WO2015098780A1 - Dispositif de frein à disque - Google Patents

Dispositif de frein à disque Download PDF

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Publication number
WO2015098780A1
WO2015098780A1 PCT/JP2014/083805 JP2014083805W WO2015098780A1 WO 2015098780 A1 WO2015098780 A1 WO 2015098780A1 JP 2014083805 W JP2014083805 W JP 2014083805W WO 2015098780 A1 WO2015098780 A1 WO 2015098780A1
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WO
WIPO (PCT)
Prior art keywords
disc brake
piston
caliper
cylinder
brake device
Prior art date
Application number
PCT/JP2014/083805
Other languages
English (en)
Japanese (ja)
Inventor
雄一郎 井上
禎雄 戸塚
純一 野際
哲弥 野口
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
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
Publication of WO2015098780A1 publication Critical patent/WO2015098780A1/fr

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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
    • 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
    • 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
    • F16D55/228—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 separate actuating member for each side
    • 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
    • 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
    • F16D2123/00—Multiple operation forces

Definitions

  • This invention relates to a disc brake device.
  • the disc brake device is used as a brake device for service braking not only for the front wheels of the car but also for the rear wheels because of its excellent heat dissipation and the ability to finely adjust the braking force during driving. May be adopted.
  • a brake device for performing the parking brake is also provided separately from the disc brake device used for the service brake.
  • a drum brake device dedicated to a parking brake is disposed inside a disc brake device dedicated to a service brake (drum-in-hat structure),
  • a structure (a twin caliper structure) is employed in which a disc brake device dedicated to a parking brake is provided separately from a disc brake device dedicated to a service brake.
  • FIG. 32 is a schematic diagram of a conventional structure in which a disc brake device dedicated to service brakes and a disc brake device dedicated to parking brakes are separately provided.
  • an opposed piston type disc brake device 2 used for a service brake and a floating type disc brake device 3 used for a parking brake are provided around the rotor 1 rotating together with the wheels in a circumferentially separated state. It has been.
  • these two brake devices 2 and 3 are each supported and fixed to the knuckle 4 which comprises a suspension apparatus.
  • a caliper 5 constituting the opposed piston type disc brake device 2 is supported and fixed to a mounting portion (stay) 6a provided on the knuckle 4, and the floating disc brake device 3 is constituted.
  • a support 7 is supported and fixed to another mounting portion 6 b provided on the knuckle 4.
  • axial direction”, “radial direction”, and “circumferential direction” refer to “axial direction”, “radial direction”, and “circumferential direction”, respectively, related to the rotor.
  • the opposed piston type disc brake device 2 dedicated to the service brake and the floating type disc brake device 3 dedicated to the parking brake are provided separately. For this reason, when it sees as one brake device provided with two functions, a service brake and a parking brake, it is inevitable that the whole device will be increased in size and weight.
  • the knuckle 4 needs to be provided with mounting portions 6a and 6b for supporting and fixing the brake devices 2 and 3, respectively, the degree of freedom regarding the shape of the knuckle 4 is reduced.
  • the knuckle 4 must be provided with a mounting part for fixing the damper, a mounting part for fixing the lower arm, etc., and ensuring the degree of freedom regarding the shape of the knuckle It is important to secure the degree of freedom.
  • an object of the present invention is to reduce the size and weight of a brake device having two functions of a service brake and a parking brake and improve the degree of freedom of the knuckle shape. It is to provide a disc brake device that realizes a structure.
  • a disc brake device having the following configurations (1) to (7).
  • An outer body portion and an inner body portion that are provided with a rotor that rotates together with a wheel are connected to both outer circumferential portions of the outer body portion and the inner body portion at positions radially outward from the outer peripheral edge of the rotor.
  • a pair (two) or more first cylinders provided opposite to each other on the outer body portion and the inner body portion, and fixed to the knuckle over the rotor.
  • An opposed piston type caliper A pair of pads supported so as to be capable of displacement in the axial direction with respect to the opposed piston caliper in a state of being disposed on both sides of the rotor; A claw portion provided on the outer side, and a second cylinder provided on the inner side and opening toward the inner side surface of the claw portion, and a portion between the pair of connecting portions in the circumferential direction; A floating type caliper supported in such a manner as to be axially displaceable with respect to the opposed piston type caliper in a state straddling the pair of pads from the outside in the radial direction; In each of the first cylinder and the second cylinder, the same number of first pistons and one second piston as the first cylinders are fitted so as to be liquid-tight and capable of displacement in the axial direction.
  • the braking force by the service brake is that the pair of pads are pressed against both side surfaces of the rotor by the first pistons by the pressure oil being fed into the first cylinder and the second cylinder, respectively. Occurs when the pair of pads are pressed against both side surfaces of the rotor by the second piston and the inner side surface of the claw portion, The brake force generated by the parking brake is generated by the second piston and the inner side surface of the claw portion only when the pair of pads are pressed against both side surfaces of the rotor.
  • the disc brake device having the above configuration (1) has an opposing piston type disc brake mechanism in which the braking force by the service brake includes the opposing piston type caliper and the first pistons, and the floating type caliper. Whereas the braking force by the parking brake is obtained only by the floating disc brake mechanism, it is obtained by both the floating disc brake mechanism composed of the second piston.
  • the number of the second cylinder and the second piston can be two or more as required.
  • the disc brake device having the configuration of (1), wherein the second piston is displaced in the axial direction in the second cylinder using an electric motor as a drive source (for example, via a speed reducer).
  • a disc brake device provided with an electric pressing device, wherein the braking force generated by the parking brake is generated using the electric pressing device.
  • a disc brake device having any one of the constitutions (1) to (4), wherein one set of each first cylinder (two in total) is provided.
  • At least one of the pair of guide pins is supported so as to be capable of displacement in the axial direction with respect to the floating caliper, and one or both guide pins are supported with respect to the opposed piston type caliper. Displacement in the axial direction is supported in an impossible manner.
  • the function of the service brake and the parking brake can be exhibited by itself. Therefore, compared with the case where each dedicated device is provided, the disc brake device can be reduced in size and weight as a whole device, and the degree of freedom of the knuckle shape can be improved. That is, in the case of the present invention, the floating caliper constituting the floating disc brake mechanism is not supported by the dedicated support, but is opposed to the opposed piston caliper constituting the opposed piston disc brake mechanism. Thus, the opposed piston type disc brake mechanism and the floating type disc brake mechanism are integrated to form one disc brake device.
  • the floating caliper is disposed in a circumferential portion between a pair of connecting portions constituting the opposed piston caliper, so that the floating caliper is moved to the opposed piston.
  • the mold caliper is supported in a state of being superimposed (mounted) in the radial direction.
  • a structure in which two dedicated devices for the service brake and the parking brake are separated in the circumferential direction or a structure that is simply continuous in the circumferential direction.
  • the overall size of the apparatus can be reduced (especially for the structure continuous in the circumferential direction, the overall length in the circumferential direction can be shortened).
  • the support of the floating type disc brake can be omitted and the number of pistons can be reduced, so that the weight and cost of the apparatus can be reduced. Further, since only one mounting portion necessary for the knuckle is required to support and fix the opposed piston type caliper, the degree of freedom regarding the shape of the knuckle can be improved. Furthermore, since the opposed piston type disc brake mechanism and the floating type disc brake mechanism use a pair of pads in common, the number of pads can be reduced. From this aspect, the weight and cost can be reduced. .
  • the brake force of the service brake can be obtained only by the floating type disc brake device. In comparison, it is possible to improve the rise (response) of the braking force.
  • the braking force and the size of the device remain substantially the same, and one piston (and piston) It is possible to omit peripheral members such as seals.
  • FIG. 1 is a front view showing a disc brake device according to a first example of an embodiment of the present invention.
  • FIG. 2 is a rear view of the disc brake device shown in FIG.
  • FIG. 3 is a left side view of the disc brake device shown in FIG.
  • FIG. 4 is a right side view of the disc brake device shown in FIG.
  • FIG. 5 is a plan view of the disc brake device shown in FIG. 6 is a bottom view of the disc brake device shown in FIG.
  • FIG. 7 is a perspective view showing the disk brake device shown in FIG. 1 as viewed from the outside in the radial direction and from the outer side.
  • FIG. 8 is a perspective view showing the disc brake device shown in FIG. 1 as viewed from the radially outer side and the inner side.
  • FIG. 1 is a front view showing a disc brake device according to a first example of an embodiment of the present invention.
  • FIG. 2 is a rear view of the disc brake device shown in FIG.
  • FIG. 3 is a left side view
  • FIG. 9 is a perspective view showing the disc brake device shown in FIG. 1 with each piston omitted and viewed from the radially inner side and the outer side.
  • FIG. 10 is a sectional view taken along line XX in FIG. 11 is a cross-sectional view taken along line XI-XI in FIG.
  • FIG. 12 is a front view showing a disc brake device of a second example of the embodiment of the present invention. 13 is a rear view of the disc brake device shown in FIG. 14 is a left side view of the disc brake device shown in FIG. 15 is a right side view of the disc brake device shown in FIG.
  • FIG. 16 is a plan view of the disc brake device shown in FIG. 17 is a bottom view of the disc brake device shown in FIG. FIG.
  • FIG. 18 is a perspective view showing the disc brake device shown in FIG. 12 as viewed radially outward and from the outer side.
  • FIG. 19 is a perspective view showing the disk brake device shown in FIG. 12 as viewed from the radially outer side and the inner side.
  • FIG. 20 is a perspective view showing the disc brake device shown in FIG. 12 with each piston omitted and viewed from the radially inner side and the outer side.
  • FIG. 21 is a front view showing a disc brake device of a third example of the embodiment of the present invention.
  • 22 is a rear view of the disc brake device shown in FIG. 23 is a left side view of the disc brake device shown in FIG. 24 is a right side view of the disc brake device shown in FIG. 25 is a plan view of the disc brake device shown in FIG.
  • FIG. 25 is a bottom view of the disc brake device shown in FIG.
  • FIG. 27 is a perspective view showing the disk brake device shown in FIG. 21 as viewed from the outside in the radial direction and from the outer side.
  • FIG. 28 is a perspective view showing the disc brake device shown in FIG. 21 as viewed radially outward and from the inner side.
  • FIG. 29 is a perspective view showing the disc brake device shown in FIG. 21 with each piston omitted and viewed from the radially inner side and the outer side.
  • 30 is a cross-sectional view taken along the line XXX-XXX in FIG. 25 in which the inner pad in the disc brake device shown in FIG. 21 is omitted.
  • FIG. 31 is a cross-sectional view taken along the line XXXI-XXXI of FIG. 25 with the outer pad omitted from the disc brake device shown in FIG.
  • FIG. 32 is a schematic diagram showing a brake device having a conventional structure for exerting two functions of a service brake and a parking brake.
  • the disc brake device 8 of the first example of the present embodiment is a hybrid type having both functions of a service brake and a parking brake, and is an opposed piston type caliper 9, a floating type caliper 10, and a pair of pads 11a.
  • 11b outer pad 11a, inner pad 11b
  • first pistons 12a, 12b first outer piston 12a, first inner piston 12b
  • second piston 13 second piston 13
  • the opposed piston type caliper 9 is capable of moving the outer pad 11a and the inner pad 11b in the axial direction (front and back direction in FIGS. 1 and 2, the left and right direction in FIGS. 3 and 4, and the vertical direction in FIGS. 5 and 6).
  • Such an opposed piston type caliper 9 is formed by casting a light alloy such as an aluminum alloy (including die-cast molding) or the like, and has an outer body portion 14 provided with the rotor 1 (see FIG. 32) interposed therebetween, and Inner body portion 15, the outer body portion 14 and the inner body portion 15 on one side in the circumferential direction (the right side of FIGS. 1, 5, 6, the turning-in side when the vehicle moves forward) and the other end in the circumferential direction (FIG.
  • connecting portions 16 a and 16 b that connect the ends of the vehicle when the vehicle moves forward, respectively, and a cover portion 17 are provided.
  • the cover portion 17 is provided in a state of projecting from the connecting portion 16b on the outlet side (the other side in the circumferential direction) to the one side in the circumferential direction, and connects the outer body portion 14 and the inner body portion 15 to each other.
  • the delivery side half of the pair of pads 11a and 11b is covered from the radially outer side.
  • an opening 18 for arranging the floating caliper 10 is formed in a portion in the circumferential direction between the connection portion 16a on the turn-in side (one circumferential direction) and the cover portion 17.
  • a first outer cylinder 19a and a first inner cylinder 19b which are the first cylinders described in the claims, are respectively connected to the inner side of the other half in the circumferential direction of the outer body portion 14 and the inner body portion 15.
  • One (one set) is provided in each state facing each other.
  • a first outer piston 12a and a first inner piston 12b made of aluminum alloy, each of which is the first piston described in the claims, are oil-tight. And is fitted so as to be capable of displacement in the axial direction.
  • an introduction port 20a that communicates with the first outer cylinder 19a and the first inner cylinder 19b is provided.
  • a pair of guides projecting in the axial direction is provided at both circumferential ends of the outer body portion 14 and the inner body portion 15 facing each other (the inner side surface of the outer body portion 14 and the outer side surface of the inner body portion 15).
  • Wall portions 21a and 21b are respectively provided.
  • guide concave grooves 22a and 22b are formed in the radial direction intermediate portions on the side surfaces facing each other in the circumferential direction of the pair of guide wall portions 21a and 21b in a direction substantially perpendicular to the both side surfaces, respectively. Yes.
  • a storage groove 23 that is recessed in the axial direction is formed over the entire width in the radial direction at a portion closer to one end in the circumferential direction on the inner side surface of the outer body portion 14 (portion aligned with the opening 18 in the circumferential direction).
  • a relief recess 24 that is recessed radially inward is formed at the radially outer end portion of the inner body portion 15 near the one end in the circumferential direction (the portion that is aligned with the opening 18 in the circumferential direction).
  • Such an opposed piston type caliper 9 is supported and fixed to a mounting portion constituting the knuckle 4 (see FIG. 32) by a pair of mounting seats 25 a and 25 b provided on the inner body portion 15.
  • the opposed piston caliper 9 and the first pistons 12a and 12b fitted in the first cylinders 19a and 19b are opposed to each other.
  • a piston type disc brake mechanism is configured.
  • the pair of pads 11a and 11b are composed of a lining (friction material) 26 and a metal back plate (pressure plate) 27 that supports the back surface of the lining 26.
  • a pair of convex ears 28a and 28b projecting from both sides in the circumferential direction are provided at the radial intermediate portions of the side edges on both sides in the circumferential direction of the back plate 27. That is, of these ears 28a and 28b, the ear part 28a on the turn-in side is provided at the radial intermediate portion of the edge part on the turn-in side of the back plate 27 so as to protrude to the turn-in side.
  • the delivery-side ear portion 28b is provided in a radially intermediate portion of the delivery-side edge of the back plate 27 so as to protrude to the delivery side.
  • These ears 28a and 28b are loosely engaged with the guide grooves 22a and 22b, respectively.
  • the floating caliper 10 is made of an aluminum alloy or an iron alloy, and has a bifurcated claw portion 29 provided at the outer side end portion, a cylinder portion 30 provided at the inner side end portion, And a bridge portion 31 provided across the rotor 1 and the pads 11a and 11b.
  • the cylinder portion 30 is provided with one second cylinder 32 that opens toward the inner side surface of the claw portion 29.
  • the second cylinder 13 is fitted with the second piston 13 made of an aluminum alloy or an iron alloy so as to be oil-tight and capable of axial displacement.
  • An introduction port 20 b communicating with the second cylinder 32 is provided on the outer peripheral surface of the cylinder portion 30.
  • the diameter of the second cylinder 32 (second piston 13) is such that the first outer cylinder 19a and the first inner cylinder 19b (first outer piston 12a and first inner piston). The diameter is smaller than the diameter of the piston 12b).
  • a pair of arms 33a and 33b projecting in the circumferential direction are formed at the inner end of the floating caliper 10, respectively.
  • a heat radiating window portion 42 penetrating in the radial direction is formed in the circumferential center portion of the bridge portion 31.
  • the floating type caliper 10 and the second piston 13 fitted in the second cylinder 32 constitute a floating type disc brake mechanism.
  • the floating caliper 10 having the above-described configuration is configured such that the inner side surface of the claw portion 29 is placed on the circumferential half piece (the turn-in side half portion) of the outer pad 11a. ) With the front end surface of the second piston 13 facing the inner side surface of one half of the circumferential direction of the inner pad 11b (half of the turn-in side). Is supported so as to be capable of axial displacement.
  • the outer side end portion of the guide pin (reverse pin) 34a is arranged at one circumferential end portion of the inner body portion 15 constituting the opposed piston type caliper 9. It is fixed with screws.
  • An intermediate portion of the guide pin 34a that protrudes to the inner side of the inner body portion 15 serves as a sliding portion in a guide hole formed at the tip of the arm portion 33a that protrudes to one side in the circumferential direction. It is inserted loosely to allow displacement in the axial direction.
  • a portion between the inner body portion 15 and the arm portion 33a, and a bolt head portion 51 provided at an end portion on the inner side of the arm portion 33a and the guide pin 34a The periphery of the intermediate portion is covered with a dustproof boot 35a made of an elastic material.
  • a guide hole that is opened only on the inner side is formed in the axial direction at a portion near the other end in the circumferential direction of the inner body portion 15.
  • the inner side end portion (the portion adjacent to the outer side of the bolt head 51) of the guide pin (slide pin) 34b is screwed and fixed to the distal end portion of the arm portion 33b protruding to the other side in the circumferential direction.
  • the outer side portion of the guide pin 34b serves as a sliding portion, and is loosely inserted into the guide hole so as to allow displacement in the axial direction.
  • the periphery of the portion of the guide pin 34b between the inner body portion 15 and the tip of the arm portion 33b is covered with a dustproof boot 35b.
  • the guide pins 34a and 34b provided apart from each other in the circumferential direction are more circumferential than the guide pins 34a provided on one circumferential side.
  • the guide pin 34b provided on the other side is disposed radially outward. Accordingly, even in the case of both the arm portions 33a and 33b, the distal end portion of the arm portion 33b on the other circumferential side is disposed more radially outward than the distal end portion of the arm portion 33a on the one circumferential side. ing.
  • the floating caliper 10 is supported by the opposed piston caliper 9 so as to be capable of displacement in the axial direction. Then, in this state, the floating caliper 10 is disposed at a portion in the circumferential direction between the connecting portions 16 a and 16 b that constitute the opposed piston caliper 9. Specifically, the claw portion 29 is disposed inside the storage groove 23 and the bridge portion 31 straddles both the pads 11a and 11b from the outside in the radial direction. Placed in. Further, the radially inner half of the cylinder portion 30 is disposed inside the escape recess 24.
  • the disc brake device 8 of the first example of the present embodiment is provided with an electric pressing device 36 in a state assembled to the floating caliper 10.
  • the electric pressing device 36 includes an electric motor housed in a casing 37 attached to an inner side surface (inner side portion) of the cylinder portion 30, and constituent members in the casing 37 and the cylinder portion 30.
  • a reduction mechanism such as a gear-type reduction gear housed in the housing and a feed screw mechanism (ball screw mechanism) housed in the cylinder portion 30 for converting the rotational motion of the output shaft of the electric motor into a linear motion.
  • the linear movement member constituting the feed screw mechanism is displaced in the axial direction, so that the second piston 13 fitted to the second cylinder 32 is It can be displaced in the axial direction within the two cylinders 32. That is, in the case of the first example of the present embodiment, the second piston 13 is not only displaced in the axial direction based on the introduction of hydraulic pressure, but also mechanically using the electric pressing device 36. It can be displaced in the axial direction.
  • the floating disc brake mechanism can be operated in two ways, hydraulic and mechanical.
  • the electric pressing device for example, a structure described in Japanese Patent Application Laid-Open No. 2012-193805 or Japanese Patent Application Laid-Open No. 2011-202696 can be employed. Since the detailed structure of the electric pressing device is described in detail in these publications and the like, detailed description thereof is omitted here.
  • the pressure oil is introduced into both the inlet ports 20a and 20b of the opposed piston type caliper 9, respectively. Then, pressurized oil is fed into the first outer cylinder 19a, the first inner cylinder 19b, and the second cylinder 32, respectively.
  • the pair of pads 11a and 11b are pressed against both side surfaces of the rotor 1 by the first outer piston 12a and the first inner piston 12b.
  • the second piston 13 is displaced in a direction approaching the rotor 1.
  • the inner pad 11 b is pressed against the inner side surface of the rotor 1.
  • the floating caliper 10 As a reaction of the pressing, the floating caliper 10 is displaced toward the inner side with respect to the opposed piston caliper 9, and the outer pad 11 a is moved by the claw portion 29. And pressed against the outer side surface of the rotor 1. As a result, the rotor 1 is strongly pressed from both sides in the axial direction to perform braking.
  • the braking force by the service brake is obtained by both the opposed piston type disc brake mechanism and the floating type disc brake mechanism.
  • the electric motor constituting the electric pressing device 36 is energized (pressure oil is not introduced into the introduction ports 20a and 20b).
  • the second piston 13 is mechanically displaced in the axial direction in the second cylinder 32 by the linear movement member constituting the feed screw mechanism being displaced in the axial direction.
  • the inner pad 11 b is pressed against the inner side surface of the rotor 1
  • the outer pad 11 a is pressed against the outer side surface of the rotor 1 by the claw portion 29.
  • the rotor 1 is clamped from both sides by the outer pad 11a and the inner pad 11b, and braking is performed.
  • the braking force by the parking brake is obtained only by the floating disc brake mechanism.
  • each device is a dedicated device. Compared with the case of providing, the size and weight of the entire apparatus can be reduced, and the degree of freedom of the knuckle shape can be improved. That is, in the case of the first example of the present embodiment, the floating caliper 10 constituting the floating disc brake mechanism is not supported by a dedicated support, but constitutes an opposed piston type disc brake mechanism. By supporting the opposed piston type caliper 9, the opposed piston type disc brake mechanism and the floating type disc brake mechanism are integrated to constitute one disc brake device 8.
  • the floating caliper 10 is disposed in the circumferential portion between the connecting portion 16a and the cover portion 17, so that the floating caliper 10 is opposed piston type.
  • the caliper 9 is supported in a state of being superimposed (mounted) in the radial direction.
  • the opposed piston type disc brake device 2 when the opposed piston type disc brake device 2 is provided with four pistons and the floating type disc brake device 3 is provided with one piston, according to the structure of the first example of the present embodiment, two pistons (and peripheral members such as piston seals) can be omitted while maintaining the braking performance of the service brake and the parking brake. Further, according to the structure of the first example of the present embodiment, the mounting portion necessary for the knuckle 4 is only one for supporting and fixing the opposed piston type caliper 9, and thus the degree of freedom regarding the shape of the knuckle 4 is sufficient. Can be improved. Furthermore, since the pair of pads 11a and 11b are used in common by the opposed piston type disc brake mechanism and the floating type disc brake mechanism, the number of pads is reduced (compared to the structure of FIG. This also makes it possible to reduce weight and cost.
  • the braking force by the service brake is obtained by operating both the opposed piston type disc brake mechanism and the floating type disc brake mechanism, the braking force of the service brake can be obtained only by the floating type disc brake device. In comparison, it is possible to improve the rise (response) of the braking force.
  • the braking force and the size of the device remain substantially the same, and one piston (and piston) It is possible to omit peripheral members such as seals.
  • the diameter of the second piston 13 made of an alloy or iron-based alloy is reduced. This is advantageous in reducing the weight.
  • the surface pressure can be easily made uniform, it is possible to effectively prevent so-called uneven wear in which the wear amount on the entry side of each of the pads 11a and 11b is larger than the wear amount on the delivery side.
  • a pair of guide pins 38a, 38b is provided in a state of being bridged in the axial direction between the outer body portion 14a and the inner body portion 15a constituting the opposed piston type caliper 9a. Is supported.
  • the outer body portion 14a and the inner body portion 15a have a radially outer end portion closer to one circumferential end than the connecting portion 16a on one circumferential side.
  • each of the extending side support portions 40a and 40b is formed in a state of projecting to one side in the circumferential direction.
  • both the axial direction both ends of the guide pin 38a of the circumferential direction one side of the said guide pins 38a and 38b are couple
  • Both end portions in the axial direction of the guide pin 38b are coupled and fixed to the both outlet side support portions 40a and 40b.
  • arm portions 41a and 41b projecting in the circumferential direction are provided at both ends in the circumferential direction of the bridge portion 31a constituting the floating caliper 10a.
  • the axial direction intermediate part of each said guide pin 38a, 38b becomes a sliding part inside the guide hole formed in the state which penetrates the front-end
  • the floating caliper 10a is disposed between the outer body portion 14a and the inner body portion 15a of the guide pins 38a and 38b. Axial displacement is supported. Further, in the case of the second example of the present embodiment, a larger heat radiating window portion 42a is formed in the circumferential central portion of the bridge portion 31a than in the case of the first example of the embodiment.
  • the number of members that protrude from the inner side of the disc brake device 8a is less than that in the case of the first example of the above embodiment. it can. For this reason, compared with the structure of the 1st example of the said embodiment, it becomes advantageous when aiming at the shortening of the dimension regarding an axial direction. Further, since the large window portion 42a is formed in the bridge portion 31a, heat from the rotor 1 can be efficiently released to the outside in the radial direction, and it is advantageous in reducing the weight. About another structure and an effect, it is the same as that of the case of the 1st example of the said embodiment.
  • a third example of the embodiment of the present invention will be described with reference to FIGS.
  • a feature of the third example of the present embodiment is that two opposed first cylinders 43a, 43b, 44a, 44b (turn-in side first outer cylinders) are opposed to the opposed piston type caliper 9b constituting the disc brake device 8b.
  • 43a, a first inlet inner cylinder 43b, a first outlet cylinder 44a, and a first outlet inner cylinder 44b) are provided, and the floating caliper 10b (floating type disc brake mechanism) is arranged accordingly.
  • the floating caliper 10b floating type disc brake mechanism
  • the turn-in side first outer cylinder 43a and the rotation are provided on the inner side of one end portion in the circumferential direction of the outer body part 14b and the inner body part 15b constituting the opposed piston type caliper 9b.
  • the turn-in side first outer cylinder 43a and the turn-out side first outer cylinder 44a are formed in the outer body part 14b so as to be separated from each other in the circumferential direction, and the inner body part.
  • the turn-in side first inner cylinder 43b and the turn-out side first inner cylinder 44b are formed in a state of being separated in the circumferential direction. Then, in each of the turn-in side first outer cylinder 43a, the turn-in side first inner cylinder 43b, the turn-out side first outer cylinder 44a, and the turn-out side first inner cylinder 44b, a turn-in side first outer piston is provided. 45a, the turn-in side first inner piston 45b, the turn-out side first outer piston 46a, and the turn-out side first inner piston 46b are fitted in an oil-tight manner and capable of displacement in the axial direction.
  • the facing piston type caliper 9b is not provided with the cover portion 17 which the structures of the first example and the second example of the embodiment had. .
  • an opening 18a that is long in the circumferential direction is formed between the coupling portion 16a on one circumferential side and the coupling portion 16b on the other circumferential side.
  • a storage groove 23a that is recessed in the axial direction is formed over the entire width in the radial direction in the circumferential intermediate portion (the portion that is aligned with the opening 18a in the circumferential direction) on the inner side surface of the outer body portion 14b.
  • the radially inner end of the inner body portion 15b in the middle in the circumferential direction avoids the turn-in side first inner cylinder 43b and the turn-out side first inner cylinder 44b.
  • a relief recess 24a that is recessed in the direction is formed.
  • the floating caliper 10b is arranged at the center position in the circumferential direction between the pair of connecting portions 16a and 16b (opening 18a) constituting the opposed piston caliper 9b having the above-described configuration.
  • the opposed piston caliper 9b is supported so as to be capable of displacement in the axial direction.
  • the outer side end portions of a pair of guide pins (reverse pins) 48a and 48b are fixed to the inner body portion 15b near both ends in the circumferential direction with screws. Has been.
  • the guide holes formed at the respective tip portions of 47a and 47b are loosely inserted so as to allow displacement in the axial direction. Further, the periphery of both guide pins 48a and 48b is covered with dustproof boots 49a and 49b made of an elastic material, respectively.
  • the floating caliper 10b is provided at the outer side end of the floating caliper 10b in a state where the floating caliper 10b is supported so as to be capable of displacement in the axial direction with respect to the opposed piston caliper 9b.
  • the claw portion 29a is disposed inside the housing concave groove 23a and at a portion in the circumferential direction between the turn-in side first outer piston 45a and the turn-out side first outer piston 46a. For this reason, in the case of the third example of the present embodiment, as shown in FIG. 31, on the both sides in the circumferential direction of the claw portion 29a, the turn-in side first outer piston 45a and the turn-out side second Notches 50 and 50 are formed so as not to contact the outer piston 46a.
  • the radially inner half of the cylinder portion 30a provided at the inner side end of the floating caliper 10b is disposed inside the escape recess 24a. Accordingly, when the floating caliper 10b is supported with respect to the opposed piston caliper 9b, when the portion arranged on the inner side is viewed from the rotor 1 side, as shown in FIG.
  • the second piston 13 fitted in the second cylinder 32 of the floating caliper 10b is disposed in the circumferential direction between the first inner piston 45b and the delivery-side first inner piston 46b.
  • the portion arranged on the outer side is viewed from the rotor 1 side, as shown in FIG.
  • the claw portion 29a is disposed in the intermediate portion in a state where both ends in the circumferential direction are radially overlapped with the turn-in side and turn-out side first outer pistons 45a, 46a.
  • the outer and inner turn-in side first cylinders 43a and 43b and the outer and inner Pressure oil is fed into the delivery-side first cylinders 44a and 44b and the second cylinder 32, respectively. Accordingly, the pads 11a and 11b are pressed against both side surfaces of the rotor 1 by the outer and inner return side first pistons 45a and 45b and the outer and inner return side first pistons 46a and 46b. At the same time (substantially simultaneously), the second piston 13 is displaced in a direction approaching the rotor 1.
  • the inner pad 11b is pressed against the inner side surface of the rotor 1, and as a reaction of the pressing, the floating caliper 10b is displaced toward the inner side with respect to the opposed piston caliper 9b, and the claw portion 29a
  • the outer pad 11 a is pressed against the outer side surface of the rotor 1.
  • the rotor 1 is strongly pressed from both sides in the axial direction to perform braking.
  • the second piston 13 is moved in the second cylinder 32 by using the electric pressing device 36 as in the case of the first example of the embodiment. Mechanically displaced in the axial direction.
  • the inner pad 11b is pressed against the inner side surface of the rotor 1
  • the outer pad 11a is pressed against the outer side surface of the rotor 1 by the claw portion 29a.
  • the rotor 1 is sandwiched from both sides by the outer pad 11a and the inner pad 11b, and braking is performed.
  • the pair of pads 11a, the counter piston disc brake mechanism constituted by the counter piston caliper 9b is used.
  • the portions near both ends in the circumferential direction of 11b can be pressed simultaneously.
  • the opposed piston type disc brake mechanism is configured before the second piston 13 and the claw portion 29a constituting the floating disc brake mechanism press the pair of pads 11a and 11b. Since each of the first pistons 45a, 45b, 46a, 46b starts to press the pair of pads 11a, 11b, it is advantageous to smoothly displace the pair of pads 11a, 11b in the axial direction. Become. For example, when the structure shown in FIG.
  • first cylinders a first outer cylinder 19a, a first inner cylinder 19b
  • a counter-piston caliper fixed to a knuckle (4) in a state of straddling the rotor (1).
  • (9) and A pair of pads (an outer pad 11a and an inner pad 11b) supported so as to be capable of displacement in the axial direction with respect to the opposed piston type caliper (9) in a state of being disposed on both sides of the rotor (1);
  • the counter piston caliper (9) is disposed between the pair of connecting portions (16a, 16b) and straddles the pair of pads (outer pad 11a, inner pad 11b) from the outside in the radial direction.
  • the braking force by the service brake is obtained by feeding the pressure oil into the first cylinders (first outer cylinder 19a, first inner cylinder 19b) and the second cylinder (32), respectively.
  • the pair of pads (outer pad 11a, inner pad 11b) are pressed against both side surfaces of the rotor (1) by the first outer piston 12a and the first inner piston 12b), and the second piston (13) and the claw
  • the pair of pads (outer pad 11a, inner pad 11b) are pressed against both side surfaces of the rotor (1) with the inner side surface of the portion (29),
  • the braking force by the parking brake is such that the pair of pads (outer pad 11a, inner pad 11b) are applied to both side surfaces of the rotor (1) between the second piston (13) and the inner side surface of the claw portion (29). It is generated only by being pressed, Disc brake device (8).
  • An electric pressing device (36) for displacing the second piston (13) in the axial direction in the second cylinder (32) using an electric motor as a drive source is provided, and the parking brake The disc brake device (8) described in [1] above, wherein the braking force generated by is generated using the electric pressing device (36).
  • the second cylinder (32) is more in the circumferential direction than at least one of the first cylinders (first outer cylinder 19a and first inner cylinder 19b) provided in the inner body portion (15).
  • the disc brake device (8) according to any one of the above [1] to [3], which is disposed on the turn-in side of the rotor (1). [5] The disc brake device (8) according to any one of claims 1 to 4, wherein one set of each of the first cylinders (the first outer cylinder 19a and the first inner cylinder 19b) is provided. . [6] A pair of guide pins (34a, 34a) supported by the floating caliper (10) in a state of being circumferentially separated from the inner body part (15) constituting the opposed piston caliper (9).
  • the disc brake device (8) according to any one of the above.
  • the floating caliper (10a) is axially bridged between the outer body part (14a) and the inner body part (15a) constituting the opposed piston caliper (9a), and A pair of guide pins (38a, 38b) supported in a circumferentially separated state is supported between the outer body portion (14a) and the inner body portion (15a) so as to be capable of displacement in the axial direction.
  • the disc brake device (8a) according to any one of claims 1 to 5.
  • the disc brake device of the present invention is not limited to the above-described embodiment, and can be appropriately modified and improved.
  • 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 December 26, 2013 (Japanese Patent Application No. 2013-269038), the contents of which are incorporated herein by reference.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Abstract

　Selon l'invention, un étrier (10) de frein de type flottant est maintenu de façon à pouvoir de déplacer en direction axiale lorsque cet étrier de frein est superposé en direction radiale par rapport à un étrier (9) de frein de type à pistons opposés. Une paire de patins est supportée sur l'étrier (9) de frein de type à pistons opposés de manière à pouvoir être déplacée en direction axiale, les deux patins étant partagés par un frein de service et un frein de stationnement. La force de freinage du frein de service est générée par de l'huile sous pression introduite à la fois dans un premier cylindre de l'étrier (9) de frein de type à pistons opposés et dans un deuxième cylindre de l'étrier (10) de frein de type flottant, et la force de freinage du frein de stationnement est générée par un deuxième piston monté dans le deuxième cylindre, lequel est déplacé en direction axiale par un dispositif de pression électrique.
PCT/JP2014/083805 2013-12-26 2014-12-19 Dispositif de frein à disque WO2015098780A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013-269038 2013-12-26
JP2013269038A JP2015124811A (ja) 2013-12-26 2013-12-26 ディスクブレーキ装置

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WO2017032988A1 (fr) * 2015-08-21 2017-03-02 Liberty Vehicle Technologies Limited Étriers de frein
EP3287657A1 (fr) * 2016-08-26 2018-02-28 Akebono Brake Industry Co., Ltd. Système de frein à disque
WO2019015715A1 (fr) * 2017-07-19 2019-01-24 Lucas Automotive Gmbh Frein à disque, système de freinage à disque et système de frein de stationnement
DE102018102511A1 (de) * 2018-02-05 2019-08-08 Lucas Automotive Gmbh Scheibenbremse mit Schwimmsattel und Festsattel
IT201800006577A1 (it) * 2018-06-22 2019-12-22 Corpo pinza di freno a disco
CN110608246A (zh) * 2018-06-14 2019-12-24 曙制动器工业株式会社 对置活塞型盘式制动装置
US11125288B2 (en) 2018-08-21 2021-09-21 Akebono Brake Industry Co., Ltd Disc brake system
CN113623342A (zh) * 2020-05-08 2021-11-09 曙制动器工业株式会社 带驻车制动功能的对置式制动钳
CN114110056A (zh) * 2021-11-30 2022-03-01 浙江吉利控股集团有限公司 制动卡钳、后桥总成和车辆
CN114658775A (zh) * 2022-01-28 2022-06-24 浙江亚太机电股份有限公司 集成电子驻车功能的液压双活塞浮动制动钳
US11655867B2 (en) 2018-08-21 2023-05-23 Akebono Brake Industry Co., Ltd Disc brake system

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JP6719916B2 (ja) * 2016-02-09 2020-07-08 Ntn株式会社 電動ブレーキ装置および電動ブレーキ装置の製造方法
DE102018210236A1 (de) * 2018-06-22 2019-12-24 Robert Bosch Gmbh Radbremsvorrichtung
JP7170573B2 (ja) * 2019-03-26 2022-11-14 曙ブレーキ工業株式会社 フローティング型ディスクブレーキ

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Cited By (21)

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Publication number Priority date Publication date Assignee Title
WO2017032988A1 (fr) * 2015-08-21 2017-03-02 Liberty Vehicle Technologies Limited Étriers de frein
CN108368896A (zh) * 2015-08-21 2018-08-03 自由车辆技术有限公司 制动卡钳
CN108368896B (zh) * 2015-08-21 2020-06-26 自由车辆技术有限公司 制动卡钳
US10544843B2 (en) 2015-08-21 2020-01-28 Liberty Vehicle Technologies Limited Brake calipers
EP3287657A1 (fr) * 2016-08-26 2018-02-28 Akebono Brake Industry Co., Ltd. Système de frein à disque
US9989115B2 (en) 2016-08-26 2018-06-05 Akebono Brake Industry Co., Ltd Disc brake system
WO2019015715A1 (fr) * 2017-07-19 2019-01-24 Lucas Automotive Gmbh Frein à disque, système de freinage à disque et système de frein de stationnement
DE102017116323A1 (de) * 2017-07-19 2019-01-24 Lucas Automotive Gmbh Scheibenbremse, Scheibenbremsanlage und Feststellbremsanlage
US11536331B2 (en) 2017-07-19 2022-12-27 Zf Active Safety Gmbh Disc brake, disc brake system, and parking brake system
DE102018102511A1 (de) * 2018-02-05 2019-08-08 Lucas Automotive Gmbh Scheibenbremse mit Schwimmsattel und Festsattel
EP3591250A1 (fr) * 2018-06-14 2020-01-08 Akebono Brake Industry Co., Ltd. Dispositif de frein à disque de type à pistons opposés
CN110608246A (zh) * 2018-06-14 2019-12-24 曙制动器工业株式会社 对置活塞型盘式制动装置
US10914350B2 (en) 2018-06-14 2021-02-09 Akebono Brake Industry Co., Ltd. Opposed-piston type disc brake device
WO2019243912A1 (fr) * 2018-06-22 2019-12-26 Freni Brembo S.P.A. Corps d'étrier de frein à disque
IT201800006577A1 (it) * 2018-06-22 2019-12-22 Corpo pinza di freno a disco
US11904822B2 (en) 2018-06-22 2024-02-20 Brembo S.P.A. Disc brake caliper body
US11125288B2 (en) 2018-08-21 2021-09-21 Akebono Brake Industry Co., Ltd Disc brake system
US11655867B2 (en) 2018-08-21 2023-05-23 Akebono Brake Industry Co., Ltd Disc brake system
CN113623342A (zh) * 2020-05-08 2021-11-09 曙制动器工业株式会社 带驻车制动功能的对置式制动钳
CN114110056A (zh) * 2021-11-30 2022-03-01 浙江吉利控股集团有限公司 制动卡钳、后桥总成和车辆
CN114658775A (zh) * 2022-01-28 2022-06-24 浙江亚太机电股份有限公司 集成电子驻车功能的液压双活塞浮动制动钳

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