JP2010025312A - Fluid pressure brake device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fluid pressure brake device which is small in size and light in weight, and low in the consumption of energy. <P>SOLUTION: The fluid pressure brake device includes: a disk 20 rotating together with a wheel; brake shoes 30 giving friction forces while abutting the disk 20; a mechanical spring 50 urging the brake shoes 30 in the direction to the disk 20; and a fluid pressure cylinder 40 reversibly urging the brake shoes 30 in a direction to the disk 20 or in the opposite direction. By making the mechanical spring 50 and the fluid pressure cylinder 40 work together to press the brake shoes 30 to the disk 20 at the time of braking, the fluid pressure cylinder 40 of a small size can be used. Therefore, the brake device can be driven with a small amount of a compressed fluid. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a fluid pressure brake device that drives and brakes a fluid pressure cylinder with fluid pressure such as hydraulic pressure or air pressure.

  Conventionally, hydraulic brakes and pneumatic brakes that use fluid pressure as a power source have been used in railway vehicles. As a brake for railway vehicles, a so-called negative is used, in which the brake is released by urging the brake in the direction of the disk by the force of a mechanical spring and by urging the brake in a direction away from each other by an actuator such as a fluid pressure cylinder. The format is widely known.

Patent Document 1 discloses a negative brake device.
JP-A-8-210392

  However, in such a conventional negative type brake, since the maximum pressing force is determined by the size of the mechanical spring, a large mechanical spring is required, and accordingly, the actuator becomes larger and the entire device becomes larger. It was.

  Accordingly, an object of the present invention is to provide a fluid pressure brake device that is small and light and consumes little energy.

The present invention includes a disk that rotates together with a wheel, a brake that abuts against the disk and applies a frictional force, a mechanical spring that biases the brake in the direction of the disk, and the brake according to fluid pressure. A fluid pressure cylinder for reversibly urging in the disk direction and the opposite direction;
The mechanical spring and the fluid pressure cylinder cooperate to press the brake against the disc during braking.

  According to the present invention, since the mechanical spring and the fluid pressure cylinder cooperate to press the brake in the disk direction, the mechanical spring can be made smaller than when the mechanical spring alone is pressed. Along with this, the hydraulic cylinder can also be made small, and can be driven with a small amount of compressed fluid. Accordingly, it is possible to obtain a fluid pressure brake device that is small and light and consumes less energy.

  Hereinafter, a hydraulic brake device 100 according to an embodiment of the present invention that uses hydraulic pressure for fluid pressure will be described with reference to FIGS. 1 and 2.

  FIG. 1 is a front view of a hydraulic brake device according to an embodiment of the present invention, and FIG. 2 is a left side view of FIG.

  The hydraulic brake device 100 is a disc brake type in which a brake 20 provided on the caliper 10 is pressed against a disc 20 that rotates with a wheel (not shown) and brakes. The hydraulic brake device 100 includes a hydraulic cylinder 40 and a mechanical spring 50, and transmits the output of the hydraulic cylinder 40 and the pressing force of the mechanical spring 50 to the control device 30 via the pressing piston 60.

  The disk 20 is disk-shaped and rotates with the wheels. In this embodiment, the disk 20 is provided separately from the wheel, but the disk 20 may be provided integrally with the wheel.

  The caliper 10 is provided so as to straddle both surfaces of the disk 20. The caliper 10 is floatingly supported by a cart (vehicle) (not shown) so as to be slidable in the direction of the center axis of the disk 20 via a slide mechanism such as a slide pin.

  The torque receiving pin 11 is provided through the caliper 10 and connected to the bracket portions 10 a and 10 b of the caliper 10. The torque receiving pin 11 supports the restrictor 30 so as to be slidable with respect to the disk 20 in the axial direction of the torque receiving pin 11. The torque receiving pin 11 receives and absorbs a braking reaction force generated when the brake 30 and the disk 20 are pressed against each other when the hydraulic brake device 100 is braked.

  Inside the bracket portions 10a and 10b of the caliper 10, a brake member 30 that abuts against the disk 20 and generates a frictional force is provided.

  The restrictor 30 is provided on both sides of the disk 20 so as to face each other in parallel with the disk 20. The restrictor 30 includes a lining 31 and abuts against the rotating disk 20 to generate a frictional force and brake. The restrictor 30 is urged toward the caliper 10 by a return spring (not shown). The return spring separates the brake member 30 from the disk 20 when the brake of the hydraulic brake device 100 is released.

  The restrictor 30 receives a pressing force from the hydraulic cylinder 40 and the mechanical spring 50 and generates a braking force by being pressed against the disk 20 in parallel.

  The bracket portion 10 a on one side of the caliper 10 includes a pressing piston 60 that transmits the output of the hydraulic cylinder 40, the mechanical spring 50, the hydraulic cylinder 40, and the pressing force of the mechanical spring 50 to the restrictor 30, and outputs from the hydraulic cylinder 40. As a result, the pressing piston 60 is moved in the axial direction, the urging force of the mechanical spring 50 provided in parallel with the hydraulic cylinder 40 is transmitted to the pressing piston 60, and the brake member 30 is pressed against the disk 20.

  In the present embodiment, the mechanical spring 50 is configured by arranging a plurality of disc springs with the pressing piston 60 and a seat plate 51 to be described later as both ends and alternately changing the direction, but a normal coil spring can also be used. The mechanical spring 50 may be disposed in the oil chamber 40a of the hydraulic cylinder 40 that is a fluid pressure cylinder.

  The mechanical spring 50 presses the brake member 30 against the disk 20 via the pressing piston 60 by an urging force when the hydraulic cylinder 40 is not loaded. In other words, when the hydraulic cylinder 40 is in an unloaded state, the restrictor 30 is pressed against the disk 20.

  The hydraulic cylinder 40 is fixed to the bracket portion 10 a of the caliper 10 with four bolts 52 through a seat plate 51 and a collar 53. The hydraulic cylinder 40 is a double-acting cylinder that is divided into two oil chambers 40a and 40b by a piston 40d. The hydraulic cylinder 40 is a double rod type, through which the rod 40c passes, and the rod 40c is fixed to the piston 40d. A pressing piston 60 is integrally provided at an end of the rod 40c on the side of the restrictor 30. The hydraulic cylinder 40 is controlled by an electromagnetic valve 70. In this embodiment, the hydraulic cylinder 40 is a double rod type, but may be a single rod type as long as it is a double acting type.

  The electromagnetic valve 70 is a 4-port 3-position solenoid valve. The electromagnetic valve 70 has three positions, a brake release position 70a, a no-load position 70b, and a brake position 70c. Here, P in FIG. 1 means being connected to the pump, and T means being connected to the tank. Since this embodiment uses hydraulic pressure as the fluid pressure, such a configuration is used, but air pressure may be used as the fluid pressure instead of hydraulic pressure. In this case, an exhaust port is provided at a portion T in FIG. 1, and the air pressure in the pneumatic cylinder is released to the atmosphere.

  When the electromagnetic valve 70 is at the brake release position 70a, pressure oil from a pump (not shown) is supplied to the oil chamber 40b, the oil chamber 40a is connected to the tank, and the rod 40c is moved in the direction opposite to the disk 20.

  When the electromagnetic valve 70 is in the no-load position 70b, the pressure oil in the oil chambers 40a and 40b is sent to the tank, and the rod 40c of the hydraulic cylinder 40 does not move in either direction.

  When the electromagnetic valve 70 is at the braking position 70 c, the pressure oil from the pump is supplied to the oil chamber 40 a, the oil chamber 40 b is connected to the tank, and the rod 40 c is moved in the direction of the disk 20.

  The pressing piston 60 is provided integrally with the rod 40 c of the hydraulic cylinder 40. The pushing piston 60 pushes the control member 30 through the heat insulating plate 66 by only the urging force of the mechanical spring 50 during braking, or the resultant force of the urging force of the mechanical spring 50 and the force by which the rod 40c of the hydraulic cylinder 40 extends in the axial direction. wear. Further, the pressing piston 60 compresses the mechanical spring 50 by the force of the rod 40c returning to the direction of the hydraulic cylinder 40 when releasing the brake, and separates the brake member 30 from the disk 20. At this time, the return spring (not shown) urges the restrictor 30 in the direction away from the disk 20, so that the restrictor 30 does not remain in contact with the disk 20.

  A heat insulating plate 66 is provided at the front end of the pressing piston 60, and the control member 30 and the pressing piston 60 come into contact with each other through the heat insulating plate 66. The heat insulating plate 66 protects the hydraulic cylinder 40 and the like from the frictional heat generated between the control wheel 30 and the disk 20 when the hydraulic brake device 100 is braked. A rubber boot 65 is provided between the pressing piston 60 and the caliper 10 to protect the sliding portion from dust and the like.

  A seat plate 51, which is a spring seat of the mechanical spring 50, is attached to the bracket portion 40 e of the hydraulic cylinder 40.

  The seat plate 51 is fixed to the bracket portion 10 a of the caliper 10 with four bolts 52 with the collar 53 interposed therebetween. One end of the mechanical spring 50 contacts the seat plate 51 to position the mechanical spring 50. Thereby, the initial urging force with which the mechanical spring 50 presses the pressing piston 60 is determined.

  A collar 53 having a hollow cylindrical shape is provided between the seat plate 51 and the caliper 10. The collar 53 determines the distance between the seat plate 51 and the caliper 10 and serves to fix the hydraulic cylinder 40. The collar 53 is fixed by fastening a bolt 52 that fastens the hydraulic cylinder 40 and the seat plate 51 to the caliper 10. The inside of the collar 53 is hollow, and a mechanical spring 50 is retractably accommodated therein.

  Hereinafter, the operation of the hydraulic brake device 100 will be described with reference to FIGS. 3 to 5.

3 is a schematic diagram of the hydraulic brake device when no hydraulic cylinder is loaded, FIG. 4 is a schematic diagram of the hydraulic brake device when the brake is released, and FIG. 5 is a schematic diagram of the hydraulic brake device when the brake is applied.
Here, as an example, the required pressing force of the restrictor 30 against the disk 20 is 5.0 kN, the spring constant of the mechanical spring 50 is 0.5 kN / mm, the clearance between the restrictor 30 and the disk 20 is 2.0 mm, and the hydraulic pressure is 500 N. A case of / cm 2 (50 N / cm 2 in the case of air pressure) and a pressure receiving area = 6 cm 2 (60 cm 2 in the case of air pressure) will be described.

  When the hydraulic cylinder 40 is unloaded, that is, when the electromagnetic valve 70 is at the unloaded position 70b, the mechanical spring 50 contacts the disc 20 with the brake 30 via the pressing piston 60 and the heat insulating plate 66 as shown in FIG. Touch and press. At this time, the mechanical spring 50 presses the brake member 30 against the disk 20 with a force of 2.0 kN.

  When the brake of the hydraulic brake device 100 is released, that is, when the position of the electromagnetic valve 70 is the brake release position 70a, the hydraulic cylinder 40 moves the pressing piston 60 to the side opposite to the disk 20 as shown in FIG. The hydraulic cylinder 40 compresses the mechanical spring 50 until the clearance between the restrictor 30 and the disk 20 becomes 2.0 mm. At this time, the hydraulic cylinder 40 has a total of 3.0 kN, which is the sum of the pressing force of 2.0 kN of the mechanical spring 50 when no load is applied and 0.5 kN × 2 = 1.0 kN necessary for securing a clearance of 2.0 mm. The power of is generated. As described above, in order to compress the mechanical spring 50 by the hydraulic cylinder 40, it is necessary to set the output of the hydraulic cylinder 40 larger than the urging force of the mechanical spring 50. Since the restrictor 30 is urged toward the caliper 10 by the return spring, it follows the movement of the pressing piston 60 and is separated from the disk 20.

  When the hydraulic brake device 100 is braked, that is, when the electromagnetic valve 70 is at the braking position 70c, the hydraulic cylinder 40 moves the pressing piston 60 toward the disk 20 as shown in FIG. In order to press the restrictor 30 against the disk 20 with a required pressing force of 5.0 kN, the hydraulic cylinder 40 has a pressing force of 3.0 kN in addition to the pressing force of 2.0 kN of the mechanical spring 50 when no load is applied. What is necessary is just to press the restrictor 30 against the disk 20.

  In other words, the pressing force of the hydraulic cylinder 40 required for pressing with the force of 5.0 kN which is the maximum pressing force by the mechanical spring 50 and the hydraulic cylinder 40 cooperating to press the brake 30 against the disk 20. Becomes 3.0 kN. When the hydraulic cylinder 40 alone exerts a pressing force of 5.0 kN, or when a mechanical spring 50 that exhibits a pressing force of 5.0 kN is used in a negative type, a large hydraulic cylinder 40 and a large amount of pressure oil are required. is there. However, in this embodiment, an equivalent pressing force can be exhibited with a small hydraulic cylinder 40 and a small amount of pressure oil. As a result, the hydraulic brake device 100 can be reduced in size and weight, and energy consumption can be reduced.

  According to the above embodiment, the following effects can be obtained.

  Since the mechanical spring 50 and the hydraulic cylinder 40 cooperate to press the brake member 30 against the disk 20, the mechanical spring 50 can be made smaller than when the mechanical spring 50 is pressed alone. Along with this, the hydraulic cylinder 40 can be made smaller, and the hydraulic cylinder 40 can be driven with a small amount of pressure oil. Therefore, it is possible to obtain a hydraulic brake that is small and light and consumes less energy.

  In addition, by setting the pressing force by the mechanical spring 50 to a force required as a parking brake, the hydraulic cylinder 40 can be used as a parking brake when there is no load. By controlling the pressure of the electromagnetic valve 70, the pressing force can also be controlled.

  The present invention is not limited to the above-described embodiment, and it is obvious that various modifications can be made within the scope of the technical idea.

  For example, the present invention can be applied not only to the disc brake type as in the present embodiment but also to the drum brake type and the tread type brake type.

  The hydraulic brake device according to the present invention can be used for a mobile body brake device including various vehicles such as railways and automobiles.

1 is a front view of a hydraulic brake device according to an embodiment of the present invention. It is a left view in FIG. It is a schematic diagram of a hydraulic brake device when no hydraulic cylinder is loaded. It is a mimetic diagram of a hydraulic brake device at the time of brake release. It is a schematic diagram of the hydraulic brake device at the time of braking.

Explanation of symbols

DESCRIPTION OF SYMBOLS 100 Hydraulic brake device 10 Caliper 11 Torque receiving pin 20 Disc 30 Brake 31 Liner 40 Hydraulic cylinder 40c Rod 50 Mechanical spring 51 Seat plate 52 Bolt 53 Collar 60 Pushing piston 65 Boot 66 Thermal insulation plate 70 Electromagnetic valve

Claims (4)

A disc that rotates with the wheels,
A brake member that abuts against the disk and applies a frictional force;
A mechanical spring that biases the restrictor toward the disk;
A fluid pressure cylinder for reversibly urging the control in the disk direction and the opposite direction according to fluid pressure;
With
A fluid pressure brake device, wherein the mechanical spring and the fluid pressure cylinder cooperate to press the brake against the disk during braking.   2. The fluid pressure brake device according to claim 1, wherein when releasing the brake, the fluid pressure cylinder pulls the brake member away from the disk.   The urging force of the fluid pressure cylinder is set larger than the urging force of the mechanical spring, and when the brake is released, the urging force of the mechanical spring is canceled by the output of the fluid pressure cylinder, and the mechanical spring is compressed. The fluid pressure brake device according to claim 1 or 2, characterized in that   The fluid pressure brake device according to any one of claims 1 to 3, wherein the fluid pressure cylinder is a hydraulic cylinder, and the hydraulic cylinder is reversibly driven by switching a valve.