WO2015122148A1 - ブレーキディスク付き鉄道車輪 - Google Patents
ブレーキディスク付き鉄道車輪 Download PDFInfo
- Publication number
- WO2015122148A1 WO2015122148A1 PCT/JP2015/000465 JP2015000465W WO2015122148A1 WO 2015122148 A1 WO2015122148 A1 WO 2015122148A1 JP 2015000465 W JP2015000465 W JP 2015000465W WO 2015122148 A1 WO2015122148 A1 WO 2015122148A1
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- WIPO (PCT)
- Prior art keywords
- wheel
- peripheral surface
- brake
- section
- disc
- Prior art date
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B61—RAILWAYS
- B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
- B61F13/00—Rail vehicles characterised by wheel arrangements, not otherwise provided for
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B61—RAILWAYS
- B61H—BRAKES OR OTHER RETARDING DEVICES SPECIALLY ADAPTED FOR RAIL VEHICLES; ARRANGEMENT OR DISPOSITION THEREOF IN RAIL VEHICLES
- B61H5/00—Applications or arrangements of brakes with substantially radial braking surfaces pressed together in axial direction, e.g. disc brakes
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B17/00—Wheels characterised by rail-engaging elements
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B17/00—Wheels characterised by rail-engaging elements
- B60B17/0006—Construction of wheel bodies, e.g. disc wheels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/0006—Noise or vibration control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/02—Braking members; Mounting thereof
- F16D65/12—Discs; Drums for disc brakes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/02—Braking members; Mounting thereof
- F16D65/12—Discs; Drums for disc brakes
- F16D65/123—Discs; Drums for disc brakes comprising an annular disc secured to a hub member; Discs characterised by means for mounting
- F16D65/124—Discs; Drums for disc brakes comprising an annular disc secured to a hub member; Discs characterised by means for mounting adapted for mounting on the wheel of a railway vehicle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/02—Braking members; Mounting thereof
- F16D2065/13—Parts or details of discs or drums
- F16D2065/1304—Structure
- F16D2065/1312—Structure circumferentially segmented
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/02—Braking members; Mounting thereof
- F16D2065/13—Parts or details of discs or drums
- F16D2065/1304—Structure
- F16D2065/1328—Structure internal cavities, e.g. cooling channels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/02—Braking members; Mounting thereof
- F16D2065/13—Parts or details of discs or drums
- F16D2065/134—Connection
- F16D2065/138—Connection to wheel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/02—Braking members; Mounting thereof
- F16D2065/13—Parts or details of discs or drums
- F16D2065/134—Connection
- F16D2065/1392—Connection elements
Definitions
- the present invention relates to a railway wheel with a brake disk (hereinafter also referred to as a “railway wheel with BD”) in which a brake disk is fastened to a wheel for a railway vehicle.
- a brake disk hereinafter also referred to as a “railway wheel with BD”
- a disc brake having excellent braking performance is often used as the speed and size of the vehicle increase.
- the disc brake is configured to press a brake lining against a sliding surface of a brake disc attached to a wheel. As a result, braking force is generated on the rotating wheels, and the speed of the vehicle is controlled.
- a central fastening type (sliding surface fastening type) brake disc that fastens the brake disc to the wheel in an area within the sliding surface, and a break disc that is fastened to the wheel in an area on the inner peripheral side from the sliding surface.
- an inner periphery fastening type brake disc There is an inner periphery fastening type brake disc.
- the inner periphery fastening type brake disc requires a part used for fastening separately from the part having the sliding surface.
- the center fastening type brake disc is advantageous in reducing the weight because it is not necessary to provide a part used for such fastening.
- FIGS. 1A and 1B are views showing the overall structure of a railway wheel with a brake disc that constitutes a disc brake of a railway vehicle.
- FIG. 1A is a plan view of a quarter circle portion
- FIG. 1B is a semicircle portion.
- Cross-sectional views along the radial direction are shown.
- 2A to 2C are views locally showing the structure of a conventional BD-equipped railway wheel.
- FIG. 2A is a perspective view of the rear surface of the brake disk as viewed from the inner peripheral surface side
- FIG. FIG. 2C is a cross-sectional view taken along the radial direction, as seen from the back side.
- the brake discs shown in FIGS. 1A, 1B, and 2A to 2C are all center-fastened types.
- the brake disc 1 includes a donut-shaped disc portion 2 having a surface 2a side as a sliding surface.
- a plurality of fin portions 3 are radially provided on the rear surface 2 b of the disk portion 2. Some of the plurality of fin portions 3 are formed with bolt holes 4 penetrating to the disc portion 2 at substantially the center position in the radial direction.
- the wheel 10 includes a boss portion 11 into which the axle is press-fitted, a rim portion 12 including a tread surface that comes into contact with the rail, and a plate portion 13 that couples them.
- the brake disc 1 is arranged so as to sandwich the plate portion 13 of the wheel 10 with the two surfaces as a set and the individual surfaces 2a facing outward.
- Bolts 5 are inserted into the respective bolt holes 4, and nuts 6 are screwed into the respective bolts 5 and tightened.
- the brake disc 1 is fastened to the wheel 10 in a state where the front end surface of the fin portion 3 is in pressure contact with the side surface 13a of the plate portion 13 of the wheel 10 over the entire radial direction.
- the brake disc 1 is fastened to the plate portion 13 in an area within the sliding surface.
- the vicinity of the central portion of the inner periphery and outer periphery of the brake disc for example, the position that divides the inner periphery and outer periphery by 1: 3 and 3: 1. It is preferable that the brake disc 1 is fastened to the wheel 10 between the position to be internally divided.
- a substantially entire surface of the brake disk 1 is a sliding surface. As shown in FIG. 1B, a large gap (e.g., between the boss portion 11 and the disc portion 2 over the entire circumference) A gap of 70 to 120 mm is formed. That is, the brake disc 1 does not extend to the vicinity of the boss portion 11, thereby reducing the weight of the brake disc 1.
- the conventional railway wheel with BD of such a structure is disclosed by patent document 1, for example.
- the brake disc 1 rotates with the wheel 10 at a high speed. Accordingly, the air around the brake disc 1 flows into the space formed between the brake disc 1 and the wheel 10, specifically, the disc portion 2 and the fin portion 3 of the brake disc 1, and the wheel. 10 flows into the space surrounded by the plate portion 13 from the inner peripheral side (the gap between the boss portion 11 and the disc portion 2) and flows out from the outer peripheral side (see solid arrows in FIGS. 2A to 2C). . In short, an air gas flow is generated in the space between the brake disc 1 and the wheel 10 during travel of the railway vehicle.
- the gap between the boss part 11 and the disc part 2 is remarkably small as compared with the center type brake disk. For this reason, the amount of air flowing into the space surrounded by the disc portion 2 and the fin portion 3 of the brake disc 1 and the plate portion 13 of the wheel 10 from this gap when the vehicle is running is small. Usually, no problematic level of aerodynamic sound is produced. Therefore, it can be said that the generation of aerodynamic noise is a problem peculiar to the center fastening type brake disc.
- Patent Document 2 discloses a railway wheel with a BD in which a rib is added along the circumferential direction between adjacent fin portions of a brake disc, and the gas flow is suppressed by the rib. According to the railway wheel with BD disclosed in this document, aerodynamic sound can be reduced to a desired level.
- FIG. 3A and 3B are views locally showing the structure of a conventional BD-equipped railway wheel disclosed in Patent Document 3, and FIG. 3A is a perspective view of the rear surface of the brake disk as viewed from the inner peripheral surface side.
- FIG. 3B shows a cross-sectional view along the radial direction.
- ribs 7 are added along the circumferential direction between the adjacent fin portions 3 for the brake disc 1, and this A slit 7 a is formed along the radial direction at the center of the rib 7 in the circumferential direction.
- the gas flow is secured by the slit 7a.
- the cooling performance to the brake disc 1 is maintained during braking, and the increase in rigidity due to the addition of the rib is mitigated, so that deformation due to thermal expansion of the brake disc 1 and stress load on the fastening bolts are caused. This reduces the deterioration of the durability of the brake disc 1 and the bolt.
- the conventional railway wheel with BD that aims to reduce aerodynamic noise is mainly intended to suppress the gas flow in the space surrounded by the disc part and the fin part of the brake disk and the plate part of the wheel.
- a rib is added to the disc part of the disc brake, and a slit is formed in the rib. For this reason, since the shape of the brake disc becomes complicated, the productivity of the brake disc must be reduced.
- the present invention has been made in view of the above problems, and an object thereof is to provide a railway wheel with a brake disk having the following characteristics: -The brake disc must have a simple shape and excellent productivity; ⁇ To effectively reduce aerodynamic noise during high-speed driving.
- a railway wheel with a brake disk according to an embodiment of the present invention, A wheel for a railway vehicle provided with a boss portion, a rim portion, and a plate portion connecting them, and A donut-shaped disk part having a sliding surface on the front side, and a brake disk provided with a plurality of fin parts projecting radially on the back surface of the disk part, A rail wheel with a brake disk clamped in a region within the sliding surface, with the two brake discs sandwiching the plate portion of the wheel with each sliding surface facing outward, Regarding the area of the cross section that crosses the space formed between the brake disc and the wheel along the circumferential direction, the minimum cross section that has the smallest cross sectional area is the outer peripheral surface of the disk portion and the rim. Existing in the area formed by the inner peripheral surface of the part, The outer peripheral surface of the disc portion is a shape along the inner peripheral surface of the rim portion in an outer region starting from the minimum cross-sectional portion.
- the inner peripheral surface of the rim portion includes a corner surface connected to a side surface of the rim portion, and a fillet surface connected to the corner surface and a side surface of the plate portion, and the minimum cross-sectional portion Can be configured to exist at the boundary between the corner surface and the fillet surface in the inner peripheral surface of the rim portion.
- the inner peripheral surface of the rim portion includes a corner surface connected to a side surface of the rim portion, and a fillet surface connected to the corner surface and a side surface of the plate portion, and the minimum cross-sectional portion Can be configured to exist in the region of the fillet surface in the inner peripheral surface of the rim portion. In the case of this configuration, it is preferable that the minimum cross-sectional portion is present on the backmost side among the outer peripheral surfaces of the disc portion.
- the corner surface on the inner peripheral surface of the rim portion may adopt a configuration in which the contour shape in a cross section along the axial direction is an arc shape.
- the railway wheel with brake disc of the present invention has the following remarkable effects: -The brake disc must have a simple shape and excellent productivity; ⁇ Aerodynamic noise during high-speed driving can be reduced effectively.
- FIG. 1A is a diagram showing an overall structure of a railway wheel with a brake disk, and shows a plan view of a 1 ⁇ 4 circle portion.
- FIG. 1B is a diagram showing the overall structure of a railway wheel with a brake disc, and shows a cross-sectional view along the radial direction of a semicircular portion.
- FIG. 2A is a diagram locally showing the structure of a conventional railway wheel with a brake disc, and shows a perspective view of the rear surface of the brake disc as seen from the inner peripheral surface side.
- FIG. 2B is a diagram locally showing the structure of a conventional railway wheel with a brake disc, and shows a plan view of the brake disc as seen from the back side.
- FIG. 1A is a diagram showing an overall structure of a railway wheel with a brake disk, and shows a plan view of a 1 ⁇ 4 circle portion.
- FIG. 1B is a diagram showing the overall structure of a railway wheel with a brake disc, and shows a cross-sectional view along the
- FIG. 2C is a diagram locally showing a structure of a conventional railway wheel with a brake disc, and shows a cross-sectional view along the radial direction.
- FIG. 3A is a diagram locally showing the structure of a conventional railway wheel with a brake disc disclosed in Patent Document 3, and shows a perspective view of the back surface of the brake disc as seen from the inner peripheral surface side.
- FIG. 3B is a diagram locally showing the structure of a conventional railway wheel with a brake disk disclosed in Patent Document 3, and shows a cross-sectional view along the radial direction.
- FIG. 4 is a diagram showing a correlation between the sum of the opening areas, the aerodynamic sound level, and the air flow rate in the railway wheel with a brake disk.
- FIG. 5A is a diagram showing a distribution of gas pressure fluctuations on a solid surface (brake disc and wheel surfaces) obtained by unsteady gas flow analysis.
- FIG. 5B is a diagram showing a distribution of gas pressure fluctuations on a solid surface (displayed through a brake disk) obtained by unsteady gas flow analysis.
- FIG. 6A is a cross-sectional view along the radial direction showing the structure of the railway wheel with a brake disk according to the first embodiment of the present invention.
- FIG. 6B is a cross-sectional view locally showing the railway wheel with a brake disk in FIG. 6A, and shows a rectangular region in FIG. 6A.
- FIG. 7A is a cross-sectional view along the radial direction showing the structure of a railway wheel with a brake disk according to a second embodiment of the present invention.
- FIG. 7B is a cross-sectional view locally showing the railway wheel with a brake disk in FIG. 7A, and shows a rectangular region in FIG. 7A.
- FIG. 8A is a cross-sectional view along the radial direction showing the structure of a railway wheel with a brake disk according to a third embodiment of the present invention.
- FIG. 8B is a cross-sectional view locally showing the railway wheel with a brake disk in FIG. 8A, and shows a rectangular region in FIG. 8A.
- FIG. 8A is a cross-sectional view along the radial direction showing the structure of a railway wheel with a brake disk according to a third embodiment of the present invention.
- FIG. 8B is a cross-sectional view locally showing the railway wheel with a brake disk in FIG. 8A, and shows a rectangular region in FIG. 8
- FIG. 9A is a cross-sectional view along the radial direction showing the structure of a railway wheel with a brake disk used as a comparative example in the analysis of the example.
- FIG. 9B is a cross-sectional view locally showing the railway wheel with a brake disk in FIG. 9A, and shows a rectangular region in FIG. 9A.
- FIG. 10 is a diagram illustrating the relationship between the heat release amount and the aerodynamic sound level, which is the analysis result of the example.
- FIG. 11 is a diagram showing a change over time in the air flow rate as an analysis result of the example.
- FIG. 4 is a diagram showing a correlation between the sum of the opening areas, the aerodynamic sound level, and the air flow rate in the railway wheel with a brake disk.
- the sum of the opening areas here refers to the entire area in the circumferential direction of the opening area when viewed from the inner peripheral side of the brake disc in the space surrounded by the disc disc and fin portions of the brake disc and the plate portion of the wheel. It is the sum total.
- the sum of the opening areas is the minimum cross-sectional area of the cross section that crosses the space formed between the brake disc and the wheel along the circumferential direction (hereinafter referred to as “space cross section”). Is the area of the smallest cross-sectional portion. For example, as in the railway wheel with BD shown in FIGS.
- the minimum cross-sectional portion is the position of the rib. Therefore, the area of the spatial cross section at the position of the rib is the sum of the opening areas shown in FIG.
- the air flow rate was obtained by thermal fluid analysis (per brake disc), and the aerodynamic sound level was obtained by experiments.
- the conventional railway wheel with BD shown in FIG. 3A and FIG. 3B that is, the railway wheel with BD in which a rib with a slit is added between the fin portions, the aerodynamic sound level based on the unsteady gas flow analysis is targeted. Direct prediction was performed. In this analysis, the traveling speed was kept constant at 360 km / h.
- the typical conditions of the model of the railway wheel with BD used for the unsteady gas flow analysis are as follows.
- the aerodynamic sound level was measured by the method described in Patent Document 2 to verify the validity of the calculation method for unsteady gas flow analysis. Specifically, after measuring sound pressure data with a precision sound level meter by experiment, frequency analysis is performed, A characteristic correction is applied, and 1/3 octave band processing is performed to calculate frequency characteristic data and an overall value. did. And about the overall value, the experimental value (114.5 [dB (A)]) and the calculated value (114.8 [dB (A)]) were compared, and both consistency was confirmed.
- FIG. 5A and FIG. 5B are diagrams showing the distribution of gas pressure fluctuations on the solid surface (brake disc and wheel surfaces) obtained by unsteady gas flow analysis.
- FIG. 5A shows both the brake disc and the surface of the wheel
- FIG. 5B shows the brake disc through it.
- the gas pressure fluctuation on the solid surface shown in FIG. 5A and FIG. 5B indicates the root mean square amount of the time differential value of the pressure, which corresponds to the sound source distribution on the solid surface (brake disc and wheel surfaces).
- the main sound source during traveling is the gas outflow region and its vicinity, that is, in the space formed between the brake disk and the wheel. It appears in the outer peripheral region of the disc portion of the brake disc and in the vicinity thereof.
- the disc disk portion and the fin portion of the brake disc which have been focused on in the prior art, and the wheel in the space formed between the brake disc and the wheel.
- the space surrounded by the plate portion it is formed by the outer peripheral region of the disc portion of the brake disc that becomes the gas outflow region, that is, the outer peripheral surface of the disc portion of the brake disc and the inner peripheral surface of the rim portion of the wheel.
- the present invention pays attention to the gas flow in the gas outflow region, adjusts the gas flow direction from between the brake disc and the wheel to be along the surface (side surface) of the rim portion of the wheel, The gas flows in the radial direction along the sliding surface generated by the rotation so as to join at a small angle. Thereby, the direction change of the gas flow in the vicinity of the confluence where it is likely to be a sound source is minimized, and aerodynamic noise is reduced.
- FIG. 6A is a cross-sectional view along the radial direction showing the structure of the railway wheel with a brake disk according to the first embodiment of the present invention.
- FIG. 6B is a cross-sectional view locally showing the railway wheel with a brake disk in FIG. 6A, and shows a rectangular region in FIG. 6A.
- the same reference numerals are given to the parts common to the conventional BD-equipped railway wheels shown in FIG. 1A, FIG. 1B and FIGS. 2A to 2C, and overlapping description will be omitted as appropriate.
- the brake disc 1 As shown in FIGS. 6A and 6B, the brake disc 1 according to the first embodiment includes a disk portion 2 and a fin portion 3.
- the brake disc 1 does not have the rib 7 as shown in FIGS. 3A and 3B.
- the plurality of fin portions 3 are only protruded radially on the back surface 2b of the disc portion 2.
- the material of the brake disc cast iron, cast steel, forged steel, aluminum, carbon, or the like can be used.
- the region of the surface 2a of the brake disc 1 that becomes a sliding surface is higher than that.
- the brake disk 1 is replaced when the sliding surface wears due to repeated braking and the wear of the sliding surface proceeds to the height of the surface 2 a of the disk portion 2.
- the wheel 10 includes a boss portion 11, a rim portion 12, and a plate portion 13.
- An inner peripheral surface 12b (range from point b1 to point b3 in FIG. 6B) of the rim portion 12 is a corner surface 12ba (range from point b1 to point b2 in FIG. 6B) connected to the side surface 12a of the rim portion 12, and a corner.
- a fillet surface 12bb (range from point b2 to point b3 in FIG. 6B) connected to the surface 12ba and the side surface 13a of the plate portion 13 is included.
- the shapes of the corner surface 12ba and the fillet surface 12bb are designed according to the specifications of the vehicle.
- the corner surface 12ba is a single R surface having an arc shape in a cross section along the axial direction of the wheel 10 and a constant radius of curvature.
- the fillet surface 12bb is a composite surface in which the contour shape in a cross section along the axial direction of the wheel 10 is a combination of a straight line and an arc, and a conical tapered surface and an R surface with a constant curvature radius are combined. is there.
- the fillet surface 12bb may be a single R surface or a free-form surface with a changing radius of curvature.
- the area of the space cross section is the minimum for the space cross section that crosses the space formed between the brake disk 1 and the wheel 10 along the circumferential direction.
- the minimum cross-sectional portion to be present exists in a region formed by the outer peripheral surface 2 c of the disc portion 2 of the brake disc 1 and the inner peripheral surface 12 b of the rim portion 12 of the wheel 10. Specifically, it exists in the boundary b2 of corner surface 12ba and fillet surface 12bb among the internal peripheral surfaces 12b of the rim
- the outer peripheral surface 2c (range from point a1 to point a3 in FIG. 6B) of the disc portion 2 of the brake disc 1 is opposed to the boundary b2 between the corner surface 12ba of the rim portion 12 and the fillet surface 12bb.
- the shape of the region (the range from the point a1 to the point a2 in FIG. 6B) on the outer side (surface 2a side) along the thickness direction from here is the corner of the inner peripheral surface 12b of the rim portion 12.
- the shape is along the surface 12ba. That is, within the region, the outer peripheral surface 2c of the disc portion 2 of the brake disc 1 and the inner peripheral surface 12b of the rim portion 12 of the wheel 10 are closely opposed to each other.
- close means that a gap of about 1 to 5 mm is formed.
- the outer peripheral surface 2c of the disc portion 2 is the inner peripheral surface 12b of the rim portion 12. It ’s not along the way.
- the brake disk 1 does not have the rib 7 and only includes the fin portion 3 on the back surface of the disc portion 2 and has a simple shape. For this reason, the manufacturing process of the brake disc 1 is not complicated, and the productivity of the brake disc 1 is excellent. Even when the brake disk 1 is manufactured by forging, the load on the mold does not increase and the mold life is not shortened. However, the outer peripheral surface 2c of the disc portion 2 of the brake disc 1 needs to be machined into a shape corresponding to the shape of the inner peripheral surface 12b of the rim portion 12 of the wheel 10, but this machining is a conventional method. Unlike the additional machining of ribs and slits, it can be easily performed in a series of machining of the brake disc 1.
- the air flowing between the brake disc 1 and the wheel 10 during the high-speed traveling finally reaches the inner peripheral surface 12b (corner surface 12ba) of the rim portion 12. It flows out along the side surface 12a of the rim
- FIG. 7A is a cross-sectional view along the radial direction showing the structure of a railway wheel with a brake disk according to a second embodiment of the present invention.
- FIG. 7B is a cross-sectional view locally showing the railway wheel with a brake disk in FIG. 7A, and shows a rectangular region in FIG. 7A.
- the railway wheel with BD of the second embodiment is based on the configuration of the first embodiment, and the following points are changed with respect to the first embodiment.
- the minimum cross section of the space cross section between the brake disc 1 and the wheel 10 is the outer peripheral surface 2c of the disc portion 2 of the brake disc 1 and the rim portion 12 of the wheel 10. It exists in the area
- the outer peripheral surface 2c of the disc part 2 of the brake disc 1 (range from the point a1 to the point a3 in FIG. 7B) is the minimum cross-sectional part (point b4 in FIG. 7B) on the fillet surface 12bb of the rim part 12. ),
- the shape of the region (the range from point a1 to point a4 in FIG. 7B) on the outer side (surface 2a side) along the thickness direction from here is the inner peripheral surface 12b of the rim portion 12.
- the shape is along a part of the corner surface 12ba and the fillet surface 12bb.
- the outer peripheral surface 2c of the disc portion 2 of the brake disc 1 and the inner peripheral surface 12b of the rim portion 12 of the wheel 10 are closely opposed to each other.
- the outer peripheral surface 2c of the disc portion 2 is the inner peripheral surface 12b of the rim portion 12. It ’s not along the way.
- the BD-equipped railway wheel according to the second embodiment having such a configuration has the same effect as that of the first embodiment.
- FIG. 8A is a cross-sectional view along the radial direction showing the structure of a railway wheel with a brake disk according to a third embodiment of the present invention.
- FIG. 8B is a cross-sectional view locally showing the railway wheel with a brake disk in FIG. 8A, and shows a rectangular region in FIG. 8A.
- the railway wheel with BD of the third embodiment is a modification of the aspect of the second embodiment.
- the minimum cross section of the space cross section between the brake disc 1 and the wheel 10 is the outer peripheral surface 2c of the disc portion 2 of the brake disc 1 and the rim portion of the wheel 10.
- the outermost surface 2c of the disk portion 2 is present on the back surface 2b side (see point a3 in FIG. 8B).
- the outer peripheral surface 2c (range from point a1 to point a3 in FIG. 8B) of the disc portion 2 of the brake disk 1 starts from the position a3 on the back surface 2b side and extends outward (from the surface 2a side) along the thickness direction. ) Is a shape along substantially the entire corner surface 12ba and part of the fillet surface 12bb of the inner peripheral surface 12b of the rim portion 12. That is, the outer peripheral surface 2c of the disc portion 2 of the brake disc 1 is opposed to the inner peripheral surface 12b of the rim portion 12 of the wheel 10 over the entire region in the thickness direction.
- the smallest cross section of the space cross section between the brake disc 1 and the wheel 10 corresponds to the position a3 on the back surface 2b side of the outer peripheral surface 2c of the disc portion 2 of the brake disc 1, and the wheel It exists in the area
- limb parts 12 (refer point b5 in FIG. 8B).
- the BD-equipped railway wheel according to the third embodiment having such a configuration has the same effect as that of the first embodiment.
- the object of analysis is the railway wheel with BD of the first embodiment shown in FIGS. 6A and 6B as Example 1 of the present invention, and the third embodiment shown in FIGS. 8A and 8B as Example 2 of the invention.
- the railway wheel with BD was adopted.
- FIGS. 9A and 9B a railway wheel with BD in which ribs 7 with slits 7a are added between the fin portions 3 is adopted.
- the railway wheel with BD shown in FIGS. 9A and 9B is the same as the conventional railway wheel with BD shown in FIGS. 3A and 3B.
- the outer peripheral surface 2c of the disc portion 2 of the brake disc 1 is separated from the inner peripheral surface 12b of the rim portion 12 without being along.
- the invention wheels 1 and 2 and the comparative example of the railway wheel with BD each have a brake disc centrally fastened.
- the typical conditions of the model of the railway wheel with BD used for the analysis are the same as those in the unsteady gas flow analysis described above.
- the unsteady gas flow analysis method is also the same. In both the unsteady gas flow analysis and the thermal fluid analysis, the traveling speed was kept constant at 360 km / h.
- the evaluation of the air flow rate was performed by the time average of the air flow rate at the minimum cross section of the space cross section between the brake disc and the wheel and the fluctuation range thereof. The results are shown in the following Table 1, FIG. 10 and FIG.
- FIG. 10 is a diagram showing the relationship between the heat release amount and the aerodynamic sound level, which is the analysis result of the example.
- FIG. 11 is a diagram showing a change over time in the air flow rate as an analysis result of the example.
- Examples 1 and 2 of the present invention can confirm that the aerodynamic sound level can be further reduced while the cooling performance is equal to or higher than that of the comparative example.
- the inventive examples 1 and 2 have an area of the minimum cross-sectional portion larger than that of the comparative example, so that the average air flow rate is increased and the cooling performance is high.
- Examples 1 and 2 of the present invention have a smaller fluctuation range of the air flow rate than the comparative example, and improve the quietness. From this, it can be said that the quietness of the railway wheel with BD and the cooling performance of the brake disc at the time of braking can be appropriately controlled by appropriately changing the area of the minimum cross section which is a design factor.
- the railway wheel with a brake disc of the present invention can be effectively used for any railway vehicle having a disc brake, and is particularly useful for a high-speed railway vehicle.
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Abstract
Description
図3A及び図3Bは、特許文献3に開示された従来のBD付き鉄道車輪の構造を局所的に示す図であって、図3Aはブレーキディスクの裏面を内周面側から見た斜視図を、図3Bは径方向に沿った断面図をそれぞれ示す。これらの図に示すように、特許文献3に開示されたBD付き鉄道車輪では、ブレーキディスク1について、隣り合うフィン部3同士の間に円周方向に沿ってリブ7を追加し、更に、このリブ7の円周方向の中央部に径方向に沿ってスリット7aが形成されている。
・ブレーキディスクが簡素な形状で生産性に優れたものであること;
・高速走行中の空力音を有効に低減すること。
ボス部、リム部、及びこれらを結合する板部を備えた鉄道車両用の車輪と、
表面側を摺動面とするドーナツ形の円板部、及び前記円板部の裏面に放射状に突設された複数のフィン部を備えたブレーキディスクと、を備え、
2枚の前記ブレーキディスクが個々の前記摺動面を外向きにした状態で前記車輪の前記板部を挟み込み、前記摺動面内の領域で締結されたブレーキディスク付き鉄道車輪であって、
前記ブレーキディスクと前記車輪との間に形成された空間を円周方向に沿って横断する断面の面積について、この断面積の最小となる最小断面部が、前記円板部の外周面と前記リム部の内周面とで形成される領域に存在し、
前記円板部の前記外周面が、前記最小断面部を起点にした外側の領域で、前記リム部の前記内周面に沿った形状である。
・ブレーキディスクが簡素な形状で生産性に優れたものであること;
・高速走行中の空力音を有効に低減できること。
<ブレーキディスク>
・新幹線(R)用の鍛鋼ディスク
・円板部の内径:417mm、円板部の外径:715mm
・円板部の摺動面からフィン部の先端面(車輪板部との接触面)までの長さ:45mm
・直径が560mmの同一円上に中心が位置する12個のボルト孔を等間隔に形成し、各ボルト孔にボルトを挿通してブレーキディスクと車輪を締結。
<車輪>
・新幹線(R)用の圧延車輪
・内径:196mm、外径:860mm
図6Aは、本発明の第1実施形態であるブレーキディスク付き鉄道車輪の構造を示す、径方向に沿った断面図である。図6Bは、図6Aのブレーキディスク付き鉄道車輪を局所的に示す断面図であり、図6Aの矩形領域を示している。以下では、前記図1A、図1B及び図2A~図2Cに示す従来のBD付き鉄道車輪と共通する部分には同一の符号を付し、重複する説明は適宜省略する。
図7Aは、本発明の第2実施形態であるブレーキディスク付き鉄道車輪の構造を示す、径方向に沿った断面図である。図7Bは、図7Aのブレーキディスク付き鉄道車輪を局所的に示す断面図であり、図7Aの矩形領域を示している。第2実施形態のBD付き鉄道車輪は、前記第1実施形態の構成を基本とし、前記第1実施形態に対し以下の点を変更したものである。
図8Aは、本発明の第3実施形態であるブレーキディスク付き鉄道車輪の構造を示す、径方向に沿った断面図である。図8Bは、図8Aのブレーキディスク付き鉄道車輪を局所的に示す断面図であり、図8Aの矩形領域を示している。第3実施形態のBD付き鉄道車輪は、前記第2実施形態の態様を変形したものである。
下記の表1、図10及び図11に結果を示す。
2:円板部、 2a:表面、 2b:裏面、 2c:外周面、
3:フィン部、 4:ボルト孔、 5:ボルト、 6:ナット、
7:リブ、 7a:スリット、
10:車輪、 11:ボス部、
12:リム部、 12a:側面、 12b:内周面、
12ba:コーナー面、 12bb:フィレット面、
13:板部、 13a:側面
Claims (5)
- ボス部、リム部、及びこれらを結合する板部を備えた鉄道車両用の車輪と、
表面側を摺動面とするドーナツ形の円板部、及び前記円板部の裏面に放射状に突設された複数のフィン部を備えたブレーキディスクと、を備え、
2枚の前記ブレーキディスクが個々の前記摺動面を外向きにした状態で前記車輪の前記板部を挟み込み、前記摺動面内の領域で締結されたブレーキディスク付き鉄道車輪であって、
前記ブレーキディスクと前記車輪との間に形成された空間を円周方向に沿って横断する断面の面積について、この断面積の最小となる最小断面部が、前記円板部の外周面と前記リム部の内周面とで形成される領域に存在し、
前記円板部の前記外周面が、前記最小断面部を起点にした外側の領域で、前記リム部の前記内周面に沿った形状である、ブレーキディスク付き鉄道車輪。 - 請求項1に記載のブレーキディスク付き鉄道車輪において、
前記リム部の前記内周面は、前記リム部の側面につながるコーナー面、及び前記コーナー面と前記板部の側面とにつながるフィレット面を含み、
前記最小断面部は、前記リム部の前記内周面のうちで前記コーナー面と前記フィレット面との境界に存在する、ブレーキディスク付き鉄道車輪。 - 請求項1に記載のブレーキディスク付き鉄道車輪であって、
前記リム部の前記内周面は、前記リム部の側面につながるコーナー面、及び前記コーナー面と前記板部の側面とにつながるフィレット面を含み、
前記最小断面部は、前記リム部の前記内周面のうちで前記フィレット面の領域に存在する、ブレーキディスク付き鉄道車輪。 - 請求項3に記載のブレーキディスク付き鉄道車輪であって、
前記最小断面部は、前記円板部の前記外周面のうちで最も裏面側に存在する、ブレーキディスク付き鉄道車輪。 - 請求項2~4のいずれかに記載のブレーキディスク付き鉄道車輪において、
前記リム部の前記内周面における前記コーナー面は、軸方向に沿った断面での輪郭形状が円弧状である、ブレーキディスク付き鉄道車輪。
Priority Applications (6)
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ES15748878T ES2732822T3 (es) | 2014-02-12 | 2015-02-03 | Rueda de vehículo ferroviario con discos de freno |
EP15748878.4A EP3106317B1 (en) | 2014-02-12 | 2015-02-03 | Railway wheel with brake discs |
JP2015562723A JP6123916B2 (ja) | 2014-02-12 | 2015-02-03 | ブレーキディスク付き鉄道車輪 |
KR1020167019062A KR101863471B1 (ko) | 2014-02-12 | 2015-02-03 | 브레이크 디스크가 부착된 철도 차륜 |
CN201580008044.1A CN106029397B (zh) | 2014-02-12 | 2015-02-03 | 带制动盘的铁道车轮 |
US15/113,849 US10259475B2 (en) | 2014-02-12 | 2015-02-03 | Railway wheel with brake disc |
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JP2014-024784 | 2014-02-12 | ||
JP2014024784 | 2014-02-12 |
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CN (1) | CN106029397B (ja) |
ES (1) | ES2732822T3 (ja) |
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WO2017099073A1 (ja) * | 2015-12-08 | 2017-06-15 | 東日本旅客鉄道株式会社 | 鉄道車両用ブレーキディスク |
JP2020122553A (ja) * | 2019-01-31 | 2020-08-13 | 株式会社栗本鐵工所 | ブレーキディスク |
CN111936759A (zh) * | 2018-04-03 | 2020-11-13 | 日本制铁株式会社 | 空气动力音降低部件、铁道车辆用制动盘单元、铁道车辆用盘式制动器、铁道车辆用车轮及铁道车辆 |
JP7410389B2 (ja) | 2019-09-20 | 2024-01-10 | 日本製鉄株式会社 | 防音車輪及び車輪ユニット |
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WO2021065392A1 (ja) * | 2019-09-30 | 2021-04-08 | 日本製鉄株式会社 | 鉄道車両用ブレーキディスクユニット |
CN115780804B (zh) * | 2022-11-25 | 2023-12-01 | 湖南湘投轻材科技股份有限公司 | 制动盘生坯成形模具、成形方法及制动盘的近净成形方法 |
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- 2015-02-03 EP EP15748878.4A patent/EP3106317B1/en active Active
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JPWO2015122148A1 (ja) | 2017-03-30 |
EP3106317A1 (en) | 2016-12-21 |
CN106029397A (zh) | 2016-10-12 |
CN106029397B (zh) | 2017-12-12 |
KR101863471B1 (ko) | 2018-05-31 |
US10259475B2 (en) | 2019-04-16 |
JP6123916B2 (ja) | 2017-05-10 |
EP3106317A4 (en) | 2018-01-03 |
US20160339932A1 (en) | 2016-11-24 |
KR20160098443A (ko) | 2016-08-18 |
TWI572790B (zh) | 2017-03-01 |
ES2732822T3 (es) | 2019-11-26 |
TW201542410A (zh) | 2015-11-16 |
MY178739A (en) | 2020-10-20 |
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