JPH09178612A - Method and apparatus for forming simulated load and clutch load tester using apparatus thereof - Google Patents

Abstract

PROBLEM TO BE SOLVED: To impart the same load characteristics as in the actual service situation simply. SOLUTION: A simulated load is formed by a driving device 3, which imparts the driving or braking in the contact and separation process of a clutch 1, on the side of the rotated and driven clutch 1. At this time, the driving torque of the driving device 3 is controlled from the load torque set by simulating the load characteristics including the mechanical impedance of the actual machine beforehand. Thus, in the connecting and separating process of the clutch, the same characteristics as the load characteristics including the mechanical impedance of the actual machine can be simulated.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention is a simulation in which a simulated load is provided for load testing, evaluation, inspection, etc. in the process of clutch engagement / disengagement of a power transmission system in a rotary drive device to which a load is connected via a clutch. The present invention relates to a load forming method and apparatus, and a clutch load test apparatus using the simulated load apparatus.

[0002]

2. Description of the Related Art In a rotary drive apparatus equipped with a clutch in a power transmission system, load tests, evaluations, inspections, etc. of the clutch itself and power transmission system members such as belts, gears and couplings in the process of engaging and disengaging the clutch. When performing this, it is most preferable to do it with the actual machine connected because it is greatly affected by the load fluctuation of the actual machine, which is the load.However, if this is not practical, the simulated load device is used instead of the actual machine. It has been conventionally done by connecting. For example, Japanese Patent Application Laid-Open No. 5-57688 discloses a model in which a load (engine) is simulated by using a low inertia drive device including a motor and a speed increasing mechanism for reducing the rotational inertia of the motor, which is larger than an actual machine. It is shown.

[0003]

However, the device disclosed in the above publication inevitably requires a large-scale device because a speed-increasing mechanism for making the rotational inertia similar to that of the actual machine is essential. In particular, when simulating an actual machine with a large load torque and a small moment of inertia, it is necessary to increase the speed increasing ratio in the speed increasing mechanism using gears and to use a motor with a large motor torque. Therefore, the speed increasing mechanism and the motor become very large. In addition, since the moment of inertia of the gear in the speed increasing mechanism remains at least on the output shaft of the clutch, the moment of inertia on the output shaft side of the clutch cannot be set below the moment of inertia of the gear. It happens that it cannot be completely simulated.

In the case where the clutch is repeatedly released and engaged many times as in the life test, in the above-mentioned device, load fluctuations are applied to the gears other than the clutch to be tested and the bearings receiving the gears, like the clutch. Therefore, the life and reliability of that part must be fully considered. The present invention has been made in view of the above points, and an object thereof is a device having the same load characteristics as the actual use condition, using a compact and simple device, and reducing the number of constituent elements as much as possible. (EN) Provided are a simulated load forming method and an apparatus therefor, and a clutch load test apparatus using this apparatus.

[0005]

In the method of forming a simulated load according to the present invention, however, the simulated load is formed by a drive device that applies driving or braking to the output side of the rotationally driven clutch in the process of engaging and disengaging the clutch. This is characterized in that the drive torque of the drive device is controlled based on the load torque set by simulating the load characteristics including the mechanical impedance of the actual machine in advance.

Further, the simulated load forming device according to the present invention provides a rotationally driven clutch, a contact / separation device for controlling contact / separation of the clutch, and a drive or braking for a simulated load on the output side of the clutch. A drive device, a drive torque control device that determines a drive torque command value based on a load torque that simulates a load characteristic including a preset mechanical impedance of an actual machine, and drives the drive device based on the drive torque command value. And a driving circuit for

An angle detector for detecting the rotation angle of the output side of the clutch is provided, and the drive torque control device sets a preset inertia moment and an output side rotation angle detection value by the angle detection detector. The drive torque command value may be determined based on this, and in this case, the drive torque control device also includes a torque detector that detects the torque on the output side of the clutch, and the drive torque control device sets a preset inertia moment that simulates the actual machine. Alternatively, the drive torque command value may be determined based on the output-side rotation angle detection value obtained by the angle detection detector and the output-side torque detection value obtained by the torque detector. Further, a switching device for switching between a drive torque command value determined by the drive torque control device and a predetermined drive torque command value set in advance based on a clutch engagement / disengagement signal from the engagement / separation device. Is also preferable.

An angle detector for detecting the rotation angle on the output side of the clutch is provided, and the drive torque control device is based on the viscosity that simulates the preset actual machine and the output side rotation angle detection value by the angle detection detector. The drive torque command value may be determined by using a torque detector that also detects the torque on the output side of the clutch in this case.
The drive torque control device determines the drive torque command value based on the viscosity that simulates a preset actual machine, the output side rotation angle detection value by the angle detection detector, and the output side torque detection value by the torque detector. It may be. A switching device for switching between the drive torque command value determined by the drive torque control device and a preset drive torque command value based on the clutch engagement / disengagement signal from the contact / separation device may be provided. preferable.

An angle detector for detecting the rotation angle of the output side of the clutch is provided, and the drive torque control device has a moment of inertia, viscosity, elasticity and external force simulating a preset actual machine and an output side by the angle detection detector. The drive torque command value may be determined based on the rotation angle detection value, and at this time, the drive torque control device is also provided with a torque detector that detects the torque on the output side of the clutch. The drive torque command value is determined based on the inertia moment, viscosity, elasticity and external force simulating the above, the output side rotation angle detection value by the angle detection detector, and the output side torque detection value by the torque detector. Good.
It is preferable to include a switching device that switches between a drive torque command value determined by the drive torque control device and a preset predetermined drive torque command value based on a clutch engagement / disengagement signal from the contact / separation device. .

In the clutch load test apparatus according to the present invention, a driving source for applying a driving force to the input side of one or a plurality of clutches and contact / separation conditions such as the number of contact / separation times and contact / separation time of each clutch are set in advance. Condition setting device, a contact / separation device that causes each clutch to contact and disengage according to the condition set by the condition setting device, and a drive device that applies driving or braking for a simulated load to the output side of each clutch. A drive torque control device that determines a drive torque command value based on a load torque that simulates a load characteristic including a preset mechanical impedance of an actual machine; and a drive that drives the drive device based on the drive torque command value. It is characterized by comprising a circuit and a counter for counting the number of times of engagement and disengagement of the clutch.

An input shaft rotation speed detector for detecting the rotation speed of the input shaft of each clutch, an output shaft rotation speed detector for detecting the rotation speed of the output shaft of each clutch, and an input shaft rotation speed detection by these detectors. A detection device for detecting slippage of each clutch based on the detected value and the output shaft rotation speed detection value, a detection means for detecting the operation sound or operation vibration of the clutch, and a signal measured by this detection means. A frequency analyzer for frequency analysis, and a defect determination device for determining a sound defect or a vibration defect of the clutch from the analysis result by the frequency analyzer, or a temperature detection means for detecting the temperature during operation of the clutch, It may be provided with a failure determination device that determines a clutch temperature failure from the temperature measurement result by the temperature detection means, and is provided with at least one of the above determination devices. Both based on the output result of the determination device, it is also preferable that the signal and the signal of the contact and separation device of the clutch of the drive torque control unit for each clutch is provided with a on-off to the switching device.

[0012]

BEST MODE FOR CARRYING OUT THE INVENTION An example of an embodiment of the present invention will be described. In FIG. 1, reference numeral 1 is a clutch, and a pulley 14 on the input shaft side of the clutch is a drive source formed of an induction motor via a belt 21. It is connected to two pulleys 20. A drive device 3 including a DC motor is connected to the output shaft 11 of the clutch 1 via a coupling 30. Reference numeral 24 in the drawing denotes a base plate on which these members are installed.

FIG. 2 shows an example of the clutch 1, which includes an output shaft 11, a boss 12 fixed to the output shaft 11, a boss 13 splined to the boss 12, and a boss 13. When the coil 15 is energized, it is formed by the input shaft 10 having the disk portion facing one end face and the pulley 14, the coil 15 and the yoke 16.
The boss 13 moves the input shaft 10 by the magnetic circuit shown by the broken line in the figure.
The rotation of the pulley 14 is transmitted to the output shaft 11 via the boss 13 and the boss 12 by being attracted to the disk portion of the. When the current to the coil 15 is cut off, the return spring 18 formed of a leaf spring returns the boss 13 to return the input shaft 10 and the output shaft 11 to each other.
And is separated. In the figure, 19 is a bearing. Since the clutch 1 is thus configured as an electromagnetic clutch, the clutch contact / separation device 9 in FIG. 1 controls the current flowing through the coil 15 in the clutch 1.

The clutch 1 has its output shaft 11
The load is connected to the worm shaft portion 17 that is integrally provided with the drive shaft. Here, the shaft of the drive device (DC motor) 3 is connected to the tip of the output shaft 11 via the coupling 30. ing. This drive device 3
The output shaft 11 of the clutch 1 is operated by a drive circuit (driver) 5 for constant current control that outputs a current proportional to a drive torque command value given from the drive torque control device 4.
Add torque to.

Here, the drive torque control device 4 is
The drive torque command value is output to the drive circuit 5 based on the load torque set by simulating the load characteristics including the mechanical impedance of the actual machine. The load torque that simulates the actual machine is determined based on the method of measuring the torque characteristics of the actual machine in advance or by measuring each parameter (moment of inertia, viscosity, elasticity) and based on the equation of motion based on that value. However, it may be obtained by any method. However, it is necessary to obtain load characteristics including the mechanical impedance of the actual machine.

As shown in FIG. 3, the drive source 2 is operated to rotate the input shaft 10 of the clutch 1 and a current proportional to the drive torque command value determined by the drive torque controller 4 is driven. The load torque generated in the driving device 3 is transmitted to the output shaft 11 of the clutch 1 by flowing the driving torque to the driving device 3 in the circuit 5. By repeatedly connecting and disconnecting the clutch 1 while transmitting the load torque to the output shaft 11 of the clutch 1, the operation of the clutch 1 in the state where the actual load torque is applied is realized.

FIG. 4 shows another example. Drive source 2 and clutch 1
The relationship between the drive device 3 and the drive device 3 is the same as that described above, but here, the angle detector 6 is connected to the drive device 3 via the coupling 31. This angle detector 6 is shown in FIG.
A rotary plate 60 having a slit as shown in FIG. 1, a transmission type photoelectric switch 61 for detecting the slit and a counter 62
The rotation angle θ of the output shaft 11 is detected from the number of slits of the rotary plate 60 and the count number of the counter 62 within a predetermined time.

The drive torque control device 4 includes a differentiating circuit 40 for differentiating the rotation angle θ to obtain an angular velocity v, and a differentiating circuit 41 for further differentiating the angular velocity v to obtain an angular acceleration α.
And a multiplier 42 are provided. Further, the drive torque control device 4 is set with an inertia moment to be simulated by an actual machine. The moment of inertia of the actual machine may be measured by mounting a torque sensor on the actual machine, or may be a value calculated from the shape, the reduction ratio, or the like.

In this case, as shown in FIG.
Clutch 1 by drive source (induction motor) 2
The input shaft 10 of is rotated. The angle detector (encoder) 6 detects the rotation angle θ of the output shaft 11 of the clutch 1. Then, the drive torque control device 4 subtracts the inertia moment m of the output shaft 11 of the clutch 1 including the drive device 3 from the desired inertia moment M (M-m),
The drive torque command value T is determined by multiplication with the angular acceleration α based on the detected rotation angle θ and output to the drive circuit 5, and the drive circuit 5 supplies a current proportional to the drive torque command value T to the drive device 3. In this way, a torque proportional to the current is generated in the drive device 3 which is a DC motor and transmitted to the output shaft 11 of the clutch 1. By repeatedly connecting and disconnecting the clutch 1 in this state, the actual machine is used. A load torque similar to that in the state can be applied to the clutch 1.

FIG. 7 shows another example. Here, the output shaft 11
In addition to the drive unit 3 and the angle detector 6, a torque sensor 7 is provided. The torque sensor 7 is, for example, as shown in FIG. 8, a detection plate 7 whose magnetic characteristics change due to deformation.
0, an excitation coil 71, and a detection coil 72. The detection plate 70 is attached to the shaft 72 connected to the output shaft 11.
Is attached, and the detection coil 72 detects that the magnetic flux in the magnetic circuit by the exciting coil 70 changes due to a change in magnetic resistance due to minute deformation of the detection plate 70 when torque is applied to the shaft 70. By calibrating so that the detection value at 72 is proportional to the torque applied to the shaft 70, the detection value of the detection coil 72 can be used as the torque detection value Ts.

In this case as well, the inertia moment M desired to be simulated in the actual machine is used. By substituting the torque detection value Ts obtained by the torque sensor 7 and the inertia moment M into the equation shown in FIG. The target angular acceleration αr and the target angle θr are obtained. Here, it is assumed that the viscosity coefficient and the elastic coefficient of the output shaft 11 of the clutch 1 are minute, and these are omitted. However, if these terms are not minute, they are also considered based on the equation of motion considering them. The target angle shall be determined.

When the target angle θr is obtained, the drive torque command value T is determined using the formula in FIG. 9 so that the rotation angle θ obtained by the angle detector 6 matches the target angle θr. . The drive circuit 5 supplies a current proportional to the drive torque command value T to the drive device 3 to generate a torque proportional to the current in the drive device 3 which is a DC motor and transmits the torque to the output shaft 11 of the clutch 1. , Clutch 1 in this state
By repeating the connection and disconnection of the above, it is possible to apply the load torque to the clutch 1 which is similar to the usage state of the actual machine. Here, as the method of determining the drive torque command value T, the PID control system for the angle is configured and the angle is controlled, but a method other than the PID control may be used.

The example shown in FIG. 10 is basically the same as that shown in FIG. 4, but the drive torque control circuit 4 includes an adder 43 for adding a torque TF by an external force simulating a preset actual machine. Between the drive torque control circuit 4 and the drive circuit 5, the drive torque command value T output from the drive torque control circuit 4 and the preset drive torque command value (T = 0 and T = T0) and clutch engagement / separation device 9
The difference lies in that a switching device 50 for switching in accordance with a signal from is provided. Then, as shown in FIGS. 11 and 12, when the clutch 1 is disengaged, the switching device 50 outputs a value of 0 preset as the drive torque command value T to the drive circuit 5 to connect the clutch 1. Within a predetermined time t0 (for example, within 10 msec) after that, T0 preset as the drive torque command value T is set.
Value is output to the drive circuit 5, and after the lapse of the above time, the inertia moment M and the rotation angle θ that simulate a preset actual machine are output.
The switching circuit 55 operates so that the drive torque command value T to which the torque TF by the external force that simulates the actual machine preset is added to the value calculated based on the above is sent to the drive circuit 5.

In this case, when the clutch 1 is disengaged, the condition of the drive torque command value T = 0 is obtained in order to satisfy the condition that the output shaft 11 of the clutch 1 is stopped. In order to satisfy the condition that a constant load torque is generated by the external force when the clutch is connected and the output shaft 11 has the same rotation speed as the input shaft 10, the torque TF by the external force is added. In order to satisfy the condition that the moment of inertia of the actual machine is smaller than the moment of inertia of this device with good responsiveness, the condition of the drive torque command value T = T0 is obtained, and the last condition is the drive torque command value. T =
Specifically, the value of T0 is set so that the output shaft 11 rotates in the same direction as the input shaft 10 of the clutch 1.

As described above, when the preset torque value is used, the set value may be set more finely or may be continuously changed. In any case, by using a preset value, it is possible to instantly realize the state of inertia moment to be simulated, particularly the state of inertia moment immediately after the clutch 1 is engaged. FIG.
3 and FIG. 14, an adder 43 for adding the torque TF by the external force and a preset drive torque command value T =
The switching device 50 for applying 0, T = T0 is applied to the example shown in FIGS. 7 and 9. Even in this case, it goes without saying that the above three conditions can be satisfactorily satisfied.

Another example is shown in FIGS. Here, the viscosity coefficient C to be simulated, which is similar to the usage state of the actual machine, is set, and the drive torque command value T is calculated from this viscosity coefficient C and the angular velocity v derived from the rotation angle θ by the angle detector 6. The drive torque control circuit 4 is used. In FIG. 16, c is the output shaft 11 of the clutch 1 including the drive device 3.
Is the viscosity coefficient of. The viscosity coefficients C and c may be measured by mounting a torque sensor on an actual machine, or may be values calculated from the shape and the characteristics of the viscous fluid. Further, the torque TF due to the external force may be measured by mounting a torque sensor on an actual machine, or may be a value calculated from the shape, the reduction ratio, or the like.

Even when the viscosity coefficient C is used in this way, as shown in FIGS. 17 and 18, the target angular acceleration αr, the target angular velocity vr, and the target angle θr are calculated to obtain the actual angle θ as the target angle. Angle control that determines the drive torque command value T so as to match θr can be applied. Further, as shown in FIG. 19 and FIG. 20 or FIG. 21 and FIG. 22, an adder 43 for adding the torque TF by the external force and a preset drive torque command value T = 0, T = T0 are applied. It is also possible to use a switching device 50 for When the drive torque command value T = T0 for the predetermined time t0 after the clutch 1 is connected is not set, the characteristic as shown in FIG. 23 can be used.

By the way, as the mechanical impedance of the actual machine, there are elastic constants in addition to the moment of inertia and the viscosity coefficient, and when all of them have values that cannot be ignored, it is desirable to apply all of them. . 24 and 25 show examples in which a preset desired inertia moment M, a preset desired viscosity coefficient C to be simulated, and a preset preset elastic constant K are used. In FIG. 25, k is an elastic constant of the output shaft 11 of the clutch 1 including the drive device 3.

In this case, as is apparent from the equation in FIG. 24, the rotation angle θ obtained from the angle detector 6 and the elastic constants K and k, the angular velocity v derived from the rotation angle θ and the viscosity coefficient C,
c, the drive torque command value T is determined from the angular acceleration α further derived from the angular velocity v and the elastic moments M and m. 26 and 27, even when the moment of inertia M, the viscosity coefficient C, and the elastic constant K are used.
As shown in, the angle control can be applied to determine the target angle θr and determine the drive torque command value T so that the actual angle θ matches the target angle θr. Further, as shown in FIGS. 28 and 29 or FIGS. 30 and 31, an adder 43 for adding the torque TF by the external force,
It is also possible to use the switching device 50 for applying the preset drive torque command values T = 0 and T = T0.

In constructing a clutch load test apparatus using the above simulated load apparatus, as shown in FIG. 32, the clutch 1 is contacted and disengaged such as the number of times of contact and separation and the contact and separation time, for example, the clutch for 1 second. 1 is connected and then the clutch 1 is disengaged for 1 second is repeatedly performed 100,000 times. A condition setting device 90 for presetting a contact / separation condition is provided, and the condition set by the condition setting device 90 is set. Accordingly, the contacting / separating device 9 may cause the clutch 1 to perform the contacting / separating operation, and a counter 91 for counting the number of times of contacting / separating the clutch 1 may be added. FIG.
Shows the flowchart of this operation. The continuous load test of the clutch 1 can be performed, and the number of connections of the clutch 1 during the load test can be confirmed by the counter 91, and basic characteristics such as the maximum transmission torque of the clutch 1 before and after the load test. It is possible to evaluate the performance of the clutch 1 by checking whether there is any change.

At this time, as shown in FIG. 34, a single drive torque control device 4 and a clutch contact / separation condition setting device 90 may control the test devices for a plurality of clutches 1. The drive torque control device 4 and the clutch engagement / disengagement condition setting device 90 require an arithmetic function and a determination function, and therefore a personal computer or a one-board microcomputer is used. This makes it possible to simultaneously perform load tests on a plurality of clutches 1 at low cost, which is very efficient.

In the example shown in FIG. 35, the input shaft 1 of the clutch 1 is shown.
An input shaft rotational speed detector 25 for detecting the rotational speed of 0 and an output shaft rotational speed detector 26 for detecting the rotational speed of the output shaft 11 of the clutch 1 are provided, and these detectors 25, 26 are provided.
The slip determining device 27 for determining the slip of the clutch 1 based on the detected input shaft rotational speed and the detected output shaft rotational speed is provided. As the rotation speed detectors 25 and 26, it is preferable to use ones including a disc having slits attached to the input shaft 10 and the output shaft 11, and a transmission type photoelectric switch for detecting the slits of each disc. it can. In this case, the output waveforms shown in FIG. 36 of the rotation speed detectors 25 and 26 are passed through the F / V converters 28 and 28 to obtain voltage outputs proportional to the pulse frequency, that is, voltage outputs proportional to the rotation speed, respectively. Then, the slip determination device 27 determines whether the clutch 1 is slipping by comparing the two voltage values.

The input shaft 1 when the clutch 1 is connected and the load torque simulating the actual machine is applied to the output shaft 11.
If the rotational speed W1 of 0 and the rotational speed W2 of the output shaft 11 have a difference of 1% or more, or as shown in FIG. Judgment, the value of the counter 91 at this time (clutch engagement count)
Is stored, the slip limit value (life) of the clutch 1 can be determined. The phenomenon of slippage of the clutch 1 is obtained by continuously measuring the rotational speed difference between the input shaft 10 and the output shaft 11 of the clutch 1 and the number of times of contact and separation of the clutch 1 while operating a predetermined number of times of contact and separation. Can also be used as a load test device for time-based examination.

By the way, the operation noise of the clutch 1 changes due to the slippage abnormality of the clutch 1, and there are various kinds of abnormality of the clutch 1 other than the slippage. FIG.
Reference numeral 8 is for making it possible to check whether or not the operation sound of the clutch 1 is abnormal, and is provided with a microphone 35 directed to the clutch 1, a frequency analyzer 36, and a sound defect determination device 37. The microphone 35 is installed as close as possible to the clutch 1 and as far as possible from other sound sources in order to minimize the influence of other noises. And the clutch 1 detected by the microphone 35
The frequency of the operating sound is analyzed by the frequency analyzer 36 to calculate the amplitude at each frequency, and the calculation result is compared with the predetermined reference value of the defective sound in the defective sound determining device 37 to determine the current operation. It is determined whether or not the operating sound of the clutch 1 being operated is normal. The reference value of the sound defect determined in advance is determined so as to correspond to the sensory test of the inspector while actually inquiring the person of the inspector.

As a method for determining abnormal sound, a defect is determined only for a sound volume near a specific frequency, for example, 100 Hz, and the value is compared with the detected sound volume to determine a sound failure. Alternatively, attention may be paid to an integral multiple frequency such as the number of revolutions, a limit value of the sum of the magnitudes of the frequencies may be set in advance, and a defect may be determined by comparing with a detection result. Alternatively, the sound defect may be determined by weighting each frequency and comparing the loudness of the sound in a plurality of frequency regions.

The number of microphones 35 is not limited to one, but a plurality of microphones may be installed around the clutch 1. Noise may be measured and the noise may be eliminated from the measurement result around the clutch 1. You may perform the signal processing which becomes only the sound. The causes of the abnormal noise during the operation of the clutch 1 are not only the noise at the frictional points due to the slip of the clutch 1, but also the abnormal noise due to the defective bearing used in the clutch 1 and the rattling of the spline portion, and the yoke. 16 and pulley 14
An abnormal sound caused by the inclusion of relics may be considered, but when a defect is judged by the sound, these abnormal causes can also be inspected / evaluated under actual load conditions.

In measuring the operation sound of the clutch 1, when it is very difficult to separate noise due to the operation sound of equipment other than the clutch 1 and the sound of other devices in the room, FIG.
As shown in FIG. 3, an accelerometer 38 is attached to a non-movable portion of the clutch 1, for example, the yoke 16, so that vibration during the operation of the clutch 1 can be detected. The amplitude of the clutch 1 is calculated and compared with a predetermined reference value of vibration failure.
It may be possible to determine whether or not there is any abnormality in the operation vibration of. The reference value of the vibration failure may be determined in the same manner as in the case of the above sound. FIG. 40 shows a flowchart of the operation. Of course, it may be possible to make a defect determination based on both sound and vibration.

The ones shown in FIGS. 41 to 43 are designed so that the temperature during the load test of the clutch 1 can be measured.
A thermometer 45 is attached to the outer surface of the yoke 16 of the clutch 1, and when the detected temperature exceeds a preset limit temperature in the temperature defect determination device 46, the determination of temperature defect is made. A general thermocouple type thermometer may be used as the thermometer 45, and the number of temperature measurement points may be one or plural. As the limit temperature value, for example, the heat resistant temperature of the coating of the conductive wire used for the coil 15 of the clutch 1 and the heat resistant temperature of the resin component are used.

The causes of the abnormal temperature during the operation of the clutch 1 are not only the heat generated by the frictional heat of the sliding portion of the clutch 1 but also the abnormal heat generation of the coil 15 and the pulley 14 and the yoke 1.
Although heat generation due to frictional heat with 6 or the like is conceivable, these abnormalities can be detected and the load test for the clutch 1 can be interrupted. The best place to measure the temperature is near the component related to the above-mentioned limit temperature value, but if you want to detect an abnormal temperature on the outer surface of the yoke 16 which is the place where it is easy to measure as described above, The relationship between the temperature near the part related to the above limit temperature value and the measurement point is grasped, and the limit temperature is set based on this relationship.

In any case, the judging devices 27, 37, 37, 37, 37, 37, 37, 37, 37, 37, 37 for judging the slip failure, the sound failure, the vibration failure, and the temperature failure as described above to interrupt the load test of the clutch 1.
In the case of controlling the test device for a plurality of clutches 1 with the single drive torque control device 4 and the clutch contact / separation condition setting device 90 as shown in FIG. As shown in FIG. 5, a switching device 65 is interposed between the drive torque control device 4 and each drive circuit 5, and a switching device 66 is interposed between the clutch contact / separation condition setting device 90 and each clutch contact / separation device 9. The load test may be terminated for the clutch 1 that is determined to have a defect even if the clutch engagement / separation conditions are not satisfied, and the load test may be continued for the clutch 1 that is not determined to have a defect. As described above, in the switching devices 65 and 66, each drive circuit 5 and the clutch contact / separation device 9 are connected.
It is desirable to be able to disconnect the drive torque control device 4 and the clutch contact / separation condition setting device 90 from each other. Although two clutches 1 have been described, it is needless to say that the same processing can be performed when the number of clutches is three or more.

In any case, when a load test is being performed on a plurality of clutches 1, the load test is promptly stopped for the clutch 1 in which an abnormality has occurred, so that an accident such as a fire caused by the abnormality will occur. It is possible to prevent undesirably, and to stop automatically when an abnormality occurs, so it is possible to carry out unmanned continuous visibility of multiple clutches 1 day and night, and it is possible to carry out a very efficient load test. Becomes Moreover, the clutch 1 in which an abnormality has occurred is immediately stopped at that time, and in order to maintain the defective state without destroying the defective state, it is easy to confirm the possibility of defectiveness later and it is also easy to study.

In the above-mentioned clutch load test apparatus, the simulated load apparatus has the configuration shown in FIG. 1, but it goes without saying that the above simulated load apparatus may be used. Further, although the one using the DC motor as the drive device 3 is shown, the drive device 3 is not limited to this. However, when the moment of inertia of the actual machine is smaller than the moment of inertia of the load device, the one capable of switching the rotation direction can realize the load characteristic having a mechanical impedance closer to that of the actual machine.

[0043]

As described above, in the simulated load forming method according to the present invention, when the simulated load is formed by the drive device that applies driving or braking to the output side of the rotationally driven clutch in the process of engaging and disengaging the clutch. In order to control the drive torque of the drive unit based on the load torque that is set by simulating the load characteristics including the mechanical impedance of the actual machine in advance, the mechanical impedance of the actual machine is also determined in the process of connecting and disconnecting the clutch. It is possible to simulate the load characteristics similar to the load characteristics including, and to perform the same load test as when the actual machine is connected.

Further, the simulated load forming device according to the present invention provides a rotationally driven clutch, a contact / separation device for controlling contact / separation of the clutch, and driving or braking for the simulated load on the output side of the clutch. A drive device, a drive torque control device that determines a drive torque command value based on a load torque that simulates a load characteristic including a preset mechanical impedance of an actual machine, and drives the drive device based on the drive torque command value. It is possible to simulate the load torque in the actual clutch engagement / disengagement process with a compact and simple device without the need for a complicated mechanical structure such as a gear. Also, by eliminating the mechanical structure such as gears, it is not necessary to consider their strength and reliability during long-term use such as life tests. It is.

An angle detector for detecting the rotation angle on the output side of the clutch is provided, and the moment of inertia preset by the drive torque control device is simulated as an actual machine and the detected output side rotation angle by the angle detection detector. When deciding the drive torque command value based on the above, it is possible to simulate the load torque due to the moment of inertia similar to the usage condition of the clutch in the actual machine without using an expensive torque sensor, despite the torque control. In addition to setting the load torque and moment of inertia of the clutch by combining the load torque of gears, motors, brakes, etc., you can easily set the load torque and moment of inertia simply by setting the values. Therefore, it is easy to change the load torque and the moment of inertia of the clutch.

Further, a torque detector for detecting the torque on the output side of the clutch is also provided, and the moment of inertia set in advance by the drive torque control device and simulating an actual machine, the detected output side rotation angle by the angle detection detector, and the above-mentioned When the drive torque command value is determined based on the output side torque detection value by the torque detector, it becomes possible to accurately simulate the load torque generated by the moment of inertia similar to the usage condition of the clutch in the actual machine. .

A switching device is provided for switching between the drive torque command value determined by the drive torque control device and a predetermined drive torque command value set in advance, based on the clutch contact / separation signal from the contact / separation device. At times, it becomes possible to quickly start the control at the moment when the moment of inertia when the clutch is engaged has a large effect on the load torque, and at the same time, the desired moment of inertia can be instantaneously simulated, resulting in good responsiveness. In addition, the output shaft is stopped when the clutch is disengaged, and the load torque can be applied to the clutch output shaft only when the clutch is engaged, so that the load torque can be applied efficiently. A drive torque command is provided based on a viscosity that simulates an actual machine preset by a drive torque control device and an output side rotation angle detection value by the angle detection detector, which is provided with an angle detector that detects a rotation angle on the output side of the clutch. When determining the value, it is possible to simulate the load torque by viscous resistance proportional to the speed without the need for a large-scale device such as a device for sealing the viscous fluid. Despite this, it is possible to simulate the load torque due to the viscous resistance similar to the clutch use conditions in the actual machine without using an expensive torque sensor, and the viscosity is smaller than the actual viscosity coefficient of the simulated load device. Coefficients can also be created virtually. Moreover, the load torque due to the viscous resistance changes depending on the viscosity of the viscous fluid and the shape of the rotating body that rotates therein. Therefore, to set the load torque due to the viscous resistance, the viscous fluid and the viscosity and the rotating body that rotates therein It is necessary to fully consider the combination of the shapes of, but since it is possible to easily set the load torque by viscous resistance just by setting the value, it is possible to easily simulate various states, It is possible to perform simulations for various viscous fluids and rotating bodies without changing the actual viscous fluids in the device.

Also in this case, a torque detector for detecting the torque on the output side of the clutch is also provided, and the viscosity simulating an actual machine preset by the drive torque control device and the output side rotation angle detection by the angle detection detector are detected. If the drive torque command value is determined based on the value and the output torque detection value obtained by the torque detector, the load torque generated by the viscous resistance similar to the operating condition of the clutch in the actual machine should be accurately simulated. You can

Further, a switching device is provided for switching between the drive torque command value determined by the drive torque control device and a predetermined drive torque command value set in advance, based on the clutch contact / separation signal from the contact / separation device. If so, good responsiveness can be obtained and load torque can be efficiently given. An angle detector that detects the rotation angle on the output side of the clutch is provided, and the drive torque control device sets a preset moment of inertia that simulates an actual machine.
If the drive torque command value is determined based on the viscosity / elasticity and external force and the output side rotation angle detection value by the angle detection detector, the inertia moment and the viscosity coefficient similar to those of the clutch used in the actual machine are used. It is possible to simulate the load torque by the elastic constant, and at this time, virtually obtain a simulated inertial moment, viscosity coefficient and elastic constant lower than the actual moment of inertia, viscosity coefficient and elastic constant of the simulated load device. In addition, it is possible to change the load torque of the clutch easily because it is sufficient to set values for these settings.

A torque detector for detecting the torque on the output side of the clutch is also provided, and the moment of inertia, viscosity, elasticity and external force simulating the actual machine preset by the drive torque control device, and the rotation angle on the output side by the angle detection detector. If the drive torque command value is determined based on the detected value and the detected torque value on the output side by the torque detector, the load generated by the moment of inertia, the viscosity coefficient, and the elastic constant similar to the usage conditions of the clutch in the actual machine. The torque can be accurately simulated.

A switching device for switching between the drive torque command value determined by the drive torque control device and a predetermined drive torque command value set in advance on the basis of the clutch contact / separation signal from the contact / separation device is provided. If so, good responsiveness can be obtained and load torque can be efficiently given. The clutch load test apparatus according to the present invention sets a condition in which a driving source that applies a driving force to the input side of one or more clutches and contact / separation conditions such as the number of contact / separation times and contact / separation time of each clutch are preset. Device,
A contact / separation device that causes each clutch to contact and disengage according to the conditions set by the condition setting device, a drive device that applies driving or braking for a simulated load to the output side of each clutch, and a preset actual machine Drive torque control device that determines the drive torque command value based on the load torque that simulates the load characteristics including the mechanical impedance, the drive circuit that drives the drive device based on the drive torque command value, and the clutch connection. Since it consists of a counter that counts the number of disengagements, it is possible to carry out a life test of the on / off operation of the clutch and simultaneously load multiple clutches. It can be carried out.

An input shaft rotation speed detector for detecting the rotation speed of the input shaft of each clutch, an output shaft rotation speed detector for detecting the rotation speed of the output shaft of each clutch, and an input shaft rotation speed detection by these detectors. When equipped with a slip determination device that determines the slip of each clutch based on the detected value and the output shaft rotation speed detection value, the slip occurrence of the clutch can be automatically detected and the rotation can be performed in time series. By looking at the numerical data, it is possible to obtain data for clarifying the phenomenon that the clutch slips.

Detecting means for detecting the operating sound or operating vibration of the clutch, a frequency analyzer for frequency-analyzing the signal measured by the detecting means, and a defective sound or vibration of the clutch is judged from the analysis result by the frequency analyzer. When equipped with a defect determination device, it is possible to automatically determine a defect in the clutch based on the operating noise and operating vibration of the clutch. It is possible to obtain data for clarifying the phenomenon in which the bad vibration occurs.

When the temperature detecting means for detecting the temperature of the clutch during operation and the defect judging device for judging the clutch temperature defect from the temperature measurement result by the temperature detecting means are provided, the abnormality of the clutch is automatically detected by the temperature. The temperature data can be detected in a timely manner, and the data for clarifying the phenomenon of abnormal heat generation of the clutch can be obtained by observing the temperature data in time series.

In addition, at least one of the above-mentioned judgment devices is provided, and based on the output result of the judgment device, the signal of the drive torque control device to each clutch and the signal of the contact / separation device of each clutch. When equipped with a switching device that turns on and off, it is possible to perform load tests on multiple clutches under load torque conditions similar to actual usage conditions, as well as slip, abnormal noise, abnormal vibration, abnormal heat generation, etc. For a clutch that has an abnormality, only the load test for that clutch can be stopped and the load test can be continued for other clutches. While preventing, continuous load test of multiple clutches can be automatically performed,
An efficient load test is possible. Moreover, since the load test is stopped at that point in the clutch where the abnormality occurs,
The state at the time of occurrence of the abnormality is maintained, and therefore, it is easy to confirm the defective portion of the clutch and examine the cause.

[Brief description of the drawings]

FIG. 1 is a block diagram of an example of an embodiment of the present invention.

FIG. 2 is a sectional view of an example of the above clutch.

FIG. 3 is a flowchart of the above operation.

FIG. 4 is a block diagram of another example of the above.

5A and 5B show an angle detector of the above, wherein FIG. 5A is a plan view and FIG. 5B is a side view.

FIG. 6 is a flowchart of the same operation.

FIG. 7 is a block diagram of another example of the above.

FIG. 8 is a schematic sectional view of the above torque sensor.

FIG. 9 is a flowchart of the above operation.

FIG. 10 is a block diagram of another example of the above.

FIG. 11 is a flowchart of the same operation.

FIG. 12 is a time chart of the same operation.

FIG. 13 is a block diagram of still another example of the same.

FIG. 14 is a flowchart of the above operation.

FIG. 15 is a block diagram of another example.

FIG. 16 is a flowchart of the above operation.

FIG. 17 is a block diagram of another example of the above.

FIG. 18 is a flowchart of the same operation as above.

FIG. 19 is a block diagram of another example of the same.

FIG. 20 is a flowchart of the above operation.

FIG. 21 is a block diagram of still another example of the same.

FIG. 22 is a flowchart of the above operation.

FIG. 23 is a time chart of another operation of the above.

FIG. 24 is a block diagram of another example of the above.

FIG. 25 is a flowchart of the above operation.

FIG. 26 is a block diagram of still another example of the above.

FIG. 27 is a flowchart of the above operation.

FIG. 28 is a block diagram of another example.

FIG. 29 is a flowchart of the above operation.

FIG. 30 is a block diagram of another example of the above.

FIG. 31 is a flowchart of the same operation as above.

FIG. 32 is a block diagram of a clutch load test device.

FIG. 33 is a flowchart of the above operation.

FIG. 34 is a block diagram of another example of the above.

FIG. 35 is a block diagram of another example of the same.

FIG. 36 is a time chart of an example of the output of the above rotation speed detector.

FIG. 37 is a flowchart of the above operation.

FIG. 38 is a block diagram of still another example of the same.

FIG. 39 is a partially enlarged block diagram of the above.

FIG. 40 is a flowchart of the above operation.

FIG. 41 is a block diagram of still another example of the same.

FIG. 42 is a block diagram of a partial enlargement of the above.

FIG. 43 is a flowchart of another operation of the above.

FIG. 44 is a block diagram of another example of the above.

FIG. 45 is a flowchart of the above operation.

FIG. 46 is a block diagram of still another example of the above.

FIG. 47 is a flowchart of the above operation.

FIG. 48 is a block diagram of another example of the same.

FIG. 49 is a flowchart of the above operation.

[Explanation of symbols]

 1 Clutch 2 Drive Source 3 Drive Device 4 Drive Torque Control Device 5 Drive Circuit

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[Procedure amendment]

[Submission date] January 23, 1996

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] Claims

[Correction method] Change

[Correction contents]

[Claims]

[Procedure amendment 2]

[Document name to be amended] Statement

[Correction target item name] 0007

[Correction method] Change

[Correction contents]

An angle detector for detecting the rotation angle of the output side of the clutch is provided, and the drive torque control device is based on a preset inertia moment that simulates the actual machine and the output side rotation angle detection value by the angle detector . The drive torque command value may be determined by using a torque detector that detects the torque on the output side of the clutch in this case, and the drive torque control device sets the inertia moment that simulates the preset actual machine. it may be configured to determine a driving torque command value based on the output-side torque value detected by the output-side rotation angle detection value and the torque detector according to the angle detector. Further, a switching device for switching between a drive torque command value determined by the drive torque control device and a predetermined drive torque command value set in advance based on a clutch engagement / disengagement signal from the engagement / separation device. Is also preferable.

[Procedure 3]

[Document name to be amended] Statement

[Correction target item name] 0008

[Correction method] Change

[Correction contents]

An angle detector for detecting the rotation angle of the output side of the clutch is provided, and the drive torque control device is based on the viscosity which simulates the preset actual machine and the output side rotation angle detection value by the angle detector . The drive torque command value may be determined, and in this case as well, the drive torque control device is provided with a torque detector that detects the torque on the output side of the clutch, and the drive torque control device sets the viscosity and the angle that simulate a preset actual machine. The drive torque command value may be determined based on the output side rotation angle detection value of the detector and the output side torque detection value of the torque detector. A switching device for switching between the drive torque command value determined by the drive torque control device and a preset drive torque command value based on the clutch engagement / disengagement signal from the contact / separation device may be provided. preferable.

[Procedure amendment 4]

[Document name to be amended] Statement

[Correction target item name] 0009

[Correction method] Change

[Correction contents]

An angle detector for detecting the rotation angle of the output side of the clutch is provided, and the drive torque control device simulates a preset actual machine by inertia moment, viscosity, elasticity and external force and the output side rotation by the angle detector . The drive torque command value may be determined based on the detected angle value, and at this time, the drive torque control device also includes a torque detector that detects the torque on the output side of the clutch, and the drive torque control device may be a preset actual device. simulated inertial moment viscous-elastic and on the basis of the output-side torque value detected by the output-side rotation angle detection value and the torque detector due to an external force and the angle detector may be configured to determine a driving torque command value . It is preferable to include a switching device that switches between a drive torque command value determined by the drive torque control device and a preset predetermined drive torque command value based on a clutch engagement / disengagement signal from the contact / separation device. .

[Procedure Amendment 5]

[Document name to be amended] Statement

[Correction target item name] 0013

[Correction method] Change

[Correction contents]

FIG. 2 shows an example of the clutch 1, which includes an output shaft 11, a boss 12 fixed to the output shaft 11, a boss 13 splined to the boss 12, and a boss 13. When the coil 15 is energized, it is formed by the input shaft 10 having the disk portion facing one end face and the pulley 14, the coil 15 and the yoke 16 .
The boss 13 is attracted to the disc portion of the input shaft 10, and the pulley 14
Is transmitted to the output shaft 11 via the boss 13 and the boss 12. When the current to the coil 15 is cut off, the return shaft 18 formed of a leaf spring returns the boss 13 to disconnect the input shaft 10 and the output shaft 11. In the figure, 19 is a bearing. Since the clutch 1 is thus configured as an electromagnetic clutch, the clutch contact / separation device 9 in FIG. 1 controls the current flowing through the coil 15 in the clutch 1.

[Procedure correction 6]

[Document name to be amended] Statement

[Correction target item name] 0035

[Correction method] Change

[Correction contents]

As a method for determining abnormal sound, a defect is determined only for a sound volume near a specific frequency, for example, 100 Hz, and the value is compared with the detected sound volume to determine a sound failure. may be so, attention to an integral multiple of the frequency of such rotational speed may be set to limit the sum of the magnitudes of the frequency in advance, it is judged bad as compared to the detection result Alternatively, the sound defect may be determined by weighting each frequency and comparing the loudness of the sound in a plurality of frequency regions.

[Procedure amendment 7]

[Document name to be amended] Statement

[Correction target item name] 0041

[Correction method] Change

[Correction contents]

In any case, when a load test is being performed on a plurality of clutches 1, the load test is promptly stopped for the clutch 1 in which an abnormality has occurred, so that an accident such as a fire caused by the abnormality will occur. In addition, it is possible to prevent undesirably, and to stop automatically if an abnormality occurs, so it is possible to carry out unmanned continuous load tests of multiple clutches 1 at night, and to carry out very efficient load tests. Becomes Moreover, the clutch 1 in which an abnormality has occurred is stopped immediately at that point, so that the defective state can be maintained later without breaking the defective state.
It is easy to confirm the location and to study it.

[Procedure amendment 8]

[Document name to be amended] Statement

[Name of item to be corrected] 0045

[Correction method] Change

[Correction contents]

An angle detector for detecting the rotation angle on the output side of the clutch is provided, and based on the moment of inertia set by the drive torque control device and simulating an actual machine, and the output side rotation angle detection value by the angle detector . When determining the drive torque command value by using the torque control, it is possible to simulate the load torque due to the moment of inertia similar to the condition of use of the clutch in the actual machine without using an expensive torque sensor, despite the torque control. In addition to setting the load torque and moment of inertia of the clutch by combining the load torque of gears, motors, brakes, etc., it is possible to easily set the load torque and moment of inertia simply by setting the values. Therefore, it becomes easy to change the load torque and the moment of inertia of the clutch.

[Procedure amendment 9]

[Document name to be amended] Statement

[Correction target item name] 0046

[Correction method] Change

[Correction contents]

[0046] The torque detector for detecting torque on the output side of the clutch is also provided, the output-side rotation angle detection value and the torque caused by the inertia moment of the driving torque control device simulating the actual machine to be set in advance and the angle detector When the drive torque command value is determined based on the output torque detection value by the detector, it is possible to accurately simulate the load torque generated by the moment of inertia similar to the usage condition of the clutch in the actual machine.

[Procedure amendment 10]

[Document name to be amended] Statement

[Correction target item name] 0047

[Correction method] Change

[Correction contents]

A switching device is provided for switching between the drive torque command value determined by the drive torque control device and a predetermined drive torque command value set in advance, based on the clutch contact / separation signal from the contact / separation device. At times, it becomes possible to quickly start the control at the moment when the moment of inertia when the clutch is engaged has a large effect on the load torque, and at the same time, the desired moment of inertia can be instantaneously simulated, resulting in good responsiveness. In addition, the output shaft is stopped when the clutch is disengaged, and the load torque can be applied to the clutch output shaft only when the clutch is engaged, so that the load torque can be applied efficiently. Comprises an angle detector for detecting the rotation angle of the output side of the clutch, the driving torque control device in advance the actual machine setting simulates the viscosity and the angle detector by the output-side rotation angle detection value and the drive torque command value based on When determining the load torque, it is possible to simulate the load torque due to the viscous resistance proportional to the speed without the need for a large-scale device such as a device for sealing the viscous fluid, and it is the torque control. Nevertheless, without using an expensive torque sensor, it is possible to simulate the load torque due to the viscous resistance similar to the clutch use conditions in the actual machine, and the viscosity coefficient smaller than the actual viscosity coefficient of the simulated load device. Can be created virtually. Moreover, the load torque due to the viscous resistance changes depending on the viscosity of the viscous fluid and the shape of the rotating body that rotates therein. Therefore, to set the load torque due to the viscous resistance, the viscous fluid and the viscosity and the rotating body that rotates therein It is necessary to fully consider the combination of shapes, but since it is possible to set the load torque by viscous resistance simply by setting the value, it is possible to easily simulate various states. It is possible to perform simulations on various viscous fluids and rotating bodies without changing the viscous fluids in the device.

[Procedure amendment 11]

[Document name to be amended] Statement

[Correction target item name] 0048

[Correction method] Change

[Correction contents]

Also in this case, a torque detector for detecting the torque on the output side of the clutch is also provided, and the viscosity that simulates the actual machine preset by the drive torque control device and the output side rotation angle detection value by the angle detector are set. If the drive torque command value is determined based on the output torque detection value by the torque detector and the torque detector, it is possible to accurately simulate the load torque generated by the viscous resistance similar to the usage condition of the clutch in the actual machine. it can.

[Procedure amendment 12]

[Document name to be amended] Statement

[Correction target item name] 0049

[Correction method] Change

[Correction contents]

Further, a switching device is provided for switching between the drive torque command value determined by the drive torque control device and a predetermined drive torque command value set in advance, based on the clutch contact / separation signal from the contact / separation device. If so, good responsiveness can be obtained and load torque can be efficiently given. An angle detector that detects the rotation angle on the output side of the clutch is provided, and the drive torque control device sets a preset moment of inertia that simulates an actual machine.
If the drive torque command value is determined based on the viscosity / elasticity and external force and the output side rotation angle detected value by the angle detector , the moment of inertia, viscosity coefficient and elasticity similar to those of the clutch used in the actual machine are used. It is possible to simulate the load torque by a constant, and at this time, it is possible to virtually obtain a simulation of the inertia moment, viscosity coefficient and elastic constant lower than the actual moment of inertia, viscosity coefficient and elastic constant of the simulated load device. In addition to these, it is only necessary to set values for these settings, and it is easy to change the load torque of the clutch.

[Procedure amendment 13]

[Document name to be amended] Statement

[Correction target item name] 0050

[Correction method] Change

[Correction contents]

A torque detector for detecting the torque on the output side of the clutch is also provided, and the moment of inertia, viscosity, elasticity and external force simulating the actual machine preset by the drive torque control device and the output side rotation angle detection by the angle detector are detected. If the drive torque command value is to be determined based on the value and the output torque detected value by the torque detector, the load torque generated by the moment of inertia, viscosity coefficient, and elastic constant similar to the usage conditions of the clutch in the actual machine. Can be accurately simulated.

Claims (16)

[Claims] 1. When forming a simulated load on the output side of a rotationally driven clutch by a driving device that drives or brakes in the clutch engagement / disengagement process, the load characteristics including the mechanical impedance of the actual machine are simulated and set in advance. A method of forming a simulated load, comprising controlling the drive torque of the drive device based on the applied load torque. 2. A rotationally driven clutch, a contact / separation device for controlling contact / separation of the clutch, a drive device for applying driving or braking for a simulated load to the output side of the clutch, and a preset actual machine. A drive torque control device that determines a drive torque command value based on a load torque that simulates load characteristics including mechanical impedance, and a drive circuit that drives the drive device based on the drive torque command value. Simulated load device. 3. An angle detector for detecting a rotation angle on the output side of the clutch is provided, and the drive torque control device presets an inertia moment that simulates an actual machine and an output side rotation angle detection value by the angle detection detector. The simulated load device according to claim 2, wherein the drive torque command value is determined on the basis of 4. A drive torque control device is provided with an angle detector for detecting a rotation angle on the output side of the clutch and a torque detector for detecting a torque on the output side of the clutch. 4. The drive torque command value is determined based on the moment of inertia, the output side rotation angle detection value by the angle detection detector, and the output side torque detection value by the torque detector. Simulated load device. 5. A switching device for switching between a drive torque command value determined by the drive torque control device and a predetermined drive torque command value set in advance based on a clutch contact / separation signal from the contact / separation device. The simulated load device according to claim 3, wherein the simulated load device is provided. 6. An angle detector for detecting the rotation angle of the output side of the clutch is provided, and the drive torque control device sets a viscosity that simulates a preset actual machine and an output side rotation angle detection value by the angle detection detector. The simulated load device according to claim 2, wherein the drive torque command value is determined based on the above. 7. The drive torque control device comprises an angle detector for detecting a rotation angle on the output side of the clutch and a torque detector for detecting a torque on the output side of the clutch, and the drive torque control device simulates a preset actual machine. 7. The simulation according to claim 6, wherein the drive torque command value is determined based on the viscosity, the output side rotation angle detection value by the angle detection detector, and the output side torque detection value by the torque detector. Load device. 8. A switching device for switching between a drive torque command value determined by a drive torque control device and a predetermined drive torque command value set in advance based on a clutch contact / separation signal from the contact / separation device. The simulated load device according to claim 6 or 7, characterized in that: 9. An angle detector for detecting the rotation angle on the output side of the clutch is provided, and the drive torque control device uses the angle of inertia detector, the moment of inertia, the viscosity, and the elasticity and the external force simulating a preset actual machine. The simulated load device according to claim 2, wherein the drive torque command value is determined based on the output side rotation angle detection value. 10. An angle detector for detecting a rotation angle on the output side of the clutch and a torque detector for detecting a torque on the output side of the clutch are provided, and the drive torque control device imitates a preset actual machine. The drive torque command value is determined based on the moment of inertia, viscosity, elasticity, and external force, the output side rotation angle detection value of the angle detection detector, and the output side torque detection value of the torque detector. The simulated load device according to claim 9. 11. A switching device for switching between a drive torque command value determined by a drive torque control device and a predetermined drive torque command value set in advance based on a clutch contact / separation signal from the contact / separation device. The simulated load device according to claim 9 or 10, wherein 12. A drive source for applying a driving force to the input side of one or a plurality of clutches, and a condition setting device for presetting contact / separation conditions such as the number of times of contact / separation and contact / separation time of each clutch.
A contact / separation device that causes each clutch to contact and disengage according to the conditions set by the condition setting device, a drive device that applies driving or braking for a simulated load to the output side of each clutch, and a preset actual machine Drive torque control device that determines the drive torque command value based on the load torque that simulates the load characteristics including the mechanical impedance, the drive circuit that drives the drive device based on the drive torque command value, and the clutch connection. A clutch load test device comprising a counter for counting the number of disengagements. 13. An input shaft rotation speed detector for detecting the rotation speed of the input shaft of each clutch, an output shaft rotation speed detector for detecting the rotation speed of the output shaft of each clutch, and an input shaft rotation by these detectors. 13. The clutch load testing device according to claim 12, further comprising: a slip determination device that determines slip of each clutch based on the detected number value and the output shaft rotational speed detected value. 14. A detection means for detecting the operation sound or the operation vibration of the clutch, a frequency analyzer for frequency-analyzing the signal measured by the detection means, and a sound defect or vibration failure of the clutch based on the analysis result by the frequency analyzer. 13. A defect judging device for judging, provided.
The described clutch load test device. 15. A temperature detecting means for detecting a temperature when the clutch is operating, and a defect judging device for judging a defective temperature of the clutch based on a temperature measurement result by the temperature detecting means. 12. The clutch load test device described in 12. 16. A drive torque control device signal to each clutch, comprising at least one of the determination devices according to claim 13, 14 or 15, and based on an output result of the determination device. 16. The clutch load test device according to claim 13 or 14 or 15, further comprising a switching device that turns on and off a signal from the contacting / separating device of each clutch.