WO2017006803A1 - Disc brake device - Google Patents

Disc brake device Download PDF

Info

Publication number
WO2017006803A1
WO2017006803A1 PCT/JP2016/069088 JP2016069088W WO2017006803A1 WO 2017006803 A1 WO2017006803 A1 WO 2017006803A1 JP 2016069088 W JP2016069088 W JP 2016069088W WO 2017006803 A1 WO2017006803 A1 WO 2017006803A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake device
disc brake
cylinder unit
rotor
piston
Prior art date
Application number
PCT/JP2016/069088
Other languages
French (fr)
Japanese (ja)
Inventor
吉川　和宏
康平 野間
Original Assignee
曙ブレーキ工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2016022346A external-priority patent/JP6680554B2/en
Application filed by 曙ブレーキ工業株式会社 filed Critical 曙ブレーキ工業株式会社
Priority to US15/741,775 priority Critical patent/US10670092B2/en
Priority to EP16821272.8A priority patent/EP3321535B1/en
Priority to CN201680040608.4A priority patent/CN107850143B/en
Publication of WO2017006803A1 publication Critical patent/WO2017006803A1/en

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/74—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with electrical assistance or drive
    • 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
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper 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
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
    • F16D55/2265—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
    • F16D55/227—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing by two or more pins
    • 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
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes

Definitions

  • the present invention relates to a disc brake device.
  • Examples of the floating type disc brake device in which the cylinder includes two pistons, ie, the first piston and the second piston, include those disclosed in Patent Document 1 and Patent Document 2.
  • Each of the disk brake devices disclosed in Patent Document 1 and Patent Document 2 has a configuration in which a cylinder including a first piston and a second piston and a support for fixing the disk brake device to a vehicle are integrally formed. It is taken. Further, the brake pad is configured to be supported by a slide pin for sliding the body on both the inner side and the outer side.
  • an object of the present invention is to provide a disc brake device that can reduce the load on the slide pin and eliminate the fear of insufficient strength during braking.
  • a body, a support, and a cylinder unit are configured separately, and the cylinder unit is a floating type disc brake device in which a first piston and a second piston are accommodated, and the cylinder unit is A disc brake device that is fixed to arm portions provided on both a return side and a return side of a rotor in a support via a cylinder mounting portion disposed on an outer peripheral side of the cylinder unit.
  • the cylinder unit plays a role as a strength member of the support, and when the braking torque is applied to the arm portion, the arm portion is located on the rotor delivery side. Spreading can be suppressed. For this reason, the disc brake device can obtain a necessary and sufficient strength even when the support is made thinner and lighter.
  • the cylinder unit plays a role as a strength member of the support, and when the braking torque is applied to the arm portion, the arm portion is prevented from spreading to the rotor delivery side. can do. Further, since the distance from the torque receiving position to the fixed position in the arm portion is increased, it is possible to obtain a large durability with a small reinforcement by the lever principle. For this reason, the disc brake device can obtain a necessary and sufficient strength even when the support is made thinner and lighter.
  • a disc brake device having a configuration as described in any one of (1) to (4) above, wherein the arrangement position of the cylinder unit is radially inner than the fixed position for fixing the cylinder unit.
  • the space is provided between the two fixed positions positioned on the side of the rotor and located on the return side and the return side of the rotor, and the body includes a space in the space provided between the fixed positions.
  • a disc brake device in which a main bridge for connecting an inner side and an outer side of the body is provided on a turning-in side and a turning-out side of the rotor, respectively.
  • the main bridge constituting the body can be passed through the configured space. As a result, it is possible to prevent a decrease in rigidity while reducing the size of the entire disc brake device.
  • the rigidity of the body can be increased.
  • a disc brake device having the configuration as described in (6) above, wherein a disc bridge device provided with a center bridge extending from the connection portion to the inner side of the body.
  • the rigidity of the body can be further increased.
  • a disc brake device having a configuration as described in any one of (1) to (7) above, wherein the support and the cylinder unit are made of different materials.
  • the disc brake device can balance light weight and strength, improve workability, and cost.
  • a disc brake device having a configuration as described in any one of (1) to (8) above, wherein the first piston and the second piston generate a pressing force by power other than hydraulic pressure. Disc brake device.
  • the disc brake device can be applied even in an environment where the hydraulic unit cannot be used, and the versatility can be further improved.
  • the disc brake device having the above-described configuration, it is possible to reduce the load on the slide pin and eliminate the fear of insufficient strength during braking.
  • FIG. 1 is a front view showing a configuration of a disc brake device according to an embodiment of the present invention.
  • FIG. 2 is a left side view showing the configuration of the disc brake device according to the present embodiment.
  • 3 is a cross-sectional view taken along the line AA in FIG.
  • FIG. 4 is a front view showing a configuration of a cylinder unit constituting the disc brake device according to the present embodiment.
  • FIG. 5 is a partially exploded perspective view of the disc brake device according to the present embodiment.
  • FIG. 6 is an exploded perspective view of the cylinder unit according to the present embodiment.
  • FIG. 7 is a view showing a first modification of the cylinder mounting portion in the cylinder unit according to the present embodiment.
  • FIG. 8 is a view showing a second modification of the cylinder mounting portion in the cylinder unit according to the present embodiment.
  • FIG. 9 is a view showing a third modification of the cylinder mounting portion in the cylinder unit according to the present embodiment.
  • FIG. 10 is a diagram showing a first modification example of the form of the body according to the present embodiment.
  • FIG. 11 is a diagram illustrating a second modification example of the form of the body according to the present embodiment.
  • FIG. 12 is a diagram illustrating a configuration example of a cylinder unit in which the opening surfaces of the bleeder hole and the inlet hole according to the present embodiment are arranged toward the inner side oblique outer circumferential direction of the rotor.
  • FIG. 13 is a diagram showing a configuration example of a cylinder unit in which the opening surfaces of the bleeder hole / inlet hole according to the present embodiment are arranged toward the axial inner side of the rotor.
  • FIG. 14 is a plan view showing a state in which a body having a center bridge is assembled to the cylinder unit shown in FIG.
  • FIG. 15 is a right side view showing an example of a disc brake device including a drive mechanism other than hydraulic pressure.
  • FIG. 1 in the drawings is a front view showing a configuration of a disc brake device according to one embodiment of the present invention
  • FIG. 2 is a left side view
  • FIG. 3 is a cross-sectional view taken along the line AA in FIG.
  • FIG. 4 is a front view showing the configuration of the cylinder unit of the disc brake device according to the present embodiment.
  • 5 is a partially exploded perspective view of the disc brake device according to the present embodiment
  • FIG. 6 is an exploded perspective view of the cylinder unit according to the present embodiment.
  • the disc brake device 10 is basically composed of a body 12, a support 26, and a cylinder unit 40, and each is configured separately.
  • the body 12 covers the support 26 and the cylinder unit 40, which will be described in detail later, and the outer brake pad 20 (hereinafter simply referred to as the outer pad 20) slides on the sliding surface of the rotor 74 by sliding the rotor 74 in the axial direction. It is a floating member that plays the role of pressing against the
  • the inner side body 14, the outer side body 18, and a bridge are provided.
  • the inner body 14 is a part located on the side where the support 26 and the cylinder unit 40 are arranged with respect to the rotor 74 when the body 12 is assembled.
  • the inner body 14 is provided with a guide hole 14b (see FIG. 3).
  • the pressure receiving portion 14a is a portion that is pressed from the inside by a second piston 50 disposed in a cylinder unit 40, which will be described in detail later.
  • the guide hole 14b is a through hole for inserting a slide pin 54 for holding the body 12 into a support 26 described later in detail.
  • the outer-side body 18 is a portion located on the opposite side of the support 26 from the rotor 74 when the body 12 is assembled.
  • the outer pad 20 is disposed on the surface of the outer side body 18 facing the rotor 74.
  • the outer pad 20 is basically composed of a lining 22 that is a friction member and a pressure plate 24 that is a steel plate to which the lining 22 is attached, and the pressure plate 24 and the outer body 18 are fastened.
  • a pin receiving portion 18 a that supports the tip of the slide pin 54 is provided on the surface of the outer body 18 that faces the rotor 74.
  • the bridge is a portion for connecting the inner side body 14 and the outer side body 18 described above, and is arranged so as to connect the two on the outer peripheral side of the rotor 74.
  • the bridge disposed on the center side of the body 12 is referred to as a main bridge 16a
  • the bridge disposed outside the body 12 is referred to as a side bridge 16
  • Both rigidity and weight reduction of the body 12 are compatible.
  • the support 26 plays a role for assembling the disc brake device 10 to a vehicle body (not shown).
  • the support 26 according to the present embodiment is configured based on a bridge 28 and arm portions 30 and 32.
  • the bridge 28 is a base member that is arranged toward the turn-in side and the turn-out side of the rotor 74, and is provided with a fastening hole 28a for fixing the support 26 to the vehicle.
  • the arm portions 30 and 32 are a pair of torque receivers that extend in the radial direction of the rotor 74 with the both ends of the rotor 74 in the bridge 28 on the entry side and the return side as base points.
  • fixing positions 30a and 32a (see FIG. 5) for fixing a cylinder unit 40, which will be described in detail later, are provided at the tips of the arm portions.
  • through holes 30a1 and 32a1 for inserting the slide pins 54 used when the cylinder unit 40 is fixed are formed.
  • an inner brake pad (hereinafter simply referred to as an inner pad 34) is disposed between the paired arm portions 30 and 32.
  • the inner pad 34 is basically composed of a lining 36 that is a friction member and a pressure plate 38 that is a steel plate.
  • the abutting portion to the arm portion 32 is an ear portion 38a provided on the pressure plate 38, and the slidability in the axial direction of the rotor 74 is improved between the ear portion 38a and the arm portions 30 and 32.
  • a pad clip is provided.
  • the inner pad 34 disposed on the support 26 is pressed against the sliding surface of the rotor 74 by being pressed by the first piston 48 provided in the cylinder unit 40.
  • the fixing positions for fixing the cylinder unit 40 are torques that receive the torque of the inner pad 34. It will be located in the radial direction outer peripheral side of the rotor 74 rather than a receiving position (position where the ear
  • the cylinder unit 40 has a cylinder block 42 and a cylinder mounting portion 52, as shown in detail in FIGS.
  • the cylinder block 42 has an inner cylinder (cylinder 44) formed in a penetrating manner, and a bleeder hole / inlet hole 46 for supplying and discharging hydraulic oil to and from the cylinder 44 from the outside of the cylinder block 42.
  • the cylinder unit 40 is provided with a first piston 48 and a second piston 50.
  • the first piston 48 is a piston for pressing the inner pad 34 and protrudes in the direction in which the rotor 74 is arranged.
  • the second piston 50 is a piston that protrudes toward the opposite side of the first piston 48 and presses the inner wall of the inner side body 14 in the body 12. For this reason, when hydraulic oil is supplied into the cylinder 44, the first piston 48 and the second piston 50 are pushed out in a relatively separated direction. Note that seals 48a and 50a and boots 48b and 50b are provided between the cylinder 44 and the first piston 48 and the second piston 50, respectively.
  • the cylinder mounting portion 52 is a support portion that extends from the outer periphery of the cylinder block 42 in both the direction of the rotor 74 in the assembled state and the direction of the rotor 74 in the assembled state.
  • the cylinder block 42 is positioned by being fixed to 26.
  • the cylinder mounting portion 52 extends so as to be substantially V-shaped with the cylinder block 42 as a base point.
  • the fixing positions 30a and 32a of the arm portions 30 and 32 of the support 26 are matched with the torque receiving positions of the arm portions 30 and 32 (the ear portions 38a of the inner pad 34 are abutted). It is provided at a position that is closer to the outer peripheral side in the radial direction of the rotor 74 than the (contact position). For this reason, the cylinder mounting part 52 in the cylinder unit 40 is fixed to the fixing positions 30a and 32a, so that the cylinder unit 40 plays a role as a strength member. Therefore, when torque is applied to the arm portions 30 and 32, it is possible to suppress the arm portions 30 and 32 from spreading toward the outlet side of the rotor 74.
  • the disc brake device 10 can cover the strength required for braking even when the support 26 is formed of a lightweight and thin member.
  • the fixed positions 30 a and 32 a are arranged so as to be closer to the outer peripheral side than the outer periphery of the rotor 74.
  • the cylinder attachment part 52 is arrange
  • the body 12, the support 26, and the cylinder unit 40 having such a configuration are assembled via the slide pins 54.
  • a sleeve 56 is disposed between the body 12 and the slide pin 54 and is held by boots 58 and 60 disposed before and after the sleeve 56. For this reason, there is little possibility that the torque input to the body 12 via the outer pad 20 will apply a load to the slide pin 54.
  • the cylinder unit 40 is assembled to the support 26 by positioning with the sleeve 56, and the sleeve 56, the cylinder mounting portion 52, and the slide pin 54 through which the support 26 is inserted are screwed with a cap nut 62 formed in a pin shape. It is made by being combined.
  • the pin 62a configured as the outer shape of the cap nut 62 is slidably engaged with the pin receiving portion 18a formed on the outer side body 18. Accordingly, when torque is input to the body 12 via the outer pad 20, the torque is transmitted to the support 26 via the cap nut 62.
  • a clip 64 is disposed between the cap nut 62 and the pin receiving portion 18a in order to improve the slidability and prevent wear during contact.
  • a shim 66 is interposed on the contact surface between the body 12 and the second piston 50.
  • the shim 66 includes a shim plate main body 68, a clamping part 70, and a claw 72.
  • the shim plate main body 68 plays the original role of the shim and improves the surface pressure between the body 12 and the second piston 50 even when there is a hardness difference between the constituent members of the body 12 and the second piston 50. be able to.
  • the sandwiching portion 70 is a portion extending in a hook shape from the shim plate main body 68 toward the body 12 side, and by sandwiching the inner side body 14 between the shim plate main body 68 and the sandwiching portion 70, The shim 66 can be fixed.
  • the claw 72 is a plurality of protrusions extending toward the second piston 50 with the shim plate body 68 as a base point. The plurality of claws 72 are configured to sandwich the outer periphery of the second piston 50.
  • the body 12 can follow the movement of the second piston 50. For this reason, when the brake is released, the body 12 also returns simultaneously with the return of the second piston 50, and dragging of the outer pad 20 fastened to the outer side body 18 can be suppressed.
  • the inner pad 34 can be held by the support 26. Thereby, in the floating type disc brake device 10, the torque of the inner pad 34 is not received by the slide pin 54.
  • the support 26 and the cylinder unit 40 are configured separately, the constituent materials of the two can be made different, and the balance between weight reduction and rigidity, ease of processing, and cost can be achieved.
  • a structure in which the support 26 is made of aluminum and the cylinder unit 40 is made of cast iron can be adopted.
  • the fixed positions 30a and 32a of the cylinder unit 40 are provided on the outer peripheral side in the radial direction of the rotor 74 with respect to the torque receiving position of the support 26.
  • the cylinder unit 40 is fixed using 32a. Therefore, when the cylinder unit 40 functions as a strength member of the support 26 and receives a braking torque, it is possible to prevent the arm portions 30 and 32 of the support 26 from spreading to the outlet side of the rotor 74.
  • the torque of the outer pad 20 is transmitted to the support 26 via the body 12 and the cap nut 62 having a short pin length. Therefore, on the outer pad 20 side, there is no need to worry about insufficient strength of the pin 62a (cap nut 62) that receives torque.
  • the load on the slide pin 54 is reduced, and the fear of insufficient strength during braking can be solved.
  • claw 72 which comprises the shim 66 clamps the outer peripheral side of the 2nd piston 50.
  • the plurality of claws 72 are fixed to the second piston 50 by mutually pressing the inner peripheral side of the second piston 50 so that the body 12 and the second piston 50 can be coupled. May be.
  • the cylinder mounting portion 52 extending from the cylinder block 42 as a base point is formed to be V-shaped from the cylinder block 42 as a base point.
  • the form of the cylinder mounting portion 52 is not limited to this. That is, as long as it can be fixed to the fixing positions 30a and 32a existing on the outer peripheral side in the radial direction of the rotor 74 with respect to the torque receiving positions of the arm portions 30 and 32, the configuration shown in FIGS. There may be.
  • the cylinder mounting portion 52 is an outer periphery of the cylinder block 42 and passes through the center of the cylinder 44. Are extended in the horizontal direction starting from the intersection of the rotor 74 and then vertically extended in the direction of the outer peripheral side of the rotor 74 in the radial direction. Even when the cylinder mounting portion 52 is configured as described above, when the cylinder unit 40 is fixed to the support 26, the cylinder mounting portion 52 (the entire cylinder unit 40) functions as a strength member of the support 26. Thus, the same effects as those of the above embodiment can be obtained.
  • FIG. 8 is a form in which the cylinder mounting portion 52 is horizontally extended from the upper half of the cylinder block 42.
  • the cylinder mounting portion 52 and the cylinder block 42 connect the fixed positions 30a and 32a of the arm portions 30 and 32 with a straight line. Become. For this reason, the effect as a strength member can be heightened.
  • the cylinder mounting portion 52 in the cylinder unit 40 shown in FIG. 9 is horizontally arranged with the intersection of the horizontal line passing through the center of the cylinder 44 and the outer peripheral line of the cylinder block 42 as a base point. It is an extended form. Even in this case, the cylinder unit 40 is fixed to the fixed positions 30a and 32a that are present on the outer peripheral side in the radial direction of the rotor 74 relative to the torque receiving positions of the arm portions 30 and 32, and If the function can be exhibited, the same effect as the above embodiment can be obtained.
  • the body 12 it is set as the form by which one big opening part is formed between the two main bridges 16a which connect the inner side body 14 and the outer side body 18. As shown in FIG. When it is set as such a structure, in addition to the improvement of heat dissipation, the weight reduction of the body 12 can be achieved.
  • a configuration like the first modification example in the form of the body 12 shown in FIG. 10 can be adopted.
  • a connecting portion 16b that connects the two main bridges 16a constituting the back portion of the body 12 is provided.
  • the center part between the two main bridges 16a may be a base point.
  • the central portion of the axial length of the body 12 is preferably a base point.
  • the rigidity of the body 12 can be increased as compared with a configuration without the connection portion 16b.
  • a high strength can be obtained with respect to an oblique force with the connecting portion 16b as a base point.
  • a connecting portion 16b in the body 12 of the form shown in FIG. 10 is used as a base point, and a center bridge 16c extending toward the inner body 14 is provided.
  • the center bridge 16c and the main bridge 16a Between them, an opening is provided. Even in such a configuration, an opening for confirming the wear state of the brake pads (the inner pad 34 and the outer pad 20) is provided between the connecting portion 16b and the outer body 18. Can do.
  • the rigidity of the body 12 can be further increased as compared with the embodiment shown in FIG.
  • pouring is usually performed from the upper side of FIG. 11, that is, the inner side body 14 side.
  • the center bridge 16c is provided, it is possible to maintain good hot water flow when hot water flows to the outer body 18.
  • wraparound when bubbles mixed in hot water rise is reduced. For this reason, deaeration property also improves and the possibility that a void will occur in the molded product after curing is reduced.
  • the cylinder unit is configured by forming an opening between the center bridge 16c and the main bridge 16a without completely covering the connection portion 16b and the inner body 14 with the center bridge 16c.
  • the degree of structural layout freedom at 40 can be kept good.
  • the bleeder hole / inlet hole 46 can be protruded from each of the openings arranged on the entrance side and the exit side of the rotor 74 via the center bridge 16c.
  • the inlet hole is a supply port for supplying hydraulic oil to the cylinder 44 of the cylinder unit 40, and the bleeder hole is a discharge port for performing air bleeding and replacement of the hydraulic oil.
  • the opening formed between the center bridge 16c and the main bridge 16a is a long hole whose long axis is the axial direction of the rotor 74, so that the brake pad (inner pad 34, outer pad 20) is lined. Even when 36 and 22 are worn, the bleeder hole / inlet hole 46 protruding from the cylinder block 42 does not interfere with the body 12.
  • the bleeder hole / inlet hole 46 is arranged on the outer peripheral side of the rotor 74 in the cylinder block 42 in the radial direction, so that operations such as bleeding of hydraulic fluid and replacement of hydraulic fluid can be performed. This can be performed from the outer peripheral side of the body 12. Thereby, compared with the case where the bleeder hole / inlet hole 46 is arranged inside the body 12, workability at the time of bleeding or replacing the hydraulic oil can be improved.
  • the bleeder hole / inlet hole 46 is opened from the opening formed between the center bridge 16 c and the main bridge 16 a of the body 12. If it is possible to access the hole / inlet hole 46, there is no need to limit the arrangement direction of the opening surface.
  • the opening surface of the bleeder hole / inlet hole 46 faces between the radially outer peripheral side and the axial inner side of the rotor 74, that is, the inner side oblique outer peripheral direction. It may be a thing, and as shown to FIG. 13, FIG.
  • FIG. 14 is a diagram (rear view) showing a configuration when the cylinder unit 40 in which the bleeder hole / inlet hole 46 is arranged toward the axial inner side of the rotor 74 is viewed from the inner side.
  • FIG. 14 is a plan view showing an example in which the body 12 having the center bridge 16c is assembled to the cylinder unit 40 shown in FIG.
  • the opening surface of the bleeder hole / inlet hole 46 may be directed to the outer circumferential side of the rotor 74 in the radial direction. This is because, in any case, the same effect can be obtained in terms of improving workability when bleeding or replacing the hydraulic oil.
  • the bleeder hole / inlet hole 46 is shown to be arranged on the radially inner peripheral side of the rotor 74 in the cylinder block 42.
  • the bleeder hole / inlet on the radially outer peripheral side of the rotor 74 in the cylinder block 42 as shown in FIGS. 12 and 13 is also applied to the above-described embodiment and the disc brake device 10 shown in FIG. The thing provided with the hole 46 can be applied.
  • the operation of the first piston 48 and the second piston 50 is described as being performed by supplying hydraulic oil into the cylinder 44.
  • the operation of the first piston 48 and the second piston 50 may be performed in a form other than hydraulic pressure.
  • a motor gear unit 76 is used as shown in FIG.
  • the motor gear unit 76 is attached to the cylinder unit 40, and power is transmitted via a gear (not shown), whereby a booster mechanism (not shown) provided in the cylinder unit 40 operates.
  • a booster mechanism not shown
  • the cylinder unit 40 is fixed to the support 26 that is a fixing member. For this reason, compared with the case where a motor is mounted in the body which is an operation
  • the cylinder unit 40 is fixed to the support 26 with a slide pin 54 that holds the body 12.
  • the cylinder is fixed to the support 26 by a fixing mechanism different from the slide pin 54.
  • the unit 40 may be fixed.
  • the body (12), the support (26), and the cylinder unit (40) are formed separately, and the cylinder unit is a floating in which the first piston (48) and the second piston (50) are accommodated.
  • the fixing position (30a, 32a) for fixing the cylinder unit in the arm portion is the outer periphery in the radial direction of the rotor than the torque receiving position in the arm portion (the position where the ear portion 38a of the inner pad 34 abuts).
  • the disc brake device according to [1] or [2], wherein a fixing position for fixing the cylinder unit in the arm portion is located on a radially outer peripheral side with respect to an outer periphery of the rotor.
  • Disc brake device described in 1. [5] The arrangement position of the cylinder unit is located on the radially inner side with respect to the fixed position for fixing the cylinder unit, and between the two fixed positions positioned on the return side and the return side of the rotor. , The space is provided, The body is provided with a main bridge (16a) for connecting the inner side and the outer side of the body, respectively, on the turn-in side and the turn-out side of the rotor in the space provided between the fixed positions.
  • the disc brake device according to any one of [1] to [4] above.
  • this invention is not limited to embodiment mentioned above, A deformation
  • the material, shape, dimensions, number, arrangement location, and the like of each component in the above-described embodiment are arbitrary and are not limited as long as the present invention can be achieved.
  • This application is based on a Japanese patent application filed on July 9, 2015 (Japanese Patent Application No. 2015-137810) and a Japanese patent application filed on February 9, 2016 (Japanese Patent Application No. 2016-022346). The contents are incorporated herein by reference.
  • the disc brake device of the present invention it is possible to provide a floating type disc brake device capable of reducing the load on the slide pin and solving the fear of insufficient strength during braking.
  • Cylinder block, 44 ......... Cylinder, 46 ......... Bleeder / inlet hole, 48 ......... First piston, 50 ?? Second piston, 52 ......... Cylinder mounting part, 54 ......... Slide pin, 56 ......... Sleeve, 58 ......... Boots, 60 ......... Boots, 62 ......... Cap nuts, 62a ......... Pins, 64 ......... Clips, 66 ......... Shim, 68 ......... Shim plate body , 70... Clamping part, 72... Claw, 74.

Abstract

A floating disc brake device (10) in which a body (12), a support (26), and a cylinder unit (40) are configured separately and a first piston (48) and a second piston (50) are housed in the cylinder unit (40), wherein the cylinder unit (40) is fixed via cylinder attachment parts (52), which are disposed on the outer circumference of the cylinder unit (40), to arm sections (30, 32) provided on both the rotor (74) leading side and trailing side of the support (26).

Description

ディスクブレーキ装置Disc brake device
　本発明は、ディスクブレーキ装置に関する。 The present invention relates to a disc brake device.
　シリンダに、第１ピストンと第２ピストンの２つのピストンを備えるフローティング型のディスクブレーキ装置としては、特許文献１や特許文献２に開示されているものを挙げることができる。 Examples of the floating type disc brake device in which the cylinder includes two pistons, ie, the first piston and the second piston, include those disclosed in Patent Document 1 and Patent Document 2.
　上記特許文献１及び特許文献２に開示されているディスクブレーキ装置は、いずれも、第１ピストンと第２ピストンを備えるシリンダと、ディスクブレーキ装置を車両に固定するサポートとを一体形成とする構成が採られている。また、ブレーキパッドは、インナ側、アウタ側共に、ボディをスライドさせるためのスライドピンにより支持する構成が採られている。 Each of the disk brake devices disclosed in Patent Document 1 and Patent Document 2 has a configuration in which a cylinder including a first piston and a second piston and a support for fixing the disk brake device to a vehicle are integrally formed. It is taken. Further, the brake pad is configured to be supported by a slide pin for sliding the body on both the inner side and the outer side.
日本国特公平５－２４３６９号公報Japanese Patent Publication No. 5-24369 日本国特開平８－２５４２３４号公報Japanese Laid-Open Patent Publication No. 8-254234
　上記特許文献１及び特許文献２に開示されているディスクブレーキ装置では、いずれも、ブレーキパッドからの制動トルクをスライドピンのみで受けることとなる。このため、高速走行からの制動時などには、スライドピンの強度不足が懸念される。また、ブレーキパッドがスライドピンに吊られた状態で支持されているため、偏摩耗の発生も懸念される。 In the disc brake devices disclosed in Patent Document 1 and Patent Document 2, the braking torque from the brake pad is received only by the slide pin. For this reason, there is a concern that the strength of the slide pin may be insufficient when braking from high speed traveling. Moreover, since the brake pad is supported in a state of being suspended from the slide pin, there is a concern about the occurrence of uneven wear.
　そこで本発明では、スライドピンへの負荷を低減し、制動時の強度不足の懸念を解消することのできるディスクブレーキ装置を提供することを目的とする。 Therefore, an object of the present invention is to provide a disc brake device that can reduce the load on the slide pin and eliminate the fear of insufficient strength during braking.
　本発明に係る上記目的は、下記構成により達成される。
（１）　ボディ、サポート、およびシリンダユニットが別体で構成され、前記シリンダユニットには、第１ピストンと第２ピストンが収容されるフローティング型のディスクブレーキ装置であって、前記シリンダユニットが、前記サポートにおけるロータの回入側と回出側の双方に設けられたアーム部に対して、前記シリンダユニットの外周側に配置されたシリンダ取付部を介して固定されているディスクブレーキ装置。 The above object of the present invention is achieved by the following configuration.
(1) A body, a support, and a cylinder unit are configured separately, and the cylinder unit is a floating type disc brake device in which a first piston and a second piston are accommodated, and the cylinder unit is A disc brake device that is fixed to arm portions provided on both a return side and a return side of a rotor in a support via a cylinder mounting portion disposed on an outer peripheral side of the cylinder unit.
（２）　上記（１）のような構成を有するディスクブレーキ装置であって、前記アーム部における前記シリンダユニットを固定する固定位置が、前記アーム部におけるトルク受け位置よりも前記ロータの半径方向外周側に位置するディスクブレーキ装置。 (2) The disc brake device having the configuration as described in (1) above, wherein a fixing position for fixing the cylinder unit in the arm portion is a radially outer peripheral side of the rotor from a torque receiving position in the arm portion. Disc brake device located in the.
　上記（１）又は（２）のような構成を有することにより、シリンダユニットがサポートの強度メンバとしての役割を担い、アーム部に制動トルクが印加された際に、ロータ回出側にアーム部が広がることを抑制することができる。このため、ディスクブレーキ装置は、サポートの薄肉化、軽量化を図った場合であっても、必要十分な強度を得ることが可能となる。 By having the configuration as described in (1) or (2) above, the cylinder unit plays a role as a strength member of the support, and when the braking torque is applied to the arm portion, the arm portion is located on the rotor delivery side. Spreading can be suppressed. For this reason, the disc brake device can obtain a necessary and sufficient strength even when the support is made thinner and lighter.
（３）　上記（１）又は（２）のような構成を有するディスクブレーキ装置であって、前記アーム部における前記シリンダユニットを固定する固定位置が、前記ロータの外周よりも半径方向外周側に位置するディスクブレーキ装置。 (3) The disc brake device having the configuration as described in (1) or (2) above, wherein the fixing position for fixing the cylinder unit in the arm portion is located on the outer peripheral side in the radial direction from the outer periphery of the rotor. Disc brake device.
　上記（３）のような構成を有する場合も、シリンダユニットがサポートの強度メンバとしての役割を担い、アーム部に制動トルクが印加された際に、ロータ回出側にアーム部が広がることを抑制することができる。また、アーム部におけるトルク受け位置から固定位置までの距離が離れることで、梃子の原理により、小さな補強で大きな耐久力を得ることが可能となる。このため、ディスクブレーキ装置は、サポートの薄肉化、軽量化を図った場合であっても、必要十分な強度を得ることが可能となる。 Even with the configuration as described in (3) above, the cylinder unit plays a role as a strength member of the support, and when the braking torque is applied to the arm portion, the arm portion is prevented from spreading to the rotor delivery side. can do. Further, since the distance from the torque receiving position to the fixed position in the arm portion is increased, it is possible to obtain a large durability with a small reinforcement by the lever principle. For this reason, the disc brake device can obtain a necessary and sufficient strength even when the support is made thinner and lighter.
（４）　上記（１）～（３）のいずれか１つのような構成を有するディスクブレーキ装置であって、前記シリンダ取付部は、前記シリンダユニットを固定する固定位置に対して、前記ボディを保持するスライドピンを介して固定されているディスクブレーキ装置。 (4) The disc brake device having the configuration as described in any one of (1) to (3) above, wherein the cylinder mounting portion holds the body with respect to a fixing position for fixing the cylinder unit. A disc brake device that is fixed via a slide pin.
　上記（４）のような構成を有することにより、ディスクブレーキ装置の組み付け性を向上させることができる。 By having the configuration as described in (4) above, it is possible to improve the assemblability of the disc brake device.
（５）　上記（１）～（４）のいずれか１つのような構成を有するディスクブレーキ装置であって、前記シリンダユニットの配置位置が、前記シリンダユニットを固定する固定位置よりも半径方向内周側に位置され、前記ロータの回入側と回出側に位置する２つの前記固定位置間に、空間が設けられる構成とされ、前記ボディには、前記固定位置間に設けられた前記空間における前記ロータの回入側と回出側にそれぞれ、前記ボディのインナ側とアウタ側を接続するメインブリッジが設けられる構成とされたディスクブレーキ装置。 (5) A disc brake device having a configuration as described in any one of (1) to (4) above, wherein the arrangement position of the cylinder unit is radially inner than the fixed position for fixing the cylinder unit. The space is provided between the two fixed positions positioned on the side of the rotor and located on the return side and the return side of the rotor, and the body includes a space in the space provided between the fixed positions. A disc brake device in which a main bridge for connecting an inner side and an outer side of the body is provided on a turning-in side and a turning-out side of the rotor, respectively.
　上記（５）のような構成を有することにより、構成された空間に、ボディを構成するメインブリッジを通すことができる。これにより、ディスクブレーキ装置全体としての小型化を図りつつ、剛性の低下を防ぐことができる。 By having the configuration as described in (5) above, the main bridge constituting the body can be passed through the configured space. As a result, it is possible to prevent a decrease in rigidity while reducing the size of the entire disc brake device.
（６）　上記（５）のような構成を有するディスクブレーキ装置であって、ボディ背肉部における前記ロータの軸方向中央部であって、回入側に配置された前記メインブリッジと回出側に配置された前記メインブリッジの間には、２つの前記メインブリッジを接続する接続部が設けられたディスクブレーキ装置。 (6) The disc brake device having the configuration as described in (5) above, wherein the main bridge and the outlet side are arranged in the axially central portion of the rotor in the back portion of the body and disposed on the inlet side. A disc brake device in which a connecting portion for connecting the two main bridges is provided between the main bridges arranged in the main bridge.
　上記（６）のような構成を有することにより、ボディの剛性を高めることができる。特に、接続部を基点とした斜め方向への負荷に対するボディの強度を高めることができる。 By having the configuration as described in (6) above, the rigidity of the body can be increased. In particular, it is possible to increase the strength of the body against a load in an oblique direction with the connection portion as a base point.
（７）　上記（６）のような構成を有するディスクブレーキ装置であって、前記接続部から前記ボディのインナ側へ延設されるセンターブリッジが設けられたディスクブレーキ装置。 (7) A disc brake device having the configuration as described in (6) above, wherein a disc bridge device provided with a center bridge extending from the connection portion to the inner side of the body.
　上記（７）のような構成を有することにより、さらにボディの剛性を高めることができる。また、ボディを鋳造する際の湯流性を良好に保つことができる。 By having the configuration as described in (7) above, the rigidity of the body can be further increased. In addition, it is possible to maintain good hot water flow when casting the body.
（８）　上記（１）～（７）のいずれか１つのような構成を有するディスクブレーキ装置であって、前記サポートと前記シリンダユニットとが異なる材料により構成されているディスクブレーキ装置。 (8) A disc brake device having a configuration as described in any one of (1) to (7) above, wherein the support and the cylinder unit are made of different materials.
　上記（８）のような構成を有することにより、ディスクブレーキ装置は、軽量化と強度確保、加工性の向上、およびコストのバランスを取ることが可能となる。 By having the configuration as described in (8) above, the disc brake device can balance light weight and strength, improve workability, and cost.
（９）　上記（１）～（８）のいずれか１つのような構成を有するディスクブレーキ装置であって、前記第１ピストン及び前記第２ピストンが、油圧以外の動力により押圧力を生じさせる構成とされたディスクブレーキ装置。 (9) A disc brake device having a configuration as described in any one of (1) to (8) above, wherein the first piston and the second piston generate a pressing force by power other than hydraulic pressure. Disc brake device.
　上記（９）のような構成を有することにより、ディスクブレーキ装置は、油圧ユニットが使用できない環境下においても適用することが可能となり、より汎用性を高めることができる。 By having the configuration as described in (9) above, the disc brake device can be applied even in an environment where the hydraulic unit cannot be used, and the versatility can be further improved.
　上記のような構成を有するディスクブレーキ装置によれば、スライドピンへの負荷を低減し、制動時の強度不足の懸念を解消することが可能となる。 According to the disc brake device having the above-described configuration, it is possible to reduce the load on the slide pin and eliminate the fear of insufficient strength during braking.
図１は、本発明の一実施形態に係るディスクブレーキ装置の構成を示す正面図である。FIG. 1 is a front view showing a configuration of a disc brake device according to an embodiment of the present invention. 図２は、本実施形態に係るディスクブレーキ装置の構成を示す左側面図である。FIG. 2 is a left side view showing the configuration of the disc brake device according to the present embodiment. 図３は、図１におけるＡ－Ａ断面を示す図である。3 is a cross-sectional view taken along the line AA in FIG. 図４は、本実施形態に係るディスクブレーキ装置を構成するシリンダユニットの構成を示す正面図である。FIG. 4 is a front view showing a configuration of a cylinder unit constituting the disc brake device according to the present embodiment. 図５は、本実施形態に係るディスクブレーキ装置の部分分解斜視図である。FIG. 5 is a partially exploded perspective view of the disc brake device according to the present embodiment. 図６は、本実施形態に係るシリンダユニットの分解斜視図である。FIG. 6 is an exploded perspective view of the cylinder unit according to the present embodiment. 図７は、本実施形態に係るシリンダユニットにおけるシリンダ取付部の第１の変形例を示す図である。FIG. 7 is a view showing a first modification of the cylinder mounting portion in the cylinder unit according to the present embodiment. 図８は、本実施形態に係るシリンダユニットにおけるシリンダ取付部の第２の変形例を示す図である。FIG. 8 is a view showing a second modification of the cylinder mounting portion in the cylinder unit according to the present embodiment. 図９は、本実施形態に係るシリンダユニットにおけるシリンダ取付部の第３の変形例を示す図である。FIG. 9 is a view showing a third modification of the cylinder mounting portion in the cylinder unit according to the present embodiment. 図１０は、本実施形態に係るボディの形態における第１の変形例を示す図である。FIG. 10 is a diagram showing a first modification example of the form of the body according to the present embodiment. 図１１は、本実施形態に係るボディの形態における第２の変形例を示す図である。FIG. 11 is a diagram illustrating a second modification example of the form of the body according to the present embodiment. 図１２は、本実施形態に係るブリーダ孔・インレット孔の開口面がロータのインナ側斜め外周方向に向けて配置されたシリンダユニットの構成例を示す図である。FIG. 12 is a diagram illustrating a configuration example of a cylinder unit in which the opening surfaces of the bleeder hole and the inlet hole according to the present embodiment are arranged toward the inner side oblique outer circumferential direction of the rotor. 図１３は、本実施形態に係るブリーダ孔・インレット孔の開口面がロータの軸方向インナ側に向けて配置されたシリンダユニットの構成例を示す図である。FIG. 13 is a diagram showing a configuration example of a cylinder unit in which the opening surfaces of the bleeder hole / inlet hole according to the present embodiment are arranged toward the axial inner side of the rotor. 図１４は、図１３に示すシリンダユニットに対して、センターブリッジを有するボディを組み付けた状態を示す平面図である。FIG. 14 is a plan view showing a state in which a body having a center bridge is assembled to the cylinder unit shown in FIG. 図１５は、油圧以外の形式の駆動機構を備えるディスクブレーキ装置の１例を示す右側面図である。FIG. 15 is a right side view showing an example of a disc brake device including a drive mechanism other than hydraulic pressure.
　以下、本発明のディスクブレーキ装置に係る実施の形態について、図面を参照して詳細に説明する。なお、図面における図１は、本発明の一実施形態に係るディスクブレーキ装置の構成を示す正面図であり、図２は左側面図である。また、図３は、図１におけるＡ－Ａ断面を示す図である。また、図４は、本実施形態に係るディスクブレーキ装置のシリンダユニットの構成を示す正面図である。さらに、図５は、本実施形態に係るディスクブレーキ装置の部分分解斜視図であり、図６は、本実施形態に係るシリンダユニットの分解斜視図である。 Hereinafter, embodiments of the disc brake device of the present invention will be described in detail with reference to the drawings. 1 in the drawings is a front view showing a configuration of a disc brake device according to one embodiment of the present invention, and FIG. 2 is a left side view. FIG. 3 is a cross-sectional view taken along the line AA in FIG. FIG. 4 is a front view showing the configuration of the cylinder unit of the disc brake device according to the present embodiment. 5 is a partially exploded perspective view of the disc brake device according to the present embodiment, and FIG. 6 is an exploded perspective view of the cylinder unit according to the present embodiment.
　本実施形態に係るディスクブレーキ装置１０は、ボディ１２とサポート２６、及びシリンダユニット４０を基本とし、それぞれが別体で構成されている。
　ボディ１２は、詳細を後述するサポート２６、およびシリンダユニット４０を覆うと共に、ロータ７４の軸線方向へのスライドにより、アウタ側ブレーキパッド２０（以下、単にアウタパッド２０と称す）をロータ７４の摺動面に押し付ける役割を担うフローティング部材である。 The disc brake device 10 according to the present embodiment is basically composed of a body 12, a support 26, and a cylinder unit 40, and each is configured separately.
The body 12 covers the support 26 and the cylinder unit 40, which will be described in detail later, and the outer brake pad 20 (hereinafter simply referred to as the outer pad 20) slides on the sliding surface of the rotor 74 by sliding the rotor 74 in the axial direction. It is a floating member that plays the role of pressing against the
　具体的な構成としては、インナ側ボディ１４とアウタ側ボディ１８、およびブリッジ（サイドブリッジ１６及びメインブリッジ１６ａ）を備える。インナ側ボディ１４は、ボディ１２を組み付けた際、ロータ７４を基準として、サポート２６やシリンダユニット４０が配置される側に位置する部位である。インナ側ボディ１４には、受圧部１４ａの他に、ガイド孔１４ｂ（図３参照）が設けられている。受圧部１４ａは、詳細を後述するシリンダユニット４０に配置される第２ピストン５０により、内側から押圧される部位である。また、ガイド孔１４ｂは、詳細を後述するサポート２６に対してボディ１２を保持するためのスライドピン５４を挿通させるための貫通孔である。 Specifically, the inner side body 14, the outer side body 18, and a bridge (side bridge 16 and main bridge 16a) are provided. The inner body 14 is a part located on the side where the support 26 and the cylinder unit 40 are arranged with respect to the rotor 74 when the body 12 is assembled. In addition to the pressure receiving portion 14a, the inner body 14 is provided with a guide hole 14b (see FIG. 3). The pressure receiving portion 14a is a portion that is pressed from the inside by a second piston 50 disposed in a cylinder unit 40, which will be described in detail later. Further, the guide hole 14b is a through hole for inserting a slide pin 54 for holding the body 12 into a support 26 described later in detail.
　アウタ側ボディ１８は、ボディ１２を組み付けた際、ロータ７４を基点として、サポート２６の配置側と反対側に位置する部位である。本実施形態に係るディスクブレーキ装置１０では、アウタ側ボディ１８におけるロータ７４との対向面に、アウタパッド２０が配置されている。 The outer-side body 18 is a portion located on the opposite side of the support 26 from the rotor 74 when the body 12 is assembled. In the disc brake device 10 according to the present embodiment, the outer pad 20 is disposed on the surface of the outer side body 18 facing the rotor 74.
　アウタパッド２０は、摩擦部材であるライニング２２と、ライニング２２が貼付されている鋼板であるプレッシャプレート２４とを基本として構成されており、プレッシャプレート２４とアウタ側ボディ１８が締結されることとなる。また、アウタ側ボディ１８のロータ７４への対向面側には、スライドピン５４の先端を支持するピン受け部１８ａが設けられている。 The outer pad 20 is basically composed of a lining 22 that is a friction member and a pressure plate 24 that is a steel plate to which the lining 22 is attached, and the pressure plate 24 and the outer body 18 are fastened. A pin receiving portion 18 a that supports the tip of the slide pin 54 is provided on the surface of the outer body 18 that faces the rotor 74.
　ブリッジは、上述したインナ側ボディ１４とアウタ側ボディ１８とを連結するための部位であり、ロータ７４の外周側で両者を連結するように配置されている。本実施形態に係るボディ１２では、ボディ１２の中央側に配置されたブリッジがメインブリッジ１６ａと呼称され、ボディ１２の外側に配置されたブリッジがサイドブリッジ１６と呼称されるように分けることで、ボディ１２の剛性と軽量化の双方が両立されている。ブリッジ（サイドブリッジ１６及びメインブリッジ１６ａ）が設けられることにより、インナ側ボディ１４が受けた押圧力がアウタ側ボディ１８に伝達され、ロータ７４の摺動面へのアウタパッド２０の押し付けが可能となる。 The bridge is a portion for connecting the inner side body 14 and the outer side body 18 described above, and is arranged so as to connect the two on the outer peripheral side of the rotor 74. In the body 12 according to the present embodiment, the bridge disposed on the center side of the body 12 is referred to as a main bridge 16a, and the bridge disposed outside the body 12 is referred to as a side bridge 16, Both rigidity and weight reduction of the body 12 are compatible. By providing the bridges (side bridge 16 and main bridge 16a), the pressing force received by the inner body 14 is transmitted to the outer body 18, and the outer pad 20 can be pressed against the sliding surface of the rotor 74. .
　サポート２６は、ディスクブレーキ装置１０を図示しない車両のボディに組付けるための役割を担う。本実施形態に係るサポート２６は、ブリッジ２８と、アーム部３０，３２とを基本として構成されている。ブリッジ２８は、ロータ７４の回入側と回出側に向けて配置されるベース部材であり、サポート２６を車両に固定するための締結孔２８ａが設けられている。 The support 26 plays a role for assembling the disc brake device 10 to a vehicle body (not shown). The support 26 according to the present embodiment is configured based on a bridge 28 and arm portions 30 and 32. The bridge 28 is a base member that is arranged toward the turn-in side and the turn-out side of the rotor 74, and is provided with a fastening hole 28a for fixing the support 26 to the vehicle.
　アーム部３０，３２は、ブリッジ２８におけるロータ７４の回入側と回出側の両端部を基点として、ロータ７４の半径方向へ延設される一対のトルク受けである。本実施形態に係るアーム部３０，３２の場合、各アーム部の先端に、詳細を後述するシリンダユニット４０を固定するための固定位置３０ａ，３２ａ（図５参照）が設けられている。固定位置３０ａ，３２ａには、シリンダユニット４０を固定する際に用いられるスライドピン５４を挿通させるための貫通孔３０ａ１，３２ａ１が形成されている。 The arm portions 30 and 32 are a pair of torque receivers that extend in the radial direction of the rotor 74 with the both ends of the rotor 74 in the bridge 28 on the entry side and the return side as base points. In the case of the arm portions 30 and 32 according to the present embodiment, fixing positions 30a and 32a (see FIG. 5) for fixing a cylinder unit 40, which will be described in detail later, are provided at the tips of the arm portions. In the fixing positions 30a and 32a, through holes 30a1 and 32a1 for inserting the slide pins 54 used when the cylinder unit 40 is fixed are formed.
　対を成すアーム部３０，３２の間には、インナ側ブレーキパッド（以下、単にインナパッド３４と称す）が配置される。インナパッド３４の構成も、アウタパッド２０と同様に、摩擦部材であるライニング３６と、鋼板であるプレッシャプレート３８が基本とされている。アーム部３２への当接部は、プレッシャプレート３８に設けられた耳部３８ａであり、耳部３８ａとアーム部３０，３２との間には、ロータ７４の軸方向への摺動性を向上させるためのパッドクリップが備えられる。サポート２６に配置されたインナパッド３４は、シリンダユニット４０に備えられた第１ピストン４８に押圧されることで、ロータ７４の摺動面へと押し付けられる。 An inner brake pad (hereinafter simply referred to as an inner pad 34) is disposed between the paired arm portions 30 and 32. As with the outer pad 20, the inner pad 34 is basically composed of a lining 36 that is a friction member and a pressure plate 38 that is a steel plate. The abutting portion to the arm portion 32 is an ear portion 38a provided on the pressure plate 38, and the slidability in the axial direction of the rotor 74 is improved between the ear portion 38a and the arm portions 30 and 32. A pad clip is provided. The inner pad 34 disposed on the support 26 is pressed against the sliding surface of the rotor 74 by being pressed by the first piston 48 provided in the cylinder unit 40.
　本実施形態に係るサポート２６では、アーム部３０，３２において、シリンダユニット４０を固定するための固定位置（シリンダ取付部５２が固定される部位）３０ａ，３２ａは、インナパッド３４のトルクを受けるトルク受け位置（耳部３８ａが当接する位置）よりも、ロータ７４の半径方向外周側に位置することとなる。 In the support 26 according to the present embodiment, in the arm portions 30 and 32, the fixing positions for fixing the cylinder unit 40 (portions where the cylinder mounting portion 52 is fixed) 30a and 32a are torques that receive the torque of the inner pad 34. It will be located in the radial direction outer peripheral side of the rotor 74 rather than a receiving position (position where the ear | edge part 38a contact | abuts).
　シリンダユニット４０は、詳細を図４、図６に示すように、シリンダブロック４２と、シリンダ取付部５２とを有する。シリンダブロック４２は、貫通形成された内筒（シリンダ４４）と、シリンダブロック４２の外部からシリンダ４４への作動油の供給・排出を行うためのブリーダ孔・インレット孔４６を有する。シリンダユニット４０には、第１ピストン４８と第２ピストン５０が備えられている。 The cylinder unit 40 has a cylinder block 42 and a cylinder mounting portion 52, as shown in detail in FIGS. The cylinder block 42 has an inner cylinder (cylinder 44) formed in a penetrating manner, and a bleeder hole / inlet hole 46 for supplying and discharging hydraulic oil to and from the cylinder 44 from the outside of the cylinder block 42. The cylinder unit 40 is provided with a first piston 48 and a second piston 50.
　第１ピストン４８は、インナパッド３４を押圧するためのピストンであり、ロータ７４の配置方向へ向けて突出する。第２ピストン５０は、第１ピストン４８と反対側へ向けて突出し、ボディ１２におけるインナ側ボディ１４の内壁を押圧するピストンである。このため、第１ピストン４８と第２ピストン５０は、シリンダ４４内に作動油が供給されると、相対的に離間する方向へと押し出されることとなる。なお、シリンダ４４と第１ピストン４８及び第２ピストン５０との間には、それぞれシール４８ａ，５０ａと、ブーツ４８ｂ，５０ｂが備えられている。 The first piston 48 is a piston for pressing the inner pad 34 and protrudes in the direction in which the rotor 74 is arranged. The second piston 50 is a piston that protrudes toward the opposite side of the first piston 48 and presses the inner wall of the inner side body 14 in the body 12. For this reason, when hydraulic oil is supplied into the cylinder 44, the first piston 48 and the second piston 50 are pushed out in a relatively separated direction. Note that seals 48a and 50a and boots 48b and 50b are provided between the cylinder 44 and the first piston 48 and the second piston 50, respectively.
　シリンダ取付部５２は、シリンダブロック４２の外周を基点として、組付け状態においてロータ７４の回入側と回出側となる方向の双方へ延設される支持部であり、シリンダ取付部５２がサポート２６に固定されることで、シリンダブロック４２の位置決めが成される。 The cylinder mounting portion 52 is a support portion that extends from the outer periphery of the cylinder block 42 in both the direction of the rotor 74 in the assembled state and the direction of the rotor 74 in the assembled state. The cylinder block 42 is positioned by being fixed to 26.
　本実施形態では、図４に示すように、シリンダ取付部５２が、シリンダブロック４２を基点としてほぼＶ字状となるように延設されている。 In the present embodiment, as shown in FIG. 4, the cylinder mounting portion 52 extends so as to be substantially V-shaped with the cylinder block 42 as a base point.
　上述したように、本実施形態に係るディスクブレーキ装置１０では、サポート２６のアーム部３０，３２における固定位置３０ａ，３２ａをアーム部３０，３２のトルク受け位置（インナパッド３４の耳部３８ａが当接する位置）よりもロータ７４の半径方向外周側となる位置に設けている。このため、固定位置３０ａ，３２ａにシリンダユニット４０におけるシリンダ取付部５２が固定されることで、シリンダユニット４０が強度メンバとしての役割を担うこととなる。よって、アーム部３０，３２にトルクが印加された際、アーム部３０，３２がロータ７４の回出側へ広がることを抑制することができる。 As described above, in the disc brake device 10 according to the present embodiment, the fixing positions 30a and 32a of the arm portions 30 and 32 of the support 26 are matched with the torque receiving positions of the arm portions 30 and 32 (the ear portions 38a of the inner pad 34 are abutted). It is provided at a position that is closer to the outer peripheral side in the radial direction of the rotor 74 than the (contact position). For this reason, the cylinder mounting part 52 in the cylinder unit 40 is fixed to the fixing positions 30a and 32a, so that the cylinder unit 40 plays a role as a strength member. Therefore, when torque is applied to the arm portions 30 and 32, it is possible to suppress the arm portions 30 and 32 from spreading toward the outlet side of the rotor 74.
　このため、ディスクブレーキ装置１０は、サポート２６が軽量、かつ薄肉な部材で構成された場合であっても、制動時に必要な強度を賄うことができるようになる。 For this reason, the disc brake device 10 can cover the strength required for braking even when the support 26 is formed of a lightweight and thin member.
　また、本実施形態に係るディスクブレーキ装置１０では、固定位置３０ａ，３２ａがロータ７４の外周よりも外周側となるように配置されている。そして、シリンダ取付部５２がＶ字状に配置され、その先端が固定位置３０ａ，３２ａに締結される構成とされたことで、２つの固定位置３０ａ，３２ａ間には、空間が形成されている。よって、この固定位置３０ａ，３２ａ間に形成された空間に、ボディ１２を構成するメインブリッジ１６ａが配置されることで、ディスクブレーキ装置１０全体の小型化を図りつつ、剛性を保つことが可能となる。 Further, in the disc brake device 10 according to the present embodiment, the fixed positions 30 a and 32 a are arranged so as to be closer to the outer peripheral side than the outer periphery of the rotor 74. And the cylinder attachment part 52 is arrange | positioned at V shape, and it was set as the structure fastened by the front-end | tip to fixed position 30a, 32a, and the space is formed between the two fixed positions 30a, 32a. . Therefore, by disposing the main bridge 16a constituting the body 12 in the space formed between the fixed positions 30a and 32a, it is possible to maintain rigidity while reducing the size of the entire disc brake device 10. Become.
　このような構成のボディ１２、サポート２６、およびシリンダユニット４０は、スライドピン５４を介して組付けられる。ボディ１２とスライドピン５４の間には、スリーブ５６が配置され、スリーブ５６の前後に配置されたブーツ５８，６０により保持される形態が採られる。このため、アウタパッド２０を介してボディ１２に入力されたトルクが、スライドピン５４に負荷をかける虞が少ない。サポート２６に対するシリンダユニット４０の組み付けは、スリーブ５６により位置決めが成されると共に、スリーブ５６、シリンダ取付部５２、およびサポート２６を挿通させたスライドピン５４に、ピン状に形成した袋ナット６２が螺合されることで成される。 The body 12, the support 26, and the cylinder unit 40 having such a configuration are assembled via the slide pins 54. A sleeve 56 is disposed between the body 12 and the slide pin 54 and is held by boots 58 and 60 disposed before and after the sleeve 56. For this reason, there is little possibility that the torque input to the body 12 via the outer pad 20 will apply a load to the slide pin 54. The cylinder unit 40 is assembled to the support 26 by positioning with the sleeve 56, and the sleeve 56, the cylinder mounting portion 52, and the slide pin 54 through which the support 26 is inserted are screwed with a cap nut 62 formed in a pin shape. It is made by being combined.
　袋ナット６２の外形として構成されているピン６２ａは、アウタ側ボディ１８に形成されたピン受け部１８ａに摺動可能に係合される。これにより、アウタパッド２０を介してボディ１２にトルクが入力された際、当該トルクは、袋ナット６２を介してサポート２６に伝達されることとなる。袋ナット６２とピン受け部１８ａとの間には、摺動性の向上や当接時の磨滅を防ぐため、クリップ６４が配置されている。 The pin 62a configured as the outer shape of the cap nut 62 is slidably engaged with the pin receiving portion 18a formed on the outer side body 18. Accordingly, when torque is input to the body 12 via the outer pad 20, the torque is transmitted to the support 26 via the cap nut 62. A clip 64 is disposed between the cap nut 62 and the pin receiving portion 18a in order to improve the slidability and prevent wear during contact.
　本実施形態に係るディスクブレーキ装置１０では、ボディ１２と第２ピストン５０との当接面に、シム６６が介在されている。シム６６は、シム板本体６８と、挟持部７０と、爪７２とを有する。 In the disc brake device 10 according to the present embodiment, a shim 66 is interposed on the contact surface between the body 12 and the second piston 50. The shim 66 includes a shim plate main body 68, a clamping part 70, and a claw 72.
　シム板本体６８は、シム本来の役割を担い、ボディ１２と第２ピストン５０との構成部材に硬度差がある場合であっても、ボディ１２と第２ピストン５０の間の面圧を改善することができる。挟持部７０は、シム板本体６８を基点としてボディ１２側へ向けてフック状に延設された部位であり、シム板本体６８と挟持部７０との間にインナ側ボディ１４を挟み込むことで、シム６６の固定を図ることができる。また、爪７２は、シム板本体６８を基点として複数、第２ピストン５０側へ向けて延設されている突起部である。複数の爪７２により、第２ピストン５０の外周が挟持される構成とされている。 The shim plate main body 68 plays the original role of the shim and improves the surface pressure between the body 12 and the second piston 50 even when there is a hardness difference between the constituent members of the body 12 and the second piston 50. be able to. The sandwiching portion 70 is a portion extending in a hook shape from the shim plate main body 68 toward the body 12 side, and by sandwiching the inner side body 14 between the shim plate main body 68 and the sandwiching portion 70, The shim 66 can be fixed. The claw 72 is a plurality of protrusions extending toward the second piston 50 with the shim plate body 68 as a base point. The plurality of claws 72 are configured to sandwich the outer periphery of the second piston 50.
　このような構成とすることで、第２ピストン５０の動きにボディ１２を追従させることができる。このため、ブレーキ開放時に、第２ピストン５０の戻りと同時にボディ１２も戻ることとなり、アウタ側ボディ１８に締結されているアウタパッド２０の引き摺りを抑制することができる。 With this configuration, the body 12 can follow the movement of the second piston 50. For this reason, when the brake is released, the body 12 also returns simultaneously with the return of the second piston 50, and dragging of the outer pad 20 fastened to the outer side body 18 can be suppressed.
　このような構成のディスクブレーキ装置１０では、サポート２６とシリンダユニット４０が別体とされているため、インナパッド３４をサポート２６に保持させることができる。これにより、フローティング型のディスクブレーキ装置１０において、インナパッド３４のトルクをスライドピン５４により受ける事が無くなる。 In the disc brake device 10 having such a configuration, since the support 26 and the cylinder unit 40 are separated, the inner pad 34 can be held by the support 26. Thereby, in the floating type disc brake device 10, the torque of the inner pad 34 is not received by the slide pin 54.
　また、サポート２６とシリンダユニット４０が別体で構成されることにより、両者の構成材料を異ならせることができ、軽量化と剛性、加工の容易性、およびコストのバランスを取ることができる。例えば、サポート２６がアルミにより構成され、シリンダユニット４０が鋳鉄により構成されるといった構造を採ることができる。 In addition, since the support 26 and the cylinder unit 40 are configured separately, the constituent materials of the two can be made different, and the balance between weight reduction and rigidity, ease of processing, and cost can be achieved. For example, a structure in which the support 26 is made of aluminum and the cylinder unit 40 is made of cast iron can be adopted.
　また、本実施形態に係るディスクブレーキ装置１０では、サポート２６のトルク受け位置よりもロータ７４の半径方向外周側に、シリンダユニット４０の固定位置３０ａ，３２ａが設けられており、この固定位置３０ａ，３２ａを利用してシリンダユニット４０が固定されている。よって、シリンダユニット４０がサポート２６の強度メンバとしての働きを担い、制動トルクを受けた際、サポート２６のアーム部３０，３２がロータ７４の回出側へ広がることを防ぐことができる。 Further, in the disc brake device 10 according to the present embodiment, the fixed positions 30a and 32a of the cylinder unit 40 are provided on the outer peripheral side in the radial direction of the rotor 74 with respect to the torque receiving position of the support 26. The cylinder unit 40 is fixed using 32a. Therefore, when the cylinder unit 40 functions as a strength member of the support 26 and receives a braking torque, it is possible to prevent the arm portions 30 and 32 of the support 26 from spreading to the outlet side of the rotor 74.
　また、アウタパッド２０のトルクは、ボディ１２を介してピン長の短い袋ナット６２を介してサポート２６に伝達される。よって、アウタパッド２０側においても、トルクを受けるピン６２ａ（袋ナット６２）の強度不足を懸念する必要性が無い。 Further, the torque of the outer pad 20 is transmitted to the support 26 via the body 12 and the cap nut 62 having a short pin length. Therefore, on the outer pad 20 side, there is no need to worry about insufficient strength of the pin 62a (cap nut 62) that receives torque.
　このため、本実施形態に係るディスクブレーキ装置１０によれば、スライドピン５４への負荷が低減され、制動時の強度不足の懸念を解消することができる。 Therefore, according to the disc brake device 10 according to the present embodiment, the load on the slide pin 54 is reduced, and the fear of insufficient strength during braking can be solved.
　また、上記実施形態では、シム６６を構成する複数の爪７２は、第２ピストン５０の外周側を挟持する旨記載した。しかしながら、複数の爪７２は、第２ピストン５０の内周側を相互に押圧することで、第２ピストン５０への固定が成され、ボディ１２と第２ピストン５０との結合が図られるようにしても良い。 Moreover, in the said embodiment, it described that the some nail | claw 72 which comprises the shim 66 clamps the outer peripheral side of the 2nd piston 50. As shown in FIG. However, the plurality of claws 72 are fixed to the second piston 50 by mutually pressing the inner peripheral side of the second piston 50 so that the body 12 and the second piston 50 can be coupled. May be.
　上記実施形態では、シリンダブロック４２を基点として延設されるシリンダ取付部５２について、シリンダブロック４２を基点としてＶ字状となるように形成する旨記載した。しかしながら、シリンダ取付部５２の形態に関しては、これに限定するものでは無い。すなわち、アーム部３０，３２のトルク受け位置よりもロータ７４の半径方向外周側に存在する固定位置３０ａ，３２ａに固定されることが可能であれば、図７から図９に示すような形態であっても良い。 In the above embodiment, it is described that the cylinder mounting portion 52 extending from the cylinder block 42 as a base point is formed to be V-shaped from the cylinder block 42 as a base point. However, the form of the cylinder mounting portion 52 is not limited to this. That is, as long as it can be fixed to the fixing positions 30a and 32a existing on the outer peripheral side in the radial direction of the rotor 74 with respect to the torque receiving positions of the arm portions 30 and 32, the configuration shown in FIGS. There may be.
　具体的には、図７に示すシリンダユニット４０におけるシリンダ取付部５２の第１の変形例の形態の場合、シリンダ取付部５２は、シリンダブロック４２の外周であって、シリンダ４４の中心を通る水平線との交点を基点として水平方向に延設された後、ロータ７４の半径方向外周側となる方向へ垂直に延設されている。シリンダ取付部５２がこのような形態とされた場合であっても、シリンダユニット４０がサポート２６に固定された際には、シリンダ取付部５２（シリンダユニット４０全体）がサポート２６の強度メンバとして働くこととなり、上記実施形態と同様な効果を得ることができる。 Specifically, in the case of the first modification of the cylinder mounting portion 52 in the cylinder unit 40 shown in FIG. 7, the cylinder mounting portion 52 is an outer periphery of the cylinder block 42 and passes through the center of the cylinder 44. Are extended in the horizontal direction starting from the intersection of the rotor 74 and then vertically extended in the direction of the outer peripheral side of the rotor 74 in the radial direction. Even when the cylinder mounting portion 52 is configured as described above, when the cylinder unit 40 is fixed to the support 26, the cylinder mounting portion 52 (the entire cylinder unit 40) functions as a strength member of the support 26. Thus, the same effects as those of the above embodiment can be obtained.
　図８に示すシリンダユニット４０におけるシリンダ取付部５２の第２の変形例の形態は、シリンダブロック４２の上半部から、シリンダ取付部５２が水平に延設される形態である。このような形態とされた場合、シリンダユニット４０がサポート２６に組付けられた際、シリンダ取付部５２とシリンダブロック４２が、アーム部３０，３２の固定位置３０ａ，３２ａ間を直線で結ぶ構成となる。このため、強度メンバとしての効果を高めることができる。 8 is a form in which the cylinder mounting portion 52 is horizontally extended from the upper half of the cylinder block 42. In the second modification of the cylinder mounting portion 52 in the cylinder unit 40 shown in FIG. In such a configuration, when the cylinder unit 40 is assembled to the support 26, the cylinder mounting portion 52 and the cylinder block 42 connect the fixed positions 30a and 32a of the arm portions 30 and 32 with a straight line. Become. For this reason, the effect as a strength member can be heightened.
　図９に示すシリンダユニット４０におけるシリンダ取付部５２の第３の変形例の形態は、シリンダ４４の中心を通る水平線とシリンダブロック４２の外周線との交点を基点として、シリンダ取付部５２が水平に延設される形態である。このような形態とされた場合であっても、アーム部３０，３２のトルク受け位置よりもロータ７４の半径方向外周側に存在する固定位置３０ａ，３２ａに固定され、かつシリンダユニット４０が、その機能を発揮することができれば、上記実施形態と同様な効果を得ることができる。 In the third modification of the cylinder mounting portion 52 in the cylinder unit 40 shown in FIG. 9, the cylinder mounting portion 52 is horizontally arranged with the intersection of the horizontal line passing through the center of the cylinder 44 and the outer peripheral line of the cylinder block 42 as a base point. It is an extended form. Even in this case, the cylinder unit 40 is fixed to the fixed positions 30a and 32a that are present on the outer peripheral side in the radial direction of the rotor 74 relative to the torque receiving positions of the arm portions 30 and 32, and If the function can be exhibited, the same effect as the above embodiment can be obtained.
　また、上記実施形態では、ボディ１２に関して、インナ側ボディ１４とアウタ側ボディ１８を接続する２つのメインブリッジ１６ａの間には、１つの大きな開口部が形成される形態とされている。このような構成とされた場合には、放熱性の向上に加え、ボディ１２の軽量化を図ることができる。 Moreover, in the said embodiment, regarding the body 12, it is set as the form by which one big opening part is formed between the two main bridges 16a which connect the inner side body 14 and the outer side body 18. As shown in FIG. When it is set as such a structure, in addition to the improvement of heat dissipation, the weight reduction of the body 12 can be achieved.
［Ｘタイプ］
　これに対し、ボディ１２の剛性を高めたい場合には、例えば図１０に示すボディ１２の形態における第１の変形例のような構成とすることもできる。具体的には、ボディ１２の背肉部を構成する２つのメインブリッジ１６ａの間に、両者を接続する接続部１６ｂが設けられるというものである。接続部１６ｂの形成位置としては、ロータ７４の円周方向においては、２つのメインブリッジ１６ａ間の中央部が基点とされると良い。また、ロータ７４の軸方向においては、ボディ１２の軸方向長さの中央部が基点とされると良い。 [X type]
On the other hand, when it is desired to increase the rigidity of the body 12, for example, a configuration like the first modification example in the form of the body 12 shown in FIG. 10 can be adopted. Specifically, a connecting portion 16b that connects the two main bridges 16a constituting the back portion of the body 12 is provided. As a formation position of the connection part 16b, in the circumferential direction of the rotor 74, the center part between the two main bridges 16a may be a base point. Further, in the axial direction of the rotor 74, the central portion of the axial length of the body 12 is preferably a base point.
　このような構成とされた場合、接続部１６ｂが無い形態に比べ、ボディ１２の剛性を高めることができる。特に、ボディ１２を平面視した際に、接続部１６ｂが基点とされた斜め方向の力に対し、高い強度を得ることができる。また、アウタ側ボディ１８と接続部１６ｂとの間に開口部が設けられる事で、ブレーキパッド（インナパッド３４、アウタパッド２０）の摩耗状態をボディ１２の外周側から確認することもできる。 In the case of such a configuration, the rigidity of the body 12 can be increased as compared with a configuration without the connection portion 16b. In particular, when the body 12 is viewed in plan, a high strength can be obtained with respect to an oblique force with the connecting portion 16b as a base point. In addition, by providing an opening between the outer side body 18 and the connecting portion 16b, it is possible to check the wear state of the brake pads (inner pad 34, outer pad 20) from the outer peripheral side of the body 12.
［Ｙタイプ］
　また、ボディ１２の形状に関しては、図１１に示すボディ１２の形態における第２の変形例のような形態とすることもできる。具体的には、図１０に示した形態のボディ１２における接続部１６ｂが基点とされて、インナ側ボディ１４に向けて延設されたセンターブリッジ１６ｃが設けられ、センターブリッジ１６ｃとメインブリッジ１６ａとの間に、それぞれ開口部が設けられるというものである。このような構成とされた場合であっても、接続部１６ｂとアウタ側ボディ１８との間には、ブレーキパッド（インナパッド３４、アウタパッド２０）の摩耗状態を確認するための開口部を設けることができる。 [Y type]
Moreover, regarding the shape of the body 12, it can also be set as a 2nd modification in the form of the body 12 shown in FIG. Specifically, a connecting portion 16b in the body 12 of the form shown in FIG. 10 is used as a base point, and a center bridge 16c extending toward the inner body 14 is provided. The center bridge 16c and the main bridge 16a Between them, an opening is provided. Even in such a configuration, an opening for confirming the wear state of the brake pads (the inner pad 34 and the outer pad 20) is provided between the connecting portion 16b and the outer body 18. Can do.
　また、このような構成とすることで、図１０に示す形態に比べ、さらにボディ１２の剛性を高めることができる。また、通常、ボディ１２を鋳造する際には、図１１の上方側、すなわちインナ側ボディ１４側から注湯が行われる。センターブリッジ１６ｃが設けられた場合には、アウタ側ボディ１８まで湯を流す際の湯流れ性を良好に保つことができる。また、注湯後においても、湯に混入している気泡が上昇する際の回り込みが小さくなる。このため、脱気性も向上し、硬化後の成形品に鬆が生じてしまう虞が低くなる。 Further, by adopting such a configuration, the rigidity of the body 12 can be further increased as compared with the embodiment shown in FIG. In addition, when casting the body 12, pouring is usually performed from the upper side of FIG. 11, that is, the inner side body 14 side. In the case where the center bridge 16c is provided, it is possible to maintain good hot water flow when hot water flows to the outer body 18. In addition, even after pouring, wraparound when bubbles mixed in hot water rise is reduced. For this reason, deaeration property also improves and the possibility that a void will occur in the molded product after curing is reduced.
［シリンダユニット変形例］
　さらに、接続部１６ｂとインナ側ボディ１４との間をセンターブリッジ１６ｃにより完全に覆うことをせず、センターブリッジ１６ｃとメインブリッジ１６ａとの間に開口部を形成する構成としたことにより、シリンダユニット４０における構造上のレイアウトの自由度を良好に保つことができる。具体的には、センターブリッジ１６ｃを介してロータ７４の回入側と回出側に配置される開口部のそれぞれから、ブリーダ孔・インレット孔４６を突出させることが可能となる。なお、インレット孔は、シリンダユニット４０のシリンダ４４に作動油を供給するための供給ポートであり、ブリーダ孔は、作動油のエア抜きや交換を行うための吐出ポートである。また、センターブリッジ１６ｃとメインブリッジ１６ａとの間に形成される開口部が、ロータ７４の軸方向を長軸とする長穴とされることで、ブレーキパッド（インナパッド３４、アウタパッド２０）のライニング３６，２２が摩耗した場合であっても、シリンダブロック４２から突出しているブリーダ孔・インレット孔４６が、ボディ１２に干渉する事が無い。 [Cylinder unit modification]
Furthermore, the cylinder unit is configured by forming an opening between the center bridge 16c and the main bridge 16a without completely covering the connection portion 16b and the inner body 14 with the center bridge 16c. The degree of structural layout freedom at 40 can be kept good. Specifically, the bleeder hole / inlet hole 46 can be protruded from each of the openings arranged on the entrance side and the exit side of the rotor 74 via the center bridge 16c. The inlet hole is a supply port for supplying hydraulic oil to the cylinder 44 of the cylinder unit 40, and the bleeder hole is a discharge port for performing air bleeding and replacement of the hydraulic oil. Further, the opening formed between the center bridge 16c and the main bridge 16a is a long hole whose long axis is the axial direction of the rotor 74, so that the brake pad (inner pad 34, outer pad 20) is lined. Even when 36 and 22 are worn, the bleeder hole / inlet hole 46 protruding from the cylinder block 42 does not interfere with the body 12.
　図１２に示すように、シリンダブロック４２におけるロータ７４の半径方向外周側にブリーダ孔・インレット孔４６が配置される構成とされることで、作動油のエア抜きや、作動油の交換といった作業をボディ１２の外周側から行うことが可能となる。これにより、ボディ１２の内側にブリーダ孔・インレット孔４６が配置された場合に比べ、作動油のエア抜きや交換をする際の作業性を向上させることができる。 As shown in FIG. 12, the bleeder hole / inlet hole 46 is arranged on the outer peripheral side of the rotor 74 in the cylinder block 42 in the radial direction, so that operations such as bleeding of hydraulic fluid and replacement of hydraulic fluid can be performed. This can be performed from the outer peripheral side of the body 12. Thereby, compared with the case where the bleeder hole / inlet hole 46 is arranged inside the body 12, workability at the time of bleeding or replacing the hydraulic oil can be improved.
　このように、ブリーダ孔・インレット孔４６がシリンダブロック４２におけるロータ７４の半径方向外周側に配置される場合、ボディ１２のセンターブリッジ１６ｃとメインブリッジ１６ａとの間に形成された開口部から、ブリーダ孔・インレット孔４６へアクセスすることが可能であれば、その開口面の配置方向は、制限する必要が無い。例えば、図１１、図１２を参照して読み取れるように、ブリーダ孔・インレット孔４６の開口面が、ロータ７４の半径方向外周側と軸方向インナ側との間、すなわちインナ側斜め外周方向に向くものであっても良いし、図１３、図１４に示すように、開口面がロータ７４の軸方向インナ側に向くように配置されても良い。なお、図１３は、ブリーダ孔・インレット孔４６がロータ７４の軸方向インナ側に向けて配置されたシリンダユニット４０をインナ側から見た場合の構成を示す図（背面図）である。また、図１４は、図１３に示すシリンダユニット４０に、センターブリッジ１６ｃを有するボディ１２を組み付けた場合の例を示す平面図である。 As described above, when the bleeder hole / inlet hole 46 is arranged on the outer peripheral side in the radial direction of the rotor 74 in the cylinder block 42, the bleeder hole / inlet hole 46 is opened from the opening formed between the center bridge 16 c and the main bridge 16 a of the body 12. If it is possible to access the hole / inlet hole 46, there is no need to limit the arrangement direction of the opening surface. For example, as can be read with reference to FIGS. 11 and 12, the opening surface of the bleeder hole / inlet hole 46 faces between the radially outer peripheral side and the axial inner side of the rotor 74, that is, the inner side oblique outer peripheral direction. It may be a thing, and as shown to FIG. 13, FIG. 14, you may arrange | position so that an opening surface may face the axial direction inner side of the rotor 74. FIG. FIG. 13 is a diagram (rear view) showing a configuration when the cylinder unit 40 in which the bleeder hole / inlet hole 46 is arranged toward the axial inner side of the rotor 74 is viewed from the inner side. FIG. 14 is a plan view showing an example in which the body 12 having the center bridge 16c is assembled to the cylinder unit 40 shown in FIG.
　また、図示しないが、ブリーダ孔・インレット孔４６は、その開口面がロータ７４の半径方向外周側に向けられるようにしても良い。いずれの場合においても、作動油のエア抜きや交換をする際の作業性が向上するという面で、同様な効果を得ることができるからである。 Although not shown, the opening surface of the bleeder hole / inlet hole 46 may be directed to the outer circumferential side of the rotor 74 in the radial direction. This is because, in any case, the same effect can be obtained in terms of improving workability when bleeding or replacing the hydraulic oil.
　なお、上記実施形態、及び図１０に示す形態に係るディスクブレーキ装置１０では、ブリーダ孔・インレット孔４６がシリンダブロック４２におけるロータ７４の半径方向内周側に配置されるように示している。しかしながら当然に、上記実施形態、及び図１０に示す形態のディスクブレーキ装置１０に対しても、図１２や図１３に示すような、シリンダブロック４２におけるロータ７４の半径方向外周側にブリーダ孔・インレット孔４６が配されたものを適用することができる。 In the disc brake device 10 according to the above embodiment and the embodiment shown in FIG. 10, the bleeder hole / inlet hole 46 is shown to be arranged on the radially inner peripheral side of the rotor 74 in the cylinder block 42. However, as a matter of course, the bleeder hole / inlet on the radially outer peripheral side of the rotor 74 in the cylinder block 42 as shown in FIGS. 12 and 13 is also applied to the above-described embodiment and the disc brake device 10 shown in FIG. The thing provided with the hole 46 can be applied.
　また、上記実施形態では、第１ピストン４８、および第２ピストン５０の稼働について、シリンダ４４内に作動油が供給されることで成される旨記載した。しかしながら、第１ピストン４８と第２ピストン５０の稼働は、油圧以外の形式により行うようにしても良い。このような構成とすることで、油圧ユニットが使用できない環境下においても、本発明に係るディスクブレーキ装置を適用することが可能となり、より汎用性を向上させることが可能となるからである。 In the above embodiment, the operation of the first piston 48 and the second piston 50 is described as being performed by supplying hydraulic oil into the cylinder 44. However, the operation of the first piston 48 and the second piston 50 may be performed in a form other than hydraulic pressure. With such a configuration, the disk brake device according to the present invention can be applied even in an environment where the hydraulic unit cannot be used, and versatility can be further improved.
　油圧以外の作動形式の具体的な一例として、図１５に示すような、モータギヤユニット７６が用いられる形態のものを挙げることができる。モータギヤユニット７６は、シリンダユニット４０に付帯され、図示しないギヤを介して動力が伝達されることで、シリンダユニット４０内に設けられた図示しない倍力機構が作動する。これにより、第１ピストン４８および第２ピストン５０が、相対的に離間する方向へ突出し、押圧力を生じさせることとなる。 As a specific example of the operation type other than the hydraulic pressure, there can be mentioned one in which a motor gear unit 76 is used as shown in FIG. The motor gear unit 76 is attached to the cylinder unit 40, and power is transmitted via a gear (not shown), whereby a booster mechanism (not shown) provided in the cylinder unit 40 operates. Thereby, the 1st piston 48 and the 2nd piston 50 will protrude in the direction which separates relatively, and will generate pressure.
　上記実施形態に係るディスクブレーキ装置１０では、シリンダユニット４０が、固定部材であるサポート２６に固定されている。このため、稼働部であるボディにモータが搭載される場合に比べ、ボディ１２の重量を軽くすることができ、モータとして、出力が小さく、小型軽量なものを採用することができる。よって、ディスクブレーキ装置全体の軽量化を図ることができる。 In the disc brake device 10 according to the above embodiment, the cylinder unit 40 is fixed to the support 26 that is a fixing member. For this reason, compared with the case where a motor is mounted in the body which is an operation | movement part, the weight of the body 12 can be made light and a small and lightweight thing can be employ | adopted as a motor with a small output. Therefore, the weight of the entire disc brake device can be reduced.
　また、上記実施形態では、サポート２６に対するシリンダユニット４０の固定について、ボディ１２を保持するスライドピン５４により共締めする構成とする旨記載した。しかしながら、固定位置３０ａ，３２ａがアーム部３０，３２におけるトルク受け位置よりもロータ７４の半径方向外周側に位置する形態であれば、スライドピン５４とは別の固定機構によりサポート２６に対してシリンダユニット４０が固定されるようにしても良い。 In the above-described embodiment, the cylinder unit 40 is fixed to the support 26 with a slide pin 54 that holds the body 12. However, as long as the fixed positions 30a and 32a are positioned on the outer peripheral side in the radial direction of the rotor 74 relative to the torque receiving position in the arm portions 30 and 32, the cylinder is fixed to the support 26 by a fixing mechanism different from the slide pin 54. The unit 40 may be fixed.
　ここで、上述した本発明に係るディスクブレーキ装置の実施の形態の特徴をそれぞれ以下に簡潔に纏めて列記する。
　［１］　ボディ（１２）、サポート（２６）、およびシリンダユニット（４０）が別体で構成され、前記シリンダユニットには、第１ピストン（４８）と第２ピストン（５０）が収容されるフローティング型のディスクブレーキ装置（１０）であって、
　前記シリンダユニットが、前記サポートにおけるロータ（７４）の回入側と回出側の双方に設けられたアーム部（３０，３２）に対して、前記シリンダユニットの外周側に配置されたシリンダ取付部（５２）を介して固定されているディスクブレーキ装置（１０）。
　［２］　前記アーム部における前記シリンダユニットを固定する固定位置（３０ａ，３２ａ）が、前記アーム部におけるトルク受け位置（インナパッド３４の耳部３８ａが当接する位置）よりも前記ロータの半径方向外周側に位置する上記［１］に記載のディスクブレーキ装置。
　［３］　前記アーム部における前記シリンダユニットを固定する固定位置が、前記ロータの外周よりも半径方向外周側に位置する上記［１］または［２］に記載のディスクブレーキ装置。
　［４］　前記シリンダ取付部は、前記シリンダユニットを固定する固定位置に対して、前記ボディを保持するスライドピン（５４）を介して固定されている上記［１］～［３］のいずれか１つに記載のディスクブレーキ装置。
　［５］　前記シリンダユニットの配置位置が、前記シリンダユニットを固定する固定位置よりも半径方向内周側に位置され、前記ロータの回入側と回出側に位置する２つの前記固定位置間に、空間が設けられる構成とされ、
　前記ボディには、前記固定位置間に設けられた前記空間における前記ロータの回入側と回出側にそれぞれ、前記ボディのインナ側とアウタ側を接続するメインブリッジ（１６ａ）が設けられる構成とされた上記［１］～［４］のいずれか１つに記載のディスクブレーキ装置。
　［６］　ボディ背肉部における前記ロータの軸方向中央部であって、回入側に配置された前記メインブリッジと回出側に配置された前記メインブリッジの間には、２つの前記メインブリッジを接続する接続部（１６ｂ）が設けられた上記［５］に記載のディスクブレーキ装置。
　［７］　前記接続部から前記ボディのインナ側へ延設されるセンターブリッジ（１６ｃ）が設けられた上記［６］に記載のディスクブレーキ装置。
　［８］　前記サポートと前記シリンダユニットとが異なる材料により構成されている上記［１］～［７］のいずれか１つに記載のディスクブレーキ装置。
　［９］　前記第１ピストン及び前記第２ピストンが、油圧以外の動力により押圧力を生じさせる構成とされた上記［１］～［８］のいずれか１つに記載のディスクブレーキ装置。 Here, the features of the above-described embodiments of the disc brake device according to the present invention will be summarized and listed below.
[1] The body (12), the support (26), and the cylinder unit (40) are formed separately, and the cylinder unit is a floating in which the first piston (48) and the second piston (50) are accommodated. Type disc brake device (10),
Cylinder mounting portion arranged on the outer peripheral side of the cylinder unit with respect to the arm portions (30, 32) provided on both the return side and the return side of the rotor (74) in the support. A disc brake device (10) fixed via (52).
[2] The fixing position (30a, 32a) for fixing the cylinder unit in the arm portion is the outer periphery in the radial direction of the rotor than the torque receiving position in the arm portion (the position where the ear portion 38a of the inner pad 34 abuts). The disc brake device according to [1], which is positioned on the side.
[3] The disc brake device according to [1] or [2], wherein a fixing position for fixing the cylinder unit in the arm portion is located on a radially outer peripheral side with respect to an outer periphery of the rotor.
[4] Any one of the above [1] to [3], wherein the cylinder mounting portion is fixed to a fixing position for fixing the cylinder unit via a slide pin (54) that holds the body. Disc brake device described in 1.
[5] The arrangement position of the cylinder unit is located on the radially inner side with respect to the fixed position for fixing the cylinder unit, and between the two fixed positions positioned on the return side and the return side of the rotor. , The space is provided,
The body is provided with a main bridge (16a) for connecting the inner side and the outer side of the body, respectively, on the turn-in side and the turn-out side of the rotor in the space provided between the fixed positions. The disc brake device according to any one of [1] to [4] above.
[6] The two main bridges between the main bridge disposed on the return side and the main bridge disposed on the return side, which are axially central portions of the rotor in the body back portion. The disc brake device according to the above [5], in which a connection portion (16b) for connecting the two is provided.
[7] The disc brake device according to [6], wherein a center bridge (16c) extending from the connection portion to the inner side of the body is provided.
[8] The disc brake device according to any one of [1] to [7], wherein the support and the cylinder unit are made of different materials.
[9] The disc brake device according to any one of [1] to [8], wherein the first piston and the second piston are configured to generate a pressing force by power other than hydraulic pressure.
　なお、本発明は、上述した実施形態に限定されるものではなく、適宜、変形、改良、等が可能である。その他、上述した実施形態における各構成要素の材質、形状、寸法、数、配置箇所、等は本発明を達成できるものであれば任意であり、限定されない。
　また、本出願は、２０１５年７月９日出願の日本特許出願（特願２０１５－１３７８１０）及び２０１６年２月９日出願の日本特許出願（特願２０１６－０２２３４６）に基づくものであり、その内容はここに参照として取り込まれる。 In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably. In addition, the material, shape, dimensions, number, arrangement location, and the like of each component in the above-described embodiment are arbitrary and are not limited as long as the present invention can be achieved.
This application is based on a Japanese patent application filed on July 9, 2015 (Japanese Patent Application No. 2015-137810) and a Japanese patent application filed on February 9, 2016 (Japanese Patent Application No. 2016-022346). The contents are incorporated herein by reference.
　本発明のディスクブレーキ装置によれば、スライドピンへの負荷を低減し、制動時の強度不足の懸念を解消することが可能なフローティング型のディスクブレーキ装置を提供することができる。 According to the disc brake device of the present invention, it is possible to provide a floating type disc brake device capable of reducing the load on the slide pin and solving the fear of insufficient strength during braking.
１０………ディスクブレーキ装置、１２………ボディ、１４………インナ側ボディ、１４ａ………受圧部、１４ｂ………ガイド孔、１６………サイドブリッジ、１６ａ………メインブリッジ、１６ｂ………接続部、１６ｃ………センターブリッジ、１８………アウタ側ボディ、１８ａ………ピン受け部、２０………アウタパッド、２２………ライニング、２４………プレッシャプレート、２６………サポート、２８………ブリッジ、２８ａ………締結孔、３０………アーム部、３０ａ………固定位置、３０ａ１………貫通孔、３２………アーム部、３２ａ………固定位置、３２ａ１………貫通孔、３４………インナパッド、３６………ライニング、３８………プレッシャプレート、３８ａ………耳部、４０………シリンダユニット、４２………シリンダブロック、４４………シリンダ、４６………ブリーダ孔・インレット孔、４８………第１ピストン、５０………第２ピストン、５２………シリンダ取付部、５４………スライドピン、５６………スリーブ、５８………ブーツ、６０………ブーツ、６２………袋ナット、６２ａ………ピン、６４………クリップ、６６………シム、６８………シム板本体、７０………挟持部、７２………爪、７４………ロータ。 10 ......... Disc brake device, 12 ......... Body, 14 ......... Inner side body, 14a ......... Pressure receiving portion, 14b ......... Guide hole, 16 ......... Side bridge, 16a ......... Main bridge, 16b ......... Connecting part, 16c ......... Center bridge, 18 ......... Outer body, 18a ......... Pin receiving part, 20 ......... Outer pad, 22 ......... Lining, 24 ......... Pressure plate, 26 ......... Support, 28 ......... Bridge, 28a ......... Fastening hole, 30 ......... Arm part, 30a ......... Fixed position, 30a1 ......... Through hole, 32 ......... Arm part, 32a ......... Fixing position, 32a1 ...... through hole, 34 ... inner pad, 36 ...... lining, 38 ...... pressure plate, 38a ...... ear, 40 ...... cylinder unit, 42 ... Cylinder block, 44 ......... Cylinder, 46 ......... Bleeder / inlet hole, 48 ......... First piston, 50 ...... Second piston, 52 ......... Cylinder mounting part, 54 ......... Slide pin, 56 ......... Sleeve, 58 ......... Boots, 60 ......... Boots, 62 ......... Cap nuts, 62a ......... Pins, 64 ......... Clips, 66 ......... Shim, 68 ......... Shim plate body , 70... Clamping part, 72... Claw, 74.

Claims (9)

  1. 　ボディ、サポート、およびシリンダユニットが別体で構成され、前記シリンダユニットには、第１ピストンと第２ピストンが収容されるフローティング型のディスクブレーキ装置であって、
    　前記シリンダユニットが、前記サポートにおけるロータの回入側と回出側の双方に設けられたアーム部に対して、前記シリンダユニットの外周側に配置されたシリンダ取付部を介して固定されているディスクブレーキ装置。     The body, the support, and the cylinder unit are configured separately, and the cylinder unit is a floating type disc brake device that houses the first piston and the second piston,
    A disk in which the cylinder unit is fixed to an arm portion provided on both the rotor inlet side and the outlet side of the support via a cylinder mounting portion arranged on the outer peripheral side of the cylinder unit. Brake device.
  2. 　前記アーム部における前記シリンダユニットを固定する固定位置が、前記アーム部におけるトルク受け位置よりも前記ロータの半径方向外周側に位置する請求項１に記載のディスクブレーキ装置。 2. The disc brake device according to claim 1, wherein a fixing position for fixing the cylinder unit in the arm portion is located on a radially outer peripheral side of the rotor with respect to a torque receiving position in the arm portion.
  3. 　前記アーム部における前記シリンダユニットを固定する固定位置が、前記ロータの外周よりも半径方向外周側に位置する請求項１または２に記載のディスクブレーキ装置。 The disc brake device according to claim 1 or 2, wherein a fixing position for fixing the cylinder unit in the arm portion is located on a radially outer peripheral side with respect to an outer periphery of the rotor.
  4. 　前記シリンダ取付部は、前記シリンダユニットを固定する固定位置に対して、前記ボディを保持するスライドピンを介して固定されている請求項１～３のいずれか１項に記載のディスクブレーキ装置。 The disc brake device according to any one of claims 1 to 3, wherein the cylinder mounting portion is fixed to a fixing position for fixing the cylinder unit via a slide pin that holds the body.
  5. 　前記シリンダユニットの配置位置が、前記シリンダユニットを固定する固定位置よりも半径方向内周側に位置され、前記ロータの回入側と回出側に位置する２つの前記固定位置間に、空間が設けられる構成とされ、
    　前記ボディには、前記固定位置間に設けられた前記空間における前記ロータの回入側と回出側にそれぞれ、前記ボディのインナ側とアウタ側を接続するメインブリッジが設けられる構成とされた請求項１～４のいずれか１項に記載のディスクブレーキ装置。     An arrangement position of the cylinder unit is located on a radially inner peripheral side with respect to a fixing position for fixing the cylinder unit, and a space is provided between the two fixing positions located on the turn-in side and the turn-out side of the rotor. It is configured to be provided,
    The body is configured to be provided with a main bridge that connects an inner side and an outer side of the body, respectively, on a turn-in side and a turn-out side of the rotor in the space provided between the fixed positions. Item 5. The disc brake device according to any one of Items 1 to 4.
  6. 　ボディ背肉部における前記ロータの軸方向中央部であって、回入側に配置された前記メインブリッジと回出側に配置された前記メインブリッジの間には、２つの前記メインブリッジを接続する接続部が設けられた請求項５に記載のディスクブレーキ装置。 Two main bridges are connected between the main bridge disposed on the return side and the main bridge disposed on the return side, which is an axially central portion of the rotor in the body back meat part. The disc brake device according to claim 5, further comprising a connecting portion.
  7. 　前記接続部から前記ボディのインナ側へ延設されるセンターブリッジが設けられた請求項６に記載のディスクブレーキ装置。 The disc brake device according to claim 6, further comprising a center bridge extending from the connection portion to the inner side of the body.
  8. 　前記サポートと前記シリンダユニットとが異なる材料により構成されている請求項１～７のいずれか１項に記載のディスクブレーキ装置。 The disc brake device according to any one of claims 1 to 7, wherein the support and the cylinder unit are made of different materials.
  9. 　前記第１ピストン及び前記第２ピストンが、油圧以外の動力により押圧力を生じさせる構成とされた請求項１～８のいずれか１項に記載のディスクブレーキ装置。 The disc brake device according to any one of claims 1 to 8, wherein the first piston and the second piston are configured to generate a pressing force by power other than hydraulic pressure.
PCT/JP2016/069088 2015-07-09 2016-06-28 Disc brake device WO2017006803A1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US15/741,775 US10670092B2 (en) 2015-07-09 2016-06-28 Disc brake device
EP16821272.8A EP3321535B1 (en) 2015-07-09 2016-06-28 Disc brake device
CN201680040608.4A CN107850143B (en) 2015-07-09 2016-06-28 Disc brake device

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2015-137810 2015-07-09
JP2015137810 2015-07-09
JP2016022346A JP6680554B2 (en) 2015-07-09 2016-02-09 Disc brake device
JP2016-022346 2016-02-09

Publications (1)

Publication Number Publication Date
WO2017006803A1 true WO2017006803A1 (en) 2017-01-12

Family

ID=57685243

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2016/069088 WO2017006803A1 (en) 2015-07-09 2016-06-28 Disc brake device

Country Status (1)

Country Link
WO (1) WO2017006803A1 (en)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08254234A (en) * 1995-03-20 1996-10-01 Nissin Kogyo Kk Disc brake for vehicle
JP2006231954A (en) * 2005-02-22 2006-09-07 Honda Motor Co Ltd Electric braking device
JP2007321975A (en) * 2006-05-02 2007-12-13 Akebono Brake Ind Co Ltd Caliper for disc brake
JP2009058035A (en) * 2007-08-31 2009-03-19 Advics:Kk Movable caliper type disk brake device
JP2014101998A (en) * 2012-10-26 2014-06-05 Akebono Brake Ind Co Ltd Disc brake device

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08254234A (en) * 1995-03-20 1996-10-01 Nissin Kogyo Kk Disc brake for vehicle
JP2006231954A (en) * 2005-02-22 2006-09-07 Honda Motor Co Ltd Electric braking device
JP2007321975A (en) * 2006-05-02 2007-12-13 Akebono Brake Ind Co Ltd Caliper for disc brake
JP2009058035A (en) * 2007-08-31 2009-03-19 Advics:Kk Movable caliper type disk brake device
JP2014101998A (en) * 2012-10-26 2014-06-05 Akebono Brake Ind Co Ltd Disc brake device

Similar Documents

Publication Publication Date Title
JP6680554B2 (en) Disc brake device
JP4741693B2 (en) Decorative plate mounting structure
WO2015098780A1 (en) Disc-brake device
WO2015174434A1 (en) Disk brake device
WO2015098781A1 (en) Disc brake device
JP2006057718A (en) Floating calliper type disk brake
WO2015137359A1 (en) Floating-type disc brake
JP6794238B2 (en) Caliper for opposed piston type disc brake
WO2017130628A1 (en) Disc brake device and brake pad for disc brake device
WO2017006803A1 (en) Disc brake device
WO2016006581A1 (en) Disc brake device
JP5332014B2 (en) Decorative plate mounting structure
US10619684B2 (en) Partially lined motor-vehicle disk brake with friction linings which are provided with pull-support in a frame-shaped holder
WO2010137715A1 (en) Disc brake for vehicles
JP2009264506A (en) Vehicular disc brake
KR102642274B1 (en) floating caliper disc brake
JP5544263B2 (en) Brake pads
JP7312797B2 (en) Caliper body for vehicle disc brakes
US20080135348A1 (en) Internal brake caliper assembly
JP5576518B2 (en) Caliper body for disc brakes for vehicles
WO2021039413A1 (en) Disc brake
JPH1182580A (en) Disc brake for vehicle
JP4288197B2 (en) Vehicle disc brake
JP5603797B2 (en) Vehicle disc brake
JP2017020557A (en) Disc brake device and connection member for disc brake device

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 16821272

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE