression pressure ratio; κ represents the air adiabatic index, κ=1.4; η _CThe expression compressor efficiency.

Total afterpower of step 6, acquisition turbosupercharger

Data acquisition process and control system are used the data that obtain in step 3, obtain the total afterpower of turbosupercharger.Concrete steps are as follows:

1. adopt to cut off the data that speed probe is gathered behind the source of the gas, render speed---time curve is hyperbolic type curve y=ax with this curve fitting ^-n, asymptotic line is x axle and y axle, curve is at first quartile.According to rotating speed---time curve is obtained this slope of a curve, i.e. the rotating speed of supercharger rotor rate over time

2. obtain supercharger excess torque sum and (use M _fExpression), calculate by formula 15.

$M_f=-I_0\frac{\mathrm{d\&omega;}}{\mathrm{dt}}=-\frac{\mathrm{\&pi;}}{30}{I}_0\frac{\mathrm{dn}}{\mathrm{dt}}---\left(15\right)$

Wherein, M _fBe supercharger excess torque sum; I ₀Moment of inertia for rotor; ω is the angular velocity of rotor; N is the supercharger rotor rotating speed; T is the time.

3. the total afterpower that obtains turbosupercharger (is used N _fExpression), calculate by formula 16.

$N_f=M_f\mathrm{\&omega;}=\frac{\mathrm{\&pi;n}}{30}{M}_f---\left(16\right)$

Wherein, N _fBe the total afterpower of turbosupercharger.

The mechanical loss power of step 7, acquisition turbosupercharger

On step 4, five, six basis, obtain the supercharger mechanical loss power.Its concrete steps are:

1. obtain friction loss factor by formula 17 and (use k ₁Expression):

$k_1=\frac{G_C{W}_I+G_T\mathrm{\&Delta;W}+N_C}{N_f\&times;{10}^3}=\frac{G_C{W}_I+(G_a+G_f)\mathrm{\&Delta;W}+N_C}{N_f\&times;{10}^3}---\left(17\right)$

Wherein: G _CBe the supercharger air compressor mass rate; G _aBe draft tube compressed air quality flow; G _fBe fuel mass flow.

2. obtain the transient state friction loss factor and (use k ₂Expression).Shut down when being the supercharger steady operation 5～6 times of axial force that the transient condition rotor born.That is:

k ₂＝(5～6)μ (18)

Wherein: μ---dynamic friction factor.

3. obtain the mechanical loss power of turbosupercharger.The axial load direction that the vehicle turbocharger turbine rotor is born changes, and when transient condition was quickened in starting, rotor axial power was pointed to turbine end; When shutting down the deceleration transient condition, rotor axial power is pointed to the pneumatic plant end.So the mechanical loss power of turbosupercharger when its steady operation is:

N＝(1-k ₁)k ₂N _f (19)

By above-mentioned steps, can obtain the mechanical loss power of turbosupercharger.

In addition, compare, the invention provides a kind of a kind of conversion method that the test figure that records under the varying environment is converted to the standard environment situation for the ease of the test figure that will record under the varying environment.The standard environment situation is: atmospheric temperature is 298K (25 ℃); Pressure is 100KPa (760mmHg).When the experimental enviroment situation is different from the standard environment situation, to real income mechanical loss power N _fConvert according to standard ambient condition, i.e. rotation speed n and flow G being comprised in the formula 19 _C, converted according to standard environment, obtain amounting to mechanical loss and (use N _CnpExpression).

$N_{\mathrm{cnp}}=k_{1\mathrm{cnp}}{k}_2{N}_{f_{\mathrm{cnp}}}=(1-\frac{G_{\mathrm{Ccnp}}{W}_I+(G_{\mathrm{Ccnp}}+G_f)\mathrm{\&Delta;W}+N_C}{N_{f_{\mathrm{cnp}}}\&times;{10}^3})(0.5~0.6\mathrm{\&mu;})\frac{\mathrm{\&pi;}{n}_{\mathrm{cnp}}}{30}{M}_{f_{\mathrm{cnp}}}---\left(20\right)$

Beneficial effect

(1) the present invention has provided a kind of device of measuring mechanical loss power of turbocharger more accurately, can measure the mechanical loss power of turbosupercharger accurately, easily.

(2) provide a kind of measuring method of mechanical loss power of turbocharger, the more original method of this method is more accurate, convenient, for the performance of analyzing, pass judgment on turbosupercharger provides the experimental test means.

Description of drawings

Fig. 1 is the structural representation of mechanical loss power of turbocharger measurement mechanism of the present invention;

Fig. 2 is the structural representation of the mechanical loss power of turbocharger measurement mechanism in the specific embodiment of the present invention;

Wherein: the outer source of the gas of 1-, 2-bleed pressure sensor, 3-gas admittance valve, 4-draft tube, the 5-air inlet pressure sensor, the 6-intake air temperature sensor, 7-air-mass flow meter, 8-fuel pressure transmitter, the 9-fuel temperature sensor, 10-fuel mass flow meter, 11-firing chamber, 12-fuel system, the 13-fuel pipe, the 14-portfire, 15-gas inlet casing, 16-turbine air inlet pressure sensor, 17-turbine inlet gas temperature sensor, the 18-turbine exhaust pipe, 19-turbine exhaust gas temperature sensor, 20-turbine exhaust pressure transducer, 21-lubricating oil inlet pressure transducer, 22-lubricating oil inlet temperature sensor, 23-quality of lubrication oil flowmeter, 24-lubricating oil return temperature sensor, 25-lubricating oil return pressure transducer, the 26-grease-box, 27-lube oil pump, 28-lube oil inlet pipe, 29-lubricating oil return pipe, the 30-heating arrangement, 31 cooling devices, 32-pneumatic plant exhaust motorized valve, the 33-speed probe, 34-compressor air inlet machine temperature sensor, 35-compressor air inlet machine pressure transducer, 36-compressor air inlet machine pipe, 37-pneumatic plant mass flowmeter, 38-compressor delivery pressure sensor, 39-compressor delivery temperature sensor, 40-pneumatic plant gas outlet;

Fig. 3 is the turbocharger rotor speed in the specific embodiment of the present invention---a time curve synoptic diagram.

Embodiment

According to technique scheme, the present invention is described in detail below in conjunction with drawings and Examples.

A kind of measurement mechanism of mechanical loss power of turbocharger, structure as shown in Figure 2, comprise: outer source of the gas 1, bleed pressure sensor 2, gas admittance valve 3, air inlet pressure sensor 5, intake air temperature sensor 6, air-mass flow meter 7, fuel pressure transmitter 8, fuel temperature sensor 9, fuel mass flow meter 10, gas inlet casing 15, turbine air inlet pressure sensor 16, turbine inlet gas temperature sensor 17, turbine exhaust pipe 18, turbine exhaust gas temperature sensor 19, turbine exhaust pressure transducer 20, lubricating oil inlet pressure transducer 21, lubricating oil inlet temperature sensor 22, quality of lubrication oil flowmeter 23, lubricating oil return temperature sensor 24, lubricating oil return pressure transducer 25, pneumatic plant exhaust motorized valve 32, speed probe 33, compressor air inlet machine temperature sensor 34, compressor air inlet machine pressure transducer 35, compressor air inlet machine pipe 36, pneumatic plant mass flowmeter 37, compressor delivery pressure sensor 38, compressor delivery temperature sensor 39, pneumatic plant gas outlet 40, data acquisition process and control system, combustion system, lubricating system, automatic temperature control system, this measurement mechanism is in use measured the mechanical loss power of peripherals turbosupercharger.

Described peripherals turbosupercharger comprises turbine, pneumatic plant, bearing body.Gas inlet casing 15 is connected with the turbine inlet of turbosupercharger, and turbine air inlet pressure sensor 16 is installed on the inwall of gas inlet casing 15, turbine inlet gas temperature sensor 17; Turbine exhaust pipe 18 is connected with the turbine outlet of turbosupercharger, and turbine exhaust gas temperature sensor 19 is installed on the inwall of turbine exhaust pipe 18, turbine exhaust pressure transducer 20; Compressor air inlet machine pipe 36 is connected with the compressor inlet of turbosupercharger, and speed probe 33 is installed on the inwall of compressor air inlet machine pipe 36, compressor air inlet machine temperature sensor 34, compressor air inlet machine pressure transducer 35, pneumatic plant mass flowmeter 37; Pneumatic plant gas outlet 40 is connected with the blower outlet of turbosupercharger, and compressor delivery pressure sensor 38 is installed on the inwall of pneumatic plant gas outlet 40, compressor delivery temperature sensor 39; Turbosupercharger is connected with lubricating oil return pipe 29 with the lube oil inlet pipe 28 of lubricating system.

The major function of described outer source of the gas 1 provides the gases at high pressure that the turbine that drives described turbosupercharger reaches higher rotation speed; Bleed pressure sensor 2 is equipped with in outer source of the gas 1 inside; Outer source of the gas 1 links to each other with the draft tube 4 of combustion system by gas admittance valve 3, and the effect of gas admittance valve 3 is that external source of the gas 1 interior gas enters draft tube 4 and plays control action.

The effect of described combustion system provides the combustion gas to the certain energy of turbosupercharger, makes the duty of turbosupercharger meet turbosupercharger and is installed in actual working state on the engine.Combustion system comprises draft tube 4, fuel system 12, portfire 14, firing chamber 11.The effect of fuel system is for the firing chamber provides fuel oil, and fuel system is connected with firing chamber 11 by fuel pipe 13, and on the inwall of fuel pipe, fuel pressure transmitter 8 is installed, fuel temperature sensor 9 and fuel mass flow meter 10.The effect of portfire is that portfire is installed in the firing chamber 11 for the indoor fuel oil of ignition combustion provides burning things which may cause a fire disaster.The effect of firing chamber 11 provides the space of oil inflame, and produces the described duty of turbosupercharger that makes and meet the combustion gas that turbosupercharger is installed in the actual working state on the engine.One end of firing chamber 11 is connected with gas admittance valve 3 by draft tube 4, and the other end links to each other with gas inlet casing 15.Air inlet pressure sensor 5 is installed, intake air temperature sensor 6, air-mass flow meter 7 on the inwall of draft tube 4.

The effect of described lubricating system is for turbosupercharger provides circulating lubricating oil, comprises grease-box 26, lube oil pump 27, lube oil inlet pipe 28, lubricating oil return pipe 29.Its annexation is: grease-box 26 is connected with turbosupercharger with lubricating oil return pipe 29 by lube oil inlet pipe 28, and supercharger lubricating oil inlet pressure transducer 21 and lubricating oil inlet temperature sensor 22 are installed, quality of lubrication oil flowmeter 23 on lube oil inlet pipe 28; Lubricating oil outlet temperature sensor 24 and lubricating oil outlet pressure transducer 25 are installed on lubricating oil return pipe 29.

Automatic temperature control system comprises cooling device 31 and heating arrangement 30, and its effect is to regulate lubricating oil temperature automatically, it is remained under the working temperature, the repeatability of warranty test and accuracy; Its principle of work is: when the lubricating system temperature value of reaching a high temperature, the open cold radiator cooler reduces the lubricating system temperature; When the lubricating system temperature is lower than low-temperature values, open heating arrangement, improve the lubricating system temperature.Preferable, high temperature values is 90 degrees centigrade, low-temperature values is 40 degrees centigrade.

Described data acquisition process and control system adopt the specific implementation of the measuring method of described mechanical loss power of turbocharger.With bleed pressure sensor 2, air inlet pressure sensor 5, intake air temperature sensor 6, air-mass flow meter 7, fuel pressure transmitter 8, fuel temperature sensor 9, fuel mass flow flowmeter 10, turbine air inlet pressure sensor 16, turbine inlet gas temperature sensor 17, turbine exhaust gas temperature sensor 19, turbine exhaust pressure transducer 20, lubricating oil inlet pressure transducer 21, lubricating oil inlet temperature sensor 22, quality of lubrication oil flowmeter 23, lubricating oil return temperature sensor 24, lubricating oil return pressure transducer 25, speed probe 33, compressor air inlet machine temperature sensor 34, compressor air inlet machine pressure transducer 35, compressor air inlet machine pipe 36, pneumatic plant mass flowmeter 37, compressor delivery pressure sensor 38, compressor delivery temperature sensor 39 connects, finish the gathering and handle of the data of sensor acquisition, obtain the mechanical loss power of measured turbosupercharger.The all the sensors that relates in this device both can be wireless senser, also can be the sensor of wired connection.

The effect of described pneumatic plant exhaust motorized valve 32 is apertures of control pneumatic plant gas outlet, and its installation site is the position of pneumatic plant gas outlet 40 near endpiece.

Concrete operations step based on a kind of mechanical loss power of turbocharger measuring method of said apparatus is as follows:

Step 1, turbosupercharger to be measured is connected to the mechanical loss power of turbocharger measurement mechanism that the present invention proposes

Gas inlet casing 15 is connected with the turbine inlet of turbosupercharger, turbine exhaust pipe 18 is connected with the turbine outlet of turbosupercharger, compressor air inlet machine pipe 36 is connected with the compressor inlet of turbosupercharger, pneumatic plant gas outlet 40 is connected with the blower outlet of turbosupercharger, and turbosupercharger is connected with lubricating oil return pipe 29 with the lube oil inlet pipe 28 of lubricating system.

The measurement mechanism of step 2, startup mechanical loss power of turbocharger

On the basis of step 1, open outer source of the gas 1, starting ignition device 14 makes turbosupercharger to be measured reach working speed.

Every data of turbosupercharger in step 3, the acquisition test process

On the basis of step 2, every data of turbosupercharger in the acquisition test process.The concrete operations step is as follows:

The 1. step: measure gas stagnation pressure in the draft tube with air inlet pressure sensor 5, measure gas stagnation temperature in the draft tube with intake air temperature sensor 6, measure gas mass flow in the draft tube with air-mass flow meter 7, measure fuel mass flow with fuel mass flow meter 10, with combustion gas stagnation pressure before the turbine air inlet pressure sensor 16 measurement turbines, with combustion gas stagnation temperature before the turbine inlet gas temperature sensor 17 measurement turbines, measure the turbine exhaust static temperature with turbine exhaust gas temperature sensor 19, measure the turbine exhaust static pressure with turbine exhaust pressure transducer 20, measure the supercharger rotor rotating speed with speed probe 33, measure the compressor air inlet machine stagnation temperature with compressor air inlet machine temperature sensor 34, measure the compressor air inlet machine stagnation pressure with compressor air inlet machine pressure transducer 35, measure the pneumatic plant mass rate with pneumatic plant mass flowmeter 37, measure the blower outlet stagnation pressure with compressor delivery pressure sensor 38, measure the blower outlet stagnation temperatures with compressor delivery temperature sensor 39, and in real time the data of each sensor acquisition are gathered to data acquisition process and control system.

The 2. step: cut off source of the gas,, gather and the record turbosupercharger is reduced to static every data during this period of time by working speed, and in real time the data of each sensor acquisition are gathered to data acquisition process and control system by the 1. each sensor described in the step.

The aerodynamic loss of step 4, acquisition turbosupercharger

Data acquisition process and control system are used the data that obtain in step 3, according to the data of the turbosupercharger that collects under working speed and the aerodynamic loss of associated hot mechanics formula acquisition supercharger.Its concrete grammar is as follows:

The 1. step: the aerodynamic loss sum that obtains turbocharger air compressor.

When air flowed in turbo-charger blower impeller, main aerodynamic loss had with the lower part:

A. the corner loss of air in passage.Comprise that inducer loss (uses W _I1Expression) and the impeller radial blade loss of airflow direction when axially changing into radially (used W _I2Expression), calculate by formula 1 and formula 2 respectively.

$W_{I1}={\mathrm{\&xi;}}_1\frac{{\mathrm{\&omega;}}_1^2}{2}---\left(1\right)$

$W_{I2}={\mathrm{\&xi;}}_2\frac{{\mathrm{<figure-callout\; id="2"\; label="c\; r"\; filenames="H2009102372775E0000021.png"\; state="\{\{state\}\}">c</figure-callout>}}_r^2}{2}---\left(2\right)$

Wherein: ω ₁Be impeller inlet place relative velocity, c _R2Be the radial component of impeller outlet place absolute velocity, ξ ₁And ξ ₂Be loss coefficient.

B. the friction loss of air-flow in impeller passage.Comprise that eddy current loss (uses W _I3Expression), calculate by formula 3.

$W_{I3}={\mathrm{\&xi;}}_3\frac{{\mathrm{<figure-callout\; id="2"\; label="c\; r"\; filenames="H2009102372775E0000021.png"\; state="\{\{state\}\}">c</figure-callout>}}_r^2}{2}---\left(3\right)$

Wherein: ξ ₃Be loss coefficient.

C. air loss and the disk friction loss of air-flow between impeller and housing.

Owing to have the gap between the blade of rotation and the housing, just have air loss inevitably.This being lost between impeller and the compressor casing shows as undercurrent and air blast circulation; Between the impeller wheel back of the body and back of the body dish, show as air blast circulation.This partial loss merged in the disk friction loss calculate.

Disk friction loss (is used W _IdExpression), calculate by formula 4.

$W_{\mathrm{Id}}=\mathrm{\&alpha;}{u}_2^2---\left(4\right)$

Wherein, α is a loss coefficient, u ₂Be the impeller outlet convected velocity.

D. the loss in the compressor casing (is used W _I4Expression), calculate by formula 5.

$W_{I4}={\mathrm{\&xi;}}_4\frac{{c_4}^2}{2}---\left(5\right)$

Wherein, ξ ₄Be volute loss coefficient, c ₄Be diffusion gas outlet absolute velocity.

Based on more than, turbocharger air compressor aerodynamic loss sum (is used W _IExpression) can calculate by formula 6:

W _I＝W _I1+W _I2+W _Id+W _I4 (6)

The 2. step: calculate the aerodynamic loss in the turbocharger turbine, mainly comprise with the lower part:

A. the energy loss in the nozzle ring (is used Δ W ₁Expression), calculate by formula 7.

Wherein: Expression nozzle ring velocity coefficient;

B. the loss in the impeller (is used Δ W _iExpression), calculate by formula 8.

$\mathrm{\&Delta;}{W}_i=(\frac{1}{{\mathrm{\&psi;}}^2}-1)\frac{{\mathrm{\&omega;}}_2^2}{2}\&times;{10}^{-3}---\left(8\right)$

Wherein: ψ represents impeller medium velocity coefficient, ω ₂Be the impeller outlet relative velocity;

C. leaving loss (is used Δ W _OutExpression), calculate by formula 9.

$\mathrm{\&Delta;}{W}_{\mathrm{out}}=\frac{{\mathrm{<figure-callout\; id="2"\; label="c"\; filenames="H2009102372775E0000021.png"\; state="\{\{state\}\}">c</figure-callout>}}_2^2}{2}\&times;{10}^{-3}---\left(9\right)$

D. impeller friction and ventilation loss (are used Δ W _RdExpression).Because the flow losses of air-flow in turbine box have been included in the ventilation loss, so calculate by formula 10.

$\mathrm{\&Delta;}{W}_{\mathrm{rd}}=\frac{75\&times;\mathrm{\&beta;}\&times;{10}^{-6}\&times;{\mathrm{\&rho;}}_{1m}{u}_1^3{D}_1^2}{M_{\mathrm{Td}}\&times;{10}^3}\&times;9.806---\left(10\right)$

Wherein, β represents the shape coefficient of hub disk; ρ _1mAverage density around the expression impeller; u ₁Rim velocity for impeller inlet; D ₁Expression impeller inlet diameter; W _TdAdiabatic expansion merit before the expression impeller.

F. air loss (is used Δ W _LeExpression), calculate by formula 11.

ΔW _le＝0.005W _Td； (11)

Based on more than, to the turbosupercharger of nozzle ring is arranged, turbine loss sum (W represents with Δ) is:

ΔW＝ΔW ₁+ΔW _i+ΔW _out+ΔW _rd+ΔW _le (12)

To there not being the turbosupercharger of nozzle ring, turbine loss sum Δ W is:

ΔW＝+ΔW _i+ΔW _out+ΔW _rd+ΔW _le (13)

Step 5, acquisition turbosupercharger are reduced to this stage pneumatic plant power consumption of 0 rotating speed by working speed

Data acquisition process and control system are used the data that obtain in step 3, obtain turbosupercharger and be reduced to this stage pneumatic plant power consumption of 0 rotating speed by working speed.

After cutting off source of the gas, the pneumatic plant flow is reduced to zero by steady state flow, and the compressor impeller power that acting consumes to air adopts the mean value of compressor power under working speed in this process, calculates by formula (14):

$N_C=\frac{G_C{c}_{p_0}{T}_{C1}^{*}({{\mathrm{\&pi;}}_C}^{\frac{\mathrm{\&kappa;}-1}{\mathrm{\&kappa;}}}-1)}{2{\mathrm{\&eta;}}_C}---\left(14\right)$

Wherein:

Expression pressurization by compressed air specific heat,

T _C1 ^*Expression compressor air inlet machine stagnation temperature; π _CThe expression pressure ratio; κ represents the air adiabatic index, κ=1.4; η _CThe expression compressor efficiency.

Total afterpower of step 6, acquisition turbosupercharger

Data acquisition process and control system are used the data that obtain in step 3, obtain the total afterpower of turbosupercharger.Concrete steps are as follows:

1. adopt to cut off the data that speed probe is gathered behind the source of the gas, render speed---time curve as shown in Figure 2, is hyperbolic type curve y=ax with this curve fitting ^-n, asymptotic line is x axle and y axle, curve is at first quartile.According to rotating speed---time curve is obtained this slope of a curve, i.e. the rotating speed of supercharger rotor rate over time

2. obtain supercharger excess torque sum and (use M _fExpression), calculate by formula 15.

$M_f=-I_0\frac{\mathrm{d\&omega;}}{\mathrm{dt}}=-\frac{\mathrm{\&pi;}}{30}{I}_0\frac{\mathrm{dn}}{\mathrm{dt}}---\left(15\right)$

Wherein, M _fBe supercharger excess torque sum; I ₀Moment of inertia for rotor; ω is the angular velocity of rotor; N is the supercharger rotor rotating speed; T is the time.

3. the total afterpower that obtains turbosupercharger (is used N _fExpression), calculate by formula 16.

$N_f=M_f\mathrm{\&omega;}=\frac{\mathrm{\&pi;n}}{30}{M}_f---\left(16\right)$

Wherein, N _fBe the total afterpower of turbosupercharger.

The mechanical loss power of step 7, acquisition turbosupercharger

On step 4, five, six basis, obtain the supercharger mechanical loss power.Its concrete steps are:

1. obtain friction loss factor by formula 17 and (use k ₁Expression):

$k_1=\frac{G_C\mathrm{\&Delta;}{W}_I+G_T\mathrm{\&Delta;W}+N_C}{N_f\&times;{10}^3}=\frac{G_C\mathrm{\&Delta;}{W}_I+(G_a+G_f)\mathrm{\&Delta;W}+N_C}{N_f\&times;{10}^3}---\left(17\right)$

Wherein: G _CBe the supercharger air compressor mass rate; G _aBe draft tube compressed air quality flow; G _fBe fuel mass flow.

2. obtain the transient state friction loss factor and (use k ₂Expression).Shut down when being the supercharger steady operation 5～6 times of axial force that the transient condition rotor born.That is:

k ₂＝(5～6)μ (18)

Wherein: μ---dynamic friction factor.

3. obtain the mechanical loss power of turbosupercharger.The axial load direction that the vehicle turbocharger turbine rotor is born changes, and when transient condition was quickened in starting, rotor axial power was pointed to turbine end; When shutting down the deceleration transient condition, rotor axial power is pointed to the pneumatic plant end.So the mechanical loss power of turbosupercharger when its steady operation is:

N＝(1-k ₁)k ₂N _f (19)

By above-mentioned steps, can obtain the mechanical loss power of turbosupercharger.

In addition, compare, the invention provides a kind of a kind of conversion method that the test figure that records under the varying environment is converted to the standard environment situation for the ease of the test figure that will record under the varying environment.The standard environment situation is: atmospheric temperature is 298K (25 ℃); Pressure is 100KPa (760mmHg).When the experimental enviroment situation is different from the standard environment situation, to real income mechanical loss power N _fConvert according to standard ambient condition, i.e. rotation speed n and flow G being comprised in the formula 19 _C, converted according to standard environment, obtain amounting to mechanical loss and (use N _CnpExpression).

$N_{\mathrm{cnp}}=k_{1\mathrm{cnp}}{k}_2{N}_{f_{\mathrm{cnp}}}=(1-\frac{G_{\mathrm{Ccnp}}\mathrm{\&Delta;}{W}_I+(G_{\mathrm{Ccnp}}+G_f)\mathrm{\&Delta;W}+N_C}{N_{f_{\mathrm{cnp}}}\&times;{10}^3})(0.5~0.6\mathrm{\&mu;})\frac{\mathrm{\&pi;}{n}_{\mathrm{cnp}}}{30}{M}_{f_{\mathrm{cnp}}}---\left(20\right)$

Claims (5)

1. the measurement mechanism of a mechanical loss power of turbocharger is characterized in that: comprise outer source of the gas, data acquisition process and control system, sensor, heating system, lubricating system, automatic temperature control system;

Described outer source of the gas links to each other with heating system, and its function provides the gases at high pressure that the turbine that drives described turbosupercharger reaches higher rotation speed;

Described heating system is connected with the peripherals turbosupercharger, and its effect provides the combustion gas to the certain energy of turbosupercharger, makes the duty of turbosupercharger meet turbosupercharger and is installed in actual working state on the engine;

Described lubricating system is connected with the bearing body of described peripherals turbosupercharger, and its effect is to provide circulating lubricating oil for turbosupercharger;

Described peripherals turbosupercharger comprises turbine, pneumatic plant, bearing body, turbine exhaust pipe, aerostatic press draft tube, aerostatic press gas outlet;

Described automatic temperature control system is connected with described lubricating system, and its effect is to regulate lubricating oil temperature automatically, it is remained under the working temperature, the repeatability of warranty test and accuracy; Its principle of work is: when the lubricating system temperature value of reaching a high temperature, the open cold radiator cooler reduces the lubricating system temperature automatically; When the lubricating system temperature is lower than low-temperature values, open heating arrangement automatically, improve the lubricating system temperature;

Described sensor comprises gas pressure sensor, liquid-pressure pick-up, gas temperature sensor, fluid temperature sensor, liquid mass flow meter, speed probe, comprises the sensor but is not limited thereto; Described sensor is positioned on the interface channel of the inside of outer source of the gas, outer source of the gas and heating system, heating system inside, lubricating system inside, on turbine exhaust tube wall, aerostatic press air inlet tube wall, the aerostatic press exhaust wall, be used to monitor temperature, pressure, liquid quality flow and the rotating speed etc. of gas or liquid, and give data acquisition process and control system the data transfer that obtains;

Described data acquisition process and control system are to adopt the specific implementation of the measuring method of described mechanical loss power of turbocharger; Data acquisition process and control system obtain data from each sensor, and handle, and obtain the mechanical loss power of measured turbosupercharger.

2. the measurement mechanism of a kind of mechanical loss power of turbocharger according to claim 1 is characterized in that: when automatic temperature control system reached 90 degrees centigrade in the lubricating system temperature, the open cold radiator cooler reduced the lubricating system temperature automatically; When the lubricating system temperature is lower than 40 degrees centigrade, open heating arrangement automatically, improve the lubricating system temperature.

3. according to the measurement mechanism of claim 1 or the described a kind of mechanical loss power of turbocharger of claim 2, it is characterized in that: comprise outer source of the gas (1), bleed pressure sensor (2), gas admittance valve (3), air inlet pressure sensor (5), intake air temperature sensor (6), air-mass flow meter (7), fuel pressure transmitter (8), fuel temperature sensor (9), fuel mass flow flowmeter (10), gas inlet casing (15), turbine air inlet pressure sensor (16), turbine inlet gas temperature sensor (17), turbine exhaust pipe (18), turbine exhaust gas temperature sensor (19), turbine exhaust pressure transducer (20), lubricating oil inlet pressure transducer (21), lubricating oil inlet temperature sensor (22), quality of lubrication oil flowmeter (23), lubricating oil return temperature sensor (24), lubricating oil return pressure transducer (25), pneumatic plant exhaust motorized valve (32), speed probe (33), compressor air inlet machine temperature sensor (34), compressor air inlet machine pressure transducer (35), compressor air inlet machine pipe (36), pneumatic plant mass flowmeter (37), compressor delivery pressure sensor (38), compressor delivery temperature sensor (39), pneumatic plant gas outlet (40), data acquisition process and control system, combustion system, lubricating system, automatic temperature control system; This measurement mechanism is in use measured the mechanical loss power of peripherals turbosupercharger;

Described peripherals turbosupercharger comprises turbine, pneumatic plant, bearing body; Turbosupercharger with the annexation of the measurement mechanism of described mechanical loss power of turbocharger is: gas inlet casing (15) is connected with the turbine inlet of turbosupercharger, its effect is that turbosupercharger is delivered in the combustion gas that combustion system produces, turbine air inlet pressure sensor (16) is installed, turbine inlet gas temperature sensor (17) on the inwall of gas inlet casing (15); Turbine exhaust pipe (18) is connected with the turbine outlet of turbosupercharger, and its effect is the waste gas after the turbine acting to be discharged, turbine exhaust gas temperature sensor (19) is installed, turbine exhaust pressure transducer (20) on the inwall of turbine exhaust pipe (18); Compressor air inlet machine pipe (36) is connected with the compressor inlet of turbosupercharger, air enters turbosupercharger by compressor air inlet machine pipe (36), speed probe (33) is installed on the inwall of compressor air inlet machine pipe (36), compressor air inlet machine temperature sensor (34), compressor air inlet machine pressure transducer (35), pneumatic plant mass flowmeter (37); Pneumatic plant gas outlet (40) is connected with the blower outlet of turbosupercharger, pneumatic plant is discharged the gases at high pressure after the air acting, compressor delivery pressure sensor (38) is installed, compressor delivery temperature sensor (39) on the inwall of pneumatic plant gas outlet (40); Turbosupercharger is connected with lubricating oil return pipe (29) with the lube oil inlet pipe (28) of lubricating system;

The major function of described outer source of the gas (1) provides the gases at high pressure that the turbine that drives described turbosupercharger reaches higher rotation speed; Bleed pressure sensor (2) is equipped with in outer source of the gas (1) inside; Outer source of the gas (1) links to each other with the draft tube (4) of combustion system by gas admittance valve (3), and the effect of gas admittance valve (3) is that the interior gas of external source of the gas (1) enters draft tube (4) and plays control action;

The effect of described combustion system provides the combustion gas to the certain energy of turbosupercharger, makes the duty of turbosupercharger meet turbosupercharger and is installed in actual working state on the engine; Combustion system comprises draft tube (4), fuel system (12), portfire (14), firing chamber (11); The effect of fuel system is to provide fuel oil for the firing chamber, fuel system is connected with firing chamber (11) by fuel pipe (13), and fuel pressure transmitter (8), fuel temperature sensor (9) and fuel mass flow meter (10) are installed on the inwall of fuel pipe; The effect of portfire is for the indoor fuel oil of ignition combustion provides burning things which may cause a fire disaster, and portfire is installed in the firing chamber (11); The effect of firing chamber (11) provides the space of oil inflame, and produces the described duty of turbosupercharger that makes and meet the combustion gas that turbosupercharger is installed in the actual working state on the engine; One end of firing chamber (11) is connected with gas admittance valve (3) by draft tube (4), and the other end links to each other with gas inlet casing (15); Air inlet pressure sensor (5) is installed, intake air temperature sensor (6), air-mass flow meter (7) on the inwall of draft tube (4);

The effect of described lubricating system is for turbosupercharger provides circulating lubricating oil, comprises grease-box (26), lube oil pump (27), lube oil inlet pipe (28), lubricating oil return pipe (29); Its annexation is: grease-box (26) is connected with turbosupercharger with lubricating oil return pipe (29) by lube oil inlet pipe (28), and supercharger lubricating oil inlet pressure transducer (21) and lubricating oil inlet temperature sensor (22) are installed, quality of lubrication oil flowmeter (23) on lube oil inlet pipe (28); Lubricating oil outlet temperature sensor (24) and lubricating oil outlet pressure transducer (25) are installed on lubricating oil return pipe (29);

Automatic temperature control system comprises cooling device (31) and heating arrangement (30), and its effect is to regulate lubricating oil temperature automatically, it is remained under the working temperature, the repeatability of warranty test and accuracy; Its principle of work is: when the lubricating system temperature value of reaching a high temperature, the open cold radiator cooler reduces the lubricating system temperature; When the lubricating system temperature is lower than low-temperature values, open heating arrangement, improve the lubricating system temperature;

Described data acquisition process and control system are to adopt the specific implementation of the measuring method of described mechanical loss power of turbocharger; With bleed pressure sensor (2), air inlet pressure sensor (5), intake air temperature sensor (6), air-mass flow meter (7), fuel pressure transmitter (8), fuel temperature sensor (9), fuel mass flow flowmeter (10), turbine air inlet pressure sensor (16), turbine inlet gas temperature sensor (17), turbine exhaust gas temperature sensor (19), turbine exhaust pressure transducer (20), lubricating oil inlet pressure transducer (21), lubricating oil inlet temperature sensor (22), quality of lubrication oil flowmeter (23), lubricating oil return temperature sensor (24), lubricating oil return pressure transducer (25), speed probe (33), compressor air inlet machine temperature sensor (34), compressor air inlet machine pressure transducer (35), compressor air inlet machine pipe (36), pneumatic plant mass flowmeter (37), compressor delivery pressure sensor (38), compressor delivery temperature sensor (39) connects, finish the gathering and handle of the data of sensor acquisition, obtain the mechanical loss power of measured turbosupercharger;

The effect of described pneumatic plant exhaust motorized valve (32) is the aperture of control pneumatic plant gas outlet, and its installation site is the position of pneumatic plant gas outlet (40) near endpiece.

4. the measuring method of a mechanical loss power of turbocharger, it is characterized in that: the concrete operations step is as follows:

Step 1, turbosupercharger to be measured is connected to the mechanical loss power of turbocharger measurement mechanism that the present invention proposes;

The measurement mechanism of step 2, startup mechanical loss power of turbocharger makes turbosupercharger to be measured reach working speed;

Every data in step 3, the acquisition test process, the concrete operations step is as follows:

The 1. step: reach data under the working speed situation by described each sensor acquisition turbosupercharger, and with the data transmission of each sensor acquisition to data acquisition process and control system;

The 2. step: cut off source of the gas,, gather and the record turbosupercharger is reduced to static every data during this period of time by working speed once more by described each sensor, and with the data transmission of each sensor acquisition to data acquisition process and control system;

The aerodynamic loss of step 4, acquisition turbosupercharger

Data acquisition process and control system are used the data that obtain in step 3, according to the data of the turbosupercharger that collects under working speed and the aerodynamic loss of associated hot mechanics formula acquisition supercharger; Its concrete grammar is as follows:

The 1. step: the aerodynamic loss sum that obtains turbocharger air compressor;

When air flowed in turbo-charger blower impeller, main aerodynamic loss had with the lower part:

A. the corner loss of air in passage; Comprise the inducer loss, use W _I1Expression, and the impeller radial blade is used W with the loss of airflow direction when axially changing into radially _I2Expression calculates by formula 1 and formula 2 respectively;

$W_{I1}={\mathrm{\&xi;}}_1\frac{{\mathrm{\&omega;}}_1^2}{2}---\left(1\right)$

$W_{I2}={\mathrm{\&xi;}}_2\frac{c_{r2}^2}{2}---\left(2\right)$

Wherein: ω ₁Be impeller inlet place relative velocity, c _R2Be the radial component of impeller outlet place absolute velocity, ξ ₁And ξ ₂Be loss coefficient;

B. the friction loss of air-flow in impeller passage; Comprise eddy current loss, use W _I3Expression is calculated by formula 3;

$W_{I3}={\mathrm{\&xi;}}_3\frac{c_{r2}^2}{2}---\left(3\right)$

Wherein: ξ ₃Be loss coefficient;

C. air loss and the disk friction loss of air-flow between impeller and housing;

The air loss of air-flow between impeller and housing merged in the disk friction loss calculate; Disk friction loss W _IdExpression calculates by formula 4;

$W_{\mathrm{Id}}={\mathrm{\&alpha;u}}_2^2---\left(4\right)$

Wherein, α is a loss coefficient, u ₂Be the impeller outlet convected velocity;

D. W is used in the loss in the compressor casing _I4Expression is calculated by formula 5;

$W_{I4}={\mathrm{\&xi;}}_4\frac{{c_4}^2}{2}---\left(5\right)$

Wherein, ξ ₄Be volute loss coefficient, c ₄Be diffusion gas outlet absolute velocity;

Based on more than, turbocharger air compressor aerodynamic loss sum is used W _IExpression can calculate by formula 6:

W _I＝W _I1+W _I2+W _Id+W _I4 (6)

The 2. step: obtain the aerodynamic loss in the turbocharger turbine, mainly comprise with the lower part:

A. the energy loss in the nozzle ring is used Δ W ₁Expression calculates by formula 7;

Wherein:

Expression nozzle ring velocity coefficient;

B. Δ W is used in the loss in the impeller _iExpression calculates by formula 8;

$\mathrm{\&Delta;}{W}_i=(\frac{1}{{\mathrm{\&psi;}}^2}-1)\frac{{\mathrm{\&omega;}}_2^2}{2}\&times;{10}^{-3}---\left(8\right)$

Wherein: ψ represents impeller medium velocity coefficient, ω ₂Be the impeller outlet relative velocity;

C. leaving loss is used Δ W _OutExpression calculates by formula 9;

$\mathrm{\&Delta;}{W}_{\mathrm{out}}=\frac{c_2^2}{2}\&times;{10}^{-3}---\left(9\right)$

D. impeller friction and ventilation loss are used Δ W _RdExpression calculates by formula 10;

$\mathrm{\&Delta;}{W}_{\mathrm{rd}}\frac{75\&times;\mathrm{\&beta;}\&times;{10}^{-6}\&times;{\mathrm{\&rho;}}_{1m}{u}_1^3{D}_1^2}{M_{\mathrm{Td}}\&times;{10}^3}\&times;9.806---\left(10\right)$

Wherein, β represents the shape coefficient of hub disk; ρ _1mAverage density around the expression impeller; u ₁Rim velocity for impeller inlet; D ₁Expression impeller inlet diameter; W _TdAdiabatic expansion merit before the expression impeller;

E. Δ W is used in air loss _LeExpression calculates by formula 11;

ΔW _le＝0.005W _Td； (11)

Based on more than, to the turbosupercharger of nozzle ring is arranged, turbine loss sum, W represents with Δ:

ΔW＝ΔW ₁+ΔW _i+ΔW _out+ΔW _rd+ΔW _le (12)

To there not being the turbosupercharger of nozzle ring, turbine loss sum Δ W is:

ΔW＝ΔW _i+ΔW _out+ΔW _rd+ΔW _le (13)

Step 5, acquisition turbosupercharger are reduced to this stage pneumatic plant power consumption of 0 rotating speed by working speed

Data acquisition process and control system are used the data that obtain in step 3, obtain turbosupercharger and be reduced to this stage pneumatic plant power consumption of 0 rotating speed by working speed, adopt the mean value of compressor power under working speed, calculate by formula (14):

$N_C=\frac{G_C{c}_{p_0}{T}_{C1}^{*}({{\mathrm{\&pi;}}_C}^{\frac{\mathrm{\&kappa;}-1}{\mathrm{\&kappa;}}}-1)}{2{\mathrm{\&eta;}}_C}---\left(14\right)$

Wherein: Expression pressurization by compressed air specific heat, T _C1 ^*Expression compressor air inlet machine stagnation temperature; π _CThe expression pressure ratio; κ represents the air adiabatic index, κ=1.4; η _CThe expression compressor efficiency;

Total afterpower of step 6, acquisition turbosupercharger

Data acquisition process and control system are used the data that obtain in step 3, obtain the total afterpower of turbosupercharger; Concrete steps are as follows:

1. adopt to cut off the data that speed probe is gathered behind the source of the gas, render speed---time curve is hyperbolic type curve y=ax with this curve fitting ^-n, asymptotic line is x axle and y axle, curve is at first quartile; According to rotating speed---time curve is obtained this slope of a curve, i.e. the rotating speed of supercharger rotor rate over time

2. obtain supercharger excess torque sum, use M _fExpression calculates by formula 15;

$M_f=-I_0\frac{\mathrm{d\&omega;}}{\mathrm{dt}}=-\frac{\mathrm{\&pi;}}{30}{I}_0\frac{\mathrm{dn}}{\mathrm{dt}}---\left(15\right)$

Wherein, M _fBe supercharger excess torque sum; I ₀Moment of inertia for rotor; ω is the angular velocity of rotor; N is the supercharger rotor rotating speed; T is the time;

3. obtain total afterpower of turbosupercharger, use N _fExpression calculates by formula 16;

$N_f=M_f\mathrm{\&omega;}=\frac{\mathrm{\&pi;n}}{30}{M}_f---\left(16\right)$

Wherein, N _fBe the total afterpower of turbosupercharger;

The mechanical loss power of step 7, acquisition turbosupercharger

On step 4, five, six basis, obtain the supercharger mechanical loss power; Its concrete steps are:

1. obtain friction loss factor by formula 17, use k ₁Expression:

$k_1=\frac{G_C{W}_I+G_T\mathrm{\&Delta;W}+N_C}{N_f\&times;{10}^3}=\frac{G_C{W}_1+(G_a+G_f)\mathrm{\&Delta;W}+N_C}{N_f\&times;{10}^3}---\left(17\right)$

Wherein: G _CBe supercharger air compressor mass rate G _aBe draft tube compressed air quality flow; G _fBe fuel mass flow; W ₁Be turbocharger air compressor aerodynamic loss sum; Δ W is a turbine loss sum; N _CFor turbosupercharger is reduced to this stage pneumatic plant power consumption of 0 rotating speed by working speed; N _fBe the total afterpower of turbosupercharger;

2. obtain the transient state friction loss factor, use k ₂Expression;

k ₂＝(5～6)μ (18)

Wherein: μ---dynamic friction factor;

3. obtain the mechanical loss power of turbosupercharger;

N＝(1-k ₁)k ₂N _f (19)

By above-mentioned steps, can obtain the mechanical loss power of turbosupercharger.

5. the measuring method of a kind of mechanical loss power of turbocharger according to claim 4, it is characterized in that: when its measurement environment is non-standard environmental aspect, its measurement result can be converted into the mechanical loss of amounting under the standard environment situation by formula 20, uses N _CnpExpression:

$N_{\mathrm{cnp}}=k_{1\mathrm{cnp}}{k}_2{N}_{f_{\mathrm{cnp}}}=(1-\frac{G_{\mathrm{Ccnp}}\mathrm{\&Delta;}{W}_I+(G_{\mathrm{Ccnp}}+G_f)\mathrm{\&Delta;W}+N_C}{N_{f_{\mathrm{cnp}}}\&times;{10}^3})(0.5~0.6\mathrm{\&mu;})\frac{{\mathrm{\&pi;n}}_{\mathrm{cnp}}}{30}{M}_{f_{\mathrm{cnp}}}---\left(20\right)$

The standard environment situation is: atmospheric temperature is 298K (25 ℃); Pressure is 100KPa (760mmHg).

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