JPH08253146A - Pitching and rolling preventive device of railway rolling stock - Google Patents

Abstract

PURPOSE: To provide a pitching and rolling preventive device of a rolling stock by which motive power consumption is reduced and a motive power part is downsized. CONSTITUTION: In a swinging preventive device of a rolling stock where a pair of hydraulic cylinders 10R and 10L are symmetrically arranged between a car body S and a bogie D by turning piston rods 11 and 11 toward the side and bottom parts 10a of its cylinders are joined to the car body S and the tips of the piston rods 11 are joined to the bogie D, operating fluid is supplied to its hydraulic cylinders 10R and 10L by a hydraulic pump 31 driven by a servomotor 32 so that the car body S is moved in the direction for offsetting swinging of the bogie D. Therefore, a useless circulating quantity of operating fluid is remarkably reduced, and motive power consumption is also remarkably reduced.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a railroad vehicle sway preventing device. More particularly, the present invention relates to a railway vehicle sway prevention device that requires reduced power.

[0002]

2. Description of the Related Art In railway vehicles, the speed of vehicles has been increased in order to realize high-speed mass transportation. This speeding up of the vehicle, together with the weight reduction of the vehicle, causes an increase in the sway of the vehicle during traveling, and as a result, the ride comfort is deteriorated. Therefore, conventionally, a shake preventing device is provided between the vehicle body and the bogie, and when the bogie shakes, the vehicle body is moved so as to cancel the shake. A so-called vehicle active vibration suppressing method is adopted.

A hydraulic pressure is used in the vibration suppressing device A'used in this active vibration suppressing method because a desired response and output can be obtained. For example, as shown in FIG. 4, a pair of hydraulic cylinders 10 </ b> R and 10 </ b> L are symmetrically arranged between the vehicle body S and the bogie D with respect to the center axis of the vehicle T, and the piston rods 11 and 11 are outwardly (laterally). And the bottom 1 of each hydraulic cylinder 10R, 10L
Reference numerals 0a and 10a are fixed to a center pin P provided at the bottom of the vehicle body S, while the tip 11a of the piston rod 11 is joined to a joining member d provided on the upper surface of the truck D. The hydraulic cylinders 10R and 10L each include a piston 1
Hydraulic pipes 20, 20 for pressure oil and return oil for operating the pumps 2, 12 are connected. And, for example,
When the truck D swings to the left in the drawing, the hydraulic oil and return oil are adjusted in the left hydraulic cylinder 10L in the drawing so that the piston rod 11 advances from the hydraulic piping 20, 20. In the right hydraulic cylinder 10R in the figure, pressure oil and return oil are adjusted so that the piston rod 11 is retracted from the hydraulic pipes 20,20.

As shown in FIG. 4, the control of the acceleration signal 42 from the accelerometer 41 provided on the vehicle body S is performed by the control device 40.
By instructing the servo valve 21 about the opening degree and flow path direction of the servo valve 21 calculated based on the acceleration, and setting the opening degree and flow path direction of the servo valve 21 to the command value. Is done by. The drive source of the hydraulic pump 31 that supplies pressure oil to the servo valve 21 has an output of several kilowatts due to the generation of hydraulic pressure for moving the vehicle body S having a weight of several tons. A large motor 32 'is used. Generally, a three-phase AC induction motor is used as the high-output motor 32 '.

By the way, since the electric power of the railway vehicle is supplied by the single-phase AC, the three-phase AC induction motor 32 is used.
In order to drive ‘′, it is necessary to convert single-phase alternating current into three-phase alternating current by a conversion device (not shown). However, there is a problem that this conversion device has a considerable volume and weight.

In addition to this, a three-phase AC induction motor 32 '
Since it is difficult to change the number of revolutions, it must be used at a constant speed. Therefore, from the hydraulic pump 31 driven by the induction motor 32 ',
The maximum discharge amount of oil is always discharged. Excess oil is returned to the return pipe 22 through the relief valve 24.
It will be returned to the oil tank 33 by a and 22B.
And thereby, the pressure of the piping 22 is maintained at a predetermined pressure.

By the way, while the return oil circulates between the hydraulic pump 31 and the oil tank 33,
Energy is supplied from the substrate and its temperature rises. Therefore, in order to suppress the temperature rise, an air-cooled cooler (not shown) is interposed in the pipes 20 and 22. However, as described above, since the maximum discharge amount is always discharged from the hydraulic pump 31 and the amount of oil returned to the return pipe 22B increases, the capacity of the cooler must be increased. Therefore, in the conventional apparatus A ', power consumption is increased and facilities are complicated. Further, since the hydraulic pump 31 is always operated at the maximum discharge rate, there is also a problem that generated noise is large.

Regarding the suppression of active vibration of the vehicle T, proposals have been made in JP-A-5-221315 and JP-A-5-213196, but proposals for improving the drive source of the hydraulic pump 31 have been made. Not not.

[0009]

SUMMARY OF THE INVENTION The present invention has been made in view of the above problems of the prior art, and provides a vehicle shake preventing device in which power consumption is reduced and a power unit is downsized. It is an object.

[0010]

SUMMARY OF THE INVENTION According to the present invention, there is provided an anti-sway device for a railway vehicle, wherein the anti-sway device is provided between a vehicle body composed of a hydraulic cylinder and a bogie, and the amount of oil supplied to the anti-sway device is adjusted. An oil amount adjusting means for performing pressure control, an oil supply means having a rotation speed control type electric motor for supplying pressure oil to the oil amount adjustment means, an electric motor control means for controlling the rotation speed control type electric motor, and the oil Control means for controlling an amount adjusting means and an electric motor control means, wherein the control means includes a piston position command value and a piston position signal of the hydraulic cylinder,
Vehicle body vibration acceleration command value and vehicle body vibration acceleration signal, pressure oil supply pressure and hydraulic cylinder internal pressure are input, and the piston position command value and piston position signal of the hydraulic cylinder and the vehicle body vibration acceleration command are input by the control means. A command value to the oil amount adjusting means and the electric motor controlling means is generated based on the value, the vehicle body vibration acceleration signal, the supply pressure of the pressure oil and the internal pressure of the hydraulic cylinder.

In the railway vehicle sway prevention device of the present invention, for example, the hydraulic cylinder of the sway prevention means has a cylinder bottom joined to a member provided on the vehicle body, and a tip end of a piston rod attached to the bogie. It is to be joined to the provided member. Here, there may be two hydraulic cylinders of the shaking prevention means, and both hydraulic cylinders may be arranged with their piston rods facing in opposite directions.

[0012]

In the arithmetic processing unit of the control means, a piston position command value, a piston position signal from a piston position detector provided on the hydraulic cylinder, a vehicle body acceleration command value, and a vehicle body vibration acceleration signal from an accelerometer provided on the vehicle body are provided. Is input, and the supply pressure of the hydraulic oil and the pressure of the hydraulic cylinder are respectively detected from a pressure detector provided in the hydraulic oil supply hydraulic pipe between the hydraulic oil supply means and the oil amount adjusting means and a pressure detector provided in the hydraulic cylinder. Internal pressure is input. Then, based on the input piston position command value and piston position signal of the hydraulic cylinder, the vehicle body vibration acceleration command value and the vehicle body vibration acceleration signal, the supply pressure of the hydraulic oil and the internal pressure of the hydraulic cylinder, Command values for the oil amount adjusting means and the electric motor control means are generated. Next, the generated command values are input to the oil amount adjusting means and the motor control means, respectively.

The oil amount adjusting means sets, for example, the valve opening and the flow passage so that the flow amount and the flow passage direction are in accordance with the input command value. In addition, the electric motor control means,
A current signal or a voltage signal according to the input command value is generated, input to the rotation speed control type electric motor, and rotated. Along with that, for example, the hydraulic pump of the pressure oil supply means is rotated at a predetermined rotation speed. In this way, the desired amount of oil is discharged from the pressure oil supply means, and the amount and flow passage direction of the discharged oil are determined by the oil amount adjusting means to move the piston of the hydraulic cylinder in the desired direction. Let Thereby, the vehicle body is moved in a direction to cancel the vibration of the bogie.

[0014]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will now be described based on embodiments with reference to the accompanying drawings, but the present invention is not limited to such embodiments. FIG. 1 is a block diagram showing one embodiment of a railcar rolling prevention device (hereinafter simply referred to as a prevention device) according to the present invention.
A rotational speed control type electric motor for supplying a hydraulic oil to the anti-sway means 1, an oil amount adjusting means 2 for adjusting the oil amount to the anti-sway means 1, And a control unit 4 for controlling the oil amount adjusting unit 2 and the motor control unit 5 as main parts. . In this embodiment, these means 1, 2, 3, 4, and 5 are provided in the vehicle body S or between the vehicle body S and the bogie D to prevent the vehicle body S from rolling. Hereinafter, each of the constituent means 1, 2, 3, 4, and 5 of the prevention device A will be described in detail.

The sway prevention means 1 is, like the conventional one,
Comprised of a pair of hydraulic cylinders 10R, 10L, the hydraulic cylinders 10R, 10L are symmetrical with respect to the central axis of the vehicle S, and the piston rods 11, 11 are directed outward (sideward),
It is provided between a pair of air springs C provided between the vehicle body S and the bogie D. The bottom 10a of the hydraulic cylinder 10 is joined to a center pin P projecting downward from the back surface of the floor of the vehicle body S. On the other hand, the tip end 11a of the piston rod 11 is joined to a joining member d which is vertically provided from the upper surface of the carriage D. An oil supply / discharge port (not clearly shown) provided at both ends of the hydraulic cylinder 10 is connected to a hydraulic pipe 20 from an oil amount adjusting means 2 described later.

In this embodiment, the hydraulic cylinder 10 has two
Although one is used, one may be used if a desired acting force is obtained.

The oil amount adjusting means 2 includes a servo valve 2
The valve opening degree and the flow passage are switched in response to a control signal from the control means 4 described later. Then, as described above, this servo valve 2
The hydraulic pipe 20 on the output side of No. 1 is connected to the oil supply / discharge port of the hydraulic cylinder 10. Also, on the input side of the servo valve 21, hydraulic pipes 22, 2 from a pressure oil supply means 3, which will be described later, are provided.
2 is connected.

The pressure oil supply means 3 is specifically designed to drive the hydraulic pump 31 by a brushless servomotor 32. The pressure oil supply means 3 is controlled by the motor control means 5 in accordance with a rotation speed command value from the control means 4 described later. It is driven by the generated current or voltage. Here, the hydraulic pump 31
Is similar to a conventionally used hydraulic pump that sucks oil from the oil tank 33 and raises the pressure to a predetermined pressure and discharges the same, and therefore a detailed description of the configuration is omitted. As the brushless servomotor 32 to be used, a conventionally known one is used. The drive source of the hydraulic pump 31 is not limited to a brushless servomotor, but may be any type of rotation speed control type electric motor, for example, a vector control type induction motor.

The electric motor control means 5 is specifically a conventionally known servo amplifier, and generates a voltage signal or a current signal in the electric motor control means 5 in response to a rotation speed command value from the control means 4 described later. Then, the brushless servomotor 32 is driven at a required rotation speed.

As shown in FIG. 2, the control means 4 has an input section 40a, an arithmetic processing section 40b, and an output section 40c as main parts. Further, the arithmetic processing unit 40b includes a piston position control unit 44, a vehicle body acceleration control unit 45, a servo valve flow rate calculation unit 46, and a rotation speed command value generation unit 47. Then, from the deviation between the piston position command value and the piston position signal, the piston position control unit 44 generates a servo valve opening command value for setting the piston to a position in accordance with the command value. From the deviation between the lateral acceleration command value (rolling acceleration command value, usually set to zero) and the vehicle lateral acceleration signal (rolling acceleration signal) 42 from the accelerometer 41, the rolling acceleration of the vehicle body S is set to zero. A servo valve opening command value is generated. The piston position control unit 44 and the vehicle body acceleration control unit 4
5 is output as the servo valve opening command value. here,
The control means 4 may be configured to input four values of a piston position command value, a piston position signal, a vehicle body lateral direction acceleration command value, and a vehicle body lateral direction acceleration signal, and output a servo valve opening command value.

Further, the servo valve flow rate calculation unit 46 calculates the flow rate from the servo valve 21 according to the following procedure.

Supply pressure ps of pressure oil and hydraulic cylinder 10
The first calculated value is calculated based on the pressure difference between the internal pressure p and the internal pressure p.

The second calculated value for the servo valve 21 is calculated by processing the first calculated value and the flow rate gain of the servo valve 21.

The flow rate command value for the servo valve 21 is calculated by processing the second calculated value and the servo valve opening command value.

By processing the flow rate command value thus obtained in the rotation speed command value generating section 47, the rotation speed command value of the servo motor 32 is calculated, and the voltage or current corresponding to the calculated rotation speed command value is obtained by the motor control means. It is output from 5. For example, the rotational speed command value is calculated by multiplying the reciprocal of the displacement volume pq per operation in the hydraulic pump 31 by the obtained flow command value.

The transfer functions used in the piston position control unit 44 and the vehicle body acceleration control unit 45 are shown in FIG.
The same as the original used in the conventional shake prevention device A ′ shown in FIG. Therefore, detailed description of the configuration is omitted.

The control means 4 having such a function is:
Specifically, it is realized by storing a program corresponding to the microcomputer.

A hydraulic pipe 22 connecting the pressure oil supply means 3 and the oil amount adjusting means 2 and a hydraulic pipe 20 connecting the oil amount adjusting means 2 and the sway preventing means 1 are respectively It is configured as follows.

That is, the hydraulic pipe 22 connecting the pressure oil supply means 3 and the oil amount adjusting means 2 is connected to the supply pipe 22 from the discharge port of the hydraulic pump 31 to the input side of the oil amount adjusting means 2.
A and a return pipe 22B from the input side of the oil amount adjusting means 2 to the oil tank 33. And this supply pipe 22
A relief pipe 22C in which a relief valve 24 is interposed is provided between A and the return pipe 22B. The relief valve 24 functions to release a part of the oil amount in the supply pipe 22A and to keep the pressure in the supply pipe 22A constant, as in the related art.
Since the rotation speed command value generation unit 47 sets the rotation speed of the servo motor 32 to drive the hydraulic pump 31, the hydraulic pump 31 theoretically operates from the hydraulic piping. Since only the amount of oil whose pressure is set as the set pressure is discharged, the return pipe 22 is supplied via the relief valve 24.
The amount of oil returning to B is significantly reduced as compared with the conventional amount of returned oil. Therefore, the temperature rise of the oil due to the circulation of the oil is significantly reduced, and the capacity of the coolers provided in the pipes 20 and 22 is also significantly reduced. In addition, this supply pipe 22
On the upstream side (front side) of the servo valve 21 of A, a branch pipe 22D to the accumulator 25 is provided. And
The accumulator 25 allows the supply pipe 2 to start and stop the hydraulic pump 31 and open and close the servo valve 21.
Pressure fluctuations within 2A are absorbed.

On the other hand, the hydraulic pipe 20 connecting the oil amount adjusting means 2 and the shake preventing means 1 is composed of a first distribution pipe 20A and a second distribution pipe 20B. This first distribution pipe 20
A and the second distribution pipe 20B are connected to the hydraulic cylinder 10 so as to operate the piston rod 11 of the hydraulic cylinder 10 in the opposite direction. For example, the first distribution pipe 20
The first branch pipe 201 of A is connected to the upper part of the right hydraulic cylinder 10R (retreat side of the pinton rod 11) in FIG. 1, and the second branch pipe 202 is connected to the left hydraulic cylinder 10L in FIG. (The side opposite to the piston rod 11). Conversely, the first branch pipe 203 of the second distribution pipe 20B is connected to the lower part of the right hydraulic cylinder 10R in FIG. 1, and the second branch pipe 204 is connected to the upper part of the left hydraulic cylinder 10L in FIG. It is connected to the. Furthermore, the first
The distribution pipe 20A and the second distribution pipe 20B are connected by a bypass pipe 20C to improve controllability. The first distribution pipe 20A and the second distribution pipe 20
Shutoff valves 23, 23 are provided in each of B,
In an emergency, a hydraulic damper is used as in the conventional case.

Next, referring to FIG. 3, a description will be given of how the prevention device A having such a configuration prevents the vehicle body S from swinging.

The strokes or piston positions of the piston rods 11, 11 of the hydraulic cylinders 10R, 10L are input to the control means 4 from stroke detectors or piston position detectors (not shown) provided on the hydraulic cylinders 10R, 10L. . The control means 4 calculates a deviation between the input stroke or the piston position and the piston position command value, and the control means 4 sets a servo valve opening command for setting the pistons 12 and 12 at a predetermined position based on the deviation. Calculate the value 1.

An acceleration signal 42 accompanying the shaking of the vehicle body S is input to the control means 4 from an accelerometer 41 provided on the vehicle body S.

The control means 4 receives the input acceleration signal 4
From 2 and the vehicle acceleration command value (normally set to zero), a servo valve opening command value 2 required for the acceleration of the vehicle body S to follow the command value is calculated. Then, the control means 4 generates a servo valve opening command value (valve opening and flow passage direction) from the sum of the servo valve opening command value 2 and the servo valve opening command value 1 calculated by the servo valve opening command value 2. Input to the servo valve 21.

At the same time, the control means 4 generates a rotation speed command value of the servo motor 32 from the inputted pressure ps of the pressure oil, the internal pressure p of the cylinder and the servo valve opening command value, and the motor control means ( Input to servo amplifier 5).

The servo valve 21 is set to the valve opening and the flow passage direction according to the servo valve opening command value from the control means 4.

The electric motor control means 5 responds to the rotation speed command value from the control means 4 to generate a voltage signal or a current signal for rotating the servo motor 32 at the command rotation speed and input the voltage signal or current signal to the servo motor 32. To do.

The servomotor 32 is the motor control means 5
The hydraulic pump 31 is driven by a voltage signal or a current signal input from the controller. The rotation speed of the servomotor 32 at this time is detected by a rotation speed detector (not shown) and fed back to the control means 4.

From the hydraulic pump 31 driven by the servo motor 32, a predetermined amount of oil and pressure oil are supplied to the servo valve 21. In addition, the pressure of the pressurized oil is
The pressure is detected by a pressure detector (not shown) provided in 2A and input to the control means 4.

The pressure oil supplied to the servo valve 21 is supplied to the hydraulic cylinders 10R and 10R by, for example, the first distribution pipe 20A.
Supplied to L. Conversely, the hydraulic cylinders 10R, 10
The oil in L is discharged through the second distribution pipe 20B. The discharged oil is collected in the oil tank 33 through the servo valve 21 and the return pipe 22B. Here, the supply of the pressure oil to the hydraulic cylinders 10R and 10L is performed to reduce the swing of the vehicle body S. For example, when the truck D swings to the left, the supply of the pressure oil is performed so that the vehicle body S moves to the right.

As described above, in this embodiment, the vehicle T
When a roll occurs in the vehicle, the vehicle S is moved by the prevention device A in a direction that cancels the direction of the vehicle D, and the vehicle S is prevented from shaking. Therefore, a comfortable ride can be provided to the passenger.

Although the present invention has been described above based on the embodiments, the present invention is not limited to such embodiments, and various modifications can be made. For example, in the embodiment, the case where the vehicle body is prevented from rolling has been described. However, by appropriately adjusting the arrangement of the hydraulic cylinders, it is possible to prevent the vehicle body from swinging with respect to the traveling direction or vertically swinging. .

In this embodiment, the flow rate of the servo valve is calculated using the difference between the supply pressure of the hydraulic oil and the internal pressure of the cylinder. Feedback control for correcting the rotation speed of the motor may be used.

[0044]

As described above in detail, in the present invention, a brushless servomotor is used as a driving means of the hydraulic pump, and the hydraulic pump is rotated at a rotation speed corresponding to a required oil amount. An excellent effect that remarkable reduction can be obtained. Further, since the amount of hydraulic oil circulated through the relief valve is significantly reduced, the rise in oil temperature due to circulation can be significantly reduced. Therefore, the cooling device can be reduced in size and weight, and the required power can be reduced.

[Brief description of drawings]

FIG. 1 is an explanatory diagram showing a block diagram of an embodiment of a vehicle body swing preventing device according to the present invention.

FIG. 2 is an explanatory diagram of control means used in the embodiment.

FIG. 3 is an explanatory diagram of an operation at the time of preventing a swing in the embodiment.

FIG. 4 is an explanatory view showing a block diagram of a conventional shake prevention device.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Sway prevention means 10 Hydraulic cylinder 11 Piston rod 12 Piston 2 Oil amount adjusting means 20, 22 Hydraulic piping 21 Servo valve 23 Shut off valve 24 Relief valve 25 Accumulator 3 Pressure oil supply means 31 Hydraulic pump 32 Brushless servomotor 33 Oil tank 4 Control Means 40a Input unit 40b Arithmetic processing unit 40c Output unit 5 Motor control means, servo amplifier A Shake prevention device T Vehicle S Body D Dolly P Center pin

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Yoshikazu Nishi 1-1 Kawasaki-cho, Akashi-shi Kawasaki Heavy Industries Ltd. Akashi factory (72) Inventor Toshinao Doi 1-1 Kawasaki-cho Akashi-shi Kawasaki Heavy Industries Ltd. Akashi Factory

Claims (3)

[Claims] 1. A shaking prevention means disposed between a vehicle body composed of a hydraulic cylinder and a bogie, an oil quantity adjusting means for adjusting an oil quantity to the shaking prevention means, and a pressure applied to the oil quantity adjusting means. A pressure oil supply unit having a rotation speed control type electric motor for supplying oil, an electric motor control unit controlling the rotation speed control type electric motor, and a control unit controlling the oil amount adjusting unit and the electric motor control unit. , The piston position command value and the piston position signal of the hydraulic cylinder, the vehicle body vibration acceleration command value and the vehicle body vibration acceleration signal, the supply pressure of the pressure oil and the internal pressure of the hydraulic cylinder are input to the control means, and are input by the control means. The piston position command value and piston position signal of the hydraulic cylinder, the vehicle body vibration acceleration command value and the vehicle body vibration acceleration signal, the pressure oil supply pressure, and the hydraulic cylinder. Anti-swing device for a railway vehicle, characterized in that the command value to the fluid level regulating means and the motor control means is generated based on the internal pressure of da. 2. The hydraulic cylinder of the swing prevention means, wherein the bottom of the cylinder is joined to a member provided on the vehicle body, and the tip end of the piston rod is joined to a member provided on the bogie. The railcar rolling prevention device according to claim 1, wherein: 3. The sway preventing means includes two hydraulic cylinders, and both hydraulic cylinders are arranged with their piston rods facing in opposite directions.
The rolling prevention device for a railway vehicle as described in the above.