JP3036237B2 - Transmission test equipment - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a test apparatus for testing a transmission or the like comprising a transmission mechanism of an automobile, etc. as a test object, and more particularly to a test apparatus without applying rotation and torque to the test object. Also, the present invention relates to a transmission test apparatus for measuring frequency characteristics between input and output of a specimen and specifying characteristics of the specimen.

[0002]

2. Description of the Related Art FIG. 7 shows a conventional apparatus.

A drive motor 101 corresponding to an engine of a vehicle is provided on the input shaft side of the specimen 1 supported on the specimen support 2.
A torque meter 102 for measuring the input shaft torque is provided;
On the output shaft side, an absorption motor 106 corresponding to a load, a gear box 105 for adjusting the absorption force, a flywheel 104 for simulating the output shaft equivalent inertia, and a torque meter 103 for measuring the output shaft torque are provided. Was. The test is performed by driving with the drive motor 101, applying a load with the absorption motor 106, detecting the torque between the input and output of the sample with the torque meters 102 and 103, or setting and controlling those torque values. Was being tested.

The above prior art is disclosed in, for example,
5, 1988 (Vol. 202), page 18, as described in a power train tester or the like.

[0005]

In a conventional apparatus, continuous rotation and torque are applied to a test piece so that
Although a durability test and a test in which the efficiency of the specimen is calculated from the rotation and torque are possible, it is necessary to continuously rotate the specimen at a high speed (6000 rpm or more in the case of an engine) and apply a torque. The entire testing machine needs to have sufficient rigidity in consideration of safety and vibration resistance, so it will be a heavy equipment and the coupling connection, torque meter, gear box and flywheel must be precise without imbalance. Was. In addition, the mounting of the specimen for each test should be below the balance appropriate for high-speed rotation.
It took a lot of work.

In addition, the rotation and torque generated by the drive motor and the absorption motor affect the test results. No consideration was given to specifying the characteristics and specifications of the mechanical elements of the above.

[0007] In view of the above, it is a first object of the present invention to test a specimen without applying rotation and torque to the specimen and without being affected by disturbance generated by the test apparatus. And a transmission test apparatus.

A second object of the present invention is to provide a transmission device capable of specifying characteristics and specifications of mechanical elements inside a specimen.

A third object of the present invention is to provide a transmission test apparatus capable of uniquely determining the quality of a specimen.

[0010]

A first object of the present invention is to provide a vibrator for applying rotational amplitude vibration to an input shaft of a specimen, a flywheel for simulating an inertia equivalent to the input shaft of the specimen, and first vibration detecting means. The output shaft is provided with a second vibration detecting means and a specimen output shaft equivalent inertia simulation flywheel, and the shaker is used to apply rotational amplitude vibration to the specimen, This is achieved by measuring the state or relationship between the output signals of the two vibration detections.

The second object is to input the output signal of both the first and second vibration detecting means to an FFT analyzer and obtain the frequency response of the vibration between the input and output of the specimen. Achieved.

[0012] The third object is achieved by providing a computer device for comparing the frequency response obtained as described above with a preset reference frequency response, and comparing the two.

[0013]

According to the first aspect of the present invention, the input shaft of the specimen is given rotational amplitude vibration by a vibrator, and the vibration on the input shaft side is detected by the first vibration detecting means, and the vibration on the output shaft side of the specimen is applied. Can be detected by the second vibration detecting means. By measuring the output waveform state of these vibration detecting means or the relationship between the two,
Since it is possible to specify the wear condition and the above-mentioned mechanical specifications, the test is performed without applying rotation and torque to the specimen and without using a device that causes disturbance such as a drive and absorption motor. can do.

According to the second aspect of the present invention, the vibration frequency of the vibrator is swept, the output signals of both the first and second vibration detecting means are input to the FFT analyzer, and the input and output of the specimen are If you can find the frequency response of the vibration,
The characteristics and specifications of the mechanical elements inside the specimen can be known.

According to a third aspect of the present invention, there is provided a computer device for comparing the specimen frequency response obtained in the second aspect with a preset reference frequency response, and determines whether there is a difference between the two frequency responses. This makes it possible to know the quality of the specimen.

The simulation flywheel provided on each of the input and output shafts of the specimen gives the specimen a moment of inertia equivalent to the actual machine.

[0017]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to FIGS.

In FIG. 1, the configuration of the present invention comprises a vibrator 3 on the input shaft side of a specimen 1 on which a specimen support base 2 is supported;
Specimen input shaft equivalent inertia simulation flywheel 6 (hereinafter F
W), vibration detecting means 4, and bearings 8a and 8b supporting the vibration detecting means 1 are connected to the input shaft of the specimen 1 by the transmission shaft 9, and the output shaft of the specimen 1 On the side, there are provided vibration detecting means 5, a specimen output shaft equivalent inertia simulation flywheel 7a, 7b, 7c (hereinafter referred to as FW), and bearings 8c, 8d, 8e, 8f for supporting them. It is connected to the output shaft of the specimen 1 by a propeller shaft 10.

The vibrator 3 applies rotational amplitude vibration (hereinafter simply referred to as vibration) and is configured as shown in FIG. In FIG. 2, a vibrator 3 includes a rotary actuator 11 for generating rotational amplitude vibration and an amplitude detector 12.
Consisting of The rotary actuator 11 is supplied with a hydraulic pressure from a hydraulic pressure source 14 through a servo valve 13, and generates an arbitrary vibration by controlling the servo valve 13. The servo valve 13 is controlled by a servo amplifier 15
, An amplitude detection amplifier 16, an adder 17, and a sine wave sweep command generator 18. The above constitutes an automatic feedback control system, and the rotary actuator 11 vibrates at the amplitude and frequency given by the sine wave sweep command generator 18.

In FIG. 1, FW6 gives a moment of inertia equivalent to that of a prime mover such as an input engine in the actual state of the specimen, and FW7a, 7b and 7c similarly have an inertia equivalent to the vehicle weight on the output side in the actual state. It gives a moment. The FW 6 is replaceable, and the inertia can be simulated arbitrarily. The FWs 7a, 7b, and 7c are three in this embodiment. It is also possible to adopt a structure in which the number of sheets can be arbitrarily used by using a clutch mechanism. With these FWs, it is possible to apply an inertia moment in the actual machine state to the input / output axis of the specimen.

1 and 2, if the amplitude and frequency are given by the sine wave sweep command generator 18, the rotary actuator 11 of the vibrator 3
Generates vibration at the amplitude and frequency, and vibrates the input shaft of the specimen 1 through the FW 6, the vibration detecting means 4, and the transmission shaft 9. As a result, vibration also appears on the output shaft of the specimen 1,
The vibration can be detected by the vibration detecting means 5. Further, by comparing the outputs of the vibration detecting means 4 and the vibration detecting means 5, it is possible to know how the vibration has changed in the specimen 1. Further, the specimen 1 is FW6, FW7a, 7b,
By adding 7c, it is possible to vibrate in the same state as the actual machine state.

By enabling the above-described vibration excitation,
The following tests can be performed.

The specimen 1 is continuously vibrated, and the vibration detecting means 4
By monitoring the vibration waveform of the vibration detecting means 5, a durability test can be performed. That is, by continuously applying vibration, wear and fatigue strain occur in the gear train and the like inside the specimen 1, and eventually damage occurs. The vibration waveform of the detecting means 5 can be determined based on a change from the initial state. If the specimen 1 deteriorates due to wear, proper rotation transmission is lost, and it is clear that the vibration waveform changes. In addition, since the amplitude and frequency of the vibration can be known from a statistical method or a test comparison of a test piece having the same strength as that of a conventional testing machine, it is possible to know how many revolutions and torques correspond to the conventional technique. A test equivalent to a durability test can be performed.

The frequency of vibration is continuously variable (sweep)
By using an FFT analyzer or the like for the vibration waveform of the vibration detecting means 5 or the vibration detecting means 4, an amplitude spectrum as shown in FIG. 4 can be obtained. be able to. Therefore, the problem of vibration when the specimen 1 is mounted on an actual machine can be cleared in advance. That is, specimen 1
Can be performed. Further, if noise is measured by a sound level meter during the sweep vibration, a noise test or the like of the specimen 1 at each vibration frequency can be performed.

Between the input and output of the specimen 1 is a rotating mechanical system composed of a gear train in which various gears are combined. The equation of motion of a rotating mechanical system is determined by the parameters of inertia moment, rigidity (spring constant) and viscous friction. These mechanical specifications have a specific value determined in a single rotary mechanical system, and characteristics, vibration, and behavior such as swing vibration resonance, frequency response, and response magnification are determined by this value. or,
These can be known by measuring the state of the vibration waveform or the state of transmission of the vibration. Furthermore, it is empirically known that wear and fatigue strain appear as changes in the vibration waveform.

If the relation between the equation of motion of one rotating mechanical system and the machine specifications is specifically shown,

[0027]

(Equation 1)

(In order to simplify the explanation, it is represented by a one-mass system shown in FIG. 6).

Here, J: inertia moment K: spring constant x: input displacement y: output displacement f: viscous friction The equation (1) is subjected to Laplace transform, and the transfer function of y / x is represented by G.
(S)

[0030]

(Equation 2)

## EQU1 ## In (Equation 2), S = jW (W
= 2π frequency) is the frequency response. From this, conversely, by obtaining the frequency response, the machine specifications can be specified. The same applies in principle to a multi-mass system.

If the frequency of the vibration is continuously swept and the outputs of the vibration detecting means 4 and the vibration detecting means 5 are simultaneously inputted to the FFT analyzer, the frequency response of the output vibration to the input vibration can be obtained. An example of the frequency response is shown in FIG. The following can be obtained from this frequency response.

The natural frequency fn in the equation (2) is

[0034]

(Equation 3)

And the response magnification Mp is

[0036]

(Equation 4)

However,

[0038]

(Equation 5)

Is as follows.

That is, since fn and Mp can be read from the frequency response, these mechanical specifications of the moment of inertia J, the spring constant k, and the viscous friction f can be obtained from the relations described above.

It is clear that the configuration shown in FIG. 1 is not a single mass system but a plurality of moments of inertia and spring constants, so that a plurality (multiple orders) of natural frequencies exist, but theoretically It is well known that in the case of an n-order vibration system, the mechanical specifications can be obtained when the frequency response is experimentally known by a method generally called modal analysis.

As described above, by obtaining the frequency response, it is possible to carry out the second invention of the present invention in which the characteristics of the internal mechanical elements of the specimen 1 and the mechanical specifications can be specified.

Further, if the viscous friction can be determined, the mechanical loss is the product of the viscous friction and the number of revolutions. Therefore, the mechanical loss of the specimen 1 can be obtained, and the influence of the mechanical loss on the transmission efficiency device side is eliminated. However, the bearings 8a to 8f may be used as hydrostatic sliding bearings in such a manner that the mechanical loss is almost negligible, or the mechanical loss in the device is measured in advance and the value is corrected. Exclusion is possible. One of the methods for measuring the mechanical loss of the apparatus in advance is to vibrate using a transmission shaft made of an integral body in place of the specimen 1, and obtain viscous friction from the frequency response at this time.

An FFT analyzer 19 which receives the output waveforms of the vibration detecting means 4 and 5 shown in FIG. 3 and obtains a frequency response, and a reference frequency response setting device 2
The third invention can be implemented below by using a processing block diagram composed of a computer device 20 for taking in the output of No.1.

As described above, it is stated that the frequency response is determined by the mechanical specifications, and that the specimen has a unique mechanical specification, and that if the frequency response can be determined experimentally, the mechanical specifications can be specified. Was. On the other hand, the design of the test specimen is provided with mechanical specifications for realizing the target characteristics, performance, and vibration mode as design specifications. Using the frequency response of this design and mechanical specifications as the reference frequency response, compare the frequency response of the specimen obtained in the test with the frequency response of the specimen.If they match, it is checked whether the specimen is completed as designed. It can be uniquely determined.

Specifically, in FIG. 3, the reference frequency response set by the reference frequency response
From the frequency response of the specimen 1 from the FT analyzer 19, the computer device 20 calculates the respective transfer functions F (j
w) S and F (jw) X are obtained, and the two are compared. If they match, it can be determined as pass, and if they do not match, it can be determined as reject.

The reference frequency response is obtained from the design machine specifications.
The frequency response obtained by computer simulation or the like may be used, but an actual frequency response statistically obtained may also be used. Further, the comparison can be simplified by comparing only the natural frequency, not the entire transfer function. In this case, the reference frequency setting device 20 only needs to set the reference natural frequency.

Further, a certain degree of variation is allowed in the frequency response, and the allowable range of acceptable products is naturally set. This can be dealt with by setting the width of the determination in comparison of the transfer functions with the purpose of eliminating the influence of measurement errors and the like.

The embodiment of the present invention has been described above. In the prior art shown in FIG.
If a vibration exciter is provided between the torque meter 102 and the
Using the output signal of the torque meter 103 as the vibration detection means and the treatment block diagram of FIG. 3 of the present invention,
Since the torques of the torque meter 2 and the torque meter 3 have a vibration waveform synchronized with the vibration, the third invention can be carried out in the same manner as the embodiment of the present invention.

[0050]

The test can be performed without applying rotation and torque to the specimen, so that the mechanical rigidity with respect to rotation and torque can be reduced, so that the weight of the apparatus can be reduced. In addition, it is not necessary to consider rotation unbalance and the like, and the mounting of the specimen becomes easy. Further, a drive motor and an absorption motor for providing rotation and torque are not required. For example, these motors have a capacity of several hundreds of kW in an automobile transmission test machine and require high-precision control. Therefore, drive control such as a thyristor leonard or a vector inverter has been used. Therefore, the elimination of these components can greatly reduce equipment costs. In addition, the influence of the rotation of these motors and the torque ripple on the test results of the specimen can be eliminated.

Further, the characteristics and specifications of the mechanical elements inside the specimen can be specified. By this, for example, the vibration mode of the specimen can be grasped, so that the problems caused by the vibration resistance and the vibration mode of the drive system as a vehicle when the specimen is mounted on the actual machine can be cleared, and measures can be taken in advance. . Further, since mechanical specifications such as viscous friction can be obtained, the mechanical loss of the specimen can be obtained with high accuracy, which can greatly contribute to experiments and development in improving fuel efficiency of automobiles.

Further, it is possible to uniquely determine whether or not the test specimen is made into a target product on a predetermined basis. Conventionally, there is no means for unambiguously determining based on a certain standard, and the inspection of pass / fail judgment at the time of completion of a product has not been carried out. Yes, can greatly contribute to quality control and quality assurance.

[Brief description of the drawings]

FIG. 1 is a configuration diagram of an apparatus showing one embodiment of the present invention.

FIG. 2 is a control block diagram of the vibration exciter 3 of FIG.

FIG. 3 is a block diagram of a vibration signal processing in one embodiment of the present invention.

FIG. 4 is a diagram showing an example of an amplitude spectrum.

FIG. 5 is a diagram showing an example of a frequency response.

FIG. 6 is a supplementary diagram of the equation of motion of the rotating system.

FIG. 7 is a configuration diagram showing an example of a conventional technique.

[Explanation of symbols]

REFERENCE SIGNS LIST 1 specimen, 2 specimen support, 3 shaker, 4 vibration detection means, 5 vibration detection means, 6 flywheel for input shaft equivalent simulation, 7a, 7b, 7c ... output shaft equivalent simulation Flywheel, 11 ... Rotary actuator, 13
... Servo valve, 14 ... Hydraulic power source, 18 ... Sine wave sweep command generator.

Claims (3)

(57) [Claims] 1. A test apparatus for testing a transmission used in a vehicle such as an automobile as a specimen, wherein a vibration exciter and a specimen input shaft for applying a rotational amplitude vibration to an input shaft of the specimen supported by a specimen support stand. An equivalent inertia simulation flywheel and first vibration detection means; a first vibration detection means on the output shaft of the specimen; and an output shaft equivalent inertia simulation flywheel for the specimen output shaft; A transmission test apparatus characterized in that a rotational amplitude vibration is applied to the specimen, and a state or a relation of output signals of both the first and second vibration detecting means 1 is measured to test the specimen. 2. The method according to claim 1, wherein the output signals of both the first and second vibration detecting means are inputted to an FFT analyzer, and the frequency response of the vibration amplitude between the input and output of the specimen is determined to specify the characteristics of the specimen. The transmission test apparatus according to claim 1, wherein: 3. An output signal of both the first and second vibration detecting means is inputted to an FFT analyzer, and a frequency response of a vibration amplitude between input and output of the specimen is obtained. 2. The transmission test apparatus according to claim 1, further comprising a computer device for comparing the reference frequency response with the reference frequency response, and judging the quality of the specimen based on a result of the comparison.