WO2011155478A1 - ブレーキディスク - Google Patents
ブレーキディスク Download PDFInfo
- Publication number
- WO2011155478A1 WO2011155478A1 PCT/JP2011/063014 JP2011063014W WO2011155478A1 WO 2011155478 A1 WO2011155478 A1 WO 2011155478A1 JP 2011063014 W JP2011063014 W JP 2011063014W WO 2011155478 A1 WO2011155478 A1 WO 2011155478A1
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- WO
- WIPO (PCT)
- Prior art keywords
- groove
- brake
- sliding
- brake disc
- reduction
- Prior art date
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Classifications
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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
- F16D65/12—Discs; Drums for disc brakes
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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
- F16D2065/1308—Structure one-part
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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
- F16D2065/1316—Structure radially segmented
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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
- F16D2065/134—Connection
- F16D2065/1356—Connection interlocking
- F16D2065/1368—Connection interlocking with relative movement both radially and axially
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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
- F16D2065/134—Connection
- F16D2065/1392—Connection elements
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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
- F16D2065/134—Connection
- F16D2065/1392—Connection elements
- F16D2065/1396—Ancillary resilient elements, e.g. anti-rattle or retraction springs
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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
- F16D69/00—Friction linings; Attachment thereof; Selection of coacting friction substances or surfaces
- F16D2069/004—Profiled friction surfaces, e.g. grooves, dimples
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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
- F16D65/12—Discs; Drums for disc brakes
- F16D65/128—Discs; Drums for disc brakes characterised by means for cooling
Definitions
- the present invention relates to a brake disc that can be suitably used for a motorcycle.
- a brake disc having a mounting portion to a wheel and a sliding portion with a brake pad is formed by press-molding a single metal plate, and the brake pad is press-contacted.
- a so-called floating brake disc having an annular sliding disc having a sliding portion, a hub disc mounted inside the sliding disc, and a plurality of connecting means for connecting both discs in a floating state has been widely put into practical use. ing.
- brake discs with a plurality of reduced holes formed in a predetermined arrangement for the purpose of reducing overall weight, improving heat dissipation in the sliding portion, cleaning the brake pads, etc. are also widely used. (For example, refer to Patent Documents 1 and 2).
- the weight of the brake disc can be reduced, the heat dissipation at the sliding portion can be improved, and the brake pad surface is cleaned by the opening edge of the reduction holes. Therefore, it is possible to prevent foreign matter from adhering to the sliding surface with the brake pad, and to prevent a reduction in braking performance.
- the heat capacity is smaller than in the other parts, so the temperature fluctuation in the part between the holes becomes larger than the other parts, and when the temperature falls There is a problem that the portion between the holes is damaged by so-called heat shrinkage, which is caused to cool and shrink before the portion.
- the sliding part is configured to be narrow and the distance between the reduction holes tends to be small due to the demand for weight reduction. Occurrence is one of the important issues.
- An object of the present invention is to provide a brake disk capable of suppressing brake pad wear, improving braking performance, and preventing heat shrinkage between the reduction holes.
- a brake disc according to the present invention is a brake disc for a motorcycle in which a plurality of weight reducing holes for weight reduction are formed in a sliding portion with a brake pad, on at least one sliding surface of the sliding portion, A plurality of grooves are formed at set intervals in the circumferential direction so as to pass through a plurality of adjacent reduction holes.
- a plurality of reduction holes are formed in the sliding part, so that the weight of the brake disk can be reduced, and the heat dissipation in the sliding part can be improved, and the brake pad surface at the opening edge of the reduction hole Therefore, it is possible to prevent a reduction in braking performance due to foreign matters adhering to the sliding surface with the brake pad.
- the braking portion can also reduce the weight of the brake disk, improve the heat dissipation in the sliding portion, and improve the cleaning effect on the surface of the brake pad.
- the heat capacity of the portion between the holes where the mitigation holes are adjacently arranged is smaller than that of the other portions, the temperature fluctuation in the portion between the holes tends to be larger than the other portions.
- a groove is formed in the portion between the holes, and since the frictional heat with the brake pad is not generated by the portion between the holes being in direct contact with the brake pad, generation of a heat spot in the portion between the holes is suppressed.
- the groove portion is formed so as to pass through a portion where heat shrinkage easily occurs between adjacent reduction holes and reduction holes arranged on both sides thereof. If comprised in this way, generation
- the groove is formed, for example, in a linear or curved shape across the inner and outer peripheral portions of the sliding portion, or in the radial direction of the sliding portion or the radius of the sliding portion, depending on the arrangement of the reduction holes. It can be formed in an inclined shape with an angle in one direction with respect to the direction.
- the groove portion is formed in an inclined shape so that the inner peripheral side of the groove portion is located on the front side in the rotation direction of the brake disc relative to the outer peripheral side.
- the groove portion is formed as in the present invention. It is preferable because the foreign matter that has entered the guide is guided to the outer peripheral side of the brake disc by contact with the brake pad and can be efficiently discharged to the outside.
- the groove is formed in a square groove shape. With this configuration, even if the sliding portion is worn, the opening width of the groove portion does not change, so that it is possible to prevent the brake operation feeling from being fluctuated slightly due to wear of the sliding portion, and a stable operation feeling can be obtained. This is preferable.
- the width of the groove is set to be the same as or larger than the diameter of the reduction hole, and the groove is formed so as to include the reduction hole.
- the width of the groove can be set to a size smaller than the diameter of the reduction hole, but if configured in this way, a corner that faces the reduction hole is formed at the intersection of the groove and the reduction hole, and the corner is easily chipped. Therefore, it is preferable to configure as in the present invention because the corner portion can be eliminated and the durability of the brake disk can be improved.
- the weight of the brake disc can be reduced, and the heat dissipation in the sliding portion can be improved, and the opening edge of the reduction hole Since the surface of the brake pad can be cleaned, the deterioration of the braking performance due to foreign matter adhering to the sliding surface with the brake pad can be prevented.
- the braking portion can also reduce the weight of the brake disk, improve the heat dissipation in the sliding portion, and improve the cleaning effect on the surface of the brake pad.
- the heat capacity of the portion between the holes where the mitigation holes are adjacently arranged is smaller than that of the other portions, the temperature fluctuation in the portion between the holes tends to be larger than the other portions.
- a groove is formed in the portion between the holes, and since the frictional heat with the brake pad is not generated by the portion between the holes being in direct contact with the brake pad, generation of a heat spot in the portion between the holes is suppressed.
- FIG. 1 Front view of brake disc Perspective view of sliding disk Front view of sliding disk IV-IV sectional view of FIG. V-V cross-sectional view of Fig. 1 Sectional view taken along line VI-VI in Figure 1 Front view of the brake disc of Example 2 Front view of comparative example brake disc Schematic illustration of bench test machine Abrasion amount graph Friction coefficient graph
- the floating brake disc 1 is a brake disc for a motorcycle, and is fitted with a flat annular slide disc 10 and an internal fit with a predetermined gap inside the slide disc 10. And a plurality of connecting means 30 for connecting the sliding disk 10 and the hub disk 20 in a floating state.
- the present invention can be applied to brake discs other than motorcycles and also to brake discs made of a single metal plate.
- the sliding disk 10 is an annular sliding portion 11 to which the brake pad 2 is slidably contacted after processing a flat metal plate made of stainless steel or carbon steel having excellent heat resistance into the shape of the annular sliding disk 10. It is manufactured by heat treatment.
- the hub disk 20 is made of a light metal material such as an aluminum alloy in order to reduce the weight, for example.
- the hub disk 20 is formed in a flat disk shape, and a mounting hole 21 through which an end of a wheel hub (not shown) is inserted is formed at the center of the hub disk 20 and surrounds the mounting hole 21.
- a plurality of bolt insertion holes 22 for attachment to the wheel hub are formed.
- the sliding disk 10 and the hub disk 20 are arranged in the same plane.
- the sliding disk 10 and the hub disk 20 are It is also possible to arrange the discs 1 in parallel planes that are spaced apart in the thickness direction (axial direction). Further, the thicknesses of both the disks 10 and 20 can be set to be the same or different.
- the present invention is characterized by the sliding disk 10, and the existing configuration of the hub disk 20 can be adopted as the configuration of the hub disk 20.
- the connecting means 30 is provided between the sliding disk 10 and the hub disk 20 at regular intervals in the circumferential direction.
- the sliding disk 10 and the hub disk 20 are connected in a floating state by eight connecting means 30, but the disks 10, 20 are connected in a floating state by a number of connecting means 30 other than eight. Is also possible.
- a semicircular braking side connecting recess 15 is formed in the inner peripheral portion of the sliding disk 10 at the position where the connecting means 30 is provided, and the hub disk
- a semi-circular hub-side connecting recess 25 is formed on the outer peripheral portion 20 so as to face the braking-side connecting recess 15, and in a state where both the disks 10, 20 are combined, the connecting recess 15, 25, a substantially circular connecting hole 31 is formed.
- a connection pin 32 is mounted in the connection hole 31, and relative rotation and relative movement in the axial direction of both the disks 10 and 20 are restricted by the connection pin 32.
- the connecting pin 32 is externally provided with a spring member 33 made of a disc spring and a washer 34 for receiving the spring member 33, and both disks 10 and 20 are constantly urged by the spring member 33 so as to be located in the same plane, Supported in a floating state.
- the connection means 30 it is also possible to employ
- a plurality of reduction holes 12 are formed in the sliding portion 11 in a predetermined arrangement for the purpose of improving the heat dissipation of the brake disc 1 and reducing the weight and cleaning the sliding surface 11a of the brake pad 2.
- the arrangement of the reduction holes 12 is preferably uniformly distributed with respect to the sliding portion 11 so that the effect of heat dissipation and weight reduction can be obtained uniformly over the entire circumference of the brake disk 1.
- the brake pad 2 rotates on the sliding surface 11a of the brake disk 1 by a certain angle, so that the entire surface of the sliding surface 11a of the brake pad 2 can be cleaned with the lip of the reduction hole 12. It is preferable to arrange it at intervals in the direction and the radial direction.
- a plurality of reduction holes 12 are formed at intervals in the radial direction on a line segment in the radial direction at a set interval in the circumferential direction, or with respect to the radial direction at a set interval in the circumferential direction.
- a plurality of reduction holes 12 are formed at intervals in the radial direction on an angled straight line, or are spaced in a radial direction on a curve that is angled with respect to the radial direction at set intervals in the circumferential direction.
- a plurality of reducing holes 12 can be formed. For example, in the brake disc 1 shown in FIG.
- the brake discs 1 are arranged at intervals in the radial direction on 48 straight lines L having an angle of 25 ° with respect to the radial direction at intervals of 7.5 ° in the circumferential direction.
- Three, two, three, two, two, and two total 14 units form one set, and eight sets in the circumferential direction, a total of 112 reduction holes 12 are formed.
- the diameter of the reduction hole 12 is preferably set to 4 to 10 mm in order to sufficiently secure the mechanical strength and braking performance of the brake disc 1, and is set to 5 mm in the brake disc 1 shown in FIG.
- the reduction hole 12 it is possible to form a long and narrow slit-like hole other than the round hole as shown in FIGS. 1 can be appropriately set in consideration of mechanical strength, braking performance, designability, heat dissipation, and the like.
- a plurality of groove portions 13 are formed at set intervals in the circumferential direction so as to pass through a plurality of adjacent reduction holes 12, and the plurality of groove portions 13 are formed in the sliding portion 11. It is formed in a linear shape or a curved shape so as to cross the sliding portion 11 over the peripheral portion and the outer peripheral portion. More specifically, the plurality of grooves 13 pass through the reduction holes 12 and are arranged on radial line segments arranged at set intervals in the circumferential direction or at radii arranged at set intervals in the circumferential direction.
- the filter so as to pass through a portion where heat shrinkage easily occurs between adjacent reduction holes 12 and the reduction holes 12 arranged on both sides thereof. That is, in the portion between the holes where the distance between the adjacent reduction holes 12 is smaller than the distance between the other adjacent reduction holes 12, heat shrinkage is likely to occur.
- the groove 13 passes through the reduction hole 12 only at a portion where the three reduction holes 12 are connected on a straight line L having an angle of 25 ° with respect to the radial direction.
- 16 pieces are formed on one side of the sliding portion 11 and a total of 32 pieces are formed on both sides.
- the groove 13 is preferably formed on both surfaces of the sliding portion 11 in order to uniformly set the braking performance on both surfaces of the sliding portion 11, but may be formed only on one surface.
- the groove 13 is preferably formed on both surfaces of the sliding part 11, it is preferable to form in the same position of both surfaces of the sliding part 11, However, Forming in a different position is also possible.
- An opening 13 a that opens outward is formed at the outer peripheral end of the groove 13, and the foreign matter that has entered the groove 13 moves to the outer peripheral side of the groove 13 by centrifugal force due to the rotation of the brake disc 1. , And is configured to be discharged to the outside from the opening 13a.
- the groove portion 13 is formed in a linear shape or a curved shape with an angle with respect to the radial direction, as shown in FIG. 1, the rotation direction of the brake disk 1 is greater on the inner peripheral side of the groove portion 13 than on the outer peripheral side. It is preferable that the groove portion 13 is formed in an inclined shape with respect to the radial direction so as to be positioned on the front side of (indicated by arrow A in FIG. 1).
- invaded in the groove part 13 will be guided to the outer peripheral side of the brake disc 1 by contact with the brake pad 2 at the time of braking, and a foreign material can be discharged
- the cross-sectional shape in the direction perpendicular to the length direction of the groove portion 13 can be arbitrarily set, but it is formed in a rectangular groove shape such as a rectangle or a square, and the inner surface of the groove portion 13 extends in the thickness direction of the sliding portion 11. If formed, the opening width of the groove portion 13 does not change even if the brake disc 1 is worn. Therefore, it is possible to prevent the brake operation feeling from being slightly changed due to the wear of the sliding portion 11, and a stable operation feeling can be obtained. Therefore, it is preferable.
- the depth of the groove portion 13 can be set to an arbitrary depth that can ensure the required mechanical strength of the brake disk 1, and the ratio of the groove portion 13 in the thickness direction of the sliding portion 11 is 70% or less, Preferably, it is set to 5% to 60%.
- the sum of the depths of the two front and back grooves 13 is set to 70% or less, preferably 5% to 60% of the thickness of the sliding part 11. Therefore, when the groove portion 13 is formed at a different position of the sliding portion 11, the depth of one groove portion 13 is 70% or less, preferably 5% to 60% of the thickness of the sliding portion 11. Will be set to.
- the depth of the groove portion 13 is set to 10% (0.5 mm) of the thickness of the sliding portion 11.
- the width of the groove 13 can be set to a size smaller than the diameter of the reduction hole 12, but when configured in this way, a corner that faces the reduction hole 12 is formed at the intersection of the groove 13 and the reduction hole 12. Therefore, it is preferable that the corner portion is easily chipped, so that the groove portion 13 is formed so as to include the reduction hole 12 by setting the same dimension as or larger than the diameter of the reduction hole 12. Further, as the groove portion 13, groove portions having different widths and different depths can be mixed, and it is also possible to form the groove portion 13 whose width and depth are changed in the middle portion in the length direction.
- the sliding disk is made of a stainless steel plate having a thickness of 5 mm and a diameter of 200 mm, and a reduction hole 12 made of a round hole having a diameter of 5 mm is arranged in the sliding part 11 as shown in FIG. 1.
- 114 of the 48 straight lines L formed at an angle of 25 ° with respect to the radial direction arranged at set intervals in the circumferential direction so as to pass through the reduction holes 12 and pass through the three reduction holes 12.
- the brake disc 1 using the sliding disc 10 in which the groove portion 13 having a width of 5 mm was formed on both sides on the 16 straight lines L arranged as described above was manufactured.
- Example 2 As shown in FIG. 7, a brake disc 1A using a sliding disk 10A having the same configuration as that of Example 1 was manufactured except that the groove 13 was inclined in the opposite direction.
- a bench testing machine 40 As a testing machine, a bench testing machine 40 as shown in FIG. 9 was used.
- the bench test machine 40 controls the AC motor 43 that rotates the brake disk 1 via a belt 41 and an inertia 42, an inverter (not shown) that controls the rotational speed of the AC motor 43, and the test disk 1.
- a caliper 44 for applying power
- a master cylinder 45 for supplying brake fluid pressure to the caliper 44
- a load cell 47 for measuring brake torque generated during braking via an arm 46 mounted coaxially with the caliper 44
- a control means 48 for controlling the AC motor 43 and the master cylinder 45 is provided.
- the AC motor 43 is controlled by an inverter to control the rotational speed of the brake disc 1, and the brake fluid pressure to the caliper 44 is controlled by the master cylinder 45, so that a brake comprising a pair of sintered pads of the caliper 44 is formed. While holding the brake disc 1 with the pad 2, the brake torque at that time can be measured by the load cell 47.
- the brake discs 1, 1A, 1B of Examples 1 and 2 and the comparative example were set on the bench test machine 40, and after sliding 10 times under the test conditions shown in Table 1, Two types of main tests were performed three times for each of the brake disks 1, 1A, and 1B when the temperature of the brake pad was set to 100 ° C and when the temperature was set to 200 ° C. And the thickness of the brake pad before and behind a test was measured, the amount of wear of a brake pad was measured, and the result shown in Table 2 and FIG. 10 was obtained. Moreover, the friction coefficient of the braking part was calculated by the following formula, and the results shown in Table 2 and FIG. 11 were obtained.
- Friction coefficient (T / P) ⁇ (1 / (R ⁇ S)) ⁇ (1/2) ⁇ (1/100)
- T Torque [Nm] obtained from the product of the length of the arm 46 and the measured value of the load cell 47
- P Hydraulic pressure to the caliper 44 [MPa]
- R Effective brake radius [m]
- S Cylinder area obtained from the piston diameter of the caliper 44 [cm 2 ]
- Examples 1 and 2 in which the groove 13 is formed have less brake pad wear than the comparative example having no groove 13, and the service life of the brake pad can be extended. Moreover, it can be seen from Table 2 and FIG. 11 that Examples 1 and 2 in which the groove 13 is formed have a larger friction coefficient and higher braking performance than the comparative example that does not have the groove 13. Further, although the amount of wear of the brake pad is larger than that of the second embodiment, it can be understood that the first embodiment is more preferable because the friction coefficient is increased and the braking performance is increased.
- the maximum temperature of the sliding disk 10 is within the set temperature range. After the braking state and the cooling state are repeated until the temperature is maintained at a substantially constant level, the brake disk is removed from the bench test machine 40, and the heat sink of the sliding disk 10 is generated. It was confirmed by visual observation.
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Abstract
Description
図1~図6に示すように、フローティングブレーキディスク1は、自動二輪車用のブレーキディスクであり、平板環状の摺動ディスク10と、摺動ディスク10の内側に所定の隙間をあけて内嵌装着したハブディスク20と、摺動ディスク10とハブディスク20とをフローティング状態に連結する複数の連結手段30とを備えている。ただし、本発明は、自動二輪車以外のブレーキディスクに対しても適用できるし、一枚物の金属板からなるブレーキディスクに対しても適用できる。
実施例1として、図1に示すように、摺動ディスクとして、厚さ5mm、直径200mmのステンレス鋼板からなり、摺動部11に直径5mmの丸孔からなる軽減孔12を図1に示す配置で114個形成し、軽減孔12と通るように周方向に設定間隔おきに配置した半径方向に対して25°の角度を付けた48本の直線Lのうちの、3つの軽減孔12を通るように配置した16本の直線L上に、幅5mmの溝部13を両面に形成した摺動ディスク10を用いたブレーキディスク1を製作した。また、実施例2として、図7に示すように、溝部13を逆向きに傾斜状に形成した以外は実施例1と同じ構成の摺動ディスク10Aを用いたブレーキディス1Aを製作した。また、比較例として、図8に示すように、溝部13を省略した以外は実施例1と同じ構成の摺動ディスク10Bを用いたブレーキディスク1Cを製作した。
試験機として、図9に示すような台上試験機40を用いた。この台上試験機40は、ベルト41及びイナーシャ42を介してブレーキディスク1を回転駆動する交流モータ43と、交流モータ43の回転数を制御する図示外のインバータと、試験ディスク1に対して制動力を付与するためのキャリパ44と、キャリパ44へのブレーキ液圧を供給するマスターシリンダ45と、キャリパ44と同軸で取り付けたアーム46を介して制動時に発生するブレーキトルクを測定するロードセル47と、交流モータ43とマスターシリンダ45を制御する制御手段48とを備えている。そして、インバータにより交流モータ43を制御してブレーキディスク1の回転数を制御するとともに、マスターシリンダ45によりキャリパ44へのブレーキ液圧を制御して、キャリパ44の1対の焼結パッドからなるブレーキパッド2でブレーキディスク1を挟持しながら、そのときのブレーキトルクをロードセル47により測定できるように構成した。
T:アーム46の長さと、ロードセル47の測定値の積から求めたトルク[Nm]
P:キャリパ44への液圧[MPa]
R:ブレーキ有効半径[m]
S:キャリパ44のピストン径から求めたシリンダ面積[cm2]
実施例1,2及び比較例のブレーキディスク1,1A,1Bを台上試験機40にセットして、摺動ディスク10の温度を測定しながら、摺動ディスク10の素材の耐熱温度以下の設定温度、例えばJFEスチール株式会社製のステンレス鋼、JFE410DBSR*AN-U(耐熱温度650℃)からなる摺動ディスクでは、600℃±20℃の設定温度に収束するように、0.2Gの減速度で制動力を作用させた制動状態と、制動力を作用させない冷却状態とを繰り返し、例えば制動状態と冷却状態を10回繰り返して行っても、摺動ディスク10の最高温度が設定温度の範囲内に略一定に維持されるまで、制動状態と冷却状態を繰り返し行った後、ブレーキディスクを台上試験機40から取外して、摺動ディスク10における熱引けの発生を目視にて確認した。
10 摺動ディスク 11 摺動部
11a 摺動面 12 軽減孔
13 溝部 13a 開口部
15 制動側連結凹部
20 ハブディスク 21 取付孔
22 ボルト挿通孔 25 ハブ側連結凹部
30 連結手段 31 連結穴
32 連結ピン 33 バネ部材
34 座金
40 台上試験機 41 ベルト
42 イナーシャ 43 交流モータ
44 キャリパ 45 マスターシリンダ
46 アーム 47 ロードセル
48 制御手段
1A ブレーキディスク 10A 摺動ディスク
1B ブレーキディスク 10B 摺動ディスク
Claims (8)
- ブレーキパッドとの摺動部に重量軽減用の複数の軽減孔を形成した自動二輪車用のブレーキディスクであって、
前記摺動部の少なくとも一方の摺動面に、隣接する複数の軽減孔を通過するように複数の溝部を周方向に設定間隔おきに形成した、
ことを特徴とするブレーキディスク。 - 前記溝部を、隣接する軽減孔間のうちの熱引けの発生し易い部位とその両側に配置される軽減孔を通過するように形成した請求項1記載のブレーキディスク。
- 前記溝部を、前記摺動部の内周部と外周部とにわたって直線状又は湾曲状に形成した請求項1又は2記載のブレーキディスク。
- 前記溝部を、前記摺動部の半径方向に対して一方向に角度を付けて傾斜状に形成した請求項1~3のいずれか1項記載のブレーキディスク。
- 前記溝部の内周側が外周側よりもブレーキディスクの回転方向の前側に位置するように、前記溝部を傾斜状に形成した請求項1~4のいずれか1項記載のブレーキディスク。
- 前記溝部の少なくとも外周側端部を開放した請求項1~5のいずれか1項記載のブレーキディスク。
- 前記溝部を角溝状に形成した請求項1~6のいずれか1項記載のブレーキディスク。
- 前記溝部の幅を軽減孔の直径と同じ寸法或いはそれ以上の寸法に設定し、前記軽減孔を含むように溝部を形成した請求項1~7のいずれか1項記載のブレーキディスク。
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EP11792435.7A EP2581622B1 (en) | 2010-06-11 | 2011-06-07 | Brake disc |
ES11792435T ES2772136T3 (es) | 2010-06-11 | 2011-06-07 | Disco de freno |
US13/703,144 US8910756B2 (en) | 2010-06-11 | 2011-06-07 | Brake disc |
JP2012519390A JP5708646B2 (ja) | 2010-06-11 | 2011-06-07 | ブレーキディスク |
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EP (1) | EP2581622B1 (ja) |
JP (1) | JP5708646B2 (ja) |
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2015169264A (ja) * | 2014-03-06 | 2015-09-28 | 株式会社ユタカ技研 | ブレーキディスク |
US10439141B2 (en) | 2012-12-28 | 2019-10-08 | Agency For Science, Technology And Research | P-type semiconducting polymers and related methods |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5428505B2 (ja) * | 2009-04-30 | 2014-02-26 | サンスター技研株式会社 | フローティングブレーキディスクの組立方法 |
JP5516328B2 (ja) * | 2010-10-28 | 2014-06-11 | 株式会社アドヴィックス | ディスクロータ |
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EP3028983B1 (de) * | 2014-12-05 | 2018-02-07 | Zollern GmbH & Co. KG | Winde, insbesondere Freifallwinde mit einer Betriebs- und Haltebremse |
DE102016201508A1 (de) * | 2016-02-02 | 2017-08-03 | Schaeffler Technologies AG & Co. KG | Reibteil |
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DE102017117256A1 (de) * | 2017-07-31 | 2019-01-31 | Shimano Inc. | Bremsscheibenrotor |
JP7267051B2 (ja) * | 2019-03-22 | 2023-05-01 | サンスター技研株式会社 | ブレーキディスク |
US11293502B1 (en) * | 2019-06-19 | 2022-04-05 | Parker-Hannifin Corporation | Lever actuated disk parking brake for a vehicle |
Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS63196843A (ja) | 1987-02-12 | 1988-08-15 | Shimadzu Corp | 荷電ビ−ム分析装置 |
JPH0573329U (ja) * | 1992-03-11 | 1993-10-08 | 株式会社ユタカ技研 | ブレーキディスク |
JPH0628374U (ja) * | 1992-09-14 | 1994-04-15 | 日信工業株式会社 | ディスクブレーキ用ロータ |
JPH06349031A (ja) | 1993-04-14 | 1994-12-22 | Sanyo Electric Co Ltd | 磁気抵抗効果型ヘッド |
JP2002295549A (ja) | 2001-02-10 | 2002-10-09 | Dr Ing H C F Porsche Ag | ディスクブレーキ |
JP2003074604A (ja) | 2001-09-06 | 2003-03-12 | Kawasaki Heavy Ind Ltd | ブレーキディスク |
JP2003301874A (ja) | 2002-03-21 | 2003-10-24 | Alex Global Technology Inc | ブレーキディスク |
JP2005308051A (ja) * | 2004-04-20 | 2005-11-04 | Advics:Kk | ディスクロータ |
JP2009526186A (ja) * | 2006-02-07 | 2009-07-16 | フレニ ブレンボ エス.ピー.エー. | ブレーキディスク |
JP2010014190A (ja) * | 2008-07-03 | 2010-01-21 | Sunstar Engineering Inc | フローティングブレーキディスク |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6349031A (ja) | 1986-08-13 | 1988-03-01 | 宮田 和臣 | 植物栽培装置 |
JPH0573329A (ja) | 1991-08-29 | 1993-03-26 | Toshiba Corp | 画像形成装置 |
JPH0628374A (ja) | 1992-07-07 | 1994-02-04 | Chubu Nippon Denki Software Kk | 管理伝票自動発行システム |
EP1342017B1 (en) * | 2000-12-06 | 2006-02-08 | Freni Brembo S.p.A. | Motorcycle lightening disc for a disc brake and respective manufacturing method |
US7097007B2 (en) * | 2003-04-11 | 2006-08-29 | Warren Lin | Vented slot brake rotor |
US7284643B1 (en) * | 2006-07-28 | 2007-10-23 | Ching-Wen Kao | Brake disk |
US8267228B2 (en) * | 2007-01-22 | 2012-09-18 | Sunstar Engineering Inc. | Brake disc having corrugated outer periphery |
US8146719B2 (en) * | 2008-04-25 | 2012-04-03 | GM Global Technology Operations LLC | Disk brake friction surfaces with tunable indent patterns for minimizing brake pad radial taper wear |
WO2010004913A1 (ja) * | 2008-07-08 | 2010-01-14 | 株式会社ユタカ技研 | フローティング型ブレーキディスク |
-
2011
- 2011-06-07 US US13/703,144 patent/US8910756B2/en active Active
- 2011-06-07 JP JP2012519390A patent/JP5708646B2/ja active Active
- 2011-06-07 ES ES11792435T patent/ES2772136T3/es active Active
- 2011-06-07 EP EP11792435.7A patent/EP2581622B1/en active Active
- 2011-06-07 WO PCT/JP2011/063014 patent/WO2011155478A1/ja active Application Filing
Patent Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS63196843A (ja) | 1987-02-12 | 1988-08-15 | Shimadzu Corp | 荷電ビ−ム分析装置 |
JPH0573329U (ja) * | 1992-03-11 | 1993-10-08 | 株式会社ユタカ技研 | ブレーキディスク |
JPH0628374U (ja) * | 1992-09-14 | 1994-04-15 | 日信工業株式会社 | ディスクブレーキ用ロータ |
JPH06349031A (ja) | 1993-04-14 | 1994-12-22 | Sanyo Electric Co Ltd | 磁気抵抗効果型ヘッド |
JP2002295549A (ja) | 2001-02-10 | 2002-10-09 | Dr Ing H C F Porsche Ag | ディスクブレーキ |
JP2003074604A (ja) | 2001-09-06 | 2003-03-12 | Kawasaki Heavy Ind Ltd | ブレーキディスク |
JP2003301874A (ja) | 2002-03-21 | 2003-10-24 | Alex Global Technology Inc | ブレーキディスク |
JP2005308051A (ja) * | 2004-04-20 | 2005-11-04 | Advics:Kk | ディスクロータ |
JP2009526186A (ja) * | 2006-02-07 | 2009-07-16 | フレニ ブレンボ エス.ピー.エー. | ブレーキディスク |
JP2010014190A (ja) * | 2008-07-03 | 2010-01-21 | Sunstar Engineering Inc | フローティングブレーキディスク |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10439141B2 (en) | 2012-12-28 | 2019-10-08 | Agency For Science, Technology And Research | P-type semiconducting polymers and related methods |
JP2015169264A (ja) * | 2014-03-06 | 2015-09-28 | 株式会社ユタカ技研 | ブレーキディスク |
Also Published As
Publication number | Publication date |
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EP2581622B1 (en) | 2019-12-18 |
US8910756B2 (en) | 2014-12-16 |
JPWO2011155478A1 (ja) | 2013-08-01 |
JP5708646B2 (ja) | 2015-04-30 |
US20130112515A1 (en) | 2013-05-09 |
ES2772136T3 (es) | 2020-07-07 |
EP2581622A1 (en) | 2013-04-17 |
EP2581622A4 (en) | 2018-03-07 |
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