Method and system for testing specimen of automotive power transmission connected to engine and analyzing engine output characteristic via specimen tested using dynamometer

Abstract: A system and method for testing a specimen such as a vehicular power transmission (automatic transmission) and analyzing an engine output characteristic of an engine connected to the power transmission in which at least a first revolutional speed on an input or output shaft of the power transmission and a first output torque of the power transmission are measured when the engine operating parameters indicate a predetermined value with the power transmission connected to the engine. A second revolutional speed on the input or output shaft of the power transmission and a second output torque of the power transmission are measured when a low inertia driving unit having the same characteristics as the engine is connected and driven with a power transmission under the same operating parameters described above. A first drive torque of the low inertia driving unit is then measured, a third revolutional speed on the input or output shaft of the power transmission and a third output torque of the power transmission are measured when a predetermined time has passed and when the same low inertia driving unit is connected and driven in the same way, and a second drive torque of the low inertia driving unit is measured when difference valued between the second and third revolutional speeds and second and third output torque fall within a predetermined range. The second drive torque being estimated as the output characteristic of the engine connected to the power transmission.

Description: BACKGROUND OF THE INVENTION : (1) Field of the invention: The present invention relates to a method and system for testing a specimen such as an automatic power transmission of a vehicle and analyzing an engine output characteristic (input torque of the power transmission) via the specimen to be tested using a dynamometer (low inertia driving unit). The present invention, more particularly, relates to the method and system in which the engine output characteristic is estimated using, e.g., a low inertia driving unit when testing since the engine output characteristic cannot actually be measured in a system in which the engine and specimen are connected together. (2) Background of the art: It is necessary to grasp engine output characteristics in analyzing and evaluating characteristics of power transmissions to be installed in automotive vehicles and for general troubleshooting for automatic transmissions. Therefore, although testing is carried out with the automotive power transmission as a specimen connected to a vehicular engine, it is difficult in construction to insert a torque meter between the engine and the power transmission. Consequently, an accurate measurement of torque of an input shaft of the power transmission cannot be made. To cope with such a problem described above, the engine output characteristic data supplied from an engine manufacturer has been used when evaluating a performance of the power transmission. However, since it cannot be accurately determined whether the actual output of the engine connected to the power transmission coincides with the derived output characteristic data, high reliability cannot rest on the obtained result. In addition, in transient performance testing of the power transmission, with a specimen power transmission connected to an engine, output control of the engine is carried out to test acceleration/deceleration endurance and gear shift 'feel' of the power transmission. US-A-4,680,959 discloses an on-line-system for emulating the operation of a motor vehicle drive train including a torque converter, a converter clutch and a shiftable ratio automatic transmission. The engine used to drive the vehicle drive train for testing its output characteristics is the actual engine later used in a vehicle. In engine driving methods as described above it is difficult to repeatedly reproduce the same engine operating conditions. Consequently there has been adopted a control system as described in US-A-4,758,978 that accurately computer-simulates the application of a large inertia to a component to be tested during test conditions. Such a system comprises two motors which are driveable coupled to both ends of the component to be tested and apply torques in opposite rotational directions to the components. A computer is supplied with signals indicating the parent rotational speed, acceleration and torque of the component as well as a signal of one of the motors which is used for simulating the virtual inertia of a vehicle. Furthermore there has been adopted a motor-driving method, in which in transient dynamometer used in the motor driving method, a low inertia driving unit having a low inertia equal to or more than that of the engine and the same output characteristic transient is used to realize a large change of speed during gear shift operation. Figure 9 shows a previously proposed transient dynamometer (refer to United States Patent Application Serial No. 427, 031 filed on October 25, 1989). The low inertia driving unit (TR-DY) 1 includes a low inertia DC motor and speed governor. The DC motor performs a torque control or speed control as a current control minor loop of a thyristor reonard method to obtain a low inertia output equal to or more than the engine. An axial output of the drive unit 1 provides a drive source for a specimen of power transmission (AT) 3 via an axial torque meter 2. The axial output of the specimen automatic transmission (AT) 3 serves as a driving force for an energy absorbing dynamometer (DY) 5 and flywheel 5A via a torque meter (TM) 4. The low inertia driving unit 1, specimen automatic transmission 3, and energy absorbing dynamometer 5 are respectively provided with self-contained control units 6, 7, and 8. The TR-DY control unit 6 carries out a torque or speed control of the low inertia driving unit 1 in response to a torque or speed command. In the torque control, a feedback control is carried out by comparing the torque command derived from an engine characteristic generator 9 with the detected torque T₁ of the torque meter 2. On the other hand, for speed control, feedback control is carried out by comparing the speed command with the detected speed N₁ of the speed detector 10. The engine characteristic generator 9 constituted by a microcomputer has a data such that an actual engine output torque T versus speed N characteristic is set or measured for each opening angle ϑ i of an engine throttle valve. Then, the engine characteristic generator 9 derives a torque to be output by the low inertia drive unit 1 from the input opening angle of the thorttle valve and from the speed detected value N₁ so as to provide the torque command output. It is noted that although the opening angle of the throttle valve ϑ₁ can be used in place of an engine intake negative pressure, the opening angle of the throttle valve ϑ i is herein used. In the previously proposed transient dynamometer, the engine characteristic generator 9 carries out data collection through an analysis of the actual engine output characteristic. In order to coincide with a behavior of an actual vehicle during the analysis of the engine output characteristic, a testing arrangement in which the torque meter, energy absorbing dynamometer, and flywheel (both absorbing dynamometer and flywheel providing a pseudo load to the power transmission) are connected to the power transmission (refer to Fig. 1 (B)). However, it is difficult to directly measure the output characteristic (torque output T₁) by means of the action of a torque converter of the automatic transmission. Therefore, a method for measuring the engine output from the torque meter in a shifted state of a four-speed (gear shift ratio of 1 : 1) manual transmission with a manual transmission connected in place of an automatic transmission has been adopted. However a manual transmission which matches the engine is not always prepared. Actually, it is often impossible to accurately measure the engine output characteristic. As described above, although the output characteristic data for the engine itself derived from the engine manufacturer may be used, the data may be different from the actual output characteristic data with the automatic transmission and load connected. SUMMARY OF THE INVENTION: It is an object of the present invention to provide a reliable method and system for testing a specimen of such automotive power transmission and analysing an engine output characteristic, i.e., output torque (input shaft torque) which can achieve analysis basis of tested data on output shaft torque of the power transmission and input/output shaft revolutional speed of the power transmission to obtain a highly reliable result without directly measuring the engine torque output. The above-described object can be achieved by providing a method for testing engine output characteristics of an engine which would normally be connected with a vehicular power transmission (1), which comprises the steps of: a) measuring an engine operating parameter including an engine load, or intake negative pressure b) measuring at least a first revolutional speed on an input or output shaft of said power transmission which would normally be connected with the engine and a first output torque of said power transmission when the measured engine operating parameter of the engine load indicates a predetermined value: c) measuring a second revolution speed on the input or output shaft of the power transmission and second output torque of the power transmission when a low inertia driving unit having the same characteristics as the engine is connected and driven with said power transmission under the same operating parameter measured in said step a): d) measuring a first drive torque of the low inertia driving unit in the state of step c); e) measuring a third revolutional speed on the input or output shaft of said power transmission and a third output torque of said power transmission when a predetermined time has elapsed after the step c) and the same low inertia driving unit is connected and driven in the same way as in the step c); and f) measuring a second drive torque of the low inertia driving unit when a difference in the values of the second and third revolutional speeds and second and third output torques fall within a predetermined range, the second drive torque being estimated as the output characteristic of the engine which would normally be connected to said power transmission. The above-described object can also be achieved by providing a system for testing an output characteristic of an engine according to the above-defined method, which would normally be connected to a vehicular power transmission, using a low inertia driving unit which has the same characteristic as the engine, said system comprising: a) first means for measuring an engine operating parameter including an engine load or intake negative pressure; b) second means for measuring at least a revolutional speed on an input or output shaft of said power transmission which would normally be connected with the engine and an output torque of said power transmission; c) third means for measuring a revolution speed on the input or output shaft of the power transmission and an output torque of the power transmission; d) fourth means for measuring a drive torque of the low inertia driving unit; e) fifth means for measuring a revolutional speed on the input or output shaft of said power transmission and an output torque of said power transmission; and f) sixth means for measuring a drive torque of the low inertia driving unit. BRIEF DESCRIPTION OF THE DRAWINGS : Fig. 1 (A) is a schematic block diagram of a system used for testing a specimen such as a vehicular automatic transmission and analyzing an engine output characteristic in a first preferred embodiment according to the present invention. Fig. 1 (B) is a schematic block diagram of a testing arrangement used in a second preferred embodiment according to the present invention. Fig. 2 is an explanatory view for explaining a learning operation carried out for the system shown in Fig. 1. Fig. 3 is a characteristic graph representing examples of the engine output characteristics. Fig. 4 is a characteristic graph of an engine revolutional speed with respect to time. Fig. 5 is an operational flowchart explaining an operation executed by the system shown in Fig. 1. Fig. 6 is an operational flowchart explaining an analyzing procedure in the second preferred embodiment according to the present invention. Figs. 7 (A) through 7 (D) are waveform charts of accelerations in a case when an actual vehicle is tested in the second preferred embodiment. Figs. 8 (A) through 8 (D) are waveform charts of accelerations in a case when an ASR driving by means of a transient dynamometer in the second preferred embodiment is carried out. Fig. 9 is a schematic block diagram of a previously proposed transient dynamometer explained in the BACKGROUND OF THE INVENTION. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS : Reference will hereinafter be made to the drawings in order to facilitate a better understanding of the present invention. Fig. 1 (A) shows a testing system for a specimen such as a vehicular power transmission to analyze an engine output characteristic in a first preferred embodiment according to the present invention. A low inertia driving unit 3 is connected to an input portion of a specimen of a power transmission (automatic transmission) 1. An energy absorbing dynamometer 5 is connected to an output portion of the power transmission 1 via a torque meter 4. The low inertia driving unit 3 is a driving unit in which a DC motor is used to provide a low inertial force with an axial rigidity taken into a special consideration and to provide inertia equal to an engine. The structure of the low inertia driving unit 3 has been explained in the BACKGROUND OF THE INVENTION. A procedure in which the output characteristic of the engine is derived from a system in which the engine is connected to a specimen power transmission will be described below. First, two types of reference data are prepared, these reference data being data T₂₀(t) representing a change of an output shaft torque of the power transmission 1 with time for each opening angle of the engine throttle valve and data N₁₀(t) representing a change of the input shaft revolutional speed of the power transmission 1 with time for each opening angle of the engine throttle valve. Both reference data are derived from the system in which the engine is connected to the power transmission (refer to Fig. 1 (B)) or derived from a case wherein the engine is connected to the power transmission and installed in a vehicle and is actually driven on a road. Next, with the testing arrangement shown in Fig. 1 (A), a data T₁₀(t)*1 which would output the data T₂₀ and N₁₀ on the basis of a certain throttle valve opening angle ϑ is calculated from a shift gear ratio and/or a predictive slip rate and supplied to the low inertia driving unit 3 as a torque command. Thus, the testing system shown in Fig. 1 (A) is prepared. It is noted that *1 of the symbol T₁₀(t)*1 denotes a first target value of the input shaft torque of the power transmission. Initially derived at the first time of testing is data representing a change of the output shaft torque of the power transmission with time is T₂₁(t), data representing a change of input shaft revolutional speed with time is N₁₁(t). Values of T₂₁(t) and N₁₁(t) at time t k (k denotes an integer) are represented by T₂₁(t k ) and N₁₁(t k ). Fig. 2 shows a characteristic graph representing the reference data and first data. The subsequent procedure will be described with reference to Fig. 2. t₁′ is derived, which outputs N₁₁(t₁′) of the same frequency as N₁₀(t₁) at the time t₁. Next, T₂₁(t₁′) at the subsequent time t₁′ is derived to compare T₂₀(t₁) with T₂₁(t₁′). If the T₁₀(t)*1 command input when deriving the first data coincides with the input shaft torque T₁₀(t) of the specimen transmission, T₂₀(t₁) coincides with T₂₁(t₁′). If they do not coincide with each other, T₂₁(t₁) is different from T₂₁(t₁′). That is to say, a difference between T₂₀(t₁) and T₂₁(t₁′) at the time t₁ provides an index for T₁₀(t₁)*1 to be deviated from T₁₀(t₁). Then, ΔT₂₁(t₁) is defined in the following equation (1): ΔT₂₁(t₁) = T₂₀(t₁) - T₂₁(t₁′) A second equation (2) is used to calculate a second command value T₁₀(t₁)*2 from the value ΔT₂₁(t₁) and the first command value T₂₀(t₁)*1: T₁₀(t₁)*2 = T₁₀(t₁)*1 + aXΔT₂₁(t₁)/i In the equation (2), a denotes an adjustment coefficient for a value of ΔT₂₁(t₁) and gives a value in a range from 0 to 1, preferably 0. 5 to 0. 7. In addition, i denotes a gear ratio. In this way, a deviation ΔT₂₁(t₁) of the output shaft torque of the specimen transmission is converted to deviation of the input shaft torque. Similarly, the second command value T₁₀(t)*2 is derived for times t₂, t₃, --, t m . The second command value T₁₀(t k )*2 is supplied to the low inertia driving unit 3 as a torque command. When the system shown in Fig. 1 is driven, a second data T₂₂(t k ) and N₁₂(t k ) are derived. Suppose that t₁ is representative, t₁′ which outputs N₁₂(t₁′) of the same frequency as N₁₀(t₁) in the same way as in the first data is derived. A difference ΔT₂₂(t₁) between T₂₀(t₁) and T₂₂(t₁′) at a time t₁′ is derived using the following equation (3): ΔT₂₂(t₁) = T₂₀(t₁) - T₂₂(t₁′) A third command value T₁₀(t₁)*3 is calculated from the following equation (4) using ΔT₂₂(t₁) and the second command value T₁₀(t₁)*2: T₁₀(t₁)*3 = T₁₀(t₁)*2 + aXΔT₂₂(t₁)/i In this way, the deriving is repeated to derive data n number of times. When deriving this data, respective ΔT 2n (t₁), ΔT 2n (t₂), ΔT 2n (t₂), ---, ΔT 2n (t m ) give substantially zeros, ,i.e., when in |Δ T 2n (t k ) | ≦ b at any time (b denotes a set value), torque detected values T 1n (t₁), T 1n (t₂), ---, T 1n (t m ) of the torque meter 2 at each time are estimated values of the input shaft torque of the specimen transmission during the driving in operation when using the reference data T₂₀(t) and N₂₀(t). In the above described method, the input shaft torque is estimated on the basis of the input shaft revolutional speed of the specimen transmission and output shaft torque. Driving is carried out with the estimated value as the command value. On the basis of the driving result, the input shaft torque is again estimated. In this way, a learning operation is carried out so as to derive an unknown input shaft torque. In this way, the estimation of the input shaft torque is carried out for each opening angle of the throttle valve. When, with the opening angle ϑ i as the parameter, a relationship between the input shaft torque T₁ and output shaft revolutional speed is derived, a graph shown in Fig. 3 is obtained. Hence, when the low inertia driving unit 3 is driven on the basis of the graph shown in Fig. 3 and the system is driven shown in Fig. 1 (A), testing equal to the actual system of intended use can be carried out, obtaining acutal input shaft torque, to investigate driving characteristics of the specimen transmission. As described above, the same or same type of specimen transmission, from which the reference data is derived, is used as the specimen transmission in the system shown in Fig. 1 (A). Load inertia is derived in the same way as the reference data described above. Reference data may be derived by increasing the revolutional speed or by decreasing the revolutional speed. When the learning operation is carried out, the revolutional direction is the same way as that used to obtain the reference data. In addition, since error easily occurs in a region such as a converter region or gear shift region in which a conversion efficiency is changed due to a torque converter action of the specimen transmission as shown in Fig. 4, the data is excluded with the range specified for such region. Fig. 5 shows an operational flowchart executed until the data shown in Fig. 3 is derived by means of the learning operation. In the flowchart shown in Fig. 5, the reference data N₁₀(t) and T₂₀(t) are first set in a computer. Then, the computer sets a correction coefficient a/i (refer to equations (2) and (4)) to convert the output shaft torque into the input shaft. Then, the predictive input shaft torque T₁₀(t)*1 is derived and input to the computer to carry out a first simulation driving. It is noted that T₁₀(t)*1 is time series data of predictive values at each of times t₁ through t m . Next, the values of the input shaft revolutional speed and output shaft torque at respective times t₁ to t m are sampled and recorded. Thereafter, a data erasure area is specified each time T 2n (t) is derived. Then, the computer determines whether all of |Δ T 2n (t) | are smaller than the set value b. If it is smaller, the torque detected value of the torque meter 2 at each time is the input shaft torque when the reference data is derived. The reference engine characteristic data shown in Fig. 3 is prepared. In addition, if any one of the values of |T 2n (t) | indicate a value equal to b or more, the second torque command value T₁₀(t)*2 is calculated to perform the second simulation, and the same processing is carried out. Although in the above described example the data is derived for each opening angle of the throttle valve, the data may be derived for each parameter value, for example, intake manifold pressure, etc. In addition, specifying a data erasure area may include a method in which the erasure area varies over time for input shaft revolutional speed, output shaft revolutional speed, and output shaft torque, i.e., N₁(t), N₂(t), and T₂(t) are displayed on a screen of a CRT (Cathode Ray Tube) (N denotes an integer) and a cursor is used to specify the data erasure area, a method in which a region of a speed ratio N₂ . i/N₁≦ K (K denotes a constant such as 0. 9) is automatically eliminated, and a method in which a space of time in which an external signal is input is automatically eliminated. Fig. 6 shows an operational flowchart of analyzing procedure in a second preferred embodiment according to the present invention. In a step S₁, with the engine 11 and specimen transmission 12 connected to the energy absorbing dynamometer 14 as the pesudo load and flywheel 15 as shown in Fig. 1 (B), waveforms of the engine revolutional speed N₁, output shaft revolutional speed N₂ of the automatic transmission 12 and output shaft torque T₂ when the opening angle of the throttle valve of the engine 11 is accelerated from ϑ o to a testing opening angle ϑ₁ are measured. The waveform example at this time is observed for the gear ranges of the automatic transmission (e.g. 1st through 3rd) as shown in Figs. 7 (A) through 7 (D). The output shaft torque T₂ also provides a particular behavior accompanied with a torque shock during shift change. In Figs. 7 (A) through 7 (D), T₁ denotes a torque predicted waveform of the engine output shaft. It is noted that the structure shown in Fig. 1 (B) and Fig. 9 is exemplified by United States Patent Application Serial No. 427, 031 filed on October 25, 1989 (which corresponds to European Patent Application No. 89311002.3 filed on October 25, 1989 and published as No. 0366446), the disclosure of which is herein incorporated by reference. The waveform charts N₁₀, N₂₀, and T₂₀ of data N₁, N₂, and T₂ caused by the pseudo load in the step S₁ may be derived from the actual measurement values of the vehicle. Next, in the construction of the dynamometer of Fig. 9, the testing conditions of both energy absorbing dynamometer 5 and flywheel 5A are met with the actual vehicle or pseudo load, the same as those in measuring step of step S₁. The specimen 3 is the same or same type of automatic transmission 12. The TR-DY control unit 6 carries out the speed control for the low inertia driving unit 1 with the waveform data N₁₀ in the step S₁ being the speed command N₁₁. In the speed control in the step S₂, the output torque T₁₁ of the low inertia driving unit 1 with the waveform data N₁₀ in the step S₁ is the speed command N₁₁. In the speed control at the step S₁, the output torque T₁₁ of the low inertia driving unit 1 is measured with respect to the change in the speed N₁₁, output torque T₂₁ of the specimen transmission 3, and revolutional speed N₂₁. The waveform charts measured at this time are shown with N₁₀, N₂₀, T₂₀ and T₁₀, measured in the step S₁ overlapped, in Figs. 8 (A) through 8 (D). The measured waveforms in the step S₃ are measured substantially in an analogous form in which a time axis is shifted by a control response delay of the transient dynamometer as compared with the waveform chart of the pseudo load, in the construction shown in Fig. 1 (B). Next, in a step S₄, the waveform data N₁₀′, N₂₀′, and T₂₀′ which are deviated from the waveform charts N₁₀, N₂₀, and T₂₀, measured in the step S₄ by constant times (normally, 0.1 seconds to 0.5 seconds) are derived so that, in a step S₅, respective deviations are derived between the measured data N₁₁, N₂₁, T₂₁ in the step S₃. Then, an output torque T₁₁ during an interval within an allowance value previously set is extracted. The extracted torque T₁₁ is derived at the throttle valve opening angle ϑ₁ from the engine revolutional speed N₁₁ and throttle opening angle ϑ₁. This is used as engine characteristic generator 9 data in a step S₆. It is noted that the torque data T₁₁ at an interval, in which the data does not fall within the allowed deviations, N₁, N₂, and T₂ is determined by means of a straight line interpolation between the torque data T₁₁ which falls in the allowance deviation. The processings in the steps S₁ through S₆ are caused by the analysis of the output torque t₁₁ at the throttle opening angle ϑ₁. Substantially the same processings are carried out for the other opening angles ϑ o through ϑ n . The engine characteristics are determined for the respective speeds for the opening angles of the throttle valves ϑ o through ϑ n . In the analyzing procedure according to the present invention, the testing conditions and engine revolutional speed (low inertia driving unit speed) are obtained substantially the same as the actual vehicle under operating conditions. These are derived by carrying out the speed control through the dynamometer which meets the testing condition for the data N₁₀, N₂₀, and T₂₀ on the testing condition in which the engine is connected to the automatic transmission in an actual vehicle or under a pseudo load. The same engine characteristics as the behaviour of the actual vehicle are derived by limiting the data N₁₁, N₂₁, and T₂₁ and each deviated value to fall within a certain range within the allowance value. The same engine characteristics as the behaviour of the actual vehicle can be derived by estimating and extracting the torque T₁₁ in the interval as the output torque of the engine. It is noted that, as in the actual analyzing operation, measurement in the step S₁ is integrally measured for the opening angles ϑ o through ϑ n to store the data at each throttle valve opening angle. Then, measurements using the transient dynamometer in the steps S₂ through S₆ and data processing are integrally made for respective throttle valve opening angles. Consequently, operation is simplified. In addition, although the method for analyzing engine output characteristics in a case, when the automatic transmission is tested, is shown in the second preferred embodiment, this method can be applied to analysis of output characteristics of another dynamometer in a case where the engine characteristic generator data in the chassis dynamometer is derived. As described hereinabove, since, in the first preferred embodiment, the learning operation is carried out in the system, in which the low inertia driving unit is used, on the basis of the input shaft revolutional speed or output shaft revolutional speed of the power transmission and output shaft torque of the power transmission in the system, in which the engine is connected to the power transmission, so that the unknown input shaft torque of the power transmission is estimated. The input shaft torque of the power transmission in the system using the engine can accurately be recognized. Then, for example, if the low inertia driving unit is driven with the estimated input shaft torque value as the torque command, testing equal to the system, in which the engine is used, can be executed grasping the input shaft torque of the power transmission. Hence, the characteristic analysis and evaluation of the specimen power transmission can be carried out with high reliability. In addition, troubleshooting of the power transmission can accurately be carried out. Furthermore, since, in the second preferred embodiment, the waveform measurement of the behavior of the power transmission connected to the vehicular engine used in the system using the actual vehicle or under pseudo load are carried out, waveform measurement of the behaviors of the DC motor and power transmission when a dynamometer having the same testing condition is used to match the speed change with that in the case of the engine connection are carried out, and the output torque of the DC motor in an interval in which both measured waveforms become analogous to each other is estimated as the engine output torque. Analysis of engine output characteristics and engine output characteristic data, which accords with the actual behaviour of a power transmission and engine actually mounted in a vehicle, can be executed. It will fully be appreciated by those skilled in the art that the foregoing description is made in terms of the preferred embodiments and various changes and modifications may be made in terms of the preferred embodiments which are to be defined by the appended claims.

Claims: A method for testing engine output characteristics of an engine which would normally be connected with a vehicular power transmission (1), characterized in that said method comprises the steps of: a) measuring an engine operating parameter including an engine load (Θ₁, ---), or intake negative pressure b) measuring at least a first revolutional speed (N₁) on an input or output shaft of said power transmission (1, 12) which would normally be connected with the engine and a first output torque (T₁) of said power transmission when the measured engine operating parameter of the engine load indicates a predetermined value: c) measuring a second revolution speed on the input or output shaft of the power transmission (1, 12) and second output torque of the power transmission (1, 12) when a low inertia driving unit (3) having the same characteristics as the engine is connected and driven with said power transmission (1, 12) under the same operating parameter measured in said step a): d) measuring a first drive torque of the low inertia driving unit (3) in the state of step c); e) measuring a third revolutional speed on the input or output shaft of said power transmission (1, 12) and a third output torque of said power transmission (1, 12) when a predetermined time has elapsed after the step c) and the same low inertia driving unit (3) is connected and driven in the same way as in the step c); and f) measuring a second drive torque of the low inertia driving unit (3) when a difference in the values of the second and third revolutional speeds and second and third output torques fall within a predetermined range, the second drive torque being estimated as the output characteristic of the engine which would normally be connected to said power transmission (3). A method as set forth in claim 1, wherein step b) comprises the step of g) deriving first and second reference data, the first reference data T₂₀(t) being data on a change of the output shaft of the power transmission (1) with time for each engine operating parameter value and the second reference data N₁₀(t) being data on a change of the revolutional speed of the input shaft of the power transmission (1,12) over time for each engine operating parameter value, both first and second reference data being derived with the power transmission (1,12) connected to the vehicular engine. A method as set forth in claim 2, wherein the step e) comprises the steps of: h) calculating a first target value data T₁₀(t)*1 of an output shaft torque of the low inertia driving unit (3) which would provide a torque which would output the first and second reference data from the power transmission (1,12) when the engine operating parameter indicates the predetermined value on the basis of a gear shift ratio of the power transmission (1, 12) and predictive slip rate of a torque converter of the power transmission (1,12) and producing a torque command to the low inertia driving unit (3), the torque command indicating the calculated first target value; and i) deriving a second data T₂₁(t) representing the change in output shaft torque of the power transmission (1,12) over time and a third data N₁₁(t) representing the change in input shaft revolutional speed of the power transmission (1,12) with time when the low inertia driving unit (3) is driven with the torque command, the second data T₂₁(t) at a time t k (k denotes an integer) being respresented by T₂₁(t k ) and the third data N₁₁(t) at a time t k being represented by N₁₁(t k ). A method as set forth in claim 3, wherein the step e) comprises the steps of: j) deriving a time (t′) at which the input shaft revolutional speed N₁₁(t′) has the same value as the second reference value N₁₀(t) and deriving the second data T₂₁(t) at a time (t₂) and deriving the second data T₂₁(t′) at the time (t′); k) determining whether a difference exists between the second reference data T₂₀(t₁) and output torque data T₂₁(t′) at the time (t′); l) deriving a second target value of the output torque using the difference and the first target value T₁₀(t₁)*1 if a difference exists in the step k); and m) providing a second target torque command of T₁₀(t′)*2 and repeating the steps j) through l). A method as set forth in claim 4, wherein the step f) compries the steps of: n) deriving the second data on the output torque of the power transmission (1,12) at times (t₁, t₂, ---, t m ) when the step e) is carried out n number of times (T 2n (t₁), T 2n (t₂), ---, T 2n (t m )); o) determining whether the first difference value (ΔT 2n (t₁), ΔT 2n (t₂), ---, ΔT 2n (t m )) at each time (t₁, t₂, ---, t m ) indicates substantially zero, i.e., | ΔT 2n (t k ) | ≦ b ( b = a value of the range of limit); and p) deriving a value of output torque of the low inertia driving unit (3) at each time, i.e., T 1n (t₁), T 1n (t₂), ---, T 2n (t m ) if it is determined in the step o) that | ΔT 2n (t k ) | ≦ b as an estimated value of the input shaft torque of the power transmission (1, 12) when the first and second reference data T₂₀(t), N₂₀(t) are derived in the step b). A method as set forth in claim 5, wherein the engine operating parameter is an opening angle of an engine throttle valve. A method as set forth in claim 4, wherein in the step k), the difference value is expressed as follows: ΔT₂₁(t₁) = T₂₀(t₁) - T₂₁(t₁′) and in the step l) the second target value is derived as follows: T₁₀(t₁)*2 = T₁₀(t₁)*1 + a x Δ T₂₁(t₁)/i, wherein a denotes an adjustment coefficient to a value of T₂₁(t₁) and i denotes a gear ratio of the power transmission (1,12), and in the same way the second target value for each time except the time t₁ (t₂, t₃, ---, t m ) is derived. A method as set forth in claim 5, wherein a torque measuring sensor is provided on the output shaft of the power transmission (12) connected to a dynamometer (14) and flywheel (15). A method as set forth in claim 1, wherein the step b) comprises the steps of: g) providing an engine corresponding to the power transmission (1, 12) to connect to the power transmission and providing a pseudo load for the power transmission; and h) measuring behaviors of the engine revolutional speed N₁, output shaft revolutional speed N₂ of the power transmission, and output shaft torque T₂ of the power transmission through their waveforms N₁₀, N₂₀, and T₂₀ when the engine is accelerated from an opening angle during engine idling to the predetermined value ϑ₁. A method as set forth in claim 9, wherein the steps c) and d) comprise the steps of: i) providing the low inertia driving unit (3) to connect to the power transmission (1, 12) in place of the engine and providing a torque measuring sensor on the output shaft of the low inertia driving unit (3) and matching the testing condition to the step g); and j) measuring the output torque T₁₁ of the low inertia driving unit (3) with respect to a change in the revolutional speed N₁₁ derived in the step h) with the low inertia driving unit controlled, the data N₁₁ being the speed command to the low inertia driving unit (3), and measuring the output torque T₂₁ of the low inertia driving unit (3) and revolutional speed N₂₁ of the output shaft of the power transmission (1,12). A method as set forth in claim 10, wherein the steps e) comprises the step of: k) deriving waveform data N₁₀′, N₂₀′, and T₂₀′ deviated by the predetermined time from the measured waveform data N₁₀, N₂₀, and T₂₀ measured in the step h). A method as set forth in claim 11, wherein the step f) comprises the steps of: l) deriving each difference value between the measured waveform data, i.e., N₁₁ and N₁₀′, N₂₁ and N₂₀′, and T₂₁ and T₂₀′ ; m) determining whether each difference value falls within the predetermined limit range; and n) extracting the second drive torque T₁₁ when each difference value falls within the predetermined limit range, the extracted second drive torque being the output torque T₁₁ of the engine when the opening angle of the throttle valve indicates the predetermined value ϑ₁. A method as set forth in claim 12, wherein the same steps l) through n) are repeated for other opening angles of the throttle valve ϑ₀ through ϑ n , n denoting an integer. A method as set forth in claim 13, wherein the output torque T₁₁ derived, when each difference value does not fall within the predetermined limit range, is derived by linear interpolation with the output torque derived when each difference value falls within the predetermined limit range. A method as set forth in claim 14, wherein the data of the output torque T₁₁ derived in the step n) is stored in an engine characteristic generator installed together with the low inertia driving unit (3). A system suitable for testing an output characteristic of an engine according to the method defined in claim 1, which would normally be connected to a vehicular power transmission, (1, 12) using a low inertia driving unit (3) which has the same characteristic as the engine, characterized in that said system comprises: a) first means for measuring an engine operating parameter including an engine load (Θ₁, ---) or intake negative pressure; b) second means for measuring at least a revolutional speed (N₁) on an input or output shaft of said power transmission (1, 12) which would normally be connected with the engine and an output torque (T₁) of said power transmission (1, 12); c) third means for measuring a revolution speed on the input or output shaft of the power transmission (1, 12) and an output torque of the power transmission (1, 12); d) fourth means for measuring a drive torque of the low inertia driving unit (3); e) fifth means for measuring a revolutional speed on the input or output shaft of said power transmission (1, 12) and an output torque of said power transmission (1, 12); and f) sixth means for measuring a drive torque of the low inertia driving unit (3).

Inventors: GOTO TAKASHI, MARUKI TOSHIMITSU, MIZUSHINA FUMIO, NAGANUMA YUKIO, SANO KAORU, GOTO, TAKASHI, MARUKI, TOSHIMITSU, MIZUSHINA, FUMIO, NAGANUMA, YUKIO, SANO, KAORU
Applicants: MEIDENSHA ELECTRIC MFG CO LTD, MEIDENSHA KABUSHIKI KAISHA
Application year: 1990
Main classification: G01M13
IPC codes: F16H59, G01M13