RU2267762C1 - Method to control speed of traction vehicles internal combustion engineering - Google Patents

Abstract

FIELD: mechanical engineering; internal combustion engines.

SUBSTANCE: according to proposed method, radius r_k of vehicle propulsor, namely, drive wheel or drive sprocket, and vehicle gross weight G, are measured, and using load brake, engine torque M_e id changed. Engine torque M_e and engine speed n set by means of governor are measured for each value of torque M_e, and fuel consumption for each value of engine torque M_e is measured and, basing on results of measurements, curve is plotted showing dependence of power N_e from engine torque M_e. Drawbar force P_dr of traction vehicle is found from expression P_dr= M_e(η_tr·i/r_k)-P_fmax, where η_tr is transmission efficiency; I is transmission gear ratio; P_fmax is traction vehicle maximum rolling resistance found from expression P_fmax=f_max·G, where f_max is maximum rolling resistance coefficient, and G is gross weight of traction vehicle. Skid coefficient δ of traction vehicle is found and result are transformed into electric signals which are sent to computer to plot curves showing dependence of drawbar force P_dr from engine torque M_e for different gears of vehicle and dependence of skid coefficient δ from drawbar force P_dr of traction vehicle after which maximum drawbar force P_drmax created by propulsors of traction vehicle with gross weight is determined and signals are formed and sent to computer to determine skid coefficient from dependence of skid coefficient δ from vehicle drawbar force P_dr, for each gear of vehicle signals are formed and sent to computer to determine corresponding value of torque M_e1 maximum drawbar force P_drmax dependence of drawbar force P_dr from torque M_e, then signal is formed and sent to computer to determine power N_e1 for maximum drawbar force P_drmax by value of torque M_e1 from curve showing dependence of engine power N_e from engine torque M_e, value of power N_e1, thus found, is compared with value of power N_e from engine specifications and if they do not coincide, engine speed n and transmission gear ratio I are adjusted.

EFFECT: improved efficiency of use of vehicle engine owing to increased accuracy of measurement of engine power with account of specific operating conditions of vehicle, reduced labor input at measurements and processing of results of measurements.

2 cl, 1 dwg

Description

The invention relates to the field of engine manufacturing, in particular to testing and regulating internal combustion engines.

A known method for determining the power and other operational parameters of an internal combustion engine, which consists in conducting bench tests of the engine, changing the load on the engine with the brake, constructing a regulatory characteristic of the dependence of the engine parameters on the magnitude of the torque and determining a number of engine operational parameters, such as speed, flow rate fuel and others (see Gunzburg B.Ya. Tractors and automobiles. - M .: VSHNZO, 1968, p. 3-69).

The disadvantage of this method is that the power is determined without taking into account the dependence of the tangential thrust of the vehicle propulsion for each transmission on the magnitude of the engine torque, which allows you to determine only a very approximate, estimated value of the engine power.

There is a method of determining the power of an internal combustion engine of a vehicle, which consists in loading an internal combustion engine, measuring the rotational speed of the engine shaft when the vehicle is moving with an allowable traction load and design speed, and determining the power from a mathematical expression that takes into account the number of revolutions, the primary torque coefficient and the torque converter parameters (see USSR patent No. 1806336, IPC G 01 M 15/00, published March 30, 1993).

A known method of regulating the number of revolutions of an internal combustion engine on a test bench with a loading device, which consists in changing the operating mode of the engine for the load and applying electrical signals to the actuator that controls the fuel supply to the engine (see USSR author's certificate No. 486138, IPC F 02 D 37 / 00 published on 1/9/1976).

A disadvantage of the known technical solutions lies in the insufficient accuracy of measuring engine power, since it does not take into account the dependence of the tangential thrust of the vehicle propulsion for each transmission on the magnitude of the torque of the fuel engine, and also does not take into account the specific operating conditions of the vehicle.

The objective of the claimed invention is to increase the efficiency of using a vehicle engine, which is achieved by the following technical result - increasing the accuracy of measuring engine power taking into account specific operating conditions of the vehicle and reducing the complexity of measuring the measurement results and their processing.

The specified technical result is achieved by the fact that the method of regulating the number of revolutions of the internal combustion engine of the traction vehicle consists in measuring the radius r _{k of the} vehicle propeller - the driving wheel or the drive sprocket, the total weight G of the vehicle, and the torque brake torque M _d of the engine, wherein the measured values of torque M _d of the engine and number of revolutions n of the engine, established via dd regulator tor for each value of the torque M _d, measured fuel consumption for each value of the torque M _d of the engine build the regulatory characteristics of the power N _e of the torque M _d of the engine on the test results, determine the traction force P _cr hook tractive vehicle by expression P _cr = M _e · (η _{rp · i / r k) -P fmax} , where _tr η - efficiency of transmission, i - ratio of the transmission, P _fmax - maximum force of traction in rolling resistance of the vehicle, determine I by the expression P _fmax = f _max · G, where f _max - maximum coefficient of rolling resistance, G - total weight of the traction vehicle is determined coefficient of slipping δ tractive vehicle, converts it to electric signals sent signals to the computer and their based construct according traction hook P _cr of the torque M _d of the engine for different transmissions of the vehicle and the dependence of the coefficient of slippage of the traction δ P _cr the hook of the traction vehicle, and then determined elyayut maximum traction force F _krmax hook tractive vehicle, which is created by propulsors tractive vehicle with full specify the weight, shape and direct the signals to a computer for determining the coefficient of slippage of the depending slipping coefficient δ of the thrust P _cr hook tractive vehicle, for of each transmission of the vehicle, signals are generated and sent to a computer to determine the corresponding value of torque M _d1 for maximum traction force P _kmax on the hook t from the dependence of the traction force P _cr on the hook of the traction vehicle on the torque M _d , then a signal is generated and sent to the computer to determine the power N _e1 for the maximum traction force P _crmax on the hook of the traction vehicle according to the magnitude of the torque M _d1 from regulatory characteristics of the dependence of engine power N _e on the value of engine torque M _d , compare the obtained value of power N _e1 with the value of power N _e from the passport data of the engine and in case of non-compliance The effects between these values control the engine speed n and the gear ratio i.

The slipping coefficient δ is determined by measuring at a predetermined distance S the values of the revolutions n _{cr of the} propulsion devices (wheels or sprockets) on the right and left sides of the traction vehicle when it is moving with full weight and the values of the revolutions n _{kx of the} propulsion _devices (wheels or sprockets) on the right and the left sides of the traction vehicle when it is idling, averaging the obtained values of the number of revolutions when the traction vehicle is moving with full weight up to the value of n _CRS and when the traction vehicle is idling means to the value of n _khsr and calculation of the slipping coefficient δ by the expression δ = (n _ksr -n _khsr ) / n _ksr .

The drawing shows graphical dependencies used in the implementation process of the claimed method.

The claimed method can be implemented on a well-known automated stand with software control, allowing to simulate the engine on a vehicle. Such a stand, as a rule, contains a test internal combustion engine, a dynamometer, an electric or hydraulic brake, a tachogenerator, a fuel metering device, sensors of various engine parameters, a computer (electronic computer) with a device for converting the measured parameters into electrical signals and entering them into a computer . Such stands are widely known, for example, from the book Stefanovsky B.S. and others. Tests of internal combustion engines. - M .: Mechanical Engineering, 1972, p. 43-49, or from USSR Patent No. 1729303, IPC G 01 M 15/00, published on 04/23/1992, or RF Patent No. 2053492, IPC G 01 M 15/00, published January 27, .1996, and can be used to implement the claimed method.

The method for regulating the operational parameters of the internal combustion engine and the traction vehicle according to the results of determining the power of the internal combustion engine is to measure the value of the radius r _{k of the} vehicle propulsion - the drive wheel or the drive sprocket and the total weight G of the vehicle.

The engine is tested using a load brake, the magnitude of the engine torque M _{d is} changed using the load brake, the sensors measure the engine torque M _{d, the} engine speed n set by the engine controller for each torque M _d , the flow rate is measured fuel for each torque value M _d engine.

The obtained data is converted into electrical signals, the signals are sent to a computer, and based on them, a regulatory characteristic A is built of the dependence of the power N _e on the magnitude of the engine torque M _d according to the test results (see dependence A - N _e = f (M _d ) in the drawing) .

The traction force P _cr on the hook of the traction vehicle is determined by the expression P _cr = M _d · (η _tr · i / r _k ) -P _fmax , where η _tr is the transmission efficiency, i is the gear ratio of the transmission, r _k is the radius propulsor of a traction vehicle, drive wheel or sprocket of a traction vehicle, P _fmax is the maximum rolling resistance of the traction vehicle, determined by the expression P _fmax = f _max · G, where f _max is the maximum coefficient of rolling resistance, G is the total weight of the traction vehicle.

The slipping coefficient δ is determined by measuring at a predetermined distance S the values of the revolutions n _{kr of the} propulsion devices (wheels or sprockets) on the right and left sides of the traction vehicle when it is moving with full weight and the values of the revolutions n _{kx of the} propulsion _devices (wheels or sprockets) on the right and the left sides of the traction vehicle at idle. Next, the obtained values of the revolutions are averaged during the movement of the traction vehicle with full weight to a value of n _crcr and during idle of the traction vehicle to a value of n _crcr and the slipping coefficient δ is calculated by the expression δ = (n _crcr -n _crcr ) / n _crcr .

The obtained values are converted into electrical signals, the signals are sent to a computer, and based on them, the dependencies B of the traction force on the hook P _cr from the engine torque M _d for various gears of the vehicle are built (see the dependence B - P _cr = f (M _d ) on drawing). Build the dependence of the slip coefficient δ on the traction force P _cr on the hook of the traction vehicle (see the dependence B - δ = f (M _d ) in the drawing).

Then determine, for example by calculation, the maximum traction force P _kmax on the hook of the traction vehicle, which is created by the propulsion of the traction vehicle with a full specified weight.

Next, they generate and send signals 1 (see the drawing) to a computer to determine the allowable skid coefficient from the dependence of the skid coefficient δ on the traction force P _cr on the hook of the traction vehicle.

In this case, signal 2 is generated and sent (see the drawing) to a computer to determine the corresponding value of the torque M _d1 for the maximum traction force P _crmax on the hook of the traction vehicle from the dependence B of the traction force P _cr on the hook of the traction vehicle on the torque M _d .

After that, a signal 3 is generated and sent to a computer to determine the power N _e1 for the maximum traction force P _kmax on the hook of the traction vehicle by the magnitude of the torque M _d1 from the regulatory characteristic of the dependence of engine power N _e on the magnitude of the engine torque M _d .

Next, the obtained power value N _{e1 is} compared with the power value Ne from the passport data of the engine and, if there is a discrepancy between these values, the engine speed n and the gear ratio i are regulated.

Thus, it provides an increase in the accuracy of measuring engine power, taking into account the specific operating conditions of the vehicle and reducing the complexity of measuring the measurement results and their processing.

Claims (2)

1. The method of controlling the number of revolutions of the internal combustion engine of a traction vehicle, which consists in measuring the radius r _{k of the} vehicle propeller — the drive wheel or the drive sprocket, the total weight G of the vehicle, and applying the load brake to change the torque M _{d of the} engine while measuring the magnitude of the torque M _{d of the} engine and the engine speed n set by the engine controller for each magnitude of the torque M _d measure the fuel consumption for each magnitude of the engine torque M _d , build a regulatory characteristic of the dependence of the power N _e on the magnitude of the engine torque M _d according to the test results, determine the traction force P _cr on the hook of the traction vehicle by the expression P _cr = M _d · ( η _tr · i / r _k ) -P _fmax , where η _tr is the transmission efficiency, i is the gear ratio of the transmission, P _fmax is the maximum rolling resistance of the traction vehicle, determined by the expression P _fmax = f _max · G, where f _max - maximum rolling resistance coefficient, G is the total weight of the traction vehicle, the slipping coefficient δ of the traction vehicle is determined, the obtained values are converted into electrical signals, the signals are sent to the computer and based on them are built the dependences of the traction force on the hook R _cr from the engine torque M _d for various gears of the vehicle and the dependence of the coefficient δ from slipping traction P _cr traction on the hook of the vehicle, after which the maximum traction force P _krmax hook tyago th vehicle posed thrusters tractive vehicle with full specify the weight, shape and direct the signals to a computer for determining the coefficient of slippage of the depending slipping coefficient δ of the thrust force P _cr hook tractive vehicle, for each transmission of the vehicle is formed and sent signals to a computer to determine the corresponding magnitude of the torque M _d1 for the maximum traction force P _kmax on the hook of the traction vehicle from the dependence of traction forces Р _кр on the hook of the traction vehicle from the torque M _d , then generate and send a signal to the computer to determine the power N _e1 for the maximum traction force Р _crmax on the hook of the traction vehicle by the magnitude of the torque M _d1 from the regulatory characteristic of the engine power N _e of the torque M _d of the engine, compares the obtained value with the power N _e1 N _e value output from the motor data sheet in case of disparity between these quantities adjusted number of n Orochi engine and the transmission ratio i of the transmission. 2. The method according to claim 1, characterized in that the slippage coefficient δ is determined by measuring at a predetermined distance S the values of the revolutions n _{cr of the} movers (wheels or sprockets) on the right and left sides of the traction vehicle when it is moving with full weight and the magnitude number of revolutions n _kx propulsion (wheels or stars) with tractive vehicle right and left sides when it is idling, averaging the obtained values of the numbers of revolutions while moving the traction vehicle with the full weight to the value n and xo _krsr Ost during a traction vehicle to a value n _khsr and slip factor calculating expression for δ = δ (n _{krsr khsr} -n) / n _krsr.