0001]The present invention relates to a disc brake device. More particularly, to a disc brake device of a railway vehicle.
BACKGROUND
[0002]In recent years, with the speeding up of railway vehicles, the disc brake system is widely used in the braking of the rail vehicle. In the disk brake system, brake caliper give a load to the brake lining. As a result, the brake lining is pressed against the brake disk. Disc brake system, to obtain a braking force by friction between the friction member and the brake disc of the brake linings.
[0003]
　Friction between the friction member and the brake disc of the brake lining increases the temperature of the brake disc. If the brake caliper is less locations loaded in any of the brake lining, in particular the temperature of the brake disc is likely to rise. If the temperature of the brake disc is excessively increased, the brake disc and brake lining is worn early. Therefore, excessive temperature rise of the brake disc, it is desirable to suppress.
[0004]
　Suppressing disc brake device the temperature rise of the brake disc, for example, it is described in JP-A-2009-257578 (Patent Document 1) and JP 2014-59011 (Patent Document 2).
[0005]
　Disc brake device described in Patent Document 1 is provided with a brake caliper having a plurality of pressing surfaces. In the disc brake device of Patent Document 1, a load is applied from the plurality of pressing surfaces on the brake lining. Therefore, the load applied from the brake caliper on the brake lining is dispersed. Pressure applied from the brake linings to the brake disk is reduced. This can suppress the wear of the brake disc and brake linings, the temperature rise of the brake disc and brake lining during braking can be suppressed, and is described in Patent Document 1.
[0006]
　Disc brake device described in Patent Document 2 is provided with a brake lining comprising a plurality of friction members, and a swinging adjustment mechanism for supporting a plurality of friction members. Swinging adjustment mechanism, it can be loaded in each of the plurality of friction members. Therefore, even if there is unevenness on the sliding surface of the brake disc, it can be pressed against the respective friction member to the brake disk. Therefore, the pressure applied from one friction member to the brake disk is reduced. Accordingly, the temperature of the brake disc can be prevented from being locally increased, it is possible to suppress the heat crack of the brake disc, and is described in Patent Document 2.
CITATION
Patent Document
[0007]
Patent Document 1: JP 2009-257578 Patent Publication
Patent Document 2: JP 2014-59011 JP
Summary of the Invention
Problems that the Invention is to Solve
[0008]
　Brake disk is fastened to the wheels by means of bolts. Disc brake device of Patent Document 1 and Patent Document 2, in order to suppress the temperature rise of the local brake disc, the temperature of the brake disc does not rise excessively. Therefore, the friction member and the brake disc of the brake lining is hard to wear prematurely.
[0009]
　However, in the disc brake device of Patent Document 1, the load applied from the pressing surface on the brake linings are equal. In the disc brake device of Patent Document 2, the load applied from the swing adjusting mechanism each friction member are equal. If this way so as to uniformly press the entire sliding surface of the brake disc, there are cases where stress is loaded to the bolt to secure the brake disc to the wheel is increased.
[0010]
　An object of the present invention, while suppressing the local temperature rise of the brake disc is to provide a disc brake device capable of suppressing the stress loaded on the further bolt.
Means for Solving the Problems
[0011]
　Disc brake device of the present embodiment, to brake a wheel attached to the axle. Disc brake device includes a brake disk, a brake lining, a brake caliper, a. Brake disk has a plurality of bolt holes arranged on the sliding surface and on the same circumference. Brake disc is fastened to the wheel by a threaded to each of a plurality of bolt holes volts. Brake lining faces the brake disc. Brake lining includes a friction member, and a substrate supporting the friction member. Brake caliper, pressed against the sliding surface of the friction member by giving a load to the back of the substrate. The back surface of the substrate is divided into an inner and outer regions by an arc-shaped boundary about the axis of the axle. When projected onto a plurality of bolt holes in the direction of the axle on the back of the substrate, the boundary passes through a region of a plurality of bolt holes projected. Brake caliper comprises an inner pressing surface which gives a load to the inner region, and an outer pressing surface which gives a load to the outer region. Load applied from the inner pressing surfaces in the inner area is different from the load given from the outside pressing surface on the outside area.
Effect of the invention
[0012]
　Disc brake device according to the present invention, while suppressing the local temperature rise of the brake disc, can be suppressed the stress loaded on the further bolt.
BRIEF DESCRIPTION OF THE DRAWINGS
[0013]
[1] Figure 1 is a front view of the disc brake device of the first embodiment from the direction of the axle.
FIG. 2 is a sectional view taken along the line II-II in FIG.
FIG. 3 is a perspective view of a brake lining.
[4] FIG. 4 is a front view of the brake lining and the brake caliper in the direction of the axle.
FIG. 5 is a rear brake lining is a diagram showing an inner pressing surface and an outer pressing surface.
FIG. 6 is a cross-sectional view of the disc brake device of the second embodiment.
[7] FIG. 7 is a perspective view of the brake lining and the brake caliper.
[8] FIG. 8 is a front view of the brake caliper in the direction of the axle.
[9] FIG. 9 is a cross-sectional view of the brake lining and the brake caliper according to the third embodiment.
[10] FIG 10 is a front view of the FEM analysis model of Example 1.
[11] FIG. 11 is a sectional view taken along line XI-XI in FIG. 10.
[12] FIG 12 is a diagram showing the heat input distribution in the brake disc in test numbers 1-4.
[13] FIG 13 is a diagram showing the heat input distribution in the brake disc in test numbers 5-9.
[14] FIG 14 is a diagram showing the relative values of the bolt safety factor for the test numbers 9.
[15] FIG 15 is a cross-sectional view of the FEM analysis model of Example 2.
[16] FIG 16 is a diagram showing the heat input distribution in the brake disc in test No. 10 to 12 and 17.
[17] FIG 17 is a diagram showing the heat input distribution in the brake disc with the test numbers 13 and 14.
[18] FIG 18 is a diagram showing the heat input distribution in the brake disc with the test numbers 15 and 16.
[19] FIG 19 is a diagram showing the relative values of the bolt safety factor for the test No. 17.
DESCRIPTION OF THE INVENTION
[0014]
　(1) The disc brake device of the present embodiment, to brake the wheels attached to the axle. Disc brake device includes a brake disk, a brake lining, a brake caliper, a. Brake disk has a plurality of bolt holes arranged on the sliding surface and on the same circumference. Brake disc is fastened to the wheel by a threaded to each of a plurality of bolt holes volts. Brake lining faces the brake disc. Brake lining includes a friction member, and a substrate supporting the friction member. Brake caliper, pressed against the sliding surface of the friction member by giving a load to the back of the substrate. The back surface of the substrate is divided into an inner and outer regions by an arc-shaped boundary about the axis of the axle. When projected onto a plurality of bolt holes in the direction of the axle on the back of the substrate, the boundary passes through a region of a plurality of bolt holes projected. Brake caliper comprises an inner pressing surface which gives a load to the inner region, and an outer pressing surface which gives a load to the outer region. Load applied from the inner pressing surfaces in the inner area is different from the load given from the outside pressing surface on the outside area.
[0015]
　In the disc brake device of the present embodiment, a load is applied from the plurality of pressing surfaces of the brake caliper on the brake lining. Therefore, the load applied from one of the pressing surfaces in the brake lining is reduced. The maximum value of the heat flux applied to the brake disc is reduced by the friction between the brake lining and the brake disc. Accordingly, local temperature rise of the brake disc can be suppressed.
[0016]
　Further, in the disc brake device of the present embodiment, the load applied from the inner pressing surfaces of the brake caliper in the inner area of ​​the brake linings is different from the load given from the outside pressing surface on the outside area. Therefore, when the brake linings are pressed against the brake disk, in the radial direction of the brake disc, the heat input distribution in the brake disc due to friction between the brake lining and the brake disc is non-uniform. As described in Example 1 to be described later, the heat input distribution in the brake disc if heterogeneous, stress loaded on the bolt for fastening the brake disc and the wheel is suppressed.
[0017]
　(2) In the disc brake device of the above (1), among from the load and an outer pressing surface given by the inner pressing surfaces in the inner area of ​​the load applied to the outer region, a better load and smaller loads of great ratio of 1.3 or more and 6.0 or less.
[0018]
　According to this structure, when the brake linings are pressed against the brake disk, in the radial direction of the brake disc, the heat input distribution in the brake disc is nonuniform without becoming locally high. Therefore, stress loaded to the bolt is further suppressed.
[0019]
　(3) Preferably, the inner pressing surfaces in the disc brake device, among the load and an outer pressing surface given by the inner pressing surfaces in the inner area of ​​the load applied to the outer region, which receives loads in the larger of (1) or the outer pressing surface of the brake disk ratio of the radial width of the sliding surface of the width and the brake disc in the radial direction is 0.4 or more, the inner pressing surfaces or outer pressing surface receives loads in smaller the ratio of the radial width of the sliding surface of the width and the brake disc in the radial direction of the brake disk is 0.25 or more.
[0020]
　According to such a configuration, a small load per unit area applied from the inner pressing surface and an outer pressing surface on the brake lining. Therefore, when the brake linings are pressed against the brake disc, the maximum value of the heat flux to the brake disc due to friction between the brake lining and the brake disc is reduced. Accordingly, local temperature rise of the brake disc can be suppressed.
[0021]
　The above disc brake device may employ the following configuration.
[0022]
　(4) In the disc brake device of the above (1), the brake caliper comprises a plurality of inner pressing surfaces, and a plurality of outer pressing surface. Total load applied from a plurality of inner pressing surfaces in the inner area is different from the total load supplied from a plurality of outer pressing surface on the outside area.
[0023]
　(5) In the disc brake device of the above (1), the brake caliper includes one inner pressing surfaces, and a plurality of outer pressing surface. Load applied to the inner region from one inner pressing surface differs from the total load supplied from a plurality of outer pressing surface on the outside area.
[0024]
　(6) In the disc brake device of the above (1), the brake caliper comprises a plurality of inner pressing surface, and one outer pressing surface. The total load applied to the inner region of a plurality of inner pressing surfaces, different from one outer pressing surface and the load applied to the outer region.
[0025]
　(7) In the disc brake device of the above (1), the brake caliper includes a pressing plate, an inner member including an inner pressing surface, an outer member including an outer pressing surface, and the pressing surface. Pressing plate faces the backside of the substrate. The inner member is attached to the inner region and the pressing plate disposed substrate between the plate pressing the inner region of the substrate. The outer member is disposed between the plate pressing the outer region of the substrate is attached to the outer region and the pressing plate of the substrate. Pressing surface gives a load to the back of the pressing plate.
[0026]
　According to such a configuration, rather than providing a load directly to the inner member and the outer member in contact with the brake lining, gives directly pressing plate load. Inner and outer members are sandwiched by the pressing plate and the back of the brake lining. By load is applied to the pressing plate, load is transmitted to the inner member and outer member. Thus, mechanism is not necessary to provide a direct load, respectively inner and outer members. According to the disc brake device of the present embodiment, it is possible to reduce the mechanism for giving a load. Thus, the structure of the disc brake device can be simplified. The disc brake device can be light in weight.
[0027]
　(8) In the disc brake device of the above (7), the inner and outer members, a spring. The spring constant of the inner member is different from the spring constant of the outer member.
[0028]
　According to such a configuration, the spring constant of the spring loaded in any of the inner region of the back surface of the brake lining is different from the spring constant of the spring loaded in any of the outer region. When plate pressed applying a load to the pressing plate is displaced, the displacement of the spring loaded in any of the inner region is the approximately the same as the displacement of the spring loaded in any of the outer region. Therefore, easy unlike load the load applied to the inner region is provided on the outside area.
[0029]
　(9) In the disc brake device of the above (7) or (8), the distance from the center of the pressing surface to the center of the inner member is different from the distance from the center of the pressing surface to the center of the outer member.
[0030]
　According to such a configuration, a load applied to the pressing plate from the pressing surface, it tends to be unevenly transmitted to the inner member and outer member. Therefore, easy unlike load the load applied to the inner region is provided on the outside area.
[0031]
　Hereinafter, with reference to the drawings, an embodiment of the present invention in detail. Its description will not be repeated the same reference numerals designate like or corresponding parts in FIG.
[0032]
　In this specification, the direction of the axle, means in a direction along the axis of the axle.
[0033]
　In the present specification, the inner bearing area, when projected inner pressing surface in the direction of the axle to the brake disc corresponds to the locus in which the inner pressing surfaces drawn on the brake disc. The outer sliding region, when projected outer pressing surface in the direction of the axle to the brake disc corresponds to the locus of the outer pressing surface is drawn on the brake disc.
[0034]
　In this specification, the gap between the inner pressing surface and an outer pressing surface corresponds to a distance in the brake disc radial direction between the inner bearing area and the outer sliding region.
[0035]
　[First Embodiment]
　FIG. 1 is a front view of the disc brake device of the first embodiment from the direction of the axle. Figure 2 is a sectional view taken along line II-II in FIG. Referring to FIGS. 1 and 2, the disk brake apparatus 1 is provided with a brake disc 2, the brake lining 3, and a brake caliper 4. Incidentally, the brake caliper in Fig. 1 are omitted. Disc brake device 1, to brake the wheels 6 attached to the axle 5. In Figure 2, the two brake disks 2, and two brake linings 3, but showing the two brake caliper 4, which are symmetrical. Therefore, in the following, one of the brake disc 2, the one brake lining 3, is described as one of the brake caliper 4. The same applies to the second and third embodiments.
[0036]
　[Brake Disk
　brake disc 2 has a plurality of bolt holes 7. A plurality of bolt holes 7 are disposed on the same circumference P of the brake disc 2. The center of the same circumference P is axis of the axle 5. Brake disc 2 is fastened to the wheel 6 by a bolt 8 which is passed through the plurality of bolt holes 7, respectively. Thus, the brake disc 2 rotates integrally with the wheel 6.
[0037]
　The shape of the brake disk 2 is a disk. The material of the brake disc 2, for example, steel, carbon fiber composite material or the like. Generally, the bolt holes are provided 10-12. However, the number of the plurality of bolt holes 7 is not particularly limited. Brake disc 2 has a sliding surface 11.
[0038]
　[Brake lining]
　FIG 3 is a perspective view of a brake lining. Referring to FIGS. 2 and 3, the brake lining 3, the friction member 9, and a substrate 10. Substrate 10 supports a friction member 9. Brake lining 3 facing the brake disc 2. More specifically, the friction member 9 is opposed to the sliding surface 11 of the brake disc 2. Brake lining 3, to brake the brake disc 2 by being pressed against the brake disc 2. Since the brake disk 2 is fixed to the wheel 6, if the rotation of the brake disk 2 to brake the rotation of the wheel 6 is braked.
[0039]
　Substrate 10 has a front 12, a back 13. The front 12, a plurality of friction members 9 is attached. Between the substrate 10 and the friction member 9, a spring element or the like, it may sandwich the other components. The material of the friction member 9, for example, cast iron, metallic sintered material, a resin (resin) system, and the like. The shape of the friction member 9 is not particularly limited. The shape of the friction member 9, for example, circular, polygonal, or the like. The number of the friction member 9 is not particularly limited. Friction member 9 may be one or may be plural.
[0040]
　Back of the substrate 1013 is divided into an inner region 14 and outer region 15. The inner region 14 and outer region 15 is divided by the boundary 16. Boundary 16 is a circular arc shape centered on the axis of the axle. A plurality of bolt holes 7 shown by a broken line is obtained by projecting a plurality of bolt holes of the brake disk in the direction of the axle on the back 13 of the substrate 10.
[0041]
　Figure 4 is a front view of the brake lining and the brake caliper in the direction of the axle. Referring to FIGS. 3 and 4, the boundary 16, passes through a plurality of bolt holes 7 that are projected.
[0042]
　[Brake caliper]
　with reference to FIGS. 2 and 4, the brake caliper 4 comprises an inner pressing surface 17 and an outer pressing surface 18. Inner pressing surface 17 and the outer pressing surface 18 is opposed to the back 13 of the substrate 10. Inner pressing surface 17 provides a load to the inner region 14. The outer pressing surface 18, giving a load to the outer region 15. More specifically, when the braking of the wheels, the inner pressing surfaces 17 provide a load to the inner region 14, the outer pressing surface 18 gives a load to the outer region 15.
[0043]
　For one brake lining 3, two arms 19 are provided. Arm 19 of each tip is branched into two. Each tip of the branched arm 19, the inner pressing member and the outer pressing member is supported. Inner pressing member includes an inner pressing surface 17, the outer pressure member comprises an outer pressing surface 18. Arm 19 is also connected to the brake cylinder 20. Brake cylinder 20, for example, a pneumatic cylinder, a hydraulic cylinder or the like. The arm 19 includes a fulcrum 21. When the brake cylinder 20 is actuated during braking, the arm 19 rotates about the pivot 21. Brake lining 3 is pressed against the brake disc, can be the inner pressing surfaces 17 provide a load to the inner region 14, an outer pressing surface 18 can be loaded in the outer region 15. According to such a configuration, it is also possible to release the brake lining 3 from the brake disk. The fulcrum 21, the bracket 22 is attached. Bracket 22 is secured to a railway vehicle bogie.
[0044]
　Load applied from the inner pressing surfaces 17 in the inner area 14 is different from the outer pushing surface 18 and the load applied to the outer region 15. To change the load to be applied to the inner region 14 may be adjusted to the length L1 from the fulcrum 21 to the inner pressing surfaces 17. To change a load given to the outer region 15 may be adjusted to the length L2 from the fulcrum 21 to the outer pressing surface 18. Thus, it is possible to adjust the load inside the pressing surface 17 and the outer pressing surface 18 is also supported by the same arm 19, provided to the load and the outer region 15 is provided in the inner region 14.
[0045]
　[Ratio of the load applied to the load and an outer region provided in the inner area]
　from the inner pressing surfaces 17 and the load applied to the inner region 14 P1, the load from the outer pushing surface 18 provided to the outer region 15 and P2 . Of loads P1 and the load P2, the ratio PL / PS to the load PL and smaller loads PS of the larger, 1.3 or more, preferably 6.0 or less. For example, in the case of P1> P2, it is a PL / PS = P1 / P2. Thus, stress is loaded to the bolt as shown in Example 1 to be described later is further suppressed.
[0046]
　If PL / PS is less than 1.3, in the radial direction of the brake disc, nearly uniform heat input distribution in the brake disc. Therefore, the lower limit of PL / PS is preferably 1.3. However, even in PL / PS is less than 1.3, or greater than PL / PS 1.0. If PL / PS is greater than 1.0, because the heat input distribution in the brake disc becomes uneven.
[0047]
　If PL / PS is greater than 6.0, in the radial direction of the brake disc 2, the heat input distribution in the brake disc 2 is increased locally. Therefore, the maximum value of the heat flux to the brake disks is increased. Therefore, the upper limit of PL / PS is preferably 6.0. However, even greater than PL / PS 6.0, it may be given a load only one of the inner region 14, or outer region 15. Given the load on both the inner region 14 and outer region 15, because the maximum value of the heat flux to the brake disks is inhibited than when any load is applied to only one.
[0048]
　Width of the inner pressing surface and an outer pressing surface]
　Figure 5 is a rear brake lining is a diagram showing an inner pressing surface and an outer pressing surface. Referring to FIG. 5, the width of the inner pressing surfaces 17 and D1, the width of the outer pressing surface 18 and D2. Of loads P1 and the load P2, the width DL in the radial direction of the brake disc pressing surface of a load PL larger (inner pressing surface 17 or the outer pressing surface 18) of the sliding surface in the radial direction of the brake disc the ratio DL / D of the width D (see FIG. 1) is preferably 0.4 or more. Further, the width DS in the radial direction of the brake disc pressing surface of a load PS smaller (inner pressing surface 17 or the outer pressing surface 18), the ratio DS between the width D of the sliding surface in the radial direction of the brake disc / D is preferably 0.25 or more. For example, in the case of P1> P2, a DL / D = D1 / D, is D1 / D is 0.4 or more. Thus, stress is loaded to the bolt as shown in Example 1 to be described later is further suppressed.
[0049]
　If DL / D is less than 0.4, a large load per unit area applied from the inner pressing surfaces 17 or the outer pressing surface 18 on the brake lining 3. When the brake lining 3 is pressed against the brake disk, the heat flux to the brake disc due to friction between the brake linings 3 and the brake disk is locally large. Therefore, uneven wear of the brake disc, heat spots tend to occur. Therefore, the lower limit of DL / D is preferably 0.4.
[0050]
　If DS / D is less than 0.25, in the same manner as described above, uneven wear of the brake disc, heat spots tend to occur. Therefore, the lower limit of the DS / D is preferably from 0.25.
[0051]
　[Inner pressing surface and an outer pressing surface gap between the '
　gap W between the inner pressing surface 17 and the outer pressing surface 18 is preferably greater than zero. If the gap W between the inner pressing surface 17 and the outer pressing surface 18 is less than 0, the amount of heat input around the bolt hole 7 of the brake disc is likely to increase. In other words, the heat input distribution in the brake disc is less likely to become uneven, or locally susceptible to heat input to the vicinity of the bolt hole 7. Accordingly, the lower limit of the gap W between the inner pressing surface 17 and the outer pressing surface 18 is preferably a 0. More preferably, the gap W between the inner pressing surface 17 and the outer pressing surface 18 is 10 (mm) or more. Thus, stress is loaded to the bolt as shown in Example 1 to be described later is further suppressed.
[0052]
　As described above, in the disc brake device of the first embodiment, a load is applied from the plurality of pressing surfaces of the brake caliper on the brake lining. Therefore, the load applied from one of the pressing surfaces in the brake lining is reduced. The maximum value of the heat flux applied to the brake disc is reduced by the friction between the brake lining and the brake disc. Accordingly, local temperature rise of the brake disc can be suppressed.
[0053]
　Further, in the disc brake device of the first embodiment, the load applied from the inner pressing surfaces of the brake caliper in the inner area of ​​the brake linings is different from the load given from the outside pressing surface on the outside area. Therefore, when the brake linings are pressed against the brake disk, in the radial direction of the brake disc, the heat input distribution in the brake disc due to friction between the brake lining and the brake disc is non-uniform. As described in Example 1 to be described later, the heat input distribution in the brake disc if heterogeneous, stress loaded on the bolt for fastening the brake disc and the wheel is suppressed.
[0054]
　Embodiments of the present invention is not limited to the first embodiment described above. The following describes a disk brake apparatus of the second embodiment.
[0055]
　[Second Embodiment]
　FIG. 6 is a cross-sectional view of the disc brake device of the second embodiment. Referring to FIG. 6, in the disc brake device of the second embodiment in that the brake caliper 4 comprises a pressing plate 23 is different from the first embodiment. In the second embodiment, the same components as the first embodiment will be omitted.
[0056]
　[Brake caliper]
　FIG 7 is a perspective view of the brake lining and the brake caliper. Figure 8 is a front view of the brake caliper in the direction of the axle. Referring to FIGS. 7 and 8, including the brake caliper 4, the pressing plate 23, the inner member 26, an outer member 27, the pressing surface 28. Pressing plate 23 includes a front 24, a back 25. Front 24 of the pressing plate 23 faces the back 13 of the substrate 10.
[0057]
　The inner member 26 is disposed between the front 24 of inner region 14 and the pressing plate 23 of the substrate 10. The inner member 26 is in the radial direction of the brake disc, is disposed inside the outer member 27. The inner member 26 includes an inner pressing surface 17. The inner member 26 is attached to the inner region 14 and the pressing plate 23 of the substrate 10. Specifically, the inner pressing surface 17 is attached to the inner region 14 of the substrate 10. The end face of the inner pressing surfaces 17 of the inner member 26 opposite is attached to the front 24 of the pressing plate 23. The inner member 26, for example, springs, rubber, a cylindrical metal.
[0058]
　The outer member 27 is disposed between the front 24 of the outer region 15 and the pressing plate 23 of the substrate 10. The outer member 27 includes an outer pressing surface 18. The outer member 27 is attached to the outer region 15 and the pressing plate 23 of the substrate 10. Specifically, the outer pressing surface 18 is attached to the outer region 15 of the substrate 10. The end face of the outer pressing surface 18 of the outer member 27 opposite side, is attached to the front 24 of the pressing plate 23. The outer member 27 is, for example, springs, rubber, a cylindrical metal.
[0059]
　Pressing surface 28 provides a load to the back 25 of the pressing plate 23. Since the inner member 26 and outer member 27 is attached to the pressing plate 23, the load given to the pressing plate 23 from the pressing surface 28, it is transmitted to the inner member 26 and outer member 27. Since the inner member 26 and outer member 27 is also attached to the substrate 10, the load transmitted to the inner member 26 and outer member 27 is provided to the substrate 10.
[0060]
　With this configuration, the inner pressing surfaces 17 can be loaded in the inner region 14. Outer pressing surface 18 can be loaded in the outer region 15. More specifically, when the braking of the wheels, the inner pressing surfaces 17 can be loaded in the inner region 14, the outer pressing surface 18 can be loaded in the outer region 15.
[0061]
　For one brake lining 3, two arms 19 are provided. The distal end of the arm 19, the pressing member is supported. The pressing member comprises a pressing surface 28. During braking, the pressing surface 28 provides a load to the pressing plate 23 in a direction towards the brake lining 3. Arm 19 is connected to the brake cylinder 20. When the brake cylinder 20 is actuated during braking, the arm 19 rotates about the pivot 21. Brake lining 3 is pressed against the brake disc 2 can be the inner pressing surfaces 17 provide a load to the inner region 14, an outer pressing surface 18 can be loaded in the outer region 15. According to such a configuration, it is also possible to release the brake lining 3 from the brake disc 2.
[0062]
　The inner member 26 and outer member 27, described disk brake apparatus not sandwiched by the pressing plate 23 and the substrate 10. In this case, give the load on each inner member 26 and outer member 27, the brake cylinder to provide a load mechanism such as an arm is additionally required for each inner member 26 and outer member 27. That is, the number of mechanisms that provide the load directly to the brake lining 3, it is necessary for the number of members in direct contact with the brake lining 3.
[0063]
　However, in the disk brake apparatus 1 of the second embodiment, the inner member 26 and outer member 27 gives a load to the substrate 10 of the brake lining 3, is sandwiched between the substrate 10 pressing plate 23. By load is applied to the pressing plate 23, load is transmitted to the inner member 26 and outer member 27. Mechanism is not necessary to provide a load to each inner member 26 and outer member 27. Given load the pressing plate 23, the load is given by dispersing the inner member 26 and outer member 27. Therefore, according to the disk brake apparatus of the second embodiment, it is possible to reduce the mechanism for giving a load. Thus, the structure of the disc brake device can be simplified. The disc brake device can be light in weight.
[0064]
　Like the first embodiment in the disc brake device of the second embodiment, the load applied from the inner pressing surfaces 17 of the inner member 26 in the inner region 14 is provided from the outer pushing surface 18 of the outer member 27 to the outer region 15 different from the load. To a given load different in load and the outer region 15 provided in the inner area 14 in the disc brake device of the second embodiment, there is the following method.
[0065]
　Will be described is the inner member 26 and outer member 27 spring. Type of spring is not particularly limited, the inner member 26 and outer member 27 is preferably a disc spring. The gap between the brake lining 3 and the pressing plate 23 is for small. Braking, given the load on the pressing plate 23, the pressing plate 23 is displaced in a direction approaching the brake lining 3. The inner member 26 and outer member 27 is sandwiched between the pressing plate 23 and the substrate 10. Therefore, when the pressing plate 23 is displaced, it is also displaced inner member 26 and outer member 27. Here, the spring constant of the spring is an inner member 26 is different from the spring constant of the spring is the outer member 27. Therefore, if the displacement of the inner member 26 is the same as the displacement of the outer member 27, the load applied from the inner pressing surfaces 17 of the inner member 26 in the inner area 14, the outer region from the outer pushing surface 18 of the outer member 27 different from the load given to the. The displacement amount of the inner member 26 even when different from the displacement of the outer member 27, different spring constant of the inner member 26 and the spring constant of the outer member 27, realistically applied to the inner region 14 load less likely the same as the load applied to the outer region 15.
[0066]
　Alternatively, as a method in which a load applied to the load and the outer region 15 provided in the inner region 14 made different, there is the following method.
[0067]
　Referring to FIG. 8, the distance L1 from the center of the pressing surface 28 to the center of the inner member 26 is different from the distance L2 from the center of the pressing surface 28 to the center of the outer member 27. In this case, the inner member 26 and outer member 27 may be a spring, it may not be spring. The inner member 26 and outer member 27 is, for example, a spring, rubber, metal cylinder or the like.
[0068]
　As described above, braking, load is applied toward the brake lining to the rear 25 of the pressing plate 23 from the pressing surface 28. The load is distributed and is transmitted to the inner member 26 and outer member 27. Distance L1 from the center of the pressing surface 28 to the center of the inner member 26, different from the center of the pressing surface 28 and the distance L2 to the center of the outer member 27, in order to balance the moment of the pressing plate 23, the inner member load given to 26 differs from the load applied to the outer member 27. Therefore, different from the load the load applied to the inner region 14 of the brake lining 3 is applied to the outer region 15.
[0069]
　The center of the pressing surface 28, when replacing the distributed load applied to the pressing plate 23 from the pressing surface 28 to the concentrated load refers to the point where the concentrated load is applied. The center of the inner member 26, when replacing the distributed load applied from the inner pressing surfaces 17 on the brake lining 3 in concentrated load refers to the point where the concentrated load is applied. Center of the outer member 27 is the same.
[0070]
　Or more, the load applied to the load and the outer region 15 provided in the inner region 14 has been described an example of how to differ. However, the disc brake device of the second embodiment is not limited to this case. May be different from the load the load applied to the inner region 14 of the brake lining 3 is applied to the outer region 15, its configuration is not particularly limited. Different and load the load applied to the inner region 14 is provided in the outer region 15, as described in Example 1 to be described later, the heat input distribution in the brake disc becomes uneven. As a result, the stress loaded on the bolt for fastening the brake disc and the wheel is suppressed.
[0071]
　[Spring constant and the ratio of the spring constant of the outer member of the inner member]
　When the inner member and the outer member is a spring, the ratio K1 / K2 of the spring constant K2 of the spring constant K1 and the outer member of the inner member, 0. 5 or more, preferably 3 or less. However, K1 / K2 is except for one. As described in the embodiment described later 2, K1 / K2 is 0.5 or more, if 3 or less (excluding 1), heat input distribution to the brake disc becomes uneven, the stress loaded to the bolt It can be suppressed.
[0072]
　As described above, in the disc brake device of the second embodiment, local temperature rise of the brake disc can be suppressed. Further, the heat input distribution in the brake disc due to friction between the brake lining and the brake disc is non-uniform. Therefore, the stress loaded on the bolt for fastening the brake disc and the wheel is suppressed. Further, in the disc brake device of the second embodiment, instead of providing a load directly to the inner member and the outer member in contact with the brake lining, gives directly pressing plate load. Inner and outer members are sandwiched by the pressing plate and the back of the brake lining. By load is applied to the pressing plate, the force is transmitted to the inner member and outer member. Thus, mechanism is not necessary to provide a load to each inner and outer members. According to the disc brake device of the second embodiment, it is possible to reduce the mechanism for giving a load. Thus, the structure of the disc brake device can be simplified. The disc brake device can be light in weight.
[0073]
　The following describes a disk brake apparatus of the third embodiment.
[0074]
　[Third Embodiment]
　FIG. 9 is a cross-sectional view of the brake lining and the brake caliper according to the third embodiment. Figure 9 shows a section along the radial direction of the brake disc. Referring to FIG. 9, the basic structure of the disc brake device of the third embodiment is the same as the configuration of the disc brake device of the second embodiment. However, in the disc brake device of the third embodiment in that the pressing plate 23 and the substrate 10 are connected by a rivet 29 is different from the second embodiment. In the third embodiment, the same components as the second embodiment will be omitted.
[0075]
　9 shows a case where the inner member 26 and outer member 27 is disk spring. Brake lining, the friction member 9, and a substrate 10. Brake caliper includes a pressing plate 23, the inner member 26, an outer member 27, and a pressing surface 28. Incidentally, generally in FIG. 9, the member indicated by reference numeral 10 "backing", the member indicated by reference numeral 23 may be referred to as a "substrate". However, in this specification, "substrate" a member indicated by reference numeral 10, a member indicated by reference numeral 23 is referred to as "pressing plate".
[0076]
　The inner member 26 and outer member 27 is disposed between the pressing plate 23 and the substrate 10. The pressing plate 23 and the substrate 10 are connected by rivets 29. The linkage by a rivet 29, pressing plate 23 can approach the substrate 10 along the axial direction of the rivet 29. Therefore, given the load on the rear of the pressing surface 28 from pressing plate 23, a load is applied to the back surface of the substrate 10.
[0077]
　Even in such a configuration, similarly to the embodiment described above, the local temperature rise of the brake disc can be suppressed. Further, the heat input distribution in the brake disc can be uneven, the stress loaded on the bolt for fastening the brake disc and the wheel is suppressed. Furthermore, the structure of the disc brake device can be simplified.
Example 1
[0078]
　In Example 1, assuming a disc brake device of the first embodiment described above, the stress load applied to the inner region is loaded to heat input distribution and bolts to the brake disc may differ from the load applied to the outer region They were examined. As a result, the load applied to the inner region Different the load applied to the outer region, the heat input distribution in the brake disc becomes uneven, stress loaded to the bolt has been found to be inhibited. It will be described in detail below.
[0079]
　The present inventors have investigated the relationship between the stress loaded on the heat input distribution and bolts to the brake disk. Specifically, the test was carried out in the following test numbers 1-9 by FEM (Finite Element Method) analysis. Test Nos. 1 to 7 as the present invention examples, the test was carried out in Test No. 8 and 9 as a comparative example.
[0080]
　[Test conditions]
　FIG 10 is a front view of the FEM analysis model of Example 1. Figure 11 is a sectional view taken along line XI-XI in FIG. 10. Referring to FIGS. 10 and 11, FEM analysis model assuming a wheel disc brake device is mounted. Disc brake device and wheels were symmetrical. Calculation region was performed on half the area of the disk brake device and a wheel. The inner circumference of the radius of the brake disc was 235 mm. The radius of the outer circumference of the brake disc was 360 mm. That is, the width of the sliding surface of the brake disc in the radial direction of the brake disc was 125 mm. Bolt holes provided at the center of the sliding surface of the brake disc. In addition, the diameter of the wheel was 860mm. The circumferential speed of the wheels of the tread was 300km / h. The total of the load applied to the rear surface of the substrate of the brake lining was 13.6KN.
[0081]
[Table 1]

[0082]
　Table 1 shows the test conditions. Referring to FIG. 5, a description for each parameter. Table 1 in "R1 (mm)" indicates the radius of the inner bearing area center. "R2 (mm)" indicates the radius of the outer sliding region center. "D1 (mm)" indicates an inner sliding region width. "D2 (mm)" indicates an outer sliding region width. "W (mm)" indicates the gap between the inner pressing surface and an outer pressing surface. That is, "W (mm)" corresponds to the gap between the inner bearing area and the outer sliding region. "P1 (kN)" indicates a load given to the inner region. "P2 (kN)" indicates a load given to the outer region. "N1" indicates the number of the inner pressing surface. "N2" indicates the number of outer pressing surface.
[0083]
　Load P1 given to the inner region exhibits total load given to all of the inner pressing surfaces. For example, in Test No. 1, the load P1 given to the inner region was 10.2KN. Further, in Test No. 1, the number of the inner pressing surfaces is two. Therefore, load P1 given to the inner region exhibits total load given to the two inner pressing surfaces. The same applies to other test numbers. The same applies to load P2 given to the outer region.
[0084]
　In Test No. 1-7, giving a load from a plurality of locations on the brake lining. Moreover, the load given to the inner region of the brake lining, different from the load given to the outer region. In Test No. 8, the load given to the inner region, was equal to the load given to the outer region. In Test No. 9, I gave a load from one place to the brake lining.
[0085]
　Figure 12 is a diagram showing the heat input distribution in the brake disc in test numbers 1-4. Figure in 12, a solid line chain line test No. 1, 1-dot chain line dot Test No. 2, 2 Test No. 3, the broken line shows the results of Test No. 4, respectively.
[0086]
　Figure 13 is a diagram showing the heat input distribution in the brake disc in test numbers 5-9. In Figure 13, the solid line chain line test numbers 5,1-dot chain line Test No. 6, 2 points Test No. 7, the dashed line E1 Test No. 8, the broken line E2 shows the results of Test No. 9, respectively.
[0087]
　Referring to FIGS. 12 and 13, the vertical axis represents heat flux J / (s · mm 2 ) and the horizontal axis represents the radial position of the sliding surface of the brake disc. The radial position, means the distance in the radial direction of the brake disc to the arbitrary position on the axial center sliding surface of the axle. 12 and 13, reference numeral "A" region of 235 ~ 297.5mm in the radial direction of the sliding surface means (inner region), code "B" of 297.5 ~ 360 mm region (outer region) It means.
[0088]
　The maximum value of the heat flux test numbers 1-7 (invention example), smaller than the maximum value of the heat flux Test No. 9 (Comparative Example). This is because, in Test No. 1-7, load one pressing surface has on the brake lining, is because smaller than Test No. 9. Therefore, in Test No. 1-7, the local temperature rise of the brake disc is suppressed.
[0089]
　Further, in Test No. 1-7, the heat flux in the region A of the brake disc, different from the heat flux of the regions B. That is, in Test Nos. 1 to 7, in the radial direction of the brake disc, the heat input distribution in the brake disc was heterogeneous. This is because, in Test No. 1-7, the load applied to the inner region of the brake lining, because different from the load applied to the outer region. Therefore, in Test No. 1-7, the stress loaded on the bolt for fastening the brake disc and the wheel is suppressed. It will be described in detail below this point.
[0090]
　To simulate the deformation of the brake disk by the FEM analysis. The FEM analysis, considering the load of the bolt imparted by the deformation of the brake disc due to thermal stress. From the results of the FEM analysis, to calculate the stress generated in the bolt in each test number. Than the calculated stress was calculated bolt safety factor in each test number. Here, the bolt safety factor was calculated by the following equation.
　(Volt safety factor) = (allowable stress of the bolt) / (stress generated on the bolt calculated by FEM analysis)
[0091]
　Figure 14 is a diagram showing the relative values ​​of the bolt safety factor for the test numbers 9. Referring to FIG. 14, the bolt safety of the test numbers 1 to 7 was higher than the bolt safety of the test numbers 8 and 9. That is, in Test Nos 1-7, stress loaded to the bolt is suppressed. In summary, the present inventors found that by FEM analysis, in the radial direction of the brake disc, if heat input distribution in the brake disc uneven, compared with the heat input distribution is uniform, loaded to the bolt that stress has been found to be suppressed.
Example 2
[0092]
　In Example 2, assuming the disc brake device of the second embodiment described above, it was examined heat input distribution in the brake disc. As a result, heat input distribution of the brake disc becomes uneven on the basis of the results of Example 1, the stress loaded to the bolt has been found to be inhibited. It will be described in detail below.
[0093]
　The present inventors examined the heat input distribution in the brake disc when the disc brake device of the second embodiment. Specifically, tests were conducted the following test numbers 10-17 by FEM analysis. Test No. 10-16 as the invention example, the test was carried out in Test No. 17 as a comparative example.
[0094]
　[Test conditions]
　FIG 15 is a cross-sectional view of the FEM analysis model of Example 2. Referring to FIG. 15, in Embodiment 2, the structure of the brake caliper is different from the first embodiment. Specifically, in Example 2, assuming the configuration of a brake caliper shown in FIG. The total of the load applied to the rear surface of the pressing plate was 13.6KN. The inner member 26 and outer member 27, assuming a disc spring. The center of the pressing surface providing the pressing plate 23 a load is 297.5mm from the center of the brake disc was 20 ° inclined position from the center line of the brake disc. The center line of the brake disc, as seen from the direction of the axle, means a line through the longitudinal center of the central and brake linings of the brake disc. Center of the inner member was 266.25mm from the center of the brake disc. Center of the outer member was 328.75mm from the center of the brake disc. Other test conditions were the same as in Example 1.
[0095]
[Table 2]

[0096]
　Table 2 shows the test conditions. Referring to FIG. 5, a description for each parameter in Table 2. In Table 2, "K1" indicates the spring constant of the inner member. "K2" indicates the spring constant of the outer member. That is, "K1 / K2" indicates the ratio of the spring constant of the spring constant and the outer member of the inner member. "Θ1" indicates the angle between the center line of the radius and the brake disc of the brake disc passing through the center of the inner member. "Θ2" indicates the angle between the center line of the radius and the brake disc of the brake disc through the center of the outer member. Other parameters are the same as in Example 1.
[0097]
　In Test No. 10 to 12 examples of the present invention, "K1 / K2" was not in 1. That is, the spring constant of the inner member is different from the spring constant of the outer member. In Test No. 13 is an example of the present invention, "θ2" is 20 °, the center of the outer member is present on the line (on the radius of the brake disc) which passes through the center of the brake disc pressing surface. Accordingly, the distance from the center of the pressing surface to the center of the outer member is equal to the radial distance of the brake disc between a center of the outer member of the pressing surfaces was 31.25 mM. For the test numbers 13 "θ1" is 30 °, the center of the inner member was not radially on the brake disc passing through the center of the pressing surface. Accordingly, the distance from the center of the pressing surface to the center of the inner member was greater than the radial distance 31.25mm brake discs between a center of the pressing surface of the inner member. Similarly Test No. 14 is an example of the present invention also, whereas "θ1" is 20 °, since "θ2" was 10 °, the distance from the center of the pressing surface to the center of the inner member, the pressing surface different from the center of the distance to the center of the outer member. In Test No. 15 and 16 are examples of the present invention, "D1" is different from "D2". In this embodiment, the inner and outer members are disc spring. Thus, "D1" corresponds to the diameter of the disc spring is an inner member, "D2" corresponds to the diameter of the disc spring is the outer member. Different diameters of the conical spring, the spring constant is different. That is, Test Nos. 15 and 16, the spring constant of the inner member is different from the spring constant of the outer member.
[0098]
　Figure 16 is a diagram showing the heat input distribution in the brake disc in test No. 10 to 12 and 17. In Figure 16, the solid line test No. 10, 1-dot chain line Test No. 11, 2-dot chain line test No. 12, the broken line shows the results of Test No. 17, respectively.
[0099]
　Figure 17 is a diagram showing the heat input distribution in the brake disc with the test numbers 13 and 14. In Figure 17, the solid line test No. 13, the broken line shows the results of Test No. 14, respectively.
[0100]
　Figure 18 is a diagram showing the heat input distribution in the brake disc with the test numbers 15 and 16. In Figure 18, the solid line test No. 15, the broken line shows the results of Test No. 16, respectively.
[0101]
　16 to 18, the vertical axis represents heat flux J / (s · mm 2 ), and the abscissa indicates the position in the radial direction of the sliding surface of the brake disc (mm).
[0102]
　16, in Test No. 17 is a comparative example, the maximum value of the heat flux in the region A was the same as the maximum value of the heat flux in the region B. This is because, in Test No. 17, because the spring constant K1 of the inner member is the same as the spring constant K2 of the outer member. That is, in Test No. 17, the load given to the inner region is because it was the same as the load given to the outer region. In Test No. 10 to 12 examples of the present invention, the maximum value of the heat flux in the region A is different from the maximum value of the heat flux in the region B. This is because, in Test No. 10 to 12, because the spring constant K1 of the inner member is different from the spring constant K2 of the outer member. That is, in Test Nos. 10-12, the load given to the inner region is different from the load given to the outer region. Therefore, in the radial direction of the brake disc, the heat input distribution in the brake disc was heterogeneous.
[0103]
　Referring to FIG. 17, in Test No. 13 and 14 are examples of the present invention, the maximum value of the heat flux in the region A is different from the maximum value of the heat flux in the region B. This is because, in Test No. 13 and 14, the distance from the center of the pressing surface to the center of the inner member, because different from the distance from the center of the pressing surface to the center of the outer member. That is, in Test Nos. 13 and 14, the load given to the inner region is different from the load given to the outer region. Therefore, in the radial direction of the brake disc, the heat input distribution in the brake disc was heterogeneous.
[0104]
　Referring to FIG. 18, in Test No. 15 and 16 are examples of the present invention, the maximum value of the heat flux in the region A is different from the maximum value of the heat flux in the region B. This is because, in Test No. 15 and 16, the diameter of the disc spring is the inner member is different from the diameter of the disc spring is the outer member. That is, in Test No. 15 and 16, the spring constant of the inner member is different from the spring constant of the outer member. Therefore, for the same reason as in Test No. 10 to 12 in the radial direction of the brake disc, the heat input distribution in the brake disc was heterogeneous.
[0105]
　Figure 19 is a diagram showing the relative values ​​of the bolt safety factor for the test No. 17. Referring to FIG. 19, the bolt safety of the test numbers 10-16, it was higher than the bolt safety factor of Test No. 17. That is, in Test Nos 10-16, stress loaded to the bolt is suppressed. As described in Example 1, in the radial direction of the brake disc, because heat input distribution in the brake disc was heterogeneous.
[0106]
　It has been described an embodiment of the present invention. However, the above-described embodiment is merely an example for implementing the present invention. Accordingly, the present invention is not limited to the embodiments described above, it can be implemented by changing the above-described embodiments without departing from the scope and spirit thereof as appropriate.
[0107]
　In the first embodiment, one arm of the brake caliper has been described for the case of supporting the inner pressing surface and an outer pressing surface. However, the support of the inner pressing surfaces and the outer pressing surface is not limited to this case. The inner pressing surface and an outer pressing surface arm that supports may be separate. That is, one independent arm may support one pressing surface. Further, one arm supporting only one or more of the outer pressing surface, one arm may support only one or more of the inner pressing surfaces.
[0108]
　In the above description, the brake caliper, been described comprising two inner pressing surfaces and two outer pressing surface. However, the number of the number and the outer pressing surface of the inner pressing surfaces is not limited to this case. Brake caliper may comprise a single inner pressing surface and one outer pressing surface. Brake caliper may include three or more inner pressing surface and more than two outer pressing surface. The number of inner pressing surfaces may be different from the number of outer pressing surface. In short, the total load applied to the inner region of the brake lining may be different from the total load applied to the outer region. Different total load total load applied to the inner region is provided in the outer region, because heat input distribution in the brake disc becomes uneven. If the brake caliper comprises a plurality of inner pressing surfaces, the total load applied to the inner region is meant the sum of loads of all of the inner pressing surfaces. The same applies to the outer pressing surface.
[0109]
　Brake caliper of this embodiment can be a lever type described above, it may be given a load in direct piston to the back of the substrate as a floating type and opposed type. In addition, as of the floating type, it may be given a load in reaction force. In short, given the way of the load to the brake lining is not particularly limited. Brake caliper may include a plurality of brake cylinders.
[0110]
　In the above description, the shape of the inner pressing surfaces and the outer pressing surface has been described is a circle. However, the shape of the inner pressing surfaces and the outer pressing surface is not limited to this case. Shape of the inner pressing surfaces and the outer pressing surface may be a polygon.
[0111]
　In the above description, when projected a plurality of bolt holes of the brake disc to the back of the substrate, the case is the boundary between the inner region and the outer region is arc on the circumference passing through the center of a plurality of bolt holes projected explained. However, the boundary between the inner region and the outer region is not limited to this case. The boundary between the inner region and the outer region may be impassable the projected area of ​​a plurality of bolt holes are.
[0112]
　In the second embodiment, in order to vary the load applied to the load and an outer region provided in the inner area, when changing only the spring constant, when changing only the position of the inner pressing surface and an outer pressing surface description did. However, the disc brake device of the present embodiment is not limited to this case. In the disc brake device of the present embodiment, the spring constant of the inner member be different from the spring constant of the outer member, and the distance from the center of the pressing surface to the center of the inner member from the center of the pressing surface to the center of the outer member distance and may be different.
DESCRIPTION OF SYMBOLS
[0113]
　　1: disk brake apparatus
　　2: brake disc
　　3: brake lining
　　4: brake caliper
　　5: axle
　　6: wheel
　　7: bolt hole
　　8: bolt
　　9: Friction member
　10: substrate
　11: sliding surface
　12: front substrate
　13: substrate rear
　14: inner region
　15: the outer region
　16: boundary
　17: inner pressing surfaces
　18: outer pressing surface
　19: arm
　20: brake cylinders
　21: fulcrum
　22: bracket
　23: pressing plate
　24: pressing plate in the front
　25: pressing plate rear
　26: inner member
　27: outer member
　28: pressing surface

WE CLAIM

A disc brake device for braking a wheel attached to the axle,
　a brake disc having a plurality of bolt holes arranged on the sliding surface and on the same circumference, was passed through each of the plurality of bolt holes and the brake disc is fastened to the wheel by bolts,
　wherein a brake disc facing the brake lining, the friction member, and a substrate for supporting the friction member, a brake lining comprising,
　a load on a rear surface of the substrate and a brake caliper for pressing the friction member to the sliding surface by applying,
　the back surface of the substrate is divided into an inner and outer regions by an arc-shaped boundary about the axis of the axle ,
　said plurality of bolt holes in the rear surface of the substrate when projected in the direction of the axle, the boundary of the plurality of projected As the area of the belt holes,
　the brake caliper comprises an inner pressing surface which gives a load to the inner region, and an outer pressing surface which gives a load to the outer region,
　provided to the inner region from the inner pressing surfaces load, differs from the load applied from the outer pushing surface to the outer region, the disc brake device.
[Requested item 2]
　A disc brake device according to claim 1,
　of the load applied to said outer region from the load and the outer pressing surface provided on the inner region from the inner pressing surfaces, the larger load and a smaller load of the ratio of a, 1.3 or more and 6.0 or less, the disc brake device.
[Requested item 3]
　A disc brake device according to claim 1,
　of the load and the outer pressing surface provided on the inner region from the inner pressing surface of the load applied to said outer region,
　the inner pressing to give a load of larger the ratio of the radial width of the sliding surface of the surface or the outer pressing surface the brake width and the brake disc in the radial direction of the disk is 0.4 or more,
　the inner pressing surface that gives a load of smaller or the ratio of the radial width of the sliding surface of the outer pressing surface the brake width and the brake disc in the radial direction of the disk is 0.25 or more, the disc brake device.
[Requested item 4]
　A disc brake device according to claim 1,
　wherein the brake caliper is provided with a plurality of the inner pressing surface comprises a plurality of said outer pressing surface, the, from the plurality of inner pressing surfaces in the inner region total load is different from the total load applied from the plurality of outer pushing surface to the outer region, the disc brake device.
[Requested item 5]
　A disc brake device according to claim 1,
　wherein the brake caliper comprises one of said inner pressing surface, a plurality of the outer pressing surface, and applied to said inner region of said one inner pressing surfaces load is different from the total load applied from the plurality of outer pushing surface to the outer region, the disc brake device.
[Requested item 6]
　A disc brake device according to claim 1,
　wherein the brake caliper is provided with a plurality of the inner pressing surface comprises one of said outer press surface, and a plurality of inner pressing surfaces in the inner region total load is different from the load given from said one outer pressing surface to the outer region, the disc brake device.
[Requested item 7]
　A disc brake device according to claim 1,
　wherein the brake caliper, pressing the plate to the back facing of the substrate, wherein the inner pressing surface, between the pressing plate and an inner region of the substrate an inner member disposed attached to the inner region and the pressing plate of the substrate, wherein the outer pressing surface, the outer region and the said substrate is disposed between the pressing plate and the outer region of the substrate It includes an outer member attached to the pressing plate, and a pressing surface that gives a load to the back surface of the pressing plate, the disk brake device.
[Requested item 8]
　A disc brake according to claim 7,
　wherein the inner member and the outer member is a spring,
　the spring constant of the inner member is different from the spring constant of the outer member, the disc brake device.
[Requested item 9]
　A disc brake device according to claim 7 or claim 8,
　the distance from the center of the pressing surface to the center of the inner member is different from the distance from the center of the pressing surface to the center of the outer member, disc brake device.