WO2017073110A1 - ディスクブレーキおよびピストン - Google Patents
ディスクブレーキおよびピストン Download PDFInfo
- Publication number
- WO2017073110A1 WO2017073110A1 PCT/JP2016/068315 JP2016068315W WO2017073110A1 WO 2017073110 A1 WO2017073110 A1 WO 2017073110A1 JP 2016068315 W JP2016068315 W JP 2016068315W WO 2017073110 A1 WO2017073110 A1 WO 2017073110A1
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- WO
- WIPO (PCT)
- Prior art keywords
- piston
- main body
- plate
- outer bottom
- disc brake
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/14—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/0006—Noise or vibration control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/14—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
-
- 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
- F16D65/183—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 with force-transmitting members arranged side by side acting on a spot type force-applying member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J1/00—Pistons; Trunk pistons; Plungers
- F16J1/005—Pistons; Trunk pistons; Plungers obtained by assembling several pieces
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J1/00—Pistons; Trunk pistons; Plungers
- F16J1/005—Pistons; Trunk pistons; Plungers obtained by assembling several pieces
- F16J1/006—Pistons; Trunk pistons; Plungers obtained by assembling several pieces of different materials
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- 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
- B60T1/00—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles
- B60T1/02—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels
- B60T1/06—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels
- B60T1/065—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels employing disc
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2121/00—Type of actuator operation force
- F16D2121/02—Fluid pressure
- F16D2121/04—Fluid pressure acting on a piston-type actuator, e.g. for liquid pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2125/00—Components of actuators
- F16D2125/02—Fluid-pressure mechanisms
- F16D2125/06—Pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2200/00—Materials; Production methods therefor
- F16D2200/0004—Materials; Production methods therefor metallic
- F16D2200/0008—Ferro
- F16D2200/0021—Steel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2200/00—Materials; Production methods therefor
- F16D2200/0034—Materials; Production methods therefor non-metallic
- F16D2200/0056—Elastomers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2250/00—Manufacturing; Assembly
- F16D2250/0023—Shaping by pressure
Definitions
- the present invention relates to a disc brake and a piston.
- a piston constituted by an inner member formed into a bottomed cylindrical shape and an outer member fitted and fixed to the outside of the inner member (see, for example, Patent Document 1).
- the above piston structure may not be able to reduce the weight effectively.
- An object of the present invention is to provide a disc brake and a piston that can be reduced in weight.
- a piston is formed in a bottomed cylindrical shape, and a main body member in which the thickness of the cylindrical portion and the bottom portion is substantially equal, and the main body A plate-like member that is fixed to the outer bottom surface of the member, is located within the range of the outer bottom surface, and is disposed at a portion including the center of the outer bottom surface.
- Sectional drawing which shows the disc brake of 1st Embodiment.
- (A) is an image figure of the adhesive layer before a deformation
- (c) is an image figure of the adhesive layer after a deformation
- (A) is sectional drawing before the deformation
- (b) is sectional drawing after a deformation
- (c) is a top view.
- (A) is sectional drawing of the example of a change of the piston of 1st Embodiment
- (b) is sectional drawing of the other example of a change.
- Sectional drawing of the principal part of the piston of 2nd Embodiment The diagram which shows the frequency response analysis result of the piston of 1st, 2nd embodiment.
- the side view of the piston of 3rd Embodiment Sectional drawing of the principal part of the piston of 3rd Embodiment.
- FIG. 1 shows a disc brake 11 of the first embodiment.
- the disc brake 11 is for a vehicle such as an automobile, specifically for a four-wheel automobile, and includes a carrier 12, a pair of pads 13, and a caliper 14.
- the disc brake 11 brakes the vehicle by stopping the rotation of the disc 15 that rotates with a wheel (not shown) to be braked.
- the carrier 12 is disposed so as to straddle the outer diameter side of the disk 15 and is fixed to the non-rotating portion of the vehicle.
- the pair of pads 13 are supported by the carrier 12 so as to be movable in the axial direction of the disk 15 in a state of being opposed to both surfaces of the disk 15.
- the caliper 14 is supported by the carrier 12 so as to be slidable in the axial direction of the disk 15 while straddling the outer diameter side of the disk 15.
- the caliper 14 stops the rotation of the disk 15 by pressing the pair of pads 13 against the disk 15, and is held in the caliper body 20 and the caliper body 20 supported by the carrier 12 across the disk 15. And a piston 21 disposed so as to face the one surface side of the disk 15.
- the caliper body 20 has a cylinder 25 to which brake fluid pressure is applied, a bridge portion 26 that straddles the disk 15, and a claw portion 27 that presses the outer pad 13 of the pair of pads 13. It is configured.
- the cylinder 25 is disposed to face the inner side (vehicle width direction inner) surface of the disk 15 in the axial direction, and has a cylindrical cylinder side portion 31 that opens to the disk 15 side, and the disk 15 of the cylinder side portion 31.
- the cylinder 25 has an accommodation hole 33 inside the cylinder side portion 31 and the cylinder bottom portion 32, and the accommodation hole 33 opens to the disk 15 side and extends along the axial direction of the disk 15.
- the piston 21 is slidably inserted into the accommodation hole 33.
- the bridge 26 extends from the cylinder 25 in the axial direction of the disk 15 so as to straddle the disk 15.
- the claw portion 27 extends from the end portion of the bridge portion 26 opposite to the cylinder 25 so as to face the cylinder 25, and is disposed to face the outer side surface (the vehicle width direction outer side) of the disk 15. .
- a pipe connection hole 35 connected to a brake pipe (not shown) is formed on the central axis of the accommodation hole 33.
- the caliper 14 advances the piston 21 toward the disc 15 by the brake fluid pressure introduced into the accommodation hole 33 through the pipe connection hole 35.
- the piston 21 moves along the axial direction of the disk 15 and presses the inner pad 13 against the disk 15 along the axial direction of the disk 15.
- the caliper body 20 moves along the axial direction of the disk 15 in the direction of separating the cylinder 25 from the disk 15 with respect to the carrier 12, and the pawl portion 27 moves the pad 13 on the outer side to the disk. 15 is pressed along the axial direction of the disk 15. In this manner, the pads 21 on both sides are sandwiched between the piston 21 and the claw portion 27 and pressed against the disk 15 to generate a frictional resistance, thereby generating a braking force.
- An annular seal groove 37 that is recessed outward in the radial direction is formed at an intermediate position on the opening side in the axial direction of the inner peripheral surface of the cylinder side portion 31 that forms the accommodation hole 33.
- An annular boot groove 38 that is recessed radially outward is formed on the opening side of the inner circumferential surface of the cylinder side portion 31 relative to the seal groove 37.
- An annular piston seal 39 that seals the gap with the piston 21 is fitted in the seal groove 37.
- One end of an annular boot 40 interposed between the piston 21 and the piston 21 is fitted in the boot groove 38.
- the piston 21 has a cylindrical main body side portion 52 (side portion) that is an opening portion 51 that is open on one side, and a main body bottom portion 53 (bottom portion) that is disposed on the side opposite to the opening portion 51 of the main body side portion 52.
- a main body member 54 having a bottomed cylindrical shape, and a plate-like member 56 that is disposed on the outer bottom surface 55 of the main body opposite to the opening 51 of the main body bottom 53 and is a separate member from the main body member 54. Yes.
- the main body side portion 52 of the main body member 54 has a boot groove 59 that is recessed radially inward from the cylindrical outermost outer diameter surface 58 of the main body member 54. Is formed.
- the main body outer bottom surface 55 of the main body bottom portion 53 is a circular flat surface orthogonal to the central axis of the main body side portion 52.
- the main body member 54 is formed from a steel plate having a constant plate thickness mainly by pressing. For this reason, the thickness of the main body bottom 53 is substantially equal to the thickness of the main body side 52.
- the plate-like member 56 has a disc shape, and on the outer peripheral side, a cylindrical outermost surface 60 having a cylindrical surface is formed on one side in the axial direction. Is formed.
- the outer diameter of the maximum outer diameter surface 60 is equal to the outer diameter of the maximum outer diameter surface 58.
- the plate-like member 56 has a constant plate thickness except for the outer diameter portion where the R chamfer 61 is formed in the radial direction.
- the plate-like member 56 has a flat circular shape on one surface 62 in the thickness direction, and the area of the surface 62 is equal to the area of the main body outer bottom surface 55 of the main body member 54.
- the plate-like member 56 has a flat circular shape on the surface 63 on the other side in the thickness direction, and the area of the surface 63 is smaller than the area of the surface 62 because the R chamfer 61 is formed. Yes.
- the surfaces 62 and 63 are arranged in parallel.
- the plate-like member 56 is also formed by pressing a steel plate having a constant plate thickness mainly by pressing.
- the material of the plate-like member 56 is the same as the material of the main body member 54, but may be different.
- the entire surface 62 of the plate member 56 is adhered to the entire surface of the main body outer bottom surface 55 of the main body member 54 with an adhesive, and the plate members 56 are fixed to the main body member 54 so that their central axes coincide with each other.
- the piston 21 including the main body member 54, the plate-like member 56, and the adhesive layer 65 (attenuating member) interposed therebetween is formed.
- the plate-like member 56 attached to the main body member 54 in this way is in a range in the radial direction of the main body outer bottom surface 55 of the main body bottom portion 53 of the main body member 54 and includes a portion including the radial center of the main body bottom portion 53. Is arranged.
- the plate-like member 56 covers the entire surface of the main body outer bottom surface 55.
- the plate-like member 56 is a reinforcing member that reinforces the main body bottom 53 of the main body member 54.
- the opening 51 of the main body member 54 becomes the opening 51 on one side in the axial direction of the piston 21, the main body side 52 of the main body member 54 becomes the cylindrical piston side 52 of the piston 21, and the main body bottom 53 of the main body member 54.
- the adhesive layer 65 and the plate-like member 56 constitute a piston bottom 67 of the piston 21 that closes the other axial side of the piston side 52.
- the surface 63 of the plate-like member 56 becomes the piston outer bottom surface 63 on the side opposite to the opening 51 of the piston 21.
- the boot groove 59 is provided in the piston side portion 52.
- a phenol-based adhesive is used as an adhesive for bonding the plate-like member 56 to the main body bottom 53 of the main body member 54. That is, the adhesive layer 65 is a phenolic resin layer.
- the piston 21 is inserted into the receiving hole 33 in the cylinder side portion 31 with the piston bottom 67 at the top, whereby the piston 21 is moved from the piston bottom 67 to the cylinder bottom 32.
- the opening 51 is disposed on the side opposite to the cylinder bottom 32.
- the piston 21 is fitted into the piston seal 39 disposed in the seal groove 37 of the cylinder side portion 31 in the piston side portion 52, and the piston seal 39 and the inner peripheral surface of the cylinder side portion 31 Supported by The other end of the boot 40 having one end fitted in the boot groove 38 of the cylinder side portion 31 is fitted in the boot groove 59 of the piston 21.
- the disc brake piston described in Patent Document 1 is composed of an inner member formed in a bottomed cylindrical shape and an outer member fitted and fixed to the outside of the inner member.
- This piston aims at weight reduction by comprising a piston combining two members. Since these members are mainly formed by pressing, the thickness of the product depends on the thickness of the steel sheet to be pressed. For this reason, if the plate thickness is selected based on the piston bottom portion where the stress generated by the brake fluid pressure is high, the thickness of the side surface portion becomes excessive, and the obtained lightening effect may be reduced.
- the piston 21 of the first embodiment includes a cylindrical main body side portion 52 that is an opening portion 51 that is open on one side, and a main body bottom portion that is disposed on the opposite side of the opening portion 51 of the main body side portion 52. 53, and a plate-like member 56 disposed in a region that is in the range of the main body outer bottom surface 55 outside the main body bottom 53 and includes the center in the radial direction of the main body bottom 53. .
- board thickness of the plate-shaped member 56 is adjusted, the intensity
- the piston bottom portion 67 where a particularly high stress is generated by the brake fluid pressure satisfies the required strength using the plate-like member 56
- the piston side portion 52 satisfies the required strength with the plate thickness of the steel plate used for press working.
- the piston bottom 67 has a structure in which the plate-like member 56 is bonded to the main body bottom 53 of the main body member 54, the piston 21 has an adhesive layer 65 that is an adhesion portion of the image shown in FIG. 3 (b) and 3 (c), kinetic energy loss occurs due to the minute deformation that occurs, and vibration damping action is obtained, and the effect of suppressing brake noise and the like is obtained. That is, since the adhesive layer 65 between the main body bottom 53 of the main body member 54 and the plate-like member 56 attenuates the vibration of the piston 21, an effect of suppressing brake squealing can be obtained.
- a phenol-based adhesive is used as an adhesive for adhering the main body member 54 and the plate-like member 56, resistance to heat generated during brake fluid and braking can be obtained.
- a structure may be adopted in which an elastic damping member is sandwiched between the main body bottom 53 of the main body member 54 and the plate-like member 56. That is, the main body member 54 and one surface of the attenuation member may be fixed with an adhesive, and the other surface of the attenuation member and the plate-like member 56 may be fixed with an adhesive.
- a plate material made of EPDM (ethylene propylene rubber) resistant to brake fluid can be used as the damping member.
- the integral piston 21A shown in FIG. 4 formed mainly by press molding is used as a reference for comparison, and a separate plate member 56 is bonded to the integral body member 54 formed mainly by press molding.
- the piston 21 of the first embodiment was compared using FEM analysis (finite element method analysis).
- the reference piston 21A is made of steel having a piston bottom 67A plate thickness of 5.8 mm and a piston side portion 52A plate thickness of 4.3 mm, and has a mass of 255 g and is generated by the addition of hydraulic pressure.
- the maximum principal stress is 116 MPa.
- FIG. 4A shows a state before the hydraulic pressure is applied to the reference piston 21A
- FIG. 4B shows a deformed state by FEM analysis when the hydraulic pressure is applied to the reference piston 21A
- FIG. 4C shows the maximum principal stress generation position X of the reference piston 21A.
- the maximum principal stress generation position X is the center in the radial direction of the piston bottom portion 67A, and the stress generated in the piston side portion 52A is smaller than that. Therefore, if the thickness of the piston bottom portion requiring rigidity is increased and the plate thickness of the piston side portion having a small rigidity required for the piston bottom portion can be reduced, a more effective weight reduction can be expected.
- the piston side portion 52 is thinned while the body bottom portion 53 of the main body member 54 is thin like the piston side portion 52.
- the piston 21 in which the thickness of the piston bottom 67 was made equal to that of the reference piston by bonding the member 56 was analyzed by FEM. From the results of the FEM analysis, as shown in Table 2, the piston 21 has a mass of 198 g even if the thickness of the piston bottom 67 is 5.9 mm, which is equivalent to that of the reference piston. The weight can be reduced by 22%.
- the stress of the piston bottom 67 is 163 MPa, which is as rigid as the reference piston.
- the same material as that of the main body member 54 can be used for the plate-like member 56, and a phenolic resin material may be used as long as the strength and temperature constraints are satisfied.
- the plate-like member 56 shown in FIG. 2 may be disposed within a range of the main body outer bottom surface 55 of the main body bottom 53 and at a portion including the center of the main body bottom 53.
- a plate-like member having an outer diameter smaller than the main body outer bottom surface 55 of the main body bottom portion 53 of the main body member 54 and less than or equal to the inner diameter of the main body side portion 52.
- the piston bottom 67B may be configured by adhering 56B to the main body outer bottom surface 55 with an adhesive layer 65B.
- the piston bottom portion 67C may be configured by adhering the member 56C to the main body outer bottom surface 55 with an adhesive layer 65C.
- the plate-like member 56 ⁇ / b> C having an outer diameter larger than the inner diameter of the main body side portion 52, that is, the inner diameter of the main body member 54, in a portion including the center of the main body bottom portion 53 of the main body outer bottom surface 55.
- the piston 21 ⁇ / b> D includes a main body member 54 ⁇ / b> D and a plate-like member 56 ⁇ / b> D that are partially different from the first embodiment.
- annular step portion 81 is formed on the outer peripheral portion on the opposite side of the opening 51 of the main body bottom 53D disposed on the opposite side of the opening 51 of the main body side 52.
- the main body bottom portion 53 ⁇ / b> D is provided with a central surface portion 82 formed of a circular flat surface orthogonal to the central axis of the main body side portion 52 inside the stepped portion 81 in the radial direction.
- the stepped portion 81 includes an annular stepped surface portion 84 that extends radially inward from the cylindrical maximum outer diameter surface 58 ⁇ / b> D of the main body member 54 ⁇ / b> D, and a central portion from the inner peripheral edge of the stepped surface portion 84. It has a cylindrical wall surface portion 85 extending to the surface portion 82 side and connected to the central surface portion 82.
- the wall surface portion 85 is disposed coaxially with the maximum outer diameter surface 58 ⁇ / b> D, and the step surface portion 84 is a flat surface parallel to the central surface portion 82.
- the central surface portion 82, the wall surface portion 85, and the stepped surface portion 84 constitute a main body outer bottom surface 55D opposite to the opening 51 of the main body bottom portion 53D.
- an annular stepped portion 91 is formed on the outer periphery of the plate-like member 56 ⁇ / b> D on the side opposite to the surface 63 ⁇ / b> D constituting the piston outer bottom surface.
- the plate-like member 56D is provided with a flat circular surface 62D inside the stepped portion 91 in the radial direction.
- the area of the surface 62D is equal to the area of the central surface portion 82 of the main body member 54D.
- the surfaces 62D and 63D are arranged in parallel.
- the step portion 91 includes an annular step surface portion 94 that extends radially inward from the cylindrical maximum outer diameter surface 60 ⁇ / b> D of the plate-like member 56 ⁇ / b> D, and an inner peripheral edge portion of the step surface portion 94. It has a cylindrical wall surface portion 95 extending to the surface 62D side and connected to the surface 62D. The wall surface portion 95 is disposed coaxially with the surface 62D, and the stepped surface portion 94 is a flat surface parallel to the surface 62D. An R chamfer 61D is formed between the maximum outer diameter surface 60D and the surface 63D.
- the entire surface 62D of the plate-like member 56D is adhered to the entire surface of the central surface portion 82 of the main body member 54D with an adhesive, and the plate-like member 56D is fixed to the main body member 54D with the central axes thereof aligned with each other.
- the piston main body 97 including the main body member 54D, the plate-like member 56D, and the adhesive layer 65D interposed therebetween is formed.
- the plate-like member 56D attached to the main body member 54D is disposed in a region that is within the radial range of the main body outer bottom surface 55D of the main body bottom portion 53D of the main body member 54D and includes the radial center of the main body bottom portion 53D. ing.
- the plate-like member 56D covers the entire surface of the central surface portion 82 in the radial center of the main body outer bottom surface 55D.
- the stepped portions 81 and 91 form an annular seal groove 96 that is recessed radially inward from the maximum outer diameter surfaces 58D and 60D in the outer peripheral portion of the piston main body 97.
- the seal groove 96 is formed in the piston main body 97 so as to surround the adhesive layer 65D.
- the piston 21D has an annular seal member 101 (attenuating member) fitted in the seal groove 96 of the piston body 97.
- the seal member 101 is an endless square ring having a rectangular cross section. Thereby, piston 21D is provided with seal member 101 between main part bottom 53D and plate-like member 56D.
- the seal member 101 is in close contact with the entire circumference of the wall surface portions 85 and 95, and seals the adhesive layer 65D on the outer side in the radial direction over the entire circumference.
- the seal member 101 is made of EPDM that is resistant to brake fluid.
- the main body bottom 53D of the main body member 54D, the adhesive layer 65D, the plate-like member 56D, and the seal member 101 constitute a piston bottom 67D of the piston 21D.
- the piston 21D can be effectively reduced in weight. From the results of the FEM analysis, as shown in Table 3, the piston 21D has a mass of 203 g even if the thickness of the piston bottom 67D is 5.9 mm, which is equivalent to the reference piston 21A, compared with the reference piston. The weight can be reduced by about 20%. In addition, the stress of the piston bottom 67D is 177 MPa, and the rigidity is comparable to that of the reference piston 21A.
- the piston 21D since the piston 21D includes the seal member 101 between the main body bottom 53D and the plate-like member 56D, it is possible to suppress the influence of the adhesive layer 65D due to the brake fluid. it can. Therefore, the durability of the piston 21D is improved.
- FIG. 8 shows the response of the radial center of the piston bottom when the loss coefficient of the rubber material as the seal member 101 is 20%, and the radial center of the piston bottom is vibrated axially with an excitation force of 1 mN. The result of the required frequency response analysis is shown. As is apparent from FIG. 8, the maximum value of acceleration / excitation force is reduced by about 18% in the piston 21D indicated by the broken line Y2 in FIG. 8 compared to the piston 21 of the first embodiment indicated by the solid line Y1 in FIG. it can.
- the main body bottom 53D of the main body member 54D and the plate-like member 56D may have a structure in which a damping member for damping vibration is sandwiched. That is, the main body member 54D and one surface of the attenuation member may be fixed with an adhesive, and the other surface of the attenuation member and the plate-shaped member 56D may be fixed with an adhesive.
- a plate material made of EPDM that is resistant to brake fluid can be used.
- the piston 21E includes a main body member 54E and a plate-like member 56E, both of which are partly different from the first embodiment.
- the main body member 54E has an annular shape orthogonal to the central axis of the main body side portion 52 on the outer peripheral side opposite to the opening portion 51 of the main body bottom portion 53E disposed on the opposite side of the opening portion 51 of the main body side portion 52.
- An annular surface portion 111 made of a flat surface is provided, and a convex portion 112 that protrudes in a direction opposite to the opening 51 is formed at the center portion in the radial direction of the main body bottom 53E. . Since this convex portion 112 is also formed by press molding, an annular surface portion 113 formed of an annular flat surface orthogonal to the central axis of the main body side portion 52 is provided on the opening 51 side of the main body bottom portion 53E.
- a concave portion 114 is formed in the central portion of 53E so as to be recessed in the direction opposite to the opening portion 51 relative to the outer annular surface portion 113 thereof.
- the convex portion 112 has a cylindrical wall surface portion 121 extending from the inner peripheral edge portion of the annular surface portion 111 in the direction opposite to the opening portion 51, and a radial direction from the edge portion of the wall surface portion 121 opposite to the opening portion 51. And a circular central surface portion 122 extending inward.
- the wall surface portion 121 is disposed coaxially with the cylindrical maximum outer diameter surface 58 of the main body member 54 ⁇ / b> E, and the central surface portion 122 is a flat surface parallel to the annular surface portion 111.
- the annular surface portion 111, the wall surface portion 121, and the central surface portion 122 constitute a main body outer bottom surface 55E opposite to the opening 51 of the main body bottom portion 53E.
- the plate-like member 56E is provided with an annular surface portion 131 formed of a flat surface on the outer peripheral side opposite to the surface 63 constituting the outer bottom surface of the piston.
- a concave portion 132 that is recessed toward the surface 63 side of the annular surface portion 131 is formed.
- the annular surface portion 131 is formed in parallel with the surface 63.
- the concave portion 132 includes a cylindrical wall surface portion 141 extending from the inner peripheral edge of the annular surface portion 131 to the surface 63 side, and a circular central surface portion 142 extending radially inward from the edge portion on the surface 63 side of the wall surface portion 141. have.
- the wall surface portion 141 is disposed coaxially with the maximum outer diameter surface 60 of the plate-like member 56E, and the central surface portion 142 is a flat surface parallel to the annular surface portion 131.
- the wall surface portion 121 of the convex portion 112 of the main body member 54E is directly fitted to the wall surface portion 141 of the concave portion 132 of the plate member 56E, so that the plate member 56E is centered on the main body member 54E. Fix them to match each other.
- the annular surface portion 111 of the main body member 54E and the annular surface portion 131 of the plate-like member 56E are brought into contact with each other.
- the convex portion 112 is press-fitted into the concave portion 132 to form the piston 21E composed of the main body member 54E and the plate-like member 56E.
- the plate-like member 56E attached to the main body member 54E is disposed in a region in the radial direction range of the main body outer bottom surface 55E of the main body bottom portion 53E of the main body member 54E and includes the radial center of the main body bottom portion 53E. Yes.
- the plate-like member 56E covers the entire surface of the central surface portion 122 at the center in the radial direction of the main body outer bottom surface 55E.
- a main body bottom 53E of the main body member 54E and a plate-like member 56E constitute a piston bottom 67E of the piston 21E.
- the piston 21E is not bonded by an adhesive, but the convex portion 112 at the center of the main body bottom 53E of the metal main body member 54E is replaced with the concave portion 132 of the metal plate-like member 56E. Therefore, it is possible to suppress the influence of the piston 21E on the brake fluid. Therefore, the durability of the piston 21E is improved.
- a convex portion may be provided on the plate-like member, and a concave portion may be provided at the center of the main body bottom of the main body member so that the convex portion and the concave portion are fitted. That is, either the central part of the main body bottom part or the plate-like member has a concave part, and either the central part of the main body bottom part or the plate-like member has a convex part. It only has to be fitted.
- the piston is a main body member that is formed in a bottomed cylindrical shape and has a cylindrical portion and a bottom portion, and the cylindrical portion and the bottom portion And a plate-like member fixed to the outer bottom surface of the main body member, and within the range of the outer bottom surface and including the center of the outer bottom surface A plate-like member disposed at the site.
- the plate-like member is bonded to the outer bottom surface by being bonded with a phenol-based adhesive, so that it is resistant to brake fluid and heat generated during braking. can get.
- an elastic damping member is disposed between the outer bottom surface and the plate-like member, so that a vibration damping action is obtained, and a brake squeal is obtained. The effect which suppresses etc. is acquired.
- the sealing member is arrange
- the outer bottom surface and the plate-like member are fixed by concave and convex fitting, so that the influence of the brake fluid on the piston can be suppressed. Accordingly, the durability of the piston is improved.
- a sixth aspect is a disc brake piston that presses a pad against a disc, and is fixed to the outer bottom surface of a main body member formed in a bottomed cylindrical shape in which the thickness of the cylindrical portion and the bottom portion is substantially equal.
- the plate-like member is disposed within a range of the outer bottom surface and is disposed at a portion including the center of the outer bottom surface. Thereby, effective weight reduction becomes possible.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Braking Arrangements (AREA)
- Gasket Seals (AREA)
- Vibration Prevention Devices (AREA)
Abstract
Description
また、第3実施形態によれば、ピストン21Eが、接着剤による接着ではなく、金属製の本体部材54Eの本体底部53Eの中央部の凸部112を、金属製の板状部材56Eの凹部132に直接嵌合させて形成されているため、ブレーキフルードによりピストン21Eが受ける影響を抑制することができる。したがって、ピストン21Eの耐久性が向上する。この場合、上記とは逆に板状部材に凸部を設け、本体部材の本体底部の中央部に凹部を設けて、これら凸部と凹部とを嵌合させても良い。つまり、本体底部の中央部、及び、板状部材の何れか一方が凹部を備え、本体底部の中央部、及び、板状部材の何れか他方が凸部を備え、これら凹部と凸部とが嵌合していれば良い。
第1の態様としては、ディスクへパッドを押圧するピストンを備えたディスクブレーキにおいて、前記ピストンは、有底筒状に形成され、筒部と底部とを有する本体部材であって、筒部と底部との肉厚がほぼ同等となっている本体部材と、前記本体部材の外底面に固定される板状部材であって、該外底面の範囲内にあり、かつ、前記外底面の中央を含む部位に配置される板状部材と、を備える。これにより、効果的な軽量化が可能となる。
Claims (6)
- ディスクブレーキにおいて、
ディスクへパッドを押圧するピストンを備え、
前記ピストンは、
有底筒状に形成され、筒部と底部とを有する本体部材であって、前記筒部と前記底部との肉厚がほぼ同等となっている本体部材と、
前記本体部材の外底面に固定される板状部材であって、該外底面の範囲内にあり、かつ、前記外底面の中央を含む部位に配置される板状部材と、
を備えるディスクブレーキ。 - 前記板状部材は、フェノール系接着剤で接着されて前記外底面に固定されている、請求項1に記載のディスクブレーキ。
- 前記外底面と前記板状部材との間には、弾性を有する減衰部材が配置される、請求項1記載のディスクブレーキ。
- 前記外底面と前記板状部材との間には、シール部材が配置される、請求項1又は2に記載のディスクブレーキ。
- 前記外底面と前記板状部材とは、凹凸嵌合で固定される、請求項1に記載のディスクブレーキ。
- ディスクへパッドを押圧するディスクブレーキ用のピストンであって、
筒部と底部との肉厚がほぼ同等な有底筒状に形成される本体部材の外底面に固定される板状部材を有し、
前記板状部材は、前記外底面の範囲内にあり、かつ、前記外底面の中央を含む部位に配置されている
ピストン。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
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US15/755,320 US10591008B2 (en) | 2015-10-26 | 2016-06-21 | Disc brake and piston |
CN201680050140.7A CN107949717B (zh) | 2015-10-26 | 2016-06-21 | 盘式制动器及活塞 |
DE112016004881.5T DE112016004881T8 (de) | 2015-10-26 | 2016-06-21 | Scheibenbremse und Kolben |
JP2017547642A JP6496834B2 (ja) | 2015-10-26 | 2016-06-21 | ディスクブレーキおよびピストン |
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JP2015-210039 | 2015-10-26 | ||
JP2015210039 | 2015-10-26 |
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WO2017073110A1 true WO2017073110A1 (ja) | 2017-05-04 |
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PCT/JP2016/068315 WO2017073110A1 (ja) | 2015-10-26 | 2016-06-21 | ディスクブレーキおよびピストン |
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US (1) | US10591008B2 (ja) |
JP (1) | JP6496834B2 (ja) |
CN (1) | CN107949717B (ja) |
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DE102019209167B4 (de) * | 2019-06-25 | 2021-12-02 | Kennametal Inc. | Dichtkolben für eine hydraulische Dehnspannhalterung sowie Dehnspannhalterung |
DE102022204043A1 (de) | 2022-04-26 | 2023-10-26 | Hl Mando Corporation | Bremskolben für fahrzeugbremse mit einer vielzahl von bremsflüssigkeitsaufnahmeabschnitten |
Citations (1)
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JPH04219534A (ja) * | 1990-03-29 | 1992-08-10 | Bendix Europ Services Technic | ディスクブレーキ |
Family Cites Families (13)
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US2937722A (en) * | 1956-09-11 | 1960-05-24 | Bendix Aviat Corp | Disk brakes |
US3486593A (en) * | 1967-06-20 | 1969-12-30 | Dayton Steel Foundry Co | Hydraulic disk brake with anti-knock back feature |
US4203354A (en) * | 1976-12-20 | 1980-05-20 | The Bendix Corporation | Hydraulic piston with metallic O-ring groove and non-metallic slidable surfaces |
JPH0771519A (ja) * | 1993-09-03 | 1995-03-17 | Nichias Corp | 制振シム構造体 |
DE69525835T2 (de) * | 1994-10-28 | 2002-10-31 | Hino Jidosha K.K., Hino | Scheibenbremse |
DE19519832B4 (de) * | 1995-05-31 | 2004-04-22 | Robert Bosch Gmbh | Hydrospeicher |
US5664848A (en) * | 1996-05-21 | 1997-09-09 | Muraski; Richard E. | Apparatus for absorbing shocks in a vehicle braking system |
JPH10122280A (ja) | 1996-10-18 | 1998-05-12 | Hosei Brake Kogyo Kk | ディスクブレーキ用ピストン |
DE10016880A1 (de) * | 2000-04-05 | 2001-10-18 | Bayerische Motoren Werke Ag | Schwingungsdämpfer für eine hydraulische Fahrzeug-Bremsanlage |
KR20090059255A (ko) * | 2007-12-06 | 2009-06-11 | 현대자동차주식회사 | 파킹 일체형 캘리퍼의 파킹 풀림 방지 장치 |
CN101718317A (zh) * | 2009-12-28 | 2010-06-02 | 万向钱潮股份有限公司 | 一种用于盘式制动器降噪的复合阻尼层减振片 |
CN201568484U (zh) * | 2009-12-30 | 2010-09-01 | 三阳工业股份有限公司 | 煞车卡钳 |
JP6504646B2 (ja) | 2014-04-28 | 2019-04-24 | 昭和鉄工株式会社 | 貯湯槽内部構造 |
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- 2016-06-21 WO PCT/JP2016/068315 patent/WO2017073110A1/ja active Application Filing
- 2016-06-21 US US15/755,320 patent/US10591008B2/en active Active
- 2016-06-21 CN CN201680050140.7A patent/CN107949717B/zh active Active
- 2016-06-21 JP JP2017547642A patent/JP6496834B2/ja active Active
- 2016-06-21 DE DE112016004881.5T patent/DE112016004881T8/de active Active
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JPH04219534A (ja) * | 1990-03-29 | 1992-08-10 | Bendix Europ Services Technic | ディスクブレーキ |
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CN107949717A (zh) | 2018-04-20 |
US10591008B2 (en) | 2020-03-17 |
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DE112016004881T5 (de) | 2018-07-12 |
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