JPH0454332A - Disc brake unit for railway vehicle - Google Patents

Abstract

PURPOSE:To surely cope with a high temperature phenomenon at the time of braking by forming a passage chamber along a circule between a metal circular plate and a case member, forming an end part of a rotation shaft to be hollow, and forming an air supply hole opening to the outer side surface of a plate member. CONSTITUTION:When a braking force is applied by a pressure member 15, a rotor member 10 and a stator member 11 slide axially in one direction to be pushed and collected, so the members are contacted with each other, and a relative rotation of the rotor member to the stator member is prohibited by friction generated at this time. In this case, a passage chamber 66 is formed along a circle between a metal circular plate 63, provided on a circle between the outer circumference of the rotor member 10 and the stator member 11 and a case member 7, and the case member, one end of a rotation shaft 9 is formed hollow, an air supply hole 61 opening toward the outer side surface of a plate member is formed, and cooling air is discharged through the outer side surface of the plate member 10 to the passage chamber 66 by this rotation shaft 9, so a high temperature heat generated at the time of braking is speedily radiated to be discharged to the passage chamber.

Description

[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to a disc brake device for a railway vehicle, and in particular to an end portion of a rotor shaft of a drive motor that transmits and imparts rotation to an axle of a railway vehicle. The present invention relates to a disc brake device.

[Conventional technology]

As a conventional structure of a disc brake device for a railway vehicle, for example, one disclosed in Japanese Utility Model Application Publication No. 64-4933 has wheels ioo as shown in FIG.

An induction motor (driving motor) 102 is installed on one side of an axle 101 that supports the induction motor 1.
A disk 1.4 is fixed to one end of the rotor shaft 103 of the caliber 105, and the disk 104 is interposed between a pair of letter pads 106 and 106 attached to the caliber 105. The induction motor 102 is fixedly installed on a vehicle side member such as a truck, and the caliber 105 is held on the vehicle side member or the induction motor 102.

A flexible joint 10 is attached to the other end of the rotor shaft 103.
A drive gear 108 is attached to the axle 101 via a shaft 7, and a driven gear 109 meshed with the drive gear 108 is attached to a corresponding end of the axle shaft 101. According to such a configuration, when the vehicle is running, the induction motor 1
The axle 101 and wheels 10o and ioo are rotated with the rotation of the rotor shaft 103 of 02, but when a brake command is issued, the band 10 of the caliber 105 is rotated.
6.106 comes into pressure contact with both surfaces of the disk 104, a braking action is performed, and the rotation of the rotor shaft 103 and the axle 101, as well as the wheels 100.100, is stopped.

However, the disc brake device disclosed in the above publication uses - discs 104, and since the discs 104 are usually made of iron-based metal material, their heat capacity is small. , it has the characteristic that it tends to reach a high temperature during braking. In addition, the iron-based metal material has a property of having extremely low strength under high temperature conditions, so during braking, the strength of the disc 104 is drastically reduced due to heat and the disc 1
04, which not only shortens the life of the disk 104, but also causes the disk 104 to become unbalanced, causing vibrations and causing early damage to the bearing of the rotor shaft 103 of the induction motor 102. This will cause problems.

In order to deal with such problems, for example,
According to Publication No. 972, as shown in FIG. 10, disks 104 and 104 are respectively fixed to both ends of the rotor shaft (hollow armature shaft) 103 of the induction motor 102, and these two disks 104 and 104 are Two calibers 10 held together
5.105 is disclosed. According to this, it can be expected that problems such as high temperature and uneven wear of the disks 104 and 104 during braking can be solved to some extent.

(Problems to be Solved by the Invention) However, even with the disc brake device disclosed in the above-mentioned Japanese Utility Model Publication No. 1-117972, it is not possible to sufficiently cope with the recent increase in the speed of railway vehicles. In other words, by simply providing two discs, since the discs are made of iron-based metal, there is a limit to how large the heat capacity can be, and if braking from high-speed running continues, the discs 104 It is natural for the disk 104 to reach a high temperature, and not only does the above-mentioned problem occur due to the high temperature of the disk 104, but the disk and caliber must be placed on both sides of the induction motor body. Therefore, the problem arises that the layout for installing the disk device becomes difficult.

The present invention has been made in view of the above-mentioned circumstances, and has improved the configuration of the disk to reduce heat generation, make the device more compact and easy to install, and achieve high speed. The technical problem is to make it possible to reliably deal with the phenomenon of high temperature even if it occurs during braking from running.

[Means for Solving the Problem] The specific means for achieving the above technical problem is to install a rotary shaft that rotates together with the rotary shaft and in the axial direction at the end of the rotary shaft that is connected to the axle of the railway vehicle. a plurality of rotor members that are slidable in the rotor member; a plurality of stator members that are disposed between the rotor members and slidably attached to the key member only in the axial direction; a pressing member that applies a braking force to the rotor member and the stator member through these plate members; a case member that includes the rotor member and the stator member; and an outer periphery of the rotor member and the stator member. a metal ring plate provided on a circumference between the metal ring plate and the case member, a passage chamber is formed on the circumference between the metal ring plate and the case member, and an end portion of the rotating shaft is provided. An air supply hole is formed in a hollow shape and opens toward the outer surface of the plate member, and cooling air is discharged from the rotating shaft through the outer surface of the plate member into the passage chamber.

[Effect]

According to the above means, the multi-plate disc brake device is
When the braking force by the pressing member is not applied, the plurality of rotor members that rotate together with the rotating shaft connected to the axle of the railway vehicle freely rotate with respect to the plurality of stator members attached to the key member. However, on the other hand, when the braking force is applied by the pressing member, the rotor member and the stator member slide in the axial direction - the larger side and are pushed together, so that the respective members are in pressure contact, The friction generated at this time prevents the rotor member from rotating relative to the stator member. In other words, the key member allows the stator member to slide only in the axial direction.
When the relative rotation of the rotor member with respect to the stator member is prevented as described above, the rotation of the axle, which is connected to the rotating shaft that rotates together with the rotor member, and thus the wheels, will stop.

Further, the present invention employs a multi-plate disc brake device consisting of a plurality of rotor members, a plurality of stator members, and a pressing member in a railway vehicle, thereby reducing the heat generated during braking when the vehicle is running at high speed. is dispersed into the frictional heat between the plurality of rotor members and stator members, which not only greatly reduces the amount of heat generated by each member, but also facilitates installation and makes the device more compact. will be planned.

Furthermore, a passage chamber is formed on the circumference between the case member and a metal ring plate provided on the circumference between the outer periphery of the rotor member and the stator member and the case member, and a passage chamber is formed on the circumference between the outer circumference of the rotor member and the stator member and the case member, and is formed into a hollow shape to form an air supply hole that opens toward the outer surface of the plate member, and the cooling air is discharged from the rotary shaft through the outer surface of the plate member into the passage chamber. Even if high-temperature heat generated by friction between the rotor member and the stator member is transmitted to the plate member, the heat is quickly radiated by the cooling air taken in from the rotating shaft and discharged to the passage chamber.

〔Example〕

Embodiments of the present invention will be described below with reference to FIGS. 1 to 7.

First, the mounting state of the disc brake device l according to the present invention will be explained based on the schematic configuration shown in FIG. 2 is attached, and a drive gear 4 fixed to one end of the rotor shaft 3 of the drive electric motor 2 meshes with a driven gear 6 fixed to an axle 5 supporting wheels 53 and 53. At the same time, the disc brake device 1 according to the present invention is attached to the opposite gear side end WI (left end portion) of the drive motor 20. Therefore, when the vehicle is running, the rotor of the drive motor 2 The rotation of the shaft 3 is transmitted to the axle 5 and the wheels 53,53 via the drive gear 4 and the driven gear 6, while when a brake command is issued, the rotation of the rotor shaft 3 is transmitted by the operation of the disc brake device 1. The braking action is performed by stopping the rotation of the axle 5 and the wheel M53.53.The axle case 54.54 holds the axle 5 rotatably at both ends thereof. and said trolley 52
A shaft spring 55.55 is interposed between.

Next, the detailed structure of the disc brake device 1 will be explained based on FIGS. 2 and 7.

This disc brake device 1 has a drum-shaped case member 7 fixed to the opposite end of the drive motor 2 using a pole 1-56.56, and the inner peripheral surface of the case member 7 is A plurality of key members 8 .
It is held so that it can rotate as a unit. Two rotor members 10 and 10 are attached to the outer periphery of the hollow shaft 9 and are rotatable together with the hollow shaft 9 and the rotor shaft 3 and are slidable in the axial direction (a-b direction in FIG. 3). Furthermore, three stator members 11...11, which are slidable only in the axial direction, are attached to the inner circumferences of the key members 8...8. Specifically (see FIG. 2), the hollow shaft 9 is integrally formed with a plurality of protrusions 9a...9a extending outward at equal angular intervals along the axial direction. A through hole 10a having the same shape as the outer diameter of the shaft 9 is formed in the center of the rotor member IO, and by fitting these together, the rotor member 10 rotates together with the hollow shaft 9 and slides in the axial direction. On the other hand, the key members 8--8 are arranged at equal angular intervals and fixedly supported by the case member 7, and the contours perpendicular to the axis of these key members 8--8 are fixedly supported by the case member 7. Notches 11a, . It is said to be able to slide freely. In this case, the rotor member lO and the stator member 11 are arranged alternately in the axial direction, and are arranged between the outer peripheral surface 10b of the rotor member 10 and the inner peripheral surface of the key members 8...8, and between the stator member 11
A slight gap exists between the inner circumferential surface 11b of the hollow shaft 9 and the outer circumferential surface of the hollow shaft 9. Incidentally, the number of rotor members 10 and stator members 11 is not limited to that shown in FIG. 3, and may be greater or less than this number.

Furthermore, as shown in FIG. 3, a ring-shaped pressure plate 12 made of a metal material with good thermal strength and conductivity is disposed close to the left side of the stator member 11 disposed at the left end. As shown in FIG. 4, this pressurizing plate 12 is provided with an insertion hole 12a in the center for inserting the hollow shaft 9, and the side surface facing the stator member 11 is formed flat. On the opposite side surface, that is, the outer surface on the side of the case member 7, a large number of passage grooves 12b and protrusions 12c are alternately provided radially from a position slightly spaced apart from the insertion hole 12a toward the outer circumference. Further, on its outer periphery, a plurality of key holes 12d into which the key member 8 is fitted are formed with a predetermined pinch, and flat portions 12e and 12f are formed in the protrusion 12c with a predetermined pinch. The piston rod 21 (
A hole 12g into which a hole (to be described later) is fitted is provided.

This pressure plate 12 is connected to the stator member 1.
1, the insertion hole 12a is fitted into the hollow shaft 9,
Further, the key member 8 is fitted into the key hole 12d so as to be slidable in the axial direction. A ring-shaped stopper plate 13 made of the same metal material as the pressure plate 12 is disposed on the right side of the stator member 11 disposed at the right end of the members. As shown in FIG. 5, this stopper play eye 3 is provided with an insertion hole 13a in the center thereof into which the hollow shaft 9 is inserted, and the side surface facing the stator member 11 is formed flat.
A large number of passage grooves 13b and protrusions 13c are alternately provided in a radial direction toward the outer circumferential direction from a position slightly spaced from the insertion hole 13a on the side surface opposite to 1, that is, on the outer surface of the case member 7 examples. Moreover, a plurality of key holes 13d into which the key members 8 are fitted are formed at a predetermined pitch on the outer periphery. This stomp plate 13 has an insertion hole 12a fitted into the hollow shaft 9, and a groove 13b and a protrusion 13.
By being firmly fixed to the key members 8...8 in a state in which the outer surface provided with the arrow mark c is in contact with the inner surface of the right side wall 7a of the case member 7, the inner surface of the right side wall 7a of the case member 7 and the stomp plate are firmly fixed. A plurality of slits 14 . . . 14 extending in the radial direction are radially formed between the passages 113 b and the projections 13 c.

On the other hand, on the left side wall 7b of the case member 7, a plurality of pistons (pressing members) 15 . A hydraulic chamber 16 for applying hydraulic pressure (oil pressure) is formed on the rear surface of the piston 15, and the hydraulic chamber 16 is connected to the hydraulic passage 1 as shown in FIG.
7 to a hydraulic pressure supply port 18 (leading to a hydraulic pressure source).

Furthermore, a plurality of gap adjustment mechanisms 19...19 are provided on the left side wall 7b of the case member 7. As shown in FIG. 3, this gap adjustment mechanism 19 includes a piston loft 21 biased leftward by a compression coil spring 20, and a stopper which restricts leftward movement by abutting a stepped surface of the piston loft 21. The plate 22 and the friction ring 24 that restricts the rightward movement of the retainer 23 fixed to the stiffener plate 22.
and has. The right end portion of the piston loft 21 is connected to a hole 1 provided in the flat portion 12e of the pressure plate 12.
2g, and therefore the pressure plate 12 is moved to the left by the compression coil spring 20, that is, to the stator member 1.
It is in a state where it is biased in the direction away from 1. Further, the friction ring 24 moves left and right when a force equal to or more than a predetermined force is applied thereto, and in response to this left and right movement, the flange member 25 fitted to the piston rod 2 and the retainer 23
The gap X between the piston rod 21, that is, the movement range of the piston rod 21 changes.

According to the above configuration, when the vehicle is running, the hollow shaft 9 and the rotor member 10, 10 rotate with the rotation of the rotor shaft 3 of the drive electric motor 2, but in this case, Since the hydraulic pressure chamber 16 on the rear surface of the piston 15 is in an unpressurized state, no force is generated for the piston 15 to press the pressure plate 12 to the right, and therefore the rotor member 10.10 is moved toward the stator. This means that it can freely rotate relative to the members 11...11.

On the other hand, when a brake command is issued, the hydraulic chamber 1
6 becomes pressurized, and accordingly, the piston 15 moves to the right, presses the pressure plate 12, and presses the rotor member 1.
0.10 and the stator members 11...11 are pressed against the stopper plate 13, and due to the mutual friction between the rotor member 10.10 and the stator members 11... As a result, the hollow shaft 9 and rotor shaft 3 stop rotating. In this case, the amount of heat generated during braking of the vehicle is
．． 10 and stator members 11...11, and is dispersed as frictional heat at multiple locations, the amount of heat generated by each member 10, 10, 11...11 is greatly reduced. This will be reduced.

Further, the rotor member 10.10 and the stator member 11
-11 to C/C combo lift (Carbon / Ca
If the C/C combo lift is configured with carbon fiber carbon fibers, even if each of the above-mentioned members 10, 10, 11, . . . The resin,
Since it is a carbon fiber/carbon composite material manufactured by performing carbonization and graphitization heat treatment after bond-strengthening with pitch etc., as shown in Figure 8, its temperature characteristics are the same as those of steel as indicated by symbol (A). Although it has a curved line, it has high strength under high temperature conditions as shown by symbol (b), so problems such as uneven wear and changes in braking force do not occur.

When the brake command is released, the pressure plate 12 is moved to the left by the force of the compression coil spring 20 of the gap adjustment mechanism 19 and returned to its original position.

The amount of heat generated during braking of the vehicle is transferred to the rotor members 10, 1.
0 and the stator members 11...11, this amount of heat is suitably radiated by the configuration shown below.

That is, the left end of the inner hole 60 of the hollow shaft 9 is opened, and this opening is used as an air supply hole 61.
A filter 62 is attached to the left side of the
The plurality of key members 8...8 include rotor members 10.
A thin metal ring plate 63 (for example, made of stainless steel) is attached so as to cover the entire outer periphery of the stator members 10 and stator members 11 . . . 11 .

As shown in FIG. 6, this metal ring plate 63 is formed by forming a metal plate into an annular shape, and has pores 63 through which dust generated by friction between the rotor member 10 and the stator member 11 passes as necessary.
It is formed by forming a large number of a. Incidentally, the illustrated one shows a state in which the key member 8 is fixed with a rivet 63b. The air taken in from the air supply hole 61 passes through the through holes 64 and 65 bored at both left and right ends of the hollow shaft 9, and as shown by the arrows X and y, the air enters the pressure plate 12. A slit 14a formed by the gap between the outer surface and the case left side wall 7b, the passage groove 12b of the pressure plate 12 and the protrusion 12c, and the stopper plate 1
The gap (slit 1
4), further passes through a passage chamber 66 formed on the circumference between the metal ring plate 63 and the inner circumferential surface of the case, and the lid of a discharge chamber 67 provided at the lower part of this passage chamber 66. The air is discharged outward from an air outlet 68a provided with a filter 69 in the member 68. As the cooling air passes through in this manner, heat is radiated from the pressure plate 12, the stopper plate 13, and the metal ring plate 63, and the rotor members 10, 10
And an excessive temperature rise of the stator members II...11 is prevented.

Furthermore, in the case where the hollow shaft 9 and the rotor shaft 3 are an integrated rotating shaft, the heat generated during braking of the vehicle is directly conducted to the bearings. However, this may lead to problems such as early damage to the bearings.
In this embodiment, the following configuration is adopted in order to suppress the above-mentioned heat conduction as much as possible.

That is,! As shown in Figure @7, the hollow shaft 9 and the rotor shaft 3 are constructed separately, and a heat insulating cuff ring 70 is interposed between them. Specifically, the hollow shaft 9
An engaging uneven surface 9a is formed on the right end of the rotor shaft 3, and this engaging uneven surface 9a and an engaging uneven surface 70a formed on the left end of the heat insulating compression ring 70 are engaged and connected. An engaging uneven surface 3b is also formed at the left end of the engaging uneven surface 3b and the heat insulating compression ring 70.
The mating concave and convex surface 70b formed on the right end of the mating surface 70b is mated with the concavo-convex surface 70b. According to such a configuration, heat conduction from the hollow shaft 9 to the rotor shaft 3 is suitably reduced,
This effectively prevents a problem in which the temperature of the rotor shaft 3 increases due to braking of the vehicle.

〔Effect of the invention〕

As described above, according to the present invention, by using a multi-plate disc brake device having a plurality of rotor members and a plurality of stator members as a brake device for a railway vehicle, braking of the vehicle can be achieved. The heat that is generated at times is dispersed as frictional heat generated at multiple locations between each member, reducing the amount of heat generated by each member, resulting in problems such as uneven wear and shortened lifespan. In addition to avoiding this, there are also advantages in that the device can be made more compact and easier to install.

Furthermore, the cooling air introduced from the air inlet of the hollow shaft is guided through the outer surfaces of the pressure plate and the stopper plate to a passage chamber provided on the circumference between the metal ring plate and the case member and discharged. Therefore, the frictional heat generated between the rotor member and the stator member during braking is also absorbed through the pressure plate and the stopper plate, and it is possible to prevent the inside of the case member from becoming high in temperature.

[Brief explanation of the drawing]

1 to 8 show embodiments of the present invention.
The figure is a schematic front view showing the installed state of the disc brake device for a railway vehicle, Figure 2 is a longitudinal sectional side view of the main part showing the internal structure of the disc brake device for a railway vehicle, and Figure 3 is the inside of the disc brake device for a railway vehicle. Fig. 4 is an explanatory view of the pressure plate, Fig. 5 is an explanatory view of the stopper plate, Fig. 6 is a perspective explanatory view of the metal ring plate, Fig. 7 is an explanatory view of the main part showing the structure.
The figure is a perspective view of the exploded arrangement of parts showing the state of connection between the rotor shaft and the hollow shaft, and FIG. 8 is a graph showing the characteristics of the C/C composite. Further, FIG. 9 is a schematic plan view showing a conventional example, and FIG. 10 is a schematic plan view showing another conventional example. 1... Disc brake device 3... Rotor shaft (rotating shaft) 5... Axle 7... Case member 8... Key member 9... Hollow shaft (rotating shaft) 10... Rotor Member (plate member) 11... Stator member (plate member) 15... Pressing member (piston) 61... Air supply hole 63... Metal ring plate 66... Passage chamber

Claims (1)

[Claims] (1) At the end of the rotating shaft connected to the axle of the railway vehicle, a plurality of rotor members that rotate together with the rotating shaft and are slidable in the axial direction, and a key member that is disposed between the rotor members. A plurality of stator members are slidably attached only in the axial direction, plate members are provided on both sides of the rotor member and the stator member, and braking force is applied to the rotor member and the stator member through these plate members. a case member that includes the rotor member and the stator member; and a metal ring plate provided on a circumference between the outer periphery of the rotor member and the stator member and the case member; forming a passage chamber on a circumference between the plate and the case member, and forming an air supply hole opening toward the outer surface of the plate member by forming an end of the rotating shaft into a hollow shape; A disc brake device for a railway vehicle, characterized in that cooling air is discharged from the rotating shaft into a passage chamber through the outer surface of a plate member.