0001]The present invention relates to a disc brake which is used as a braking device for rail vehicles, in particular, the wheel or the brake lining is pressed against the sliding surface of the fixed brake disc to the axle, and a railway disc brake for a vehicle having the same.
BACKGROUND
[0002]Recently, railway vehicles, automobiles, as a braking device for land transportation vehicles such as motorcycles, with the speed and size of the vehicle, has become much that the disk brake is used. Disc brake is a device for obtaining a braking force by the friction due to sliding between the brake disc and the brake linings.
[0003]
　For disc brake for a railway vehicle, a donut-shaped circular plate-shaped brake disk fixed mounted on wheels or axles, the sliding surface of the brake disc, to generate a braking force by pressing the brake lining by a brake caliper . Accordingly, by braking the rotation of the wheel or axle, to decelerate the moving and the vehicle.
[0004]
　In the disc brake, during braking, noise, called a "brake squeal" occurs. Brake squeal is thought to occur to produce the unstable vibration entire brake unit is called "self-excited vibration". Such vibration is caused by friction when pressed against a brake lining to the brake disc during braking. The self-excited vibration, changing a steady energy excitation energy at the inside of the system from the outside, a vibration amplitude is increased by vibrating itself. To reduce brake noise, it is necessary to suppress the self-excited vibration generated by friction during braking.
[0005]
　Patent Document 1, the brake disc, configured disk brake so as to press the pads is disclosed through the piston. This disc brake pad is moved to the trailing side (touch end side) is the downstream side in the rotational direction of the brake disc by frictional resistance when pressed to the brake disk. Thus, the contact area of ​​the piston of the pad, as compared with the leading side is the upstream side in the rotating direction of the brake disc, it is larger in the trailing side. With this configuration, by suppressing the self-excited vibration, there is a brake noise can be suppressed.
[0006]
　Patent Document 2, the brake linings is disclosed that includes a substrate and a plurality of friction members. Each friction member is attached to the substrate via an elastic member. Support rigidity of the elastic member is different to the position of the friction member on the substrate. With this configuration, there is a brake noise can be suppressed.
[0007]
　Patent Document 3, the brake linings is disclosed that includes a substrate and a plurality of friction members. Figure 1 is a plan view showing a structure of a brake lining disclosed in Patent Document 3. Each friction member 3 is attached to the substrate 6 through an elastic member. Two adjacent friction member 3 is connected by a plate-like member 4.
CITATION
Patent Document
[0008]
Patent Document 1: JP 2002-340056 Patent Publication
Patent Document 2: JP 2011-214629 Patent Publication
Patent Document 3: JP 2012-251597 JP
Summary of the Invention
Problems that the Invention is to Solve
[0009]
　Was the technique disclosed in Patent Document 1, to be applied to existing vehicles, not only the brake linings, this must be changed to a brake caliper for applying a pressing force, affect the overall disc brake design . Therefore, it is very difficult to apply this technique to an existing vehicle.
[0010]
　In the configuration of the brake lining in Patent Document 2, the support rigidity of the elastic member, it is necessary to change the position on the substrate, the production management becomes complicated.
[0011]
　The two friction members in the brake lining of Patent Document 3 are connected by a plate-like member, rotation of the friction member, and it is an object to suppress the variation of the friction coefficient of the respective frictional member. In Patent Document 3, considering for reducing brake noise is not made.
[0012]
　Accordingly, an object of the present invention is to provide a brake lining and the disc brakes, it is possible to easily reduce brake noise.
Means for Solving the Problems
[0013]
　Brake lining according to this embodiment, a brake lining which is pressed against the sliding surface of the brake disc fixed to a wheel or an axle of a railway vehicle,
　each of the surface opposite to the sliding surface of the brake disc, respectively a plurality of friction members but which are disposed with a gap from each other,
　and a back plate fixed to the back surface of the friction member,
　a substrate of the respective friction member, to support in the region including the central portion of the friction member,
　the friction the back side of the member, and an elastic member interposed between the back plate and the substrate,
　each other and adjacent two of said friction member pair, is secured to the pair of friction members It said a backing plate integrally,
　in any of the set of friction members, two of said friction member, wherein are arranged along the circumferential direction of the brake disk, a brake lining for railway vehicles.
[0014]
　Disc brake of this embodiment, a brake disc fixed to a wheel or an axle of a railway vehicle,
　is pressed against the sliding surface of the brake disc, with a, and the brake lining, a disc brake.
Effect of the invention
[0015]
　Brake linings and disc brake, of the present invention, it is possible to reduce brake noise. The brake lining of the present invention is easy to apply to existing vehicles, it is easy to manufacture management.
BRIEF DESCRIPTION OF THE DRAWINGS
[0016]
[1] Figure 1 is a plan view of a conventional brake linings.
FIG. 2 is a perspective view showing the amplitude distribution generated during braking of a conventional brake lining.
[Figure 3A] Figure 3A is a plan view of a brake lining according to one embodiment of the present invention.
[Figure 3B] Figure 3B is a B-B sectional view of FIG. 3A.
[Figure 4A] Figure 4A is a plan view for explaining the inclination angle of the pair of friction members.
[Figure 4B] Figure 4B is a plan view showing a range of pressing pressure in the brake lining is applied.
[Figure 4C] Figure 4C is a plan view for explaining the inclination angle of the pair of friction members disposed near the brake lining ends.
[Figure 5A] Figure 5A is a plan view of a brake lining provided in the disc brake of the present invention embodiment.
[Figure 5B] Figure 5B is a plan view of a brake lining provided in the disc brake of Comparative Example 1.
[Figure 5C] Figure 5C is a plan view of a brake lining provided in the disc brake of Comparative Example 2.
FIG. 6 is an example invention, the brake lining provided respectively to the disc brake of Example 1, and Example 2 is a diagram showing the ratio of the maximum squeal indicators.
DESCRIPTION OF THE INVENTION
[0017]
　The present inventors have, a conventional brake lining shown in FIG. 1, by two arrangement directions of the friction member 3 in a set of the friction member 3, the amplitude of Unstable oscillation mode of the friction member 3 is found different .
[0018]
　Figure 2 is a perspective view showing the amplitude distribution generated during braking of a conventional brake lining. Distribution of the amplitudes are those obtained by analysis by FEM (finite element method). 2, close to black (darker) as part larger amplitude unstable oscillation mode.
[0019]
　From Figure 2, the amplitude of the unstable vibration mode, the arrangement direction of the two friction members 3, (in FIG. 2, indicated by broken lines.) Circumferential direction of the brake disc when in line with the smaller diameter direction of the brake disc and if large it can be seen along the. Of Unstable vibration modes of the vibration of the friction member 3, such vibration is a major factor in brake noise. In this brake lining, an intermediate portion in the direction along the circumferential direction of the brake disc (center line bisecting the brake lining in the longitudinal direction), are arranged a pair of friction members 3, the pair of friction members excessive vibration occurs to concentrate on.
[0020]
　Railway vehicle brake lining of the present invention and the disc brake, it is has been completed based on these findings. Brake lining according to the invention, as described above, each of the surface faces the sliding surface of the brake disc, and a plurality of friction members that are each disposed with a gap from one another, are secured to the back surface of the friction member and the back plate is, the respective friction member, a substrate supporting in the region including the central portion of the friction member, the back side of the friction member, and an elastic member interposed between the substrate and the back plate, the It is provided. As a set of two adjacent friction members together, the back plate fixed to the pair of friction members are integral. In any set of friction members, the two friction members are arranged along the circumferential direction of the brake disc.
[0021]
　Disc brake of the present invention comprises a brake disc fixed to a wheel or an axle of a railway vehicle, and the brake lining is pressed against the sliding surface of the brake disc, the.
[0022]
　Hereinafter, the railway vehicle disc brake of the present invention will be described in detail embodiments thereof.
　3A and 3B are diagrams showing an example of a brake lining provided in the disc brake for a railway vehicle according to the present invention. Figure 3A, a plan view of a brake lining, in Figure 3B, a sectional view taken along line B-B in FIG. 3A, respectively. Figure 3A shows a state viewed brake lining, from the brake disc side, which is the surface side.
[0023]
　Disc brake of the present invention, as shown in FIG. 3B, includes a brake disc 1, the brake lining 2, a. Brake lining 2 is attached to a brake caliper (not shown). Brake disc 1, in plan view, a donut-shaped disk shape. Brake disc 1 is attached by bolts to a wheel or an axle (not shown) and is firmly fixed.
[0024]
　Brake caliper is actuated during braking, it is pressed against the brake lining 2 on the sliding surface 1a of the brake disc 1. Accordingly, friction due to sliding between the brake disc 1 and the brake lining 2 occurs, the braking force is generated. Thus, disc brakes, brake the rotation of the wheel or axle, to decelerate the moving and the vehicle.
[0025]
　Brake lining 2 includes a plurality of friction members 3, a back plate 4, the elastic member 5, a substrate 6 to hold all of these, the. A plurality of friction members 3 are disposed with a gap from each other. Surface of the friction member 3 is opposed to the sliding surface 1a of the brake disc 1.
[0026]
　Friction members 3 are sintered copper material, made of a resin material. Friction members 3 are in the embodiment shown in FIG. 3A, the plane shape is circular, and each other, have substantially the same diameter. At the center of the friction member 3, the small holes 3a are formed. This is the small hole 3a, the rivet 7 is inserted, the rivet 7, the friction member 3 is attached to the substrate 6. The planar shape of the friction member 3 is not limited to a circular shape, for example, a square, or a polygon such as a hexagon.
[0027]
　The back surface of the friction member 3, in order to maintain its strength and rigidity, a back plate 4 made of a thin metal plate such as steel is fixed. Together two friction member 3 adjacent the pair, with respect to the set of the friction member 3, one of the back plate 4 is provided. Backing plate 4 is of the integral over the friction member 3 both constituting the friction member 3 of the pair. A pair of friction members 3 are in a state of being connected with the back plate 4. Number of sets of the friction member 3 is not particularly limited. Of the friction member 3 both set, since the two friction member 3, the total number of the friction member 3 is an even number.
[0028]
　Back plate 4, in this embodiment, the connecting portion connecting the substantially the same size and the disc portion of the shape as each of the pair of friction members 3 in a plan view, these two disc portion (see FIG. 3A) with the door. Width of the connecting portion (the length in the direction orthogonal to the longitudinal direction of the back plate 4) is smaller than the width of the disk portion. Thus, back plate 4 as a whole has a shape constricted in the longitudinal direction intermediate portion.
[0029]
　Also in the friction member 3 of one pair, two friction members 3, (FIG. 3A, indicated by broken lines.) Circumferential direction of the brake disk are arranged in the. Set of friction members are arranged along the radial direction of the brake disc 1 3 is not present.
[0030]
　Here, the arrangement direction of the two friction members 3 forming the set may not exactly match the circumferential direction of the brake disk 1, some tilt from the circumferential direction is allowed. In the present invention, "the friction member 3 is arranged along the circumferential direction of the brake disc" The inclination angle θ is defined below, means that at 45 ° or less.
[0031]
　Figure 4A is a plan view for explaining the inclination angle of the pair of friction members. In one set of the friction member 3, a straight line passing through the center of the friction member 3 and L1, the midpoint of the centers of both the friction member 3 and P. The straight line L1 corresponds to the array direction of the friction member 3. A circle passing through the middle point P around the center C of the brake disc 1 and A. The tangent of the circle A at the midpoint P and L2. Tangent L2 corresponds to the circumferential direction of the brake disk 1 at the mid-point P. The angle θ formed by the straight line L1 and tangent L2 and the tilt angle. However, the inclination angle θ of when the L1 and L2 are matched, and 0 °. When the planar shape of the friction member 3 is not circular, in the above definition, "center" is assumed to be "the center of gravity."
[0032]
　Each friction member 3, together with the back plate 4 is attached to the substrate 6 by rivets 7 inserted through a small hole 3a in the center of each of the friction member 3. That is, the friction member 3 is in the region including the central portion of the friction member 3, by a rivet 7, and is supported by the substrate 6. The back side of the friction member 3, between the back plate 4 and the substrate 6, the elastic member 5 is interposed. Thus, a plurality of friction member 3 is in a state of being individually resiliently supported. As the elastic member 5, FIG. 3B, is exemplified a disc spring, it may be employed a leaf spring or a coil spring.
[0033]
　Back plate 4, when the external force is applied, is deformable. Therefore, at the time of braking, the friction member 3 is individually movable. Thus, it is possible to equalize the contact pressure between the brake linings 2 and the brake disk 1 during braking.
[0034]
　Further, a pair of friction members 3, by being in a state of being connected with the back plate 4 integral, as compared with the case not coupled in the back plate, the movement is restricted. Therefore, regardless of the running speed of the brake start time, the coefficient of friction between the brake disc 1 and the brake lining 2 can be stabilized.
[0035]
　Moreover, a pair of friction members 3, since it is fastened to the substrate 6 by two rivets 7, during braking, not be rotated about the center of a pair of friction members 3, the substrate 6 it is possible to prevent the looseness in the connection occurs. Even if the slack in their fastening portion has occurred, so long as the fastening portions of the two positions is not damaged at the same time, it does not have the friction member 3 落失 immediately. Therefore, it is possible to ensure sufficient durability and reliability of the disc brake.
[0036]
　Moreover, the friction member 3, because the position of the rivet 7 just below the center in the supporting point is resiliently supported, never be greatly inclined moving in contact with the brake disk 1 during braking, the contact surface There were uniformly worn over the entire region, uneven wear does not occur.
[0037]
　As described above, even in the friction member 3 of one pair, the arrangement direction of the arrangement direction of the two friction members 3, and two rivet 7 (fastening member) is along the circumferential direction of the brake disk 1 , a set of friction members are arranged along the radial direction of the brake disc 1 3 is not present. Therefore, for any of the friction member 3, when the vibration during braking, the amplitude of the unstable vibration mode is small. Thus, it is possible to reduce brake noise. To achieve this effect, the inclination angle θ is more preferably preferably at 25 ° or less, 15 ° or less.
[0038]
　In general, the inclination angle θ can be reduced to about brake noise close to 0 °. However, in certain cases, the inclination angle θ is better to a particular size of angle other than 0 ° can be reduced brake squeal. The following describes such a case.
[0039]
　Figure 4B is a plan view showing a range of pressing pressure in the brake lining is applied. (The surface on which the friction member 3 is provided a surface on the opposite side) back surface of the substrate 6, the pressure is applied pressed by the brake caliper. Shaded portion in FIG. 4B is pressed against the pressure applied region (hereinafter, referred to as "press area".) Is an example of a P. In the brake lining 2, the friction member is, generally-are arranged along two circles concentric. 3 pairs along the outer circle and (6) a friction member 3out is sequence of three pairs of friction members 3in along the inside of the circle are arranged.
[0040]
　Any of the friction member 3 (friction member 3out and the friction member 3in) also has a portion which does not fall within the press area P. In the outer friction member set of friction members disposed on both longitudinal end sides of the substrate 6 of 3out 3out, portions not within the pressing region P is small. In addition, even a pair of friction members 3in disposed at the center in the longitudinal direction of the substrate 6 of the inner friction member 3in, although parts that do not fall within the pressing region P is greater than a set of friction members 3out above, for the most part fall within the press area P.
[0041]
　On the other hand, the friction member 3 other than the above portion is often not enter the press area P. In two sets of friction members 3in arranged longitudinally opposite ends of the substrate 6 of the inner friction member 3in, most often part not within the press area P. In the friction member 3, parts that do not fall into the pressing territory within P is likely to vibrate than the part falling within the pressing region P. Such a vibration can be a cause of brake squeal.
[0042]
　Figure 4C is, in the brake lining is a plan view for explaining the inclination angle of the pair of friction members disposed on the inner end portion. If the inclination angle θ by rotating the pair of friction members 3in around the midpoint of the centers of both the friction members 3in was 0 °, the pair of friction members 3in, as indicated by a broken line in FIG. 4C To position. In this case, the friction member 3in longitudinal end side of the substrate 6 of the pair of friction members 3in the most part, specifically, about 70% of the area is not within the press area P. Thus, the friction member 3in is easy to vibrate, may increase the brake noise.
[0043]
　In the embodiment shown in FIG. 4C, a pair of friction members 3in the inner end, so that the angle between the edge of the pressing region P crossing the opposing direction and these friction members 3in these friction members 3in smaller the inclination angle θ is attached to. Inclination angle θ is 10 ~ 20 °, for example, 15 °. With this configuration, for any of the friction member 3in of this pair of frictional members 3in, the ratio of the portion not enter the press area P has a 60% or less by area. Therefore, compared to when the inclination angle θ was 0 °, the vibration is suppressed as a whole, it can be reduced brake squeal.
[0044]
　Referring to FIG. 3A, the substrate 6, the intermediate portion in the direction along the circumferential direction of the brake disc 1, the friction member 3 is not disposed. This also amplitude unstable oscillation mode of the friction member 3 is reduced, the brake squeal is reduced.
[0045]
　When applying the configuration of the brake linings in existing vehicles, for example, only the arrangement direction of the friction member, sufficient if changed to a proper direction, it is not necessary to change the brake caliper or the like. Further, in this brake lining, the support rigidity of the elastic member 5 does not need to be changed depending on the position on the substrate 6. Thus, the brake lining 2, as well it is easy to apply to existing vehicles, it is easy to manufacture management.
Example
[0046]
　In order to confirm the effect of the present invention, three types of brake lining for each (present invention examples, the brake lining of Comparative Example 1, and Comparative Example 2) was evaluated squeal index. Squeal index was determined from the results of analysis by FEM (finite element method). Specifically, first, the FEM complex eigenvalue analysis, was calculated damping ratio of the vibration for each frequency. Among them, those negative value, i.e., the unstable, total for each frequency range of 1/3-octave bands was determined and the absolute value. Among the values ​​of each band, to extract the largest one, it was used as an index squeal it. As the value of brake noise index is small, the brake noise hardly occurs, it means that small that sound even when brake noise occurs.
[0047]
　FIGS. 5A ~ 5C are a plan view of the brake lining which is subject to analysis. Any of the brake lining, is provided with six pairs of the friction member (12 friction members).
[0048]
　Figure 5A is a plan view of a brake lining provided in the disc brake of the present invention embodiment. In this brake lining, all pairs of the friction member, are arranged along the circumferential direction of the brake disc.
[0049]
　Figure 5B is a plan view of a brake lining provided in the disc brake of Comparative Example 1. The brake lining includes four sets of friction members which are arranged along the circumferential direction of the brake disc, and two pairs of friction members arranged along the radial direction of the brake disc.
[0050]
　Figure 5C is a plan view of a brake lining provided in the disc brake of Comparative Example 2. In this brake lining, all pairs of the friction member, the radial direction of the brake disc
are arranged in the.
[0051]
　Figure 6 shows the ratio of the maximum squeal indication of these brake lining. In Figure 6, when the first reference value of squeal index of Comparative Example 1, shows a relative value. As shown in FIG. 6, the magnitude of the maximum squeal indicators, in the present invention example while being reduced by about 20% Comparative Example 1, is about three times that of Comparative Example 2 Comparative Example 1.
[0052]
　Magnitude of the maximum squeal index is correlated with the number of arranged along the radial direction of the brake disc (circumferential direction are not arranged along) pair of friction members, a large number of the sets of friction member about, maximum squeal index increases. That is, by Haisuru a set of friction members that are not arranged along the circumferential direction of the brake disc, it was confirmed that the reduced brake squeal.
Industrial Applicability
[0053]
　Railway vehicle disc brake of the present invention, any railway vehicle can be effectively utilized, inter alia, the travel speed is useful for high-speed railway vehicle as the wide from low speed to high speed.
DESCRIPTION OF SYMBOLS
[0054]
　　1: brake disc, 1a: sliding surface, 2: brake lining, 3: Friction member, 4: back plate, 5: elastic member, 6: substrate 7: Rivet

WE CLAIM

A brake lining pressed against the sliding surface of the brake disc fixed to a wheel or an axle of a railway vehicle,
　each of the surface opposite to the sliding surface of the brake disc, each of which is disposed with a gap from each other a plurality of friction members,
　and a back plate fixed to the back surface of the friction member,
　each friction member, a substrate supporting in the region including the central portion of the friction member,
　the back side of the friction member, said substrate and and an elastic member interposed between the back plate,
　together with the adjacent two of the friction members a set, the back plate fixed to the pair of friction members are integral ,
　in any of the set of friction members, two of said friction member, wherein are arranged along the circumferential direction of the brake disc, brake linings for railway vehicles.
[Requested item 2]
　A brake lining according to claim 1,
　in the substrate, an intermediate portion in the direction along the circumferential direction of the brake disc, the friction member is not disposed, the brake linings.
[Requested item 3]
　And the brake disc fixed to a wheel or an axle of a railway vehicle,
　is pressed against the sliding surface of the brake disc, comprising a brake lining according to claim 1 or 2, disc brakes.