JP2001208652A - Dynamometer apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a dynamometer apparatus capable of evaluating the control system of an antilock brake for aircraft and high-speed vehicles in high speed ranges in excess of 500 km/hr, and conducting a landing simulation test for control of aircraft. SOLUTION: A detecting and calculating means for the coefficient of friction between a drum and a tire is prepared based on the idea of calculating the coefficient of friction between the drum and tire from the peripheral velocity of the drum, the pressure load of the tire and a predetermined calculating means. To simulate the required coefficient of friction, the peripheral velocity of the drum and the pressure load of the tire can be controlled to the required values, and the coefficient of friction and lift can be measured through the measurement of the peripheral velocity of the drum and the pressure load of the tire.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a dynamometer device capable of accurately simulating the control system of a brake or an anti-lock brake of an aircraft, a high-speed vehicle, etc., and accurately simulating landing conditions of an aircraft leg. The part can be automatically loaded to enable simulation of the friction coefficient between the actual machine tire and the ground according to the peripheral speed of the rotating drum, and also to enable simulation by combining lift and magnetic levitation force.
The present invention relates to a dynamometer device capable of accurately simulating the actual machine state in a high speed range of m / hr or more and performing highly accurate evaluation of the system.

[0002]

2. Description of the Related Art The performance evaluation of anti-lock brakes for aircraft, high-speed vehicles, etc. is considered to be no longer sufficient by simulation evaluation alone because of the speeding up.
In other words, for tires simulated landing on a rotating drum loaded with the inertial mass of the actual machine, whether or not the brakes are optimally controlled is to be tested by reproducing the load condition of the actual machine. I have.

Conventionally, using a high-speed rotating drum as described above,
The tire is brought into contact with it to give the peripheral speed of the drum, but in order to simulate the coefficient of friction, an adhesive agent must be applied to the drum, and it cannot be said that it accurately reproduces the situation of the actual machine Was something.

[0004] In addition, a shimmy test apparatus has been proposed for reproducing a swinging vibration of a wheel called a shimmy in a front-wheel landing system of an aircraft and for checking shimmy occurrence conditions. This uses a vertically movable rigid body that realizes torsional rigidity equivalent to the front fuselage of the actual machine via a torsional rigidity adjusting member, and abuts the tire on the front leg of the aircraft attached to the rotating drum that is driven to rotate. And simulated landing, giving disturbance to the pedestal from the disturbance actuator to generate shimmy,
Measure the vibration of each leg in the axial direction.

Further, in the conventional shimmy test apparatus, in order to solve the problem that the load fluctuation acting on the nose gear due to the brake operation during taxiing cannot be reproduced and the occurrence of shimmy cannot be faithfully simulated, the front body rigidity of the actual machine is reduced. A shimmy testing apparatus has been proposed (Patent No. 2886158) that includes a simulated torsion axis and an arm extending in a direction away from the torsion axis, and that simulates a front body moment of inertia of an actual machine by an arm and a ballast attached to the torsion axis. ing.

[0006]

In the shimmy test apparatus described above, the front leg is mounted on a rigid body that can move up and down.
It can be assumed that the performance of antilock brakes will be evaluated by simulating the reduction or fluctuation of the tire pressing force due to the lift during landing on an aircraft.However, the accurate reproduction of the friction coefficient between the tire and the rotating drum is based on the aforementioned high-speed rotation. This is not possible as in the case of the drum device.

[0007] The present invention is applicable to 500 km / hr of aircraft, high-speed vehicles, etc.
The purpose of this study is to evaluate the control system of anti-lock brakes in the high-speed range and to provide a dynamometer device that can simulate landing landing of aircraft legs, especially the friction between the actual machine tires and the ground according to the peripheral speed of the rotating drum. It is an object of the present invention to provide a dynamometer device capable of simulating a coefficient, a lift, and the like, and accurately simulating an actual machine state to evaluate a control system with high accuracy.

[0008]

The present inventors have conducted various studies on the configuration and control method of a dynamometer device having a configuration capable of simulating the friction coefficient of an actual machine. Controlling the drum peripheral speed and the tire pressing load to required values in order to simulate the required coefficient of friction using automatic load means that makes the load variable, in other words, the drum peripheral speed and the tire pressing load It was noted that real-time measurement made it possible to actually measure the maximum coefficient of friction between the drum and each tire.

[0009] Therefore, the inventors of the present invention calculate the friction coefficient between the drum and the tire from the drum peripheral speed, the tire pressing load, and the predetermined calculation means, and detect the friction coefficient between the drum and the tire.・ Calculation means are provided, whereby the drum peripheral speed and the tire pressing load can be controlled to required values in order to simulate the required friction coefficient, and the friction coefficient and the friction coefficient are measured by measuring the drum peripheral speed and the tire pressing load. It was found that lift could be measured.

[0010] Further, the inventors have found that the above-mentioned method makes it possible to calculate the maximum friction coefficient between the drum surface and the tire at the time of braking and skidding and to calculate the maximum friction coefficient approximate curve with the drum peripheral speed. I learned.

That is, the present invention provides a rotary drum portion having a drive source, a flywheel detachable coaxially with the drum, a tire holding portion for variably contacting a tire with the drum with a pressing force and a direction thereof, Device control means for controlling at least one of a drum peripheral speed and a tire pressing load in order to simulate a required friction coefficient and a lift; or further, a means for detecting and calculating a friction coefficient between the drum and the tire. It is a dynamometer device characterized by the following.

Still further, according to the present invention, in the dynamometer apparatus having the above-described structure, the pressing force of the tire is corrected in accordance with the peripheral speed of the drum by performing lift correction and correcting the frictional force on the drum surface to match the actual machine frictional force. Is a dynamometer device having an automatic load means for making the variable.

[0013]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A dynamometer device according to the present invention realizes high load and high speed rotation by using a dynamic pressure bearing against a thrust and / or a radial load by hydraulic pressure for a bearing of a large diameter rotating drum. At a peripheral speed of 550k
In addition to realizing ultra-high speeds of m / hr or more, peripheral speeds are calibrated in advance when measuring the mechanical loss of the bearings, etc. during rotational inertia measurement, corrected when calculating the ideal rolling distance, and simulating the load conditions of the actual machine. Automatic load means for making a lift correction to the pressing load of the tire or the like and a correction of the frictional force on the drum surface to the actual frictional force in accordance with the actual load to make the pressing load variable.

As a result, the present invention provides an evaluation of a control system for an anti-lock brake in a high-speed region exceeding 550 km / hr, a simulation test for landing on an aircraft leg, and in particular, a distance between an actual tire and the ground according to the peripheral speed of a rotating drum. It is possible to accurately simulate the actual machine condition such as the friction coefficient and lift of the control system and to evaluate the control system with high accuracy.

[0015] The dynamometer apparatus according to the present invention provides a free run (free run), that is, a rotary drum portion and a tire that can supply the mechanical inertia of an actual machine scheduled when a drive motor is turned off after a required rotation by a rotary drum and a flywheel. A device system consisting of a tire holding unit for variably contacting the pressing force and the direction with the drum, and controlling one or more of a drum peripheral speed and a tire pressing load to simulate a required friction coefficient and lift. And a control system of automatic load means for correcting and making the pressing load variable by detecting and calculating the coefficient of friction between the drum and the tire. The rotary drum and the flywheel of the device system may be of a single structure, or may be of a coaxially detachable type in order to make the size, load load and the like variable.

A configuration example of the dynamometer device will be described with reference to the front view and the top view shown in FIGS. Central rotating drum
1 is rotatably supported at both ends of a rotating shaft 2 by bearings 3 mounted on a base 4. The rotary drum 1 itself is a two-part type divided at the center in the width direction, and has a connecting mechanism (not shown) in each drum so that it can be engaged and disengaged from the rotary shaft 2 when necessary.

One of the rotating shafts 2 is connected to a motor 5 serving as a driving source via a gear box 6. Further, flywheels 10 and 11 can be connected to the other of the rotating shaft 2.
Here, the two flywheels 10 and 11 each have a built-in coupling mechanism, and can be disengaged and disengaged when necessary with a rotating shaft 14 having both ends supported by bearings 13 and 13 mounted on a base 12. Has become.

Further, a sub-weight is separately detachable from each of the flywheels 10, 11, so that the weight of each can be arbitrarily increased or decreased. In short, in the rotating system, the rotating body having various inertial masses can be realized by the two-split rotary drum 1 and the flywheels 10 and 11 having different weights.

It is necessary that the bearings 3 and 13 have an ability to cope with a load that fluctuates in a required range, and any known bearing mechanism can be adopted. Here, an oil lifter / radial bearing or a dynamic thrust bearing is employed as a dynamic pressure bearing configured to resist thrust and / or radial load by hydraulic pressure.

The tire holding unit 20 mounts an arm 22 pivotally supported so that the tire 21 rotates when the tread of the tire 21 is brought into contact with the outer peripheral surface of the rotating drum 1, on a horizontally movable slider frame 23, An actuator 24 that enables the frame 23 to reciprocate in the horizontal direction is configured so that the contact (pressing) load of the tire 21 on the rotating drum 1 can be variously changed. The tire 21 has a brake system inside or outside the wheel.

Here, the slider frame 23 is a horizontal rail.
A hydraulic actuator 24 having legs for gripping the rod 25 and capable of moving the rod in the horizontal direction allows the frame 23 to reciprocate in the horizontal direction. Pressing force can be set for the rotating drum 1 of
For example, an actual load can be detected by a load cell.

The tire holding unit 20 can measure the number of rotations of the tire wheel, and can measure a load state of a load in three axial directions including a tangential direction of the drum surface, or can measure a load in the same three axial directions. It is configured in. Specifically, the camber angle set by the leg of the actual machine is reproduced and can be adjusted arbitrarily.

[0023] The control means includes a device control means for controlling at least one of a drum peripheral speed and a tire pressing load in order to simulate a required friction coefficient and a lift, and a detection and detection of a friction coefficient between the drum and the tire. An automatic load unit is used in which the calculation unit and the above unit are combined to perform lift correction on the pressing load of the tire and correction of the frictional force on the drum surface to match the frictional force of the actual machine to make the pressing load variable.

The apparatus control means can change the drum peripheral speed and the tire pressing load by controlling the electric motor 5 and controlling the actuator 24 in the above-described configuration of the rotating drum section and the tire holding section, respectively. It is possible to correct the control system based on actual measurement by a required sensor such as a drum tachometer or a load cell, and to accurately control the drum peripheral speed and the tire pressing load. When performing real-time correction, which will be described later, it is necessary to appropriately program the setting, actual measurement, correction setting step speed, correction convergence degree, and the like.

In the present invention, the means for detecting and calculating the coefficient of friction between the drum and the tire calculates the coefficient of friction between the drum and the tire by predetermined calculating means based on the peripheral speed of the drum and the pressing load of the tire. It is. First, the maximum friction coefficient between the rotating drum and each tire is actually measured using a dynamometer device, and from this, characteristic data of the drum peripheral speed and the tire maximum friction coefficient are obtained.

Further, in the control system, the friction coefficient detection / calculation means and the device control means complement each other with predetermined correction means to realize the desired detection / calculation or control. A servo system that corrects the tire pressing load such that the rear load in the tangential direction of the drum becomes equal to that of the actual machine based on the ratio of the maximum coefficient of friction between the actual machine and the equipment can be used as the compensating means.

More specifically, the minimum value of the rotational speed of the rotary drum and the maximum value of the brake torque are searched to calculate the maximum friction coefficient between the surface of the rotary drum and the tire at the time of brake skid, and the minimum value of the wheel rotational speed is obtained. Or, in the time axis of the maximum value of the brake torque, brake torque: T _pi , pressing load: _Epi / tire displacement: Def _pi , wheel rotation angular acceleration: α
_pi, drum peripheral speed: V, I: tire / wheel / brake rotor inertia moment, r _0: on the basis of the data of the tire-free radius, to calculate the μ _max.

[0028] Now, a drum peripheral speed to maximum coefficient of friction (between the tires and drum) approximation of curve type, i.e., a linear equation by the least squares method to obtain the quadratic equation and logarithmic Logμ _max = BLogV + LogA, also, Find the coefficient of the approximate expression.

An example of a method for calculating an approximate curve of the maximum friction coefficient with respect to the drum peripheral speed is as follows. Case 1: Maximum friction coefficient = constant regardless of drum peripheral speed Case 2: Maximum friction coefficient is a linear function of drum peripheral speed, A
X + B calculates A and B by the least square method of the analysis result (drum peripheral speed, maximum friction coefficient) data.

[0030] In the dynamometer device, a drum peripheral speed signal and a specified tire pressing load signal are input together with a correction signal.
A tire pressing load control signal is output. To correct,
There is a correction between the maximum friction coefficient (μ _max ) approximation curve between the tire and the drum and the friction coefficient (μ _spec ) between the actual tire and the ground.

In a tire-brake system mounted on an aircraft or a magnetically levitated vehicle, a lift corresponding to the machine speed (peripheral speed) is applied to the tire in consideration of a reduction in the tire pressing force due to the lift at the time of landing. Perform correction to add to the load.

In the dynamometer device of the present invention, the brake control ability is evaluated by the ratio of the theoretically calculated rolling distance of the drum to the measured rolling distance by using the actually measured maximum friction coefficient of the drum (a function of the peripheral speed of the drum). Is possible.

In order to evaluate the braking efficiency, it is necessary to measure the rolling distance of the drum. For example, one of the measurement channels is assigned to a brake start signal, a rising point of this signal is searched, and analysis is performed. Set the reference address.

In calculating the ideal rolling distance, it is necessary to estimate the mechanical loss of the dynamometer. For example, the relationship between the peripheral speed of the drum and the mechanical loss of the dynamometer is obtained in advance with a constant pressing load, In the relationship between the peripheral speed and the mechanical loss of the dynamometer, it is preferable to calculate the mechanical loss from the peripheral speed and the pressing load data and substitute it into an ideal distance calculation formula to greatly improve the estimation accuracy.

The range from the braking distance start signal on to the braking distance stop signal off is evaluated, and the ideal braking distance X
Calculate _ideal . That is, from the wheel pressing load / drum peripheral speed data and the approximate expression of the curve of the drum peripheral speed versus the maximum friction coefficient (between the tire and the drum) obtained earlier, the drum angular speed, the drum peripheral speed when the braking distance start signal is on, and the drum peripheral speed The stop time in calculation is calculated using the values of the diameter, the moment of inertia of the drum, the mechanical loss torque of the dynamometer, and the wheel pressing load.

In short, the brake control ability can be evaluated based on the theoretically calculated ratio of the drum rolling distance to the actually measured rolling distance using the actually measured maximum friction coefficient of the drum, which is a function of the drum peripheral speed.

[0037]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS In the dynamometer shown in FIGS.
Assuming 2133mm, the mechanical equivalent inertial weight is 1900-5700kgf for 350mm drum only and 3200-70 for 2 drum
00kgf, using a flywheel, 3200-10,000kg
It could be changed arbitrarily in the range of f in 300kgf steps. Further, wheel pressing load control of 0 to 5000 kg or 0 to 13000 kg per wheel is possible.

A radial and thrust load opposed type dynamic pressure bearing by hydraulic pressure is adopted, a drum peripheral speed of 550 km / hr is obtained at 1368 rpm, a maximum radial load of 13 tons, and a drag load of 6 to.
n, a device with an excellent load-carrying performance with a side load of 6 tons was obtained.

[0039] In the dynamometer device having the above-described configuration, the tire camber angle of the legs of the aircraft is set to 8.5 °, and the lift generated in accordance with the gliding speed of the aircraft is used for correcting the wheel pressing load control. When the peripheral speed vs. maximum friction coefficient curve was determined, the results in FIG. 3 were obtained. This makes it possible to calculate the braking efficiency based on the ratio of the theoretically calculated drum rolling distance to the actually measured rolling distance.

[0040]

The dynamometer device according to the present invention has the following features.
It is possible to simulate the friction coefficient and the lift between the actual machine tire and the ground according to the peripheral speed of the rotating drum, and to accurately simulate the actual machine state to perform a highly accurate evaluation of the control system.

That is, it is possible to evaluate an anti-lock brake control system in a high-speed region exceeding 500 km / hr of an aircraft, a high-speed vehicle, etc., and to perform a landing simulation test of an aircraft leg, such as an aircraft or a high-speed vehicle. Design and evaluation can be performed easily.

[Brief description of the drawings]

FIG. 1 is an explanatory front view showing a configuration example of a dynamometer device according to the present invention.

FIG. 2 is an explanatory top view showing a configuration example of a dynamometer device according to the present invention.

FIG. 3 is a graph showing a curve of a drum peripheral speed between a tire and a drum versus a maximum friction coefficient.

[Explanation of symbols]

 1 rotating drum 2,14 rotating shaft 3,13 bearing 4,12 base 5 electric motor 6 gearbox 10,11 flywheel 20 tire holding part 21 tire 22 arm 23 slider frame 24 actuator 25 horizontal rail

Claims (9)

[Claims] 1. A rotary drum having a drive source, a flywheel detachable coaxially with the drum, a tire holding portion for variably contacting a tire with a pressing force and a direction of the drum, and a required friction coefficient. A dynamometer device having device control means for controlling at least one of a drum peripheral speed and a tire pressing load to simulate lift and a lift, or a means for detecting and calculating a friction coefficient between a drum and a tire. 2. A rotary drum unit having a driving source, a flywheel detachable coaxially with the drum, a tire holding unit for variably contacting a tire with the drum with a pressing force and a direction thereof, and a required friction coefficient. And a device control means for controlling the drum peripheral speed and the tire pressing load to simulate the lift, detecting and calculating the coefficient of friction between the drum and the tire, and the tire pressing load according to the drum peripheral speed. A dynamometer device having automatic load means for performing a lift correction and a correction of the frictional force on the drum surface to match the actual frictional force to vary the pressing load. 3. The rotating drum portion and / or the flywheel bearing portion has a dynamic pressure bearing against a thrust and / or a radial load by hydraulic pressure.
3. A dynamometer device according to claim 1. 4. The rotary drum unit and / or the flywheel is a coaxially detachable split type.
3. A dynamometer device according to claim 1. 5. The tire holding unit is capable of measuring a load (load) in three axial directions including a tangential direction of a drum surface.
Or the dynamometer device according to claim 2. 6. The method according to claim 1, wherein the detection / calculation means calculates a friction coefficient between the drum and the tire by a predetermined calculation means based on a drum peripheral speed and a tire pressing load. Dynamometer device. 7. The apparatus control means and the detection / calculation means complement each other with a predetermined correction means, so that a target detection / calculation means is provided.
3. The dynamometer device according to claim 1, wherein the dynamometer device performs calculation or control. 8. The servo system according to claim 7, wherein the correction means corrects the tire pressing load based on the ratio of the maximum friction coefficient between the actual machine and the equipment so that the rear load in the tangential direction of the drum becomes equal to that of the actual machine. 3. A dynamometer device according to claim 1. 9. The brake control ability according to claim 1 or 2, wherein the measured maximum friction coefficient of the drum (a function of the peripheral speed of the drum) is used to evaluate the brake control ability by the ratio of the theoretically calculated rolling distance to the measured rolling distance. 3. A dynamometer device according to claim 1.