WO2017090737A1 - Dispositif de freinage - Google Patents

Dispositif de freinage Download PDF

Info

Publication number
WO2017090737A1
WO2017090737A1 PCT/JP2016/084996 JP2016084996W WO2017090737A1 WO 2017090737 A1 WO2017090737 A1 WO 2017090737A1 JP 2016084996 W JP2016084996 W JP 2016084996W WO 2017090737 A1 WO2017090737 A1 WO 2017090737A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake
lever
eccentric
brake device
rotates
Prior art date
Application number
PCT/JP2016/084996
Other languages
English (en)
Japanese (ja)
Inventor
鈴木　努
Original Assignee
Ｋｙｂ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 Ｋｙｂ株式会社 filed Critical Ｋｙｂ株式会社
Publication of WO2017090737A1 publication Critical patent/WO2017090737A1/fr

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61H—BRAKES OR OTHER RETARDING DEVICES SPECIALLY ADAPTED FOR RAIL VEHICLES; ARRANGEMENT OR DISPOSITION THEREOF IN RAIL VEHICLES
    • B61H5/00—Applications or arrangements of brakes with substantially radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes

Definitions

  • the present invention relates to a brake device.
  • the force of an actuator is applied to the force point of a pair of link arms that can rotate around a fulcrum, and the brake lining supported by the point of action of the link arm is brought into sliding contact with the brake disc to brake the rotation of the wheel.
  • a brake device is used.
  • JP10-505038A one end of a caliper lever is connected to each other, and the other end is pivotally attached to each brake pad.
  • An eccentric transmission device provided at a fulcrum between both ends of the caliper lever includes a caliper lever.
  • a brake caliper unit that pivots is disclosed.
  • the eccentric body transmission device has an eccentric pin that rotates in response to a force generated by a brake force generator, and rotates the caliper lever around one end by the rotation of the eccentric pin.
  • This invention aims at improving the mechanical efficiency of a brake device.
  • a support portion is rotatably supported and provided on both sides of the brake disc, the one end portions are connected by a connecting member, and the other end portions are slidably contacted with the brake disc and rubbed.
  • a pair of link arms that support a brake lining that applies force; an actuator that is provided on the connecting member to move the output member forward and backward; and a lever that is pivotally connected to the output member and that is rotated by the forward and backward movement of the output member.
  • An eccentric cam and the eccentric cam has a rotating portion connected to the lever and rotating around the rotating shaft, and a center axis at a position offset from the rotating shaft.
  • An eccentric portion that is pivotably connected to one end portion and pivots in an arc shape around the rotation axis by the rotation of the lever.
  • FIG. 1 is a plan view of a brake device according to an embodiment of the present invention.
  • FIG. 2 is a cross-sectional view of the periphery of the connecting member in the brake device.
  • FIG. 3 is a diagram for explaining the positional relationship between the lever and the adjuster in the height direction.
  • the brake device 100 is mainly applied to a railway vehicle.
  • the brake device 100 brakes the wheel 1 by sandwiching a brake disc 1 a that rotates together with the wheel 1. Specifically, as shown in FIG. 1, the brake device 100 sandwiches the brake disc 1 a from both sides with a pair of brake linings 2, and the friction force between the brake disc 1 a and the brake lining 2 causes the wheels 1 to move. Brakes rotation.
  • the brake disc 1a is formed on both front and back surfaces of the wheel 1 and rotates integrally with the wheel 1. Instead of the structure in which the brake disk 1a is formed integrally with the wheel 1, a separate brake disk 1a that rotates together with the wheel 1 may be provided.
  • the brake lining 2 is opposed to the brake disk 1a with a predetermined interval (state shown in FIG. 1) when not braking. During braking, the brake lining 2 moves toward the brake disc 1a and is pressed against the brake disc 1a in parallel.
  • the brake lining 2 includes a back plate portion 2a supported by the lining holding portion 3 of the brake device 100, and a friction member 2b that contacts the brake disc 1a during braking.
  • the friction member 2b includes a plurality of segments and is fixed to the surface of the back plate portion 2a. The brake lining 2 brakes the rotation of the wheel 1 by the frictional force generated by the contact between the friction member 2b and the brake disc 1a.
  • the lining holding part 3 has a dovetail groove (not shown) into which the back plate part 2a of the brake lining 2 is inserted.
  • Anchor blocks 4 that are fixed to the lining holder 3 by a pair of anchor bolts 5 are respectively provided at the upper and lower ends of the lining holder 3.
  • the anchor block 4 fixes the end of the back plate portion 2a of the brake lining 2 in the longitudinal direction (the direction perpendicular to the paper surface in FIG. 1). Thereby, the brake lining 2 inserted in the dovetail is held by the lining holding part 3.
  • the brake device 100 includes a pair of link arms on which a brake body 10 and a support portion 32 between one end portion 31 and the other end portion 33 are rotatably supported with respect to the brake body 10.
  • a connecting member 35 that connects the end portions 31 of the link arm 30
  • an actuator 20 that is provided on the connecting member 35 and advances and retracts the rod 21 as an output member, and the rod 21 that is rotatably connected to the rod 21.
  • the link arm is provided on at least one of the lever 40 rotated by the advancement and retraction of the lever 40 and the one end 31 of the pair of link arms 30, and the force transmitted by the rotation of the lever 40 is boosted to support the support 32 as a fulcrum.
  • a constant clearance is maintained between the booster unit 50 that rotates 30 and the brake disc 1a when wear of the brake lining 2 progresses. It includes a Justa 60, a.
  • the brake body 10 is supported by a carriage (not shown) when the brake device 100 is applied to a railway vehicle.
  • the brake body 10 is supported by a vehicle body (not shown) when the brake device 100 is applied to a vehicle other than a railway vehicle.
  • the actuator 20 is a fluid pressure actuator that is actuated by the pressure of the working fluid such as hydraulic pressure such as hydraulic pressure or air pressure.
  • Actuator 20 operates based on a driver's braking operation, and moves rod 21 forward and backward.
  • the actuator 20 may be other types such as a mechanical actuator that operates by rotation of an electric motor.
  • the actuator 20 includes a diaphragm 22 as an elastic film that elastically deforms due to the pressure of the working fluid and moves the rod 21 back and forth, and a return spring 23 that biases the rod 21 against the pressure of the working fluid.
  • the diaphragm 22 is sandwiched between the case 20a and the cover 20b, and defines a pressure chamber (not shown) between the cover 20b.
  • the diaphragm 22 is deformed when the working fluid is supplied to and discharged from the pressure chamber.
  • the rod 21 advances and retreats with the deformation of the diaphragm 22. Specifically, when the working fluid is supplied to the pressure chamber, the rod 21 retreats in the direction in which the brake device 100 enters a braking state, and when the working fluid is discharged from the pressure chamber, the rod device 100 Enter in the direction of the non-braking state.
  • the rod 21 has a flat portion 21 a that is in surface contact with the diaphragm 22.
  • the rod 21 advances and retreats with respect to the brake body 10 and can swing in the direction in which the brake lining 2 can move (left and right in FIG. 1).
  • the center of the brake disc 1a is located on the extension line of the central axis along which the rod 21 reciprocates.
  • the return spring 23 pushes the rod 21 back in the direction in which the brake device 100 is in a non-braking state.
  • the rod 21 is pushed out in the direction in which the brake device 100 enters the braking state.
  • the link arms 30 are respectively provided facing both surfaces of the brake disc 1a.
  • One end portions 31 of the pair of link arms 30 are connected by a connecting member 35.
  • the other end portion 33 of the link arm 30 supports the brake lining 2 slidably in contact with the brake disc 1a to apply a frictional force so as to be swingable.
  • the link arm 30 has a pair of arm portions 30a provided at the top and bottom.
  • one end 31 of one link arm 30 is provided with a connecting shaft 31 a that penetrates and connects the connecting member 35 and the link arm 30.
  • One end 31 of the other link arm 30 is connected through the connecting member 35, the link arm 30, and the pair of levers 40 so as to boost the force generated by the advancement and retraction of the rod 21 of the actuator 20. Is provided.
  • a booster unit 50 may be provided at one end 31 of one link arm 30 and one end 31 of the other link arm 30. In that case, each booster unit 50 can rotate one link arm 30 and the other link arm 30, respectively.
  • the booster unit 50 will be described later in detail.
  • the support portion 32 of the link arm 30 is provided with an arm shaft 32 a that penetrates and connects the link arm 30 and the brake body 10.
  • the link arm 30 is rotatably supported by the brake body 10 by an arm shaft 32a.
  • a circumferential tangential force acting on the brake lining 2 from the brake disc 1a during braking of the brake device 100 acts on the brake body 10 from the support portion 32 via the arm shaft 32a.
  • the other end portion 33 of the link arm 30 is provided with a lining shaft 33 a that penetrates and connects the link arm 30 and the lining holding portion 3.
  • the lining holding part 3 is rotatably supported by the link arm 30 by the lining shaft 33a.
  • the lever 40 transmits the force generated by the forward / backward movement of the rod 21 of the actuator 20 to the booster unit 50.
  • One end 41 of the lever 40 is rotatably connected to the rod 21.
  • the other end portion 42 of the lever 40 is connected to a large-diameter portion 52 as a rotating portion described later of the boosting unit 50.
  • the lever 40 rotates between the rod 21 and the large diameter portion 52 when the rod 21 advances and retreats with respect to the brake body 10.
  • the booster unit 50 has an eccentric cam 51 that rotates about the rotation axis A ⁇ b> 1 by the rotation of the lever 40.
  • the eccentric cam 51 has a large-diameter portion 52 that is connected to the lever 40 and rotates about the rotation axis A 1, and a central axis A 2 that is offset from the rotation axis A 1.
  • the eccentric cam 51 has a smaller diameter than the large-diameter portion 52.
  • an eccentric portion 53 that is rotatably connected to the one end portion 31 of the link arm 30.
  • the center axis A2 of the eccentric cam 51 is provided such that the position with respect to the link arm 30 is the same position as the center axis of the connecting shaft 31a.
  • the central axis of the large diameter portion 52 is the rotation axis A1 of the eccentric cam 51.
  • the other end portion 42 of the lever 40 is connected to the large diameter portion 52 so as not to be relatively rotatable. Therefore, when the rod 21 moves back and forth and the lever 40 rotates, the large diameter portion 52 rotates around the rotation axis A1.
  • the eccentric portions 53 are provided on both sides of the large diameter portion 52 in the axial direction. That is, the large diameter portion 52 is provided between the pair of eccentric portions 53.
  • the eccentric portion 53 rotates in an arc shape around the rotation axis A1 with the distance between the rotation axis A1 and the center axis A2 as a radius.
  • the eccentric cam 51 has a large-diameter portion 52 in the center in the axial direction, and has eccentric portions 53 having a smaller diameter than the large-diameter portion 52 at both ends thereof. Therefore, since the eccentric cam 51 has a small diameter from the center toward both ends, it is easy to process and assemble.
  • the adjuster 60 includes a sleeve 61 that is rotatably provided around the central axis in the case 20a, and a rod 62 that is inserted into the sleeve 61.
  • the rod 62 has a threaded portion 62 a that is threadedly engaged with the sleeve 61.
  • the sleeve 61 rotates through a link (not shown). As a result, the rod 62 moves out of the sleeve 61 by a size corresponding to the amount of wear of the brake lining 2. Thereby, the adjuster 60 always maintains the clearance between the brake disc 1a and the brake lining 2 at a constant size.
  • the adjuster 60 is provided as a single assembly together with the actuator 20 and the booster unit 50, so that the degree of freedom in design is high. Further, the adjuster 60 is provided so as to be shifted outside the movable range of the lever 40. Therefore, as shown in FIG. 3, the adjuster 60 and the lever 40 can be provided at the same height. Therefore, since it is not necessary to design the lever 40 to avoid other members, the booster unit 50 can be operated by the single lever 40.
  • the brake device 100 changes from the non-braking state (the state shown in FIG. 1) to the braking state.
  • the large-diameter portion 52 rotates around the rotation axis A1 by the force transmitted through the lever 40, and the eccentric portion 53 rotates in an arc shape around the rotation axis A1. It rotates in the counterclockwise direction in FIG. Thereby, since the eccentric part 53 rotates in the direction away from the rod 21, the one end parts 31 of a pair of link arms 30 move in the direction away from each other.
  • the link arm 30 is rotatably supported by the brake body 10 by the support portion 32, when the one end portion 31 moves in a direction away from each other, the other end portion 33 moves in a direction close to each other. Therefore, the brake lining 2 moves toward the brake disc 1a and is pressed in contact with the brake disc 1a in parallel, so that the rotation of the wheel 1 is braked.
  • the eccentric cam 51 is moved from the rod 21 to the lever 21 by the lever ratio between the length L3 of the lever 40 and the distance L4 between the rotation axis A1 and the center axis A2 of the eccentric portion 53.
  • the force transmitted through 40 is doubled by L3 / L4 and transmitted to the link arm 30. Therefore, a large braking force can be obtained without providing a large actuator. Therefore, the brake device 100 can be reduced in size and weight.
  • the link arm 30 is supported such that the support portion 32 between the one end portion 31 and the other end portion 33 is rotatable with respect to the brake body 10.
  • An eccentric cam 51 that rotates the link arm 30 by boosting the force transmitted to the rod 21 by the rotation of the lever 40 is provided at one end 31 of the link arm 30. Therefore, the circumferential tangential force that acts on the brake lining 2 from the brake disc 1 a during braking of the brake device 100 acts on the arm shaft 32 a of the support portion 32 and does not act on the eccentric cam 51. Therefore, since the frictional resistance when the eccentric cam 51 rotates does not increase, the mechanical efficiency during braking of the brake device 100 can be improved.
  • the force transmitted from the eccentric cam 51 to the one end portion 31 of the link arm 30 is the distance L1 between the one end portion 31 and the support portion 32, and the support portion 32 and the other end portion 33. It is boosted to L1 / L2 times by the lever ratio with the distance L2 between them.
  • the force that presses the brake lining 2 against the brake disc 1a is the force transmitted from the eccentric cam 51 to the one end 31 of the link arm 30. It is the same level of power.
  • the force transmitted from the rod 21 of the actuator 20 via the lever 40 by the eccentric cam 51 is boosted at a large magnification. Therefore, even if the link arm 30 is shortened to reduce the distance L1 in order to reduce the size and weight of the brake device 100, a sufficiently large braking force can be obtained.
  • the eccentric cam 51 is provided at the one end 31 of the link arm 30, so that the design freedom of the position of the arm shaft 32 a of the support portion 32 is increased. Therefore, it is possible to arrange the arm shaft 32 a at a position facing the side surface of the wheel 1. Therefore, the distance L1 can be made larger than the distance L2, and the force boosted by the eccentric cam 51 can be further boosted to press the brake lining 2 against the brake disc 1a.
  • Brake device 100 changes from a braking state to a non-braking state (the state shown in FIG. 1) when actuator 20 operates in a direction opposite to that during braking based on a driver's braking release operation.
  • the eccentric cam 51 rotates in the other direction (clockwise in FIG. 1) when the eccentric portion 53 rotates in an arc shape around the rotation axis A1 by the force transmitted through the lever 40.
  • the one end part 31 of a pair of link arm 30 moves to the direction which adjoins mutually.
  • the other end portions 33 of the pair of link arms 30 move in directions away from each other.
  • the brake lining 2 is separated from the brake disc 1a, and the braking of the wheel 1 is released.
  • the adjuster 60 functions and the rod 62 retracts from the sleeve 61. Thereby, the clearance between the brake disc 1a and the brake lining 2 is always maintained at a constant size.
  • the link arm 30 is supported such that a support portion 32 between one end portion 31 and the other end portion 33 is rotatable with respect to the brake body 10.
  • An eccentric cam 51 that rotates the link arm 30 by boosting the force transmitted to the rod 21 by the rotation of the lever 40 is provided at one end 31 of the link arm 30. Therefore, the circumferential tangential force that acts on the brake lining 2 from the brake disc 1 a during braking of the brake device 100 acts on the arm shaft 32 a of the support portion 32 and does not act on the eccentric cam 51. Therefore, since the frictional resistance when the eccentric cam 51 rotates does not increase, the mechanical efficiency during braking of the brake device 100 can be improved.
  • a brake device 100 that clamps and brakes a brake disc 1a that rotates with a wheel 1 includes a brake body 10 supported by a vehicle body or a carriage, and one end 31 and the other end 33 with respect to the brake body 10.
  • the support portions 32 are rotatably supported and are respectively provided on both sides of the brake disc 1a.
  • One end portions 31 are connected to each other by a connecting member 35, and the other end portions 33 are connected to the brake disc 1a.
  • a pair of link arms 30 that support the brake lining 2 that slides and applies a frictional force, an actuator 20 that is provided on the connecting member 35 and moves the rod 21 back and forth, and is pivotally connected to the rod 21 so that the rod 21 moves forward and backward.
  • the link arm 30 is supported such that the support portion 32 between the one end portion 31 and the other end portion 33 is rotatable with respect to the brake body 10.
  • An eccentric cam 51 that rotates the link arm 30 by boosting the force transmitted to the rod 21 by the rotation of the lever 40 is provided at one end 31 of the link arm 30. Therefore, the circumferential tangential force that acts on the brake lining 2 from the brake disc 1 a during braking of the brake device 100 acts on the arm shaft 32 a of the support portion 32 and does not act on the eccentric cam 51. Therefore, since the frictional resistance when the eccentric cam 51 rotates does not increase, the mechanical efficiency during braking of the brake device 100 can be improved.
  • the eccentric portion 53 is formed in a pair having a smaller diameter than the large-diameter portion 52, and the large-diameter portion 52 is connected to the lever 40 such that the lever 40 cannot be relatively rotated. 53.
  • the eccentric cam 51 has a small diameter from the center toward both ends, so that it is easy to process and assemble.
  • a needle bearing (not shown) as a rolling bearing may be provided on the outer periphery of the large diameter portion 52 of the eccentric cam 51.
  • the eccentric cam 51 can be smoothly rotated when the actuator 20 is operated, so that the mechanical efficiency of the brake device 100 can be improved.

Landscapes

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

Abstract

Le dispositif de freinage (100) de l'invention est équipé : d'une paire de bras de liaison (30) dans laquelle une partie soutien (32) est soutenue de manière à permettre sa rotation entre des parties extrémité (31) et d'autres parties extrémité (33) vis-à-vis d'un corps principal de frein (10), les parties extrémité (31) sont couplées entre elles par un élément de couplage (35), et chaque partie extrémité (33) soutient une garniture de frein (2) ; d'un actionneur (20) qui est agencé sur l'élément de couplage (35), et qui soumet un élément sortie (21) à un mouvement de va-et-vient ; d'un levier (40) qui exerce une rotation sous l'effet de va-et-vient de l'élément sortie (21) ; et d'une came excentrique (51) en rotation avec un axe de rotation (A1) pour centre sous l'effet de la rotation du levier (40). La came excentrique (51) possède : une partie grand diamètre (52) à laquelle est couplé le levier (40), et qui exerce une rotation avec l'axe de rotation (A1) pour centre ; et une partie excentrée (53) qui possède un axe central (A2) en une position décalée par rapport à l'axe de rotation (A1), qui est couplée de manière à permettre sa rotation aux parties extrémité (31) des bras de liaison (30), et exerce une rotation en arc avec l'axe de rotation (A1) pour centre sous l'effet de la rotation du levier (40).
PCT/JP2016/084996 2015-11-26 2016-11-25 Dispositif de freinage WO2017090737A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015230279A JP6609172B2 (ja) 2015-11-26 2015-11-26 ブレーキ装置
JP2015-230279 2015-11-26

Publications (1)

Publication Number Publication Date
WO2017090737A1 true WO2017090737A1 (fr) 2017-06-01

Family

ID=58763539

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2016/084996 WO2017090737A1 (fr) 2015-11-26 2016-11-25 Dispositif de freinage

Country Status (2)

Country Link
JP (1) JP6609172B2 (fr)
WO (1) WO2017090737A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020004402A1 (fr) * 2018-06-27 2020-01-02 曙ブレーキ工業株式会社 Dispositif de type frein à disque

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010280386A (ja) * 2010-09-22 2010-12-16 Nabtesco Corp 鉄道車両用ディスクブレーキ装置
JP2013087910A (ja) * 2011-10-20 2013-05-13 Toyota Motor Corp 制動力調整装置

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010280386A (ja) * 2010-09-22 2010-12-16 Nabtesco Corp 鉄道車両用ディスクブレーキ装置
JP2013087910A (ja) * 2011-10-20 2013-05-13 Toyota Motor Corp 制動力調整装置

Also Published As

Publication number Publication date
JP2017096437A (ja) 2017-06-01
JP6609172B2 (ja) 2019-11-20

Similar Documents

Publication Publication Date Title
JP6393521B2 (ja) ブレーキ装置
KR101846765B1 (ko) 브레이크 장치
JP6277076B2 (ja) ブレーキ装置
JP6746469B2 (ja) 電動式ブレーキ
JP6438327B2 (ja) ブレーキ装置
WO2017090734A1 (fr) Dispositif de freinage
JP6514642B2 (ja) パーキングブレーキユニット
KR101922476B1 (ko) 주차기능을 갖는 전자식 캘리퍼 브레이크
TW201923248A (zh) 浮動卡鉗式的碟制動裝置
WO2017090737A1 (fr) Dispositif de freinage
KR20110136419A (ko) 디스크 브레이크 장치
JPH0130661Y2 (fr)
JPH11344058A (ja) ディスクブレ―キ
JP2019173926A (ja) 車両用ディスクブレーキ装置
JP2017172726A (ja) ブレーキ装置
JP2017172729A (ja) ブレーキ装置
KR20100090026A (ko) 차량용 주차 브레이크
JP2010190233A (ja) ディスクブレーキのブレーキトルクアンカー

Legal Events

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

Ref document number: 16868680

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 16868680

Country of ref document: EP

Kind code of ref document: A1