JP2012052586A

JP2012052586A - Disk brake device

Info

Publication number: JP2012052586A
Application number: JP2010194608A
Authority: JP
Inventors: Shigeru Yoshizawa; 茂吉澤; Takayuki Shindo; 隆行進藤; Hideyuki Hasegawa; 英之長谷川
Original assignee: Akebono Brake Industry Co Ltd
Current assignee: Akebono Brake Industry Co Ltd
Priority date: 2010-08-31
Filing date: 2010-08-31
Publication date: 2012-03-15

Abstract

PROBLEM TO BE SOLVED: To inexpensively achieve a structure in which a braked side friction surface of a disk is brought into uniform contact with a braking side friction surface of a lining, regardless of the elastic deformation or the like of a caliper 12 and in which uneven abrasion of the linings of both pads can be prevented.SOLUTION: A plurality of elastic members such as leaf springs 30a, 30b is held as deviated inward or outward in a radial direction from each other between a pair of pad supports 18a, 18b provided on a caliper 12 and pressure plates of the pads supported by the pad supports 18a, 18b. The pads supported by the pad supports 18a, 18b are supported as displacable by swinging with respect to the pad supports 18a, 18b to thereby achieve uniform contact between the frictional surfaces.

Description

この発明は、新幹線等の高速鉄道車両の制動に使用するディスクブレーキの改良に関する。具体的には、キャリパの弾性変形に拘らず、ディスクの被制動側摩擦面とパッドのライニングの制動側摩擦面とを均一に当接させて、このパッドのライニングが偏磨耗する事を防止できる構造の実現を意図したものである。 The present invention relates to an improvement in a disc brake used for braking a high-speed railway vehicle such as a Shinkansen. Specifically, regardless of the elastic deformation of the caliper, the brake-side friction surface of the disk and the brake-side friction surface of the pad lining can be uniformly abutted to prevent uneven wear of the pad lining. It is intended to realize the structure.

新幹線等の高速鉄道車両には、通常、電気式と機械式との制動装置が使用されており、機械式としてはディスクブレーキ装置が多く使用されている。この様な鉄道車両用のディスクブレーキ装置に関する発明を記載した刊行物として、例えば特許文献１〜８が存在する。このうちの特許文献１には、被制動側となるディスク付車輪に関する発明が、特許文献２にはディスクの具体的な構造及び製造方法に関する発明が、特許文献３〜４には、制動側であるパッド押圧機構に関する発明が、特許文献５〜７には、ライニングを複数のセグメントに分割すると共に、これら各セグメントをプレッシャプレートに対し変位可能に支持したパッドに関する発明が、特許文献８には、制動力を発生させる為のアクチュエータの設置構造を工夫した発明が、それぞれ記載されている。鉄道車両用のディスクブレーキ装置は、特許文献１に記載された様なディスク付車輪と、特許文献３〜４に記載された様なパッド押圧機構とを組み合わせて成る。即ち、このディスク付車輪を構成する一対のディスクの両側に一対のパッドを配置し、制動時には前記パッド押圧機構によりこれら両パッドライニングの制動側摩擦面を、前記両ディスクの被制動側摩擦面に押圧する。本発明は、前記パッド押圧機構を構成するキャリパの弾性変形に拘らず、前記両制動側摩擦面と前記両被制動側摩擦面との擦れ合い部の面圧分布を均一にする事を意図している。そこで、本発明の前提となるディスクブレーキ装置の構造及び作用に就いて、図２９〜３０により説明する。尚、図３０は、前記特許文献３〜４のうちの特許文献４に即した、パッド押圧機構の構造を示している。 In high-speed railway vehicles such as Shinkansen, electric and mechanical braking devices are usually used, and disk brake devices are often used as mechanical devices. As publications describing inventions relating to such disc brake devices for railway vehicles, for example, Patent Documents 1 to 8 exist. Of these, Patent Document 1 discloses an invention related to a wheel with a disk on the brake side, Patent Document 2 discloses an invention related to a specific structure and manufacturing method of the disk, and Patent Documents 3 to 4 describe an invention related to a brake side. The invention related to a certain pad pressing mechanism is disclosed in Patent Documents 5 to 7, and the invention related to a pad that divides the lining into a plurality of segments and supports these segments so as to be displaceable with respect to the pressure plate, The inventions that devise the actuator installation structure for generating the braking force are described respectively. A disk brake device for a railway vehicle is formed by combining a wheel with a disk as described in Patent Document 1 and a pad pressing mechanism as described in Patent Documents 3 to 4. That is, a pair of pads are arranged on both sides of the pair of disks constituting the disk-equipped wheel, and the braking side friction surfaces of both the pad linings are made the braking side friction surfaces of the both disks by the pad pressing mechanism during braking. Press. The present invention intends to make the surface pressure distribution of the rubbing portion between the both brake-side friction surfaces and the both brake-side friction surfaces uniform, regardless of the elastic deformation of the caliper constituting the pad pressing mechanism. ing. Therefore, the structure and operation of the disc brake device which is the premise of the present invention will be described with reference to FIGS. FIG. 30 shows the structure of the pad pressing mechanism in accordance with Patent Document 4 out of Patent Documents 3 to 4.

先ず、ディスク付車輪１は、図２９に示す様に、一対のディスク２、２により、鉄道車両用の車輪３をサンドイッチ状に挟持している。そして、これら両ディスク２、２及び車輪３の円周方向複数箇所で互いに整合する部分に形成した各取付孔にスプリングピン４、４を挿通すると共に、これら各スプリングピン４、４等を挿通したボルト５、５とナット６、６とを螺合し更に締め付けている。この構成により、前記車輪３の両側に前記両ディスク２、２を、この車輪３と共に回転する様に支持している。これら両ディスク２、２の外側面（互いに反対側の側面）のうちの径方向外半部が、被制動側摩擦面７、７である。尚、前記ディスク２、２をアルミニウム合金製とする場合には、この被制動側摩擦面７、７部分は、セラミックス材料を混合した、アルミニウム合金基複合材料製とし、この被制動側摩擦面７、７部分の耐摩耗性を確保する事が、例えば特許文献２に記載されて従来から知られている。 First, as shown in FIG. 29, the disc-equipped wheel 1 has a pair of discs 2 and 2 sandwiching a rail vehicle wheel 3 in a sandwich shape. Then, the spring pins 4 and 4 are inserted into the mounting holes formed in the portions aligned with each other in the circumferential direction of both the disks 2 and 2 and the wheel 3, and the spring pins 4 and 4 are inserted. Bolts 5 and 5 and nuts 6 and 6 are screwed together and further tightened. With this configuration, the discs 2 and 2 are supported on both sides of the wheel 3 so as to rotate together with the wheel 3. The radially outer half of the outer surfaces (side surfaces opposite to each other) of the two disks 2 and 2 is the braked friction surfaces 7 and 7. When the disks 2 and 2 are made of an aluminum alloy, the brake-side friction surfaces 7 and 7 are made of an aluminum alloy-based composite material mixed with a ceramic material. Securing the wear resistance of the seven parts is described in, for example, Patent Document 2 and is conventionally known.

又、前記パッド押圧機構部分は、図３０に示す様に構成している。特許請求の範囲に記載した固定支持部に相当する固定フレーム８は、上端部に設けた取付部９により、車台等の、前記車輪３（図２９）の周囲部分に取付固定される。又、この取付部９から下方に垂れ下がった垂下部１０に上下一対の支持軸１１、１１を設けている。この取付部９を前記車台等に結合固定した状態で、これら両支持軸１１、１１は、前記車輪３の回転軸に対し平行になる。そして、これら両支持軸１１、１１の両端部に、キャリパ１２の基部１３を構成する、上下２箇所ずつ、合計４箇所に設けた支持板部１４、１４を結合固定している。前記両支持軸１１、１１の中間部は、それぞれ前記垂下部１０の上下２箇所位置に設けたガイド筒部１５、１５に、軸方向の変位を可能に挿通している。互いに対向する前記支持板部１４、１４同士の間隔は、それぞれ前記両ガイド筒部１５、１５の軸方向長さよりも長い。又、これら両ガイド筒部１５、１５の両端開口部と前記各支持板部１４、１４との間には、弾性変形可能なベローズ１６、１６を設けている。この構成により前記キャリパ１２を前記固定フレーム８に対し、前記車輪３の軸方向の変位を可能に支持している。尚、本明細書及び特許請求の範囲で、「軸方向」、「径方向」、「周方向」とは、特に断わらない限り、それぞれディスクブレーキ装置を組み立てた状態での、車輪及びディスクに関するこれら各方向で表す。 The pad pressing mechanism is configured as shown in FIG. The fixed frame 8 corresponding to the fixed support portion described in the claims is attached and fixed to a peripheral portion of the wheel 3 (FIG. 29) such as a chassis by an attachment portion 9 provided at the upper end portion. In addition, a pair of upper and lower support shafts 11 are provided on a hanging portion 10 that hangs downward from the mounting portion 9. In a state where the attachment portion 9 is coupled and fixed to the chassis or the like, both the support shafts 11 and 11 are parallel to the rotation axis of the wheel 3. Support plate portions 14, 14 provided at a total of four locations, two at the top and bottom, constituting the base portion 13 of the caliper 12, are coupled and fixed to both end portions of both the support shafts 11, 11. The intermediate portions of the support shafts 11 and 11 are inserted through guide tube portions 15 and 15 provided at two positions above and below the hanging portion 10 so as to be axially displaceable. An interval between the support plate portions 14 and 14 facing each other is longer than an axial length of the guide tube portions 15 and 15, respectively. Bellows 16, 16 that are elastically deformable are provided between the opening portions at both ends of the guide tube portions 15, 15 and the support plate portions 14, 14. With this configuration, the caliper 12 is supported with respect to the fixed frame 8 such that the wheel 3 can be displaced in the axial direction. In the present specification and claims, the terms “axial direction”, “radial direction”, and “circumferential direction” refer to wheels and discs in a state where the disc brake device is assembled unless otherwise specified. Expressed in each direction.

前記キャリパ１２は、それぞれの基端部を前記基部１３に連続させた、一対の押圧腕１７ａ、１７ｂを有する。これら両押圧腕１７ａ、１７ｂは、この基部１３から前記車輪３を軸方向両側から挟む位置にまで延出されており、それぞれの先端部にパッド支持部１８ａ、１８ｂを、それぞれ設けている。これら両パッド支持部１８ａ、１８ｂのうちの一方（図３０の手前側）のパッド支持部１８ａは、単なる枠状とし、このパッド支持部１８ａの内側面｛前記ディスク２（図２９）の被制動側摩擦面７に対向する面｝に、一方のパッド１９ａを支持している。このパッド１９ａは、プレッシャプレート２０ａの内側面に、ライニング２１ａを添着したバックプレートをリベットにより結合固定したもので、このうちのプレッシャプレート２０ａを前記パッド支持部１８ａに対し、相対変位を阻止した状態で支持している。 The caliper 12 has a pair of pressing arms 17 a and 17 b in which respective base end portions are connected to the base portion 13. Both the pressing arms 17a and 17b are extended from the base portion 13 to a position where the wheel 3 is sandwiched from both sides in the axial direction, and pad support portions 18a and 18b are provided at respective tip portions. One of these pad support portions 18a and 18b (front side in FIG. 30) has a simple frame shape, and the inner surface of the pad support portion 18a {the braked disk 2 (FIG. 29) One pad 19a is supported on the surface facing the side friction surface 7}. The pad 19a is obtained by connecting and fixing a back plate attached with a lining 21a to the inner side surface of the pressure plate 20a by a rivet, and the pressure plate 20a is in a state in which relative displacement with respect to the pad support portion 18a is prevented. I support it.

これに対して、他方（図３０の奥側）のパッド支持部１８ｂに関しては、制動力発生用の、複数組のアクチュエータを内蔵している。即ち、このパッド支持部１８ｂの複数箇所に、それぞれがこのパッド支持部１８ｂの内側面側に開口するシリンダ孔を形成し、これら各シリンダ孔内にピストンを密に嵌装すると共に、これら各シリンダ孔内に、ブレーキオイル、圧縮空気等の圧力流体を給排自在としている。尚、前記各アクチュエータは、ダイヤフラム式、ベローズ式等、圧力流体の給排により軸方向寸法を拡縮できるものであれば、シリンダ式に限らずに採用できる。又、前記パッド支持部１８ｂの内側面側に他方のパッド１９ｂを、軸方向の変位を可能に支持している。即ち、このパッド１９ｂに関しても、プレッシャプレート２０ｂの内側面に、ライニング２１ｂを添着したバックプレートをリベットにより結合固定して成るが、このうちのプレッシャプレート２０ｂを前記パッド支持部１８ｂに対し、軸方向の変位のみを可能に支持している。この為の支持構造に就いては、従来から知られているが、後述する、本発明の実施の形態の第１例部分で、簡単に図示並びに説明する。 On the other hand, the other (back side in FIG. 30) pad support portion 18b incorporates a plurality of sets of actuators for generating a braking force. That is, a cylinder hole that opens to the inner surface side of the pad support portion 18b is formed at a plurality of locations of the pad support portion 18b, and a piston is closely fitted in each cylinder hole. Pressure fluid such as brake oil and compressed air can be supplied and discharged freely in the hole. The actuators can be employed without being limited to the cylinder type as long as the axial dimension can be expanded and reduced by the supply and discharge of pressure fluid, such as a diaphragm type and a bellows type. The other pad 19b is supported on the inner side of the pad support 18b so as to be capable of axial displacement. That is, the pad 19b is also formed by connecting and fixing a back plate attached with a lining 21b to the inner side surface of the pressure plate 20b with a rivet, and the pressure plate 20b is axially connected to the pad support portion 18b. Supports only the displacement of. A support structure for this purpose has been known in the art, but will be briefly illustrated and described in a first example of an embodiment of the present invention, which will be described later.

制動時には、前記各シリンダ孔内に圧力流体を送り込み、前記各ピストンをこれら各シリンダ孔から突出させる等により、前記各アクチュエータの軸方向寸法を拡大する。そして、前記他方のパッド１９ｂのライニング２１ｂを、図３０に矢印αで示す様に、前記車輪３の両側面に支持した一対のディスク２、２（図２９）のうちの一方のディスク２の被制動側摩擦面７に押し付ける。すると、この押し付けの反作用として、前記キャリパ１２が図３０の矢印β方向に変位し、前記一方のパッド１９ａのライニング２１ａを、他方のディスク２の被制動側摩擦面７に押し付ける。この結果、一対のパッド１９ａ、１９ｂのライニング２１ａ、２１ｂの制動側摩擦面２２、２２と、前記両ディスク２、２の被制動側摩擦面７、７とが摩擦しあって、制動が行われる。 At the time of braking, a pressure fluid is sent into each cylinder hole, and the axial dimension of each actuator is expanded by, for example, projecting each piston from each cylinder hole. Then, the lining 21b of the other pad 19b is covered by one disk 2 of the pair of disks 2 and 2 (FIG. 29) supported on both side surfaces of the wheel 3, as indicated by an arrow α in FIG. Press against the braking friction surface 7. Then, as a reaction of this pressing, the caliper 12 is displaced in the direction of arrow β in FIG. 30, and the lining 21 a of the one pad 19 a is pressed against the braked friction surface 7 of the other disk 2. As a result, the braking friction surfaces 22 and 22 of the linings 21a and 21b of the pair of pads 19a and 19b and the braked friction surfaces 7 and 7 of the two disks 2 and 2 are rubbed to perform braking. .

上述の様な鉄道車両用のディスクブレーキ装置の場合、前記両ディスク２、２の被制動側摩擦面７、７と、前記両ライニング２１ａ、２１ｂの制動側摩擦面２２、２２との擦れ合い部の面圧が、次の(A) 〜(C) の様な現象に基づいて、不均一になり易い。
(A) 前記キャリパ１２の弾性変形
このキャリパ１２を構成する前記両押圧腕１７ａ、１７ｂは前記基部１３に対し、片持ち式に支持されており、前記両パッド支持部１８ａ、１８ｂは、前記両押圧腕１７ａ、１７ｂの先端部に設けている。従って、制動時にこれら両押圧腕１７ａ、１７ｂは特許文献４の図５に誇張して示されている様に、先端部に向かうに従って互いの間隔が拡がる方向に弾性変形する。そして、前記両押圧腕１７ａ、１７ｂの先端部に支持された一対のパッド１９ａ、１９ｂのライニング２１ａ、２１ｂの制動側摩擦面２２、２２に関しても、同じ方向に傾斜する。
(B) 前記両ディスク２、２の被制動側摩擦面７、７の偏摩耗
これら両ディスク２、２の被制動側摩擦面７、７の周速は、径方向外側程速く、従ってこれら両被制動側摩擦面７、７の摩耗は、径方向外側程進み易い。この結果、図３１の（ａ）に誇張して示す様に、ディスク２の被制動側摩擦面７が、径方向外側程凹む。
(C) 制動時に於ける、このディスク２の熱変形
制動時にこのディスク２は、パッド１９ａ、１９ｂのライニング２１ａ、２１ｂとの摩擦により温度上昇する。又、前記ディスク２は、前述した通り、被制動側摩擦面７部分をアルミニウム合金基複合材料製とし、残りの部分はアルミニウム合金製としている。アルミニウム合金基複合材料の線膨張係数は、アルミニウム合金の線膨張係数よりも低い。この為、制動開始直後、前記ディスク２のうちの被制動側摩擦面７部分のみが温度上昇している状態では、このディスク２は、図３１の（ｂ）に誇張して示す様に、外径側ほどライニング２１ａ（２１ｂ）から遠ざかる方向に傾斜する。これに対して、制動開始後時間を経過して、前記ディスク２全体が温度上昇すると、図３１の（ｃ）に誇張して示す様に、外径側ほどライニング２１ａ（２１ｂ）に近付く方向に傾斜する。 In the case of the disc brake device for a railway vehicle as described above, the frictional portions between the brake-side friction surfaces 7 and 7 of the both disks 2 and 2 and the brake-side friction surfaces 22 and 22 of the both linings 21a and 21b. The surface pressure tends to be non-uniform based on the following phenomena (A) to (C).
(A) Elastic deformation of the caliper 12 The pressing arms 17a and 17b constituting the caliper 12 are supported in a cantilever manner with respect to the base 13, and the pad support portions 18a and 18b are It is provided at the tip of the pressing arms 17a, 17b. Accordingly, during braking, both the pressing arms 17a and 17b are elastically deformed in a direction in which the distance between the pressing arms 17a and 17b increases toward the tip as shown in FIG. The braking side friction surfaces 22 and 22 of the linings 21a and 21b of the pair of pads 19a and 19b supported at the tip portions of the pressing arms 17a and 17b are also inclined in the same direction.
(B) Uneven wear of the brake-side friction surfaces 7 and 7 of the disks 2 and 2 The peripheral speeds of the brake-side friction surfaces 7 and 7 of both the disks 2 and 2 are faster toward the outside in the radial direction. The wear of the brake-side frictional surfaces 7 and 7 tends to progress toward the outer side in the radial direction. As a result, as shown exaggeratedly in FIG. 31 (a), the brake side friction surface 7 of the disk 2 is recessed toward the outer side in the radial direction.
(C) Thermal deformation of the disk 2 during braking The temperature of the disk 2 rises due to friction between the pads 19a and 19b and the linings 21a and 21b during braking. Further, as described above, the disk 2 has a brake-side friction surface 7 portion made of an aluminum alloy-based composite material and the remaining portion made of an aluminum alloy. The linear expansion coefficient of the aluminum alloy matrix composite material is lower than that of the aluminum alloy. For this reason, immediately after the start of braking, in the state where only the braked friction surface 7 of the disk 2 has a temperature rise, the disk 2 is externally shown as exaggerated in FIG. The diameter side is inclined in a direction away from the lining 21a (21b). In contrast, when the temperature of the entire disk 2 rises after a lapse of time after the start of braking, the outer diameter side approaches the lining 21a (21b) as shown in an exaggerated manner in FIG. Tilt.

上述した(A) 〜(C) の様な理由により、前記ディスク２の被制動側摩擦面７と前記ライニング２１ａ、２１ｂの制動側摩擦面２２との擦れ合い部の面圧が不均一になった場合、理由に関係なく、ディスク２やパッド１９ａ、１９ｂの耐久性低下、制動力の安定性低下等の問題を生じる。このうちの耐久性低下の第一の形態は、前記被制動側摩擦面７と前記制動側摩擦面２２との摩擦面の温度上昇が不均一になる事に基づく、各部の熱膨張量の不均一化に伴って発生する引っ張り応力による亀裂等の損傷として現れる。又、第二の形態は、前記ライニング２１ａ、２１ｂの偏摩耗として現れる。又、前記制動力の安定性低下は、前記各アクチュエータが発生する推力と、この推力に基づいて発生する制動力とが比例しなくなる現象として現れる。 For the reasons (A) to (C) described above, the surface pressure of the frictional portion between the brake-side friction surface 7 of the disk 2 and the brake-side friction surface 22 of the linings 21a and 21b becomes uneven. In this case, problems such as a decrease in durability of the disk 2 and the pads 19a and 19b and a decrease in braking force stability occur regardless of the reason. Of these, the first form of durability reduction is the non-uniform thermal expansion of each part based on the uneven temperature rise of the friction surface between the braked friction surface 7 and the brake friction surface 22. It appears as damage such as cracks due to the tensile stress generated with the homogenization. The second form appears as uneven wear of the linings 21a and 21b. The reduction in the stability of the braking force appears as a phenomenon in which the thrust generated by each actuator is not proportional to the braking force generated based on the thrust.

一方、前記特許文献３には、一対の押圧腕の中間部を揺動変位可能に支持すると共に、これら両押圧腕の先端部にそれぞれパッドを、揺動変位可能に枢支し、これら両押圧腕の基端部同士の間隔をアクチュエータにより拡縮する構造が記載されている。この様な特許文献３に記載された構造によれば、ディスク側の被制動側摩擦面と、パッド側の制動側摩擦面との面圧分布をほぼ均一にできるものと考えられる。但し、上述の様な特許文献３に記載された構造は、制動時に前記被制動側摩擦面と前記制動側摩擦面とを押し付け合う力の反力を、複数箇所に設置した枢支部により支承する必要がある。繰り返し加わる反力に拘らず、これら各枢支部の耐久性を確保する為には、これら各枢支部を含むディスクブレーキ装置全体が大型化し、製造コストが嵩むものと考えられる。 On the other hand, in Patent Document 3, an intermediate part of a pair of pressing arms is supported so as to be able to swing and displace, and a pad is pivotally supported at the tip part of both pressing arms so as to be able to swing and displace. A structure is described in which the distance between the base ends of the arms is expanded or reduced by an actuator. According to such a structure described in Patent Document 3, it is considered that the surface pressure distribution between the brake side friction surface on the disk side and the brake side friction surface on the pad side can be made substantially uniform. However, the structure described in Patent Document 3 as described above supports the reaction force of the force that presses the brake-side friction surface and the brake-side friction surface at the time of braking by pivots provided at a plurality of locations. There is a need. Regardless of the reaction force repeatedly applied, in order to ensure the durability of each of the pivots, it is considered that the entire disc brake device including these pivots is enlarged and the manufacturing cost increases.

これに対して、前記特許文献５〜７に記載された発明の構造の様に、ライニングを複数のセグメントに分割し、更にこれら各セグメントをプレッシャプレートに対し、それぞれ独立した変位を可能に支持したパッドを使用すれば、前述の(A) 〜(C) の様な理由による、ディスクの被制動側摩擦面とライニングの制動側摩擦面との擦れ合い部の面圧の不均一を、多少は改善できる可能性がある。但し、上述の様な構造のパッドを使用しても、前記ディスクの被制動側摩擦面と前記プレッシャプレートとの距離に、径方向外方と内方とで差が生じた場合には、この差を解消できない為、前記面圧の不均一を改善する効果は限られるものと考えられる。しかも、消耗品であるパッドに、多くの弾性部材を組み込む必要がある等、パッドの製造コストが嵩む為、鉄道車両のランニングコストを抑える面から不利である。 On the other hand, like the structure of the invention described in Patent Documents 5 to 7, the lining is divided into a plurality of segments, and each of the segments is supported so as to be capable of independent displacement with respect to the pressure plate. If a pad is used, the unevenness of the surface pressure of the frictional part between the braked friction surface of the disk and the braking side friction surface of the lining due to the reasons (A) to (C) described above is somewhat increased. There is a possibility of improvement. However, even if the pad having the structure as described above is used, if there is a difference between the radially outer side and the inner side in the distance between the brake side friction surface of the disk and the pressure plate, this Since the difference cannot be resolved, it is considered that the effect of improving the non-uniformity of the surface pressure is limited. In addition, it is disadvantageous from the standpoint of reducing the running cost of the railway vehicle because the pad manufacturing cost increases because it is necessary to incorporate many elastic members into the consumable pad.

特開２００９−２３７５号公報JP 2009-2375 A 特開２００６−３２８４７４号公報JP 2006-328474 A 特開２００８−１５１１６８号公報JP 2008-151168 A 特開２００８−２８１１５６号公報JP 2008-281156 A 特開２００６−１９４４２９号公報JP 2006-194429 A 特開２００６−３０７８９５号公報JP 2006-307895 A 特表平１０−５０７２５０号公報Japanese National Patent Publication No. 10-507250 特開２００９−１３３４６２号公報JP 2009-133462 A

本発明は、上述の様な事情に鑑みて、キャリパの弾性変形や、ディスクの偏摩耗、熱変形に拘らず、ディスクの被制動側摩擦面とパッドのライニングの制動側摩擦面とを均一に当接させて、このパッドのライニングの偏磨耗を抑えられる構造を、低コストで実現すべく発明したものである。 In view of the circumstances as described above, the present invention makes the brake-side friction surface of the disk and the brake-side friction surface of the pad lining uniform, regardless of the elastic deformation of the caliper, uneven wear of the disk, or thermal deformation. The invention has been invented to realize a structure that can be brought into contact with the pad to suppress uneven wear of the lining of the pad at a low cost.

本発明のディスクブレーキ装置は、特許文献３、４に記載される等により従来から知られているディスクブレーキ装置と同様に、一対のディスクと、固定支持部と、キャリパと、一対のパッドと、アクチュエータとを備える。
このうちの両ディスクは、車輪の両側面にこの車輪と同心に支持固定されて、それぞれの外側面を、この車輪の回転中心軸に対し直交する方向に存在する被制動側摩擦面としている。
又、前記固定支持部は、車台等の、前記車輪の周囲部分に設けられている。
又、前記キャリパは、前記固定支持部に支持された基部、及び、この基部から前記両ディスクを軸方向両側から挟む位置にまで延出された一対の押圧腕を備える。
又、前記両パッドは、プレッシャプレート、及び、このプレッシャプレートのうちの前記両ディスクの外側面と対向する面に添着されたライニングを備える。そして、このうちのプレッシャプレートを前記両押圧腕の先端部で前記両ディスクの外側面に対向する部分に設けられた一対のパッド支持部に支持している。
又、前記アクチュエータは、前記両パッドを遠近動させる為のもので、このアクチュエータにより、前記両パッドのライニングの制動側摩擦面を前記両被制動側摩擦面に押し付けて制動を行う様にしている。 The disc brake device of the present invention is a pair of discs, a fixed support portion, a caliper, a pair of pads, and the like, as is conventionally known from the disc brake devices described in Patent Documents 3 and 4, etc. An actuator.
Both of these discs are supported and fixed concentrically with the wheel on both side surfaces of the wheel, and the outer side surfaces of the respective disks serve as brake-side friction surfaces existing in a direction orthogonal to the rotation center axis of the wheel.
Moreover, the said fixed support part is provided in the surrounding parts of the said wheels, such as a chassis.
The caliper includes a base portion supported by the fixed support portion, and a pair of pressing arms extending from the base portion to a position where the both disks are sandwiched from both sides in the axial direction.
Each of the pads includes a pressure plate and a lining attached to a surface of the pressure plate facing the outer surface of the disks. Of these, the pressure plate is supported by a pair of pad support portions provided at the tip portions of the pressing arms at portions facing the outer surfaces of the disks.
Further, the actuator is for moving both the pads far and away, and the brake is performed by pressing the braking side friction surfaces of the linings of the pads against the both brake side friction surfaces. .

特に、本発明のディスクブレーキ装置に於いては、前記両パッド支持部のうちの少なくとも一方のパッド支持部と当該パッド支持部に支持された前記プレッシャプレートとの間に複数の弾性部材を、径方向に関して内外にずらせた状態で挟持している。即ち、前記少なくとも一方のパッド支持部と前記プレッシャプレートとの径方向外寄り部分同士の間、並びに、当該パッド支持部とこのプレッシャプレートとの径方向内寄り部分同士の間に、それぞれ弾性部材を挟持している。そして、前記少なくとも一方のパッド支持部に支持されたパッドを当該パッド支持部に対し、径方向に関して外寄り部分と内寄り部分とが軸方向に関して相対変位する方向への、揺動変位を可能に支持している。
この様な本発明を実施する場合に好ましくは、請求項２に記載した発明の様に、前記各弾性部材を、前記両パッド支持部と前記両プレッシャプレートとの間にそれぞれ複数ずつ、径方向に関して内外にずらせた状態で挟持する。そして、前記両パッドを前記両パッド支持部に対し、それぞれ揺動変位を可能に支持する。 In particular, in the disc brake device of the present invention, a plurality of elastic members are provided between the at least one pad support portion of the two pad support portions and the pressure plate supported by the pad support portion. It is held in a state where it is shifted inward and outward with respect to the direction. That is, elastic members are respectively provided between the radially outer portions of the at least one pad support portion and the pressure plate, and between the radially inward portions of the pad support portion and the pressure plate. It is pinched. Further, the pad supported by the at least one pad support portion can be oscillated and displaced in a direction in which the outer portion and the inner portion relative to the pad support portion are displaced relative to each other in the axial direction. I support it.
In the case of carrying out the present invention as described above, preferably, as in the invention described in claim 2, a plurality of each of the elastic members is provided between the two pad support portions and the two pressure plates. Hold in a state where it is shifted in and out. Then, both the pads are supported by the two pad support portions so as to be able to swing and displace.

上述の様な本発明のディスクブレーキ装置を実施する場合に、例えば請求項３に記載した発明の様に、前記キャリパの基部を、前記固定支持部に設けた、前記車輪の回転中心軸と平行な支持軸に沿った変位を可能に支持する。そして、前記両押圧腕の先端部にそれぞれ設けた、前記両パッド支持部のうち、一方のパッド支持部にのみ前記アクチュエータを設ける。
或は、請求項４に記載した発明の様に、前記キャリパの基部を前記固定支持部に、前記車輪の回転方向の変位を阻止した状態で支持する。そして、前記両押圧腕の先端部にそれぞれ設けた、前記両パッド支持部に、それぞれ前記アクチュエータを設ける。 When implementing the disc brake device of the present invention as described above, for example, as in the invention described in claim 3, the base portion of the caliper is provided in the fixed support portion and parallel to the rotation center axis of the wheel. Supports displacement along a flexible support axis. And the said actuator is provided only in one pad support part among the said pad support parts each provided in the front-end | tip part of both the said press arms.
Or like the invention described in Claim 4, the base part of the said caliper is supported by the said fixed support part in the state which prevented the displacement of the rotation direction of the said wheel. And the said actuator is each provided in the said both pad support part provided in the front-end | tip part of both the said press arms, respectively.

又、本発明のディスクブレーキ装置を実施する場合に好ましくは、請求項５に記載した発明の様に、前記両パッドを構成するライニングの一部で径方向中間部分に、周方向に関して一端縁から他端縁まで連続する周方向凹溝若しくは周方向不連続部を存在させる。
或は、請求項６に記載した発明の様に、前記両パッドを構成するライニングの一部で周方向に関して中間部の複数箇所部分に、内周縁から外周縁まで連続する、それぞれが径方向に長い径方向凹溝若しくは径方向不連続部を存在させる。
そして、前記両パッドを径方向（請求項５に記載した発明の場合）或いは周方向（請求項６に記載した発明の場合）に撓み易くして、前記両ディスクの被制動側摩擦面の凹凸や変形（反り）に追従し易くなる。 Further, when the disc brake device of the present invention is implemented, preferably, as in the invention described in claim 5, a part of the lining constituting the two pads is formed in a radially intermediate portion and from one end edge in the circumferential direction. A circumferential groove or circumferential discontinuity that continues to the other end edge is present.
Alternatively, as in the invention described in claim 6, a part of the lining constituting the both pads is continuous from the inner peripheral edge to the outer peripheral edge in a plurality of portions in the intermediate portion with respect to the circumferential direction. There are long radial grooves or radial discontinuities.
Then, the two pads are easily bent in the radial direction (in the case of the invention described in claim 5) or the circumferential direction (in the case of the invention described in claim 6), and the unevenness of the friction side of the braked side of the both disks is It becomes easy to follow and deformation (warp).

又、本発明を実施する場合に、例えば請求項７に記載した発明の様に、前記各弾性部材を、前記両パッド支持部の幅方向両端寄り部分に設置された、これら両パッド支持部に沿った方向に長い板ばねとする。
或は、請求項８に記載した発明の様に、前記各弾性部材を、圧縮コイルばねと皿板ばねとエラストマーのブロックとのうちから選択される何れかとする。そして、径方向外側と径方向内側とでそれぞれ複数個ずつの弾性部材を、前記両パッド支持部と前記プレッシャプレートとの間に挟持する。
この様な請求項８に記載した発明を実施する場合に好ましくは、請求項９に記載した発明の様に、前記両パッドのライニングを、周方向に関して一端縁から他端縁まで連続する周方向凹溝若しくは周方向不連続部、及び、それぞれが径方向に長い径方向凹溝若しくは径方向不連続部により複数の部分に分割された状態で、前記プレッシャプレートの内側面に添着する。そして、前記各弾性部材を、軸方向に関して前記各部分に重畳する位置で、前記パッド支持部と前記プレッシャプレートとの間に挟持する。 Further, when carrying out the present invention, for example, as in the invention described in claim 7, the respective elastic members are installed on both the pad support portions disposed at both ends of the both pad support portions in the width direction. The leaf spring is long in the direction along.
Alternatively, as in the invention described in claim 8, each of the elastic members is selected from a compression coil spring, a plate spring, and an elastomer block. Then, a plurality of elastic members are sandwiched between the pad support portions and the pressure plate respectively on the radially outer side and the radially inner side.
When the invention described in claim 8 is carried out, preferably, as in the invention described in claim 9, the linings of the two pads are circumferentially connected from one edge to the other edge in the circumferential direction. The groove is attached to the inner surface of the pressure plate in a state where the groove is divided into a plurality of portions by a concave groove or a circumferential discontinuous portion and a radial concave groove or a radial discontinuous portion that is long in the radial direction. And each said elastic member is clamped between the said pad support part and the said pressure plate in the position which overlaps with each said part regarding an axial direction.

上述の様に構成する本発明のディスクブレーキ装置に組み込まれる一対のパッドのうちの少なくとも一方のパッドは、複数の弾性部材の存在に基づき、径方向に関して外寄り部分と内寄り部分とが軸方向に関して相対変位する方向に揺動変位する。即ち、制動時に於ける一対の押圧腕同士の弾性変形や、ディスクの偏摩耗等により、これら両押圧腕の先端部に設けたパッド支持部の内側面とこのディスクの非制動側摩擦面とが非平行になると、前記少なくとも一方のパッド支持部に支持されたパッドが、前記方向に揺動変位する。そしてこのパッドを構成するライニングの制動側摩擦面と前記ディスクの被制動側摩擦面とを平行なままに維持する。この為、本発明のディスクブレーキ装置によれば、キャリパの弾性変形に拘らず、ディスクの被制動側摩擦面とパッドのライニングの制動側摩擦面とを均一に当接させる事ができて、このライニングが偏磨耗する事を防止できる。又、アクチュエータが発生する推力と前記各摩擦面同士の摩擦により得られる制動力とを関連付けたままにできて、安定した制動力を得られる。 Based on the presence of a plurality of elastic members, at least one of the pair of pads incorporated in the disc brake device of the present invention configured as described above has an outer portion and an inner portion in the axial direction with respect to the radial direction. Oscillating displacement in the direction of relative displacement. That is, due to elastic deformation between a pair of pressing arms during braking, uneven wear of the disk, etc., the inner side surface of the pad support provided at the tip of both pressing arms and the non-braking side friction surface of the disk When it becomes non-parallel, the pad supported by the at least one pad support portion swings and displaces in the direction. The braking side friction surface of the lining constituting the pad and the braked friction surface of the disk are kept parallel. Therefore, according to the disc brake device of the present invention, the brake-side friction surface of the disc and the brake-side friction surface of the pad lining can be brought into uniform contact regardless of the elastic deformation of the caliper. It is possible to prevent uneven wear of the lining. Further, the thrust generated by the actuator and the braking force obtained by the friction between the friction surfaces can be kept associated with each other, and a stable braking force can be obtained.

この様に、ライニングの偏摩耗を防止すべく、前記被制動側摩擦面と前記制動側摩擦面とを均一に当接させる為に、前述の特許文献３に記載された発明の構造の様に、制動時に大きな力が加わる複数箇所に枢軸による揺動支持部を設ける必要がない。この為、揺動支持部の耐久性確保の為に、重量が嵩んだり制作費が嵩む事を防止できて、前記パッドのライニングが偏磨耗する事を防止すると共に安定した制動力を得られる構造を、低コストで実現できる。特に、請求項２に記載した発明の様に、前記両パッドを前記両パッド支持部に揺動変位を可能に支持すれば、上述の様な作用・効果を顕著に得られる。 As described above, in order to uniformly contact the brake side friction surface and the brake side friction surface in order to prevent uneven wear of the lining, the structure of the invention described in Patent Document 3 is used. In addition, it is not necessary to provide pivot support portions by pivots at a plurality of locations where a large force is applied during braking. For this reason, in order to ensure the durability of the swinging support portion, it is possible to prevent the weight from increasing and the production cost from increasing, and it is possible to prevent the pad lining from being unevenly worn and to obtain a stable braking force. The structure can be realized at low cost. In particular, as described in the second aspect of the present invention, if the two pads are supported on the two pad support portions so as to be able to swing and displace, the above-described operations and effects can be obtained remarkably.

本発明の実施の形態の第１例を、車輪及び一対のディスクを省略して上方から見た状態で示す正投影図。The orthographic projection figure which shows the 1st example of embodiment of this invention in the state which abbreviate | omitted the wheel and a pair of discs, and was seen from upper direction. 同じく径方向内方から見た状態で示す正投影図。The orthographic projection shown in the state similarly seen from radial inside. 同じく斜視図。Similarly perspective view. 図１のイ部拡大図。FIG. 図３のロ部拡大図。The B section enlarged view of FIG. 図３のハ−ハ断面図。FIG. 図６と反対側のパッド及びパッド支持部に関する、図６と同様の図。The same figure as FIG. 6 regarding the pad and pad support part on the opposite side to FIG. 本例の構造に組み込む板ばねの形状の第１例を示す斜視図（Ａ）及び第２例を示す斜視図（Ｂ）。The perspective view (A) which shows the 1st example of the shape of the leaf | plate spring incorporated in the structure of this example, and the perspective view (B) which shows a 2nd example. 本発明の実施の形態の第２例を示す、図５と同様の図。The figure similar to FIG. 5 which shows the 2nd example of embodiment of this invention. 同じく図６と同様の図。The same figure as FIG. 同じく図７と同様の図。The same figure as FIG. 同じく図８と同様の図。The same figure as FIG. 本発明の実施の形態の第３例を示す、図４と同様の図。The figure similar to FIG. 4 which shows the 3rd example of embodiment of this invention. 同じく図２と同様の図。The same figure as FIG. 同じく図５と同様の図。The same figure as FIG. 同じく図６と同様の図。The same figure as FIG. 同じく図７と同様の図。The same figure as FIG. 同じく圧縮ばねを１個取り出して示す斜視図。The perspective view which similarly takes out and shows one compression spring. 本発明の実施の形態の第４例を示す、図５と同様の図。The figure similar to FIG. 5 which shows the 4th example of embodiment of this invention. 同じく図６と同様の図。The same figure as FIG. 同じく図７と同様の図。The same figure as FIG. 同じく圧縮ばねを１個取り出して示す斜視図。The perspective view which similarly takes out and shows one compression spring. 本発明の実施の形態の第５例を示す、図４と同様の図。The figure similar to FIG. 4 which shows the 5th example of embodiment of this invention. 同じく図２と同様の図。The same figure as FIG. 同じく図５と同様の図。The same figure as FIG. 同じく図６と同様の図。The same figure as FIG. 同じく図７と同様の図。The same figure as FIG. 押圧ユニットを１個取り出して、押圧面側から見た斜視図（Ａ）、反対側から見た斜視図（Ｂ）、側面図（Ｃ）、押圧面から見た正投影図（Ｄ）。The perspective view (A) which took out one press unit and was seen from the press surface side, the perspective view (B) seen from the opposite side, the side view (C), and the orthographic view (D) seen from the press surface. 本発明のディスクブレーキ装置を構成する為の鉄道車両用のディスク付車輪の１例を示す断面図。Sectional drawing which shows one example of the wheel with a disk for railway vehicles for comprising the disk brake apparatus of this invention. 同じく固定支持部及びパッドを組み付けたキャリパの構造の１例を示す斜視図。The perspective view which shows an example of the structure of the caliper which similarly assembled | attached the fixed support part and the pad. ディスクの被制動側摩擦面が変位する形態の３例を示す部分断面図。The fragmentary sectional view which shows three examples of the form which the to-be-brake side friction surface of a disk displaces.

［実施の形態の第１例］
図１〜８は、請求項１〜３、５〜７に対応する、本発明の実施の形態の第１例を示している。尚、本例を含めて本発明の特徴は、前述の(A) 〜(C) の様な現象に拘らず、一対のディスク２、２の被制動側摩擦面７、７（図２９参照）と、一対のパッド１９ａ、１９ｂのライニング２１ａ、２１ｂの制動側摩擦面２２、２２との擦れ合い部の面圧が不均一になるのを防止する為の構造にある。その他の部分の構造及び作用に就いては、図３０により先に説明した通りであり、又、基本的には、特許文献４に記載される等により従来から知られている構造と同様である。就いては、前記図３０に記載した構造と同等部分には同一符号を付して、重複する説明を省略若しくは簡略にし、以下、本例の特徴部分、及び先に説明しなかった部分を中心に説明する。 [First example of embodiment]
FIGS. 1-8 has shown the 1st example of embodiment of this invention corresponding to Claims 1-3, 5-7. The features of the present invention including this example are the braked friction surfaces 7 and 7 of the pair of disks 2 and 2 regardless of the phenomena (A) to (C) described above (see FIG. 29). In addition, the surface pressure of the frictional portions 22 and 22 of the linings 21a and 21b of the pair of pads 19a and 19b is prevented from becoming uneven. The structure and operation of the other parts are as described above with reference to FIG. 30, and are basically the same as those conventionally known as described in Patent Document 4. . Therefore, the same parts as those in the structure shown in FIG. 30 are denoted by the same reference numerals, and redundant explanations are omitted or simplified. Hereinafter, the characteristic parts of this example and parts not explained above will be mainly described. Explained.

それぞれが押圧腕１７ａ、１７ｂの先端部に設けられた一対のパッド支持部１８ａ、１８ｂのうちの一方のパッド支持部１８ｂに、それぞれが油圧シリンダ型、又は、エアシリンダ型のアクチュエータ２３を、このパッド支持部１８ｂの長さ方向（上下方向）に互いに直列に並べて、複数組設けている。これら各アクチュエータ２３は、図６に示す様に、シリンダ孔２４内にピストン２５を密に（気密若しくは液密に）嵌装して成る。前記一方のパッド支持部１８ｂの内側面には、支持プレート２６を、軸方向の変位を可能に支持している。即ち、この支持プレート２６の上下両端部に配置した上下一対のアンカピン２７、２７により、この支持プレート２６を前記パッド支持部１７ｂに、軸方向の変位を可能に支持している。且つ、前記パッド１９ｂから前記支持プレート２６に伝えられたブレーキトルクを、前記パッド支持部１７ｂにより支承可能としている。 The hydraulic cylinder type or air cylinder type actuators 23 are respectively connected to one of the pad support portions 18b of the pair of pad support portions 18a and 18b provided at the distal ends of the pressing arms 17a and 17b. A plurality of sets are provided side by side in series in the length direction (vertical direction) of the pad support portion 18b. As shown in FIG. 6, each of these actuators 23 is formed by fitting a piston 25 in a cylinder hole 24 tightly (airtight or liquid tightly). A support plate 26 is supported on the inner side surface of the one pad support portion 18b so as to be capable of axial displacement. That is, the support plate 26 is supported on the pad support portion 17b by a pair of upper and lower anchor pins 27, 27 disposed at both upper and lower ends of the support plate 26 so as to be capable of axial displacement. In addition, the brake torque transmitted from the pad 19b to the support plate 26 can be supported by the pad support portion 17b.

前記支持プレート２６に前記パッド１９ｂを支持する為に、この支持プレート２６の前面に一対の係止突条２８、２８を、径方向に関して互いに離隔した状態で設けている。これら両係止突条２８、２８の互いに対向する面は、前記支持プレート２６の前面から離れるに従って互いに近付く方向に傾斜している。従って、前記両係止突条２８、２８同士の間部分には、開口部の幅が狭く、奥に向かうに従って幅が広くなる、あり溝状の係止部が設けられている。一方、前記パッド１９ｂのプレッシャプレート２０ｂの裏面には、この様な係止部に係止する為の係止凸部２９が設けられている。この係止凸部２９は、前記プレッシャプレート２０ｂの裏面から離れるに従って幅寸法が大きくなる。この様な係止凸部２９は、前記両係止突条２８、２８同士の間の係止部に、前記支持プレート２６の端部から滑り込ませる事で係合させる。これら係止凸部２９と、両係止突条２８、２８から成る係止部とを係合させた状態で、図４から明らかな通り、前記プレッシャプレート２０ｂは前記支持プレート２６に対し、厚さ方向に関する若干の遠近動を可能に支持される。即ち、これら両プレート２０ｂ、２６同士が分離する事はないが、このうちのプレッシャプレート２０ｂの裏面と支持プレート２６の表面との遠近動を可能としている。本例の場合には、これら両プレート２０ｂ、２６の互いに対向する面同士が遠近動する分、この支持プレート２６に対する、このプレッシャプレート２０ｂの揺動変位を可能にしている。 In order to support the pad 19b on the support plate 26, a pair of locking protrusions 28, 28 are provided on the front surface of the support plate 26 so as to be separated from each other in the radial direction. The mutually opposing surfaces of both the locking ridges 28 and 28 are inclined so as to approach each other as the distance from the front surface of the support plate 26 increases. Accordingly, a dovetail-shaped locking portion is provided in a portion between the locking ridges 28, 28. The width of the opening is narrow and the width increases toward the back. On the other hand, on the back surface of the pressure plate 20b of the pad 19b, a locking projection 29 for locking to such a locking portion is provided. The width of the locking projection 29 increases as the distance from the back surface of the pressure plate 20b increases. Such a locking projection 29 is engaged with a locking portion between the locking protrusions 28, 28 by sliding from the end of the support plate 26. As is apparent from FIG. 4, the pressure plate 20 b is thicker than the support plate 26 in a state in which these locking projections 29 are engaged with the locking portions including both locking protrusions 28 and 28. It is supported to allow a slight movement in the vertical direction. That is, the plates 20b and 26 are not separated from each other, but the back and forth movement of the pressure plate 20b and the surface of the support plate 26 are enabled. In the case of this example, the pressure plate 20b can be oscillated and displaced with respect to the support plate 26 by the distance between the opposing surfaces of the plates 20b and 26.

但し、この揺動変位に拘らず、前記パッド１９ｂを構成するライニング２１ｂの制動側摩擦面２２と、前記ディスク２の被制動側摩擦面７との当接圧が、これら両摩擦面２２、７同士の当接面に全体に亙って十分に高く、且つ、ほぼ均一になる様に、プレッシャプレート２０ｂの裏面と支持プレート２６の表面との間に、図３、５に示す様に、一対の板ばね３０ａ、３０ｂを挟持している。これら両板ばね３０ａ、３０ｂはそれぞれ、図８の（Ａ）又は（Ｂ）に示す様に、平板状の基板部３１ａ、３１ｂと、この基板部３１ａ、３１ｂの幅方向端縁から９０度未満（例えば４０〜６０度程度）曲げ起こされた、曲げ起こし部３２ａ、３２ｂとから成る。 However, regardless of the swing displacement, the contact pressure between the braking side friction surface 22 of the lining 21b constituting the pad 19b and the braking side friction surface 7 of the disk 2 causes these friction surfaces 22, 7 to be in contact with each other. As shown in FIGS. 3 and 5, a pair of contact surfaces between each other is provided between the back surface of the pressure plate 20 b and the front surface of the support plate 26 so as to be sufficiently high and substantially uniform over the entire surface. The leaf springs 30a and 30b are sandwiched. As shown in FIG. 8A or FIG. 8B, the two plate springs 30a and 30b are each less than 90 degrees from the flat plate-like substrate portions 31a and 31b and the widthwise edges of the substrate portions 31a and 31b. It consists of bent raised portions 32a and 32b (for example, about 40 to 60 degrees).

尚、図８のうちの（Ａ）には、長尺な一体型の板ばね３０ａ、３０ｂを、（Ｂ）には寸法が短い分割型の板ばね３０ａ、３０ｂを、それぞれ示している。何れにしても、前記曲げ起こし部３２ａ、３２ｂの、軸方向に関する高さは、前記両係止突条２８、２８の高さよりも大きい。それぞれが曲げ起こし部３２ａ、３２ｂと基板部３１ａ、３１ｂとから成る、前記両板ばね３０ａ、３０ｂは、それぞれの基板部３１ａ、３１ｂを前記支持プレート２６の幅方向両端部に、ねじ３３、３３等により支持固定する。この状態で、前記両曲げ起こし部３２ａ、３２ｂは、前記両係止突条２８、２８を幅方向両側から挟む位置に存在し、それぞれの先端縁がこれら両係止突条２８、２８よりも軸方向に突出する。 In FIG. 8, (A) shows the long integrated leaf springs 30a and 30b, and (B) shows the split leaf springs 30a and 30b having short dimensions. In any case, the height of the bent raised portions 32a, 32b in the axial direction is larger than the height of the locking protrusions 28, 28. The plate springs 30a and 30b, each of which is formed of bent raised portions 32a and 32b and substrate portions 31a and 31b, are provided with screws 33 and 33 at both ends in the width direction of the support plate 26. Support and fix with etc. In this state, the two bent raising portions 32a and 32b are present at positions sandwiching the locking ridges 28 and 28 from both sides in the width direction, and the respective leading edges thereof are more than the locking ridges 28 and 28. Project in the axial direction.

従って、これら両係止突条２８、２８から成る係止部と前記係止凸部２９とを係合させる事により、前記支持プレート２６に対して前記プレッシャプレート２０ｂを組み付けた状態では、前記両曲げ起こし部３２ａ、３２ｂがこのプレッシャプレート２０ｂの裏面を弾性的に押圧する。そして、他の外力が作用しない状態では、図１、４、６に示す様に、前記プレッシャプレート２０ｂの裏面と前記支持プレート２６の表面とを最も離隔した状態とする。この状態で、このプレッシャプレート２０ｂの裏面と前記両係止突条２８、２８の先端縁とが離隔すると同時に、前記係止凸部２９の先端面と前記支持プレート２６の表面とが離隔する。そして、これら各部分が離隔した分、前記プレッシャプレート２０ｂが前記支持プレート２６に対して、前記両曲げ起こし部３２ａ、３２ｂの弾性変形に基づいて、揺動変位可能になる。 Therefore, by engaging the locking projections 29 formed by the locking protrusions 28, 28 with the locking projections 29, the pressure plate 20b is assembled to the support plate 26 in the state where both the pressure plates 20b are assembled. The bent raised portions 32a and 32b elastically press the back surface of the pressure plate 20b. In a state where no other external force is applied, the back surface of the pressure plate 20b and the surface of the support plate 26 are most separated as shown in FIGS. In this state, the back surface of the pressure plate 20b and the leading edges of the locking protrusions 28 and 28 are separated from each other, and at the same time, the leading end surface of the locking projection 29 and the surface of the support plate 26 are separated. The pressure plate 20b can be oscillated and displaced with respect to the support plate 26 based on the elastic deformation of the two bent raising portions 32a and 32b by the distance between these portions.

以上の説明は、アクチュエータ２３を設けた一方のパッド支持部１８ｂに対して、前記パッド１９ｂを揺動変位可能に支持する為の構造に就いて示した。本例の場合には、アクチュエータを設けていない、他方のパッド支持部１８ａに対しても前記パッド１９ａを、図７に示す様な構造により、揺動変位可能に支持している。尚、このパッド１９ａを前記パッド支持部１７ａに支持する部分の構造に関しても、前記一方のパッド支持部１７ｂの場合と同様であるから、同等部分には同一符号を付して、重複する説明を省略する。 In the above description, the structure for supporting the pad 19b so as to be able to swing and displace with respect to the one pad support portion 18b provided with the actuator 23 has been shown. In the case of this example, the pad 19a is supported so as to be swingable and displaceable by the structure as shown in FIG. Note that the structure of the portion that supports the pad 19a on the pad support portion 17a is the same as that of the one pad support portion 17b. Omitted.

上述の様に構成する本例のディスクブレーキ装置に組み込まれる、前記両パッド１９ａ、１９ｂは、ぞれぞれ径方向に離隔して配置した、それぞれ一対ずつの板ばね３０ａ、３０ｂの存在に基づき、径方向に関して外寄り部分と内寄り部分とが軸方向に関して相対変位する方向に揺動変位する。例えば、制動時に前記両パッド１９ａ、１９ｂの制動側摩擦面２２、２２を前記両ディスク２、２の被制動側摩擦面７、７に押し付けると、この押し付けに伴って前記両パッド１９ａ、１９ｂに加わる反力に基づき、前記キャリパ１２を構成する、前記両押圧腕１７ａ、１７ｂが弾性変形する。そして、これら両押圧腕１７ａ、１７ｂの先端部に設けた前記両パッド支持部１８ａ、１８ｂの内側面が、径方向外方に向うに従って互いの間隔が広がる方向に弾性変形する。 The two pads 19a and 19b incorporated in the disc brake device of this example configured as described above are based on the existence of a pair of leaf springs 30a and 30b, respectively, which are spaced apart from each other in the radial direction. The outer portion and the inner portion in the radial direction are oscillated and displaced in a direction in which they are relatively displaced in the axial direction. For example, when the braking side friction surfaces 22 and 22 of the two pads 19a and 19b are pressed against the brake side friction surfaces 7 and 7 of the two disks 2 and 2 during braking, the two pads 19a and 19b are pressed against the pads 19a and 19b. Based on the reaction force applied, the pressing arms 17a and 17b constituting the caliper 12 are elastically deformed. Then, the inner side surfaces of the pad support portions 18a and 18b provided at the distal ends of the pressing arms 17a and 17b are elastically deformed in a direction in which the distance between them increases toward the outer side in the radial direction.

この様に、前記両パッド支持部１８ａ、１８ｂの内側面同士が非平行になると、これら両パッド支持部１８ａ、１８ｂに支持された前記両パッド１９ａ、１９ｂが、径方向内側に配置した板ばね３０ａの曲げ起こし部３２ａを弾性的に押し潰しつつ揺動変位する。そして、前記両パッド１９ａ、１９ｂを構成するライニング２１ａ、２１ｂの制動側摩擦面２２、２２と、前記両ディスク２、２の被制動側摩擦面７、７とを平行なままに維持する。これら各摩擦面２２、７同士が、前記キャリパ１２の弾性変形以外の原因で非平行になる傾向になった場合でも、非平行になる方向及びその程度に応じて、前記各板ばね３０ａ、３０ｂの曲げ起こし部３２ａ、３２ｂのうちの何れかの曲げ起こし部３２ａ、３２ｂが適正量だけ押し潰される。そして、前記キャリパ１２が弾性変形した場合と同様に、前記各摩擦面２２、７同士を平行なままに維持する。 In this way, when the inner side surfaces of the two pad support portions 18a and 18b are not parallel to each other, the two pads 19a and 19b supported by the two pad support portions 18a and 18b are arranged on the radially inner side. The bending raising part 32a of 30a is rocked and displaced while being elastically crushed. The braking side friction surfaces 22 and 22 of the linings 21a and 21b constituting the both pads 19a and 19b and the braked friction surfaces 7 and 7 of the disks 2 and 2 are maintained in parallel. Even when the friction surfaces 22 and 7 tend to be non-parallel due to a cause other than the elastic deformation of the caliper 12, the leaf springs 30a and 30b are changed depending on the non-parallel direction and the degree thereof. Any one of the bent raised portions 32a and 32b of the bent raised portions 32a and 32b is crushed by an appropriate amount. Then, as in the case where the caliper 12 is elastically deformed, the friction surfaces 22 and 7 are maintained in parallel.

この為、本例のディスクブレーキ装置によれば、前記キャリパ１２の弾性変形や前記両ディスク２、２の偏摩耗、更にはこれら両ディスク２、２の熱変形に拘らず、前記各摩擦面７、２２同士を均一に当接させる事ができる。そして、前記両ライニング２１ａ、２１ｂが偏磨耗する事を防止できる。又、前記各アクチュエータ２３が発生する推力と前記各摩擦面７、２２同士の摩擦により得られる制動力とを関連付けたままにできて、安定した制動力を得られる。尚、鉄道車両用のブレーキ装置の場合、レールと車輪との接触部に作用する摩擦力が限られており、従って、前記両ディスク２、２と前記両ライニング２１ａ、２１ｂとの擦れ合い部に作用させる摩擦力に関しても限られた値に止まる。従って、前記両パッド１９ａ、１９ｂを前記各板ばね３０ａ、３０ｂを介して前記両ディスク２、２に押し付けても、必要十分な押し付け力を確保できる。 For this reason, according to the disc brake device of this example, each friction surface 7 is independent of the elastic deformation of the caliper 12, the partial wear of the discs 2 and 2, and the thermal deformation of the discs 2 and 2. , 22 can be brought into contact with each other uniformly. And it can prevent that both said linings 21a and 21b wear out. Further, the thrust generated by each actuator 23 and the braking force obtained by the friction between the friction surfaces 7 and 22 can be kept associated with each other, and a stable braking force can be obtained. In the case of a brake device for a railway vehicle, the frictional force acting on the contact portion between the rail and the wheel is limited, so that the frictional portion between the two disks 2 and 2 and the two linings 21a and 21b is limited. The applied frictional force is limited to a limited value. Therefore, even if both the pads 19a and 19b are pressed against the both disks 2 and 2 via the leaf springs 30a and 30b, a necessary and sufficient pressing force can be secured.

上述の様に本例の場合には、前記両パッド支持部１８ａ、１８ｂの内側面に前記各板ばね３０ａ、３０ｂを、径方向に離隔して配置するのみの、簡単な構造で、前記各摩擦面２２、７同士を平行なままに維持できる。この為、各部の信頼性及び耐久性を考慮しても、これら各摩擦面２２、７同士を平行なままに維持する為の構造を小型且つ軽量に構成できて、前記両パッド１９ａ、１９ｂのライニング２１ａ、２１ｂが偏磨耗する事を防止すると共に安定した制動力を得られる構造を、低コストで実現できる。 As described above, in the case of this example, the leaf springs 30a and 30b are simply arranged on the inner side surfaces of the pad support portions 18a and 18b so as to be separated from each other in the radial direction. The friction surfaces 22 and 7 can be maintained parallel to each other. For this reason, even if the reliability and durability of each part are taken into consideration, the structure for maintaining the friction surfaces 22 and 7 in parallel with each other can be configured to be small and light, and the pads 19a and 19b A structure capable of preventing the linings 21a and 21b from being unevenly worn and obtaining a stable braking force can be realized at low cost.

［実施の形態の第２例］
図９〜１２も、請求項１〜３、５〜７に対応する、本発明の実施の形態の第２例を示している。本例の場合には、板ばね３０ｃ、３０ｄを構成する曲げ起こし部３２ｃ、３２ｄを、基端部３１ｃ、３１ｄの片側縁の複数箇所に設けている。これら各曲げ起こし部３２ｃ、３２ｄの設置位置は、両パッド１９ａ、１９ｂ（図３０参照）を構成するライニング２１ａ、２１ｂの構造との関係で規制している。即ち、これら両パッド１９ａ、１９ｂのライニング２１ａ、２１ｂは、それぞれ複数枚のセグメント３４ａ〜３４ｄを（バックプレートを介して）プレッシャプレート２０ａ、２０ｂに添着固定して成る。前記各曲げ起こし部３２ｃ、３２ｄは、前記各セグメント３４ａ〜３４ｄの径方向両端部の、ほぼ円周方向中央部を押圧する様にしている。そして、前記両プレッシャプレート２０ａ、２０ｂを僅かに弾性変形させつつ、前記各セグメント３４ａ〜３４ｄ毎に分割された前記両ライニング２１ａ、２１ｂを両ディスク２、２の被制動側摩擦面７、７（図２９参照）に、より均一に当接させる様にしている。本例の場合、前記各曲げ起こし部３２ｃ、３２ｄの幅寸法を小さくした分、前記各板ばね３０ｃ、３０ｄを構成する弾性金属板の厚さを大きくして、前記各曲げ起こし部３２ｃ、３２ｄの弾性を確保している。
板ばね３０ｃ、３０ｄの形状を異ならせた以外の部分の構成及び作用は、上述した実施の形態の第１例と同様であるから、同等部分には同一符号を付して、重複する説明は省略する。 [Second Example of Embodiment]
9 to 12 also show a second example of the embodiment of the present invention corresponding to claims 1 to 3 and 5 to 7. In the case of this example, bending raising portions 32c and 32d constituting the leaf springs 30c and 30d are provided at a plurality of locations on one side edge of the base end portions 31c and 31d. The installation positions of the bent raising portions 32c and 32d are restricted in relation to the structure of the linings 21a and 21b constituting both pads 19a and 19b (see FIG. 30). That is, the linings 21a and 21b of these pads 19a and 19b are each formed by attaching and fixing a plurality of segments 34a to 34d to the pressure plates 20a and 20b (via the back plate). Each of the bent raised portions 32c and 32d presses substantially the central portion in the circumferential direction at both radial ends of the segments 34a to 34d. The both linings 21a and 21b divided into the segments 34a to 34d are made to be elastically deformed by the pressure plates 20a and 20b, and the brake side friction surfaces 7 and 7 ( (See FIG. 29). In the case of this example, the thickness of the elastic metal plate constituting each of the leaf springs 30c, 30d is increased by the reduction in the width dimension of each of the bending raising portions 32c, 32d, and the bending raising portions 32c, 32d The elasticity of the is secured.
Since the configuration and operation of the parts other than the shapes of the leaf springs 30c and 30d are the same as those of the first example of the above-described embodiment, the same parts are denoted by the same reference numerals, and overlapping description is omitted. Omitted.

［実施の形態の第３例］
図１３〜１８は、請求項１〜３、５、６、８、９に対応する、本発明の実施の形態の第３例を示している。本例の場合には、一対のパッド１９ａ、１９ｂの径方向外端部及び内端部を押圧する為の弾性部材として、圧縮コイルばね３５、３５を使用している。この為に、これら各圧縮コイルばね３５、３５の基部を、両パッド支持部１８ａ、１８ｂの径方向両端部の複数箇所に形成した保持凹部３６（図１７参照）に緩く内嵌している。そして、前記各圧縮コイルばね３５、３５の先端面を、前記両パッド１９ａ、１９ｂを構成するプレッシャプレート２０ａ、２０ｂの裏面に突き当てている。前記各圧縮コイルばね３５、３５の先端面を前記両プレッシャプレート２０ａ、２０ｂの裏面に突き当てる位置は、上述した実施の形態の第２例で、前記各曲げ起こし部３２ｃ、３２ｄの先端部を両プレッシャプレート２０ａ、２０ｂの裏面に当接させる場合と同様に、各セグメント３４ａ〜３４ｄの径方向両端部の、ほぼ円周方向中央部としている。
弾性部材を板ばねから圧縮コイルばね３５、３５に変更した以外の部分の構成及び作用は、上述した実施の形態の第２例と同様であるから、同等部分には同一符号を付して、重複する説明は省略する。 [Third example of embodiment]
FIGS. 13-18 has shown the 3rd example of embodiment of this invention corresponding to Claims 1-3, 5, 6, 8, and 9. FIG. In the case of this example, compression coil springs 35 and 35 are used as elastic members for pressing the radially outer end and inner end of the pair of pads 19a and 19b. For this purpose, the base portions of these compression coil springs 35 and 35 are loosely fitted into holding recesses 36 (see FIG. 17) formed at a plurality of locations on both ends in the radial direction of both pad support portions 18a and 18b. And the front end surface of each said compression coil spring 35 and 35 is contact | abutted on the back surface of the pressure plates 20a and 20b which comprise both said pads 19a and 19b. The position where the front end surfaces of the compression coil springs 35 and 35 abut against the back surfaces of the pressure plates 20a and 20b is the second example of the embodiment described above, and the front end portions of the bending raising portions 32c and 32d are arranged. Similarly to the case where the pressure plates 20a and 20b are brought into contact with the back surfaces of the pressure plates 20a and 20b, the central portions of the segments 34a to 34d are substantially circumferentially located at both ends in the radial direction.
Since the configuration and operation of the portion other than changing the elastic member from the leaf spring to the compression coil springs 35 and 35 are the same as in the second example of the above-described embodiment, the same reference numerals are given to the equivalent portions, A duplicate description is omitted.

［実施の形態の第４例］
図１９〜２２も、請求項１〜３、５、６、８、９に対応する、本発明の実施の形態の第４例を示している。本例の場合には、一対のパッド１９ａ、１９ｂの径方向外端部及び内端部を押圧する為の弾性部材である圧縮コイルばね３５ａ、３５ａの先端部に鍔部３７を設け、この鍔部３７を、前記両パッド１９ａ、１９ｂを構成するプレッシャプレート２０ａ、２０ｂの裏面に突き当てている。
圧縮コイルばね３５ａ、３５ａの形状を変更した以外の部分の構成及び作用は、上述した実施の形態の第３例と同様であるから、同等部分には同一符号を付して、重複する説明は省略する。 [Fourth Example of Embodiment]
19 to 22 show a fourth example of the embodiment of the invention corresponding to claims 1 to 3, 5, 6, 8, and 9, respectively. In the case of this example, a flange 37 is provided at the tip of compression coil springs 35a and 35a, which are elastic members for pressing the radially outer end and inner end of the pair of pads 19a and 19b. The portion 37 is abutted against the back surfaces of the pressure plates 20a and 20b constituting the pads 19a and 19b.
Since the configuration and operation of the portion other than the shape of the compression coil springs 35a and 35a are the same as those in the third example of the above-described embodiment, the same parts are denoted by the same reference numerals, and redundant description is omitted. Omitted.

［実施の形態の第５例］
図２３〜２８も、請求項１〜３、５、６、８、９に対応する、本発明の実施の形態の第４例を示している。本例の場合には、一対のパッド１９ａ、１９ｂの径方向外端部及び内端部を押圧する為の弾性部材として、皿板ばね３８、３８を組み込んだ押圧ユニット３９、３９を使用している。これら各押圧ユニット３９、３９はそれぞれ、ガイドピン４０に押圧プレート４１と前記皿板ばね３８とを外嵌して成る。そして、このうちのガイドピン４０を、支持プレート２６に形成したガイド孔４２に軸方向の変位を可能に内嵌すると共に、前記押圧プレート４１を両パッド１９ａ、１９ｂを構成するプレッシャプレート２０ａ、２０ｂの裏面に突き当てている。この状態で、前記皿板ばね３８を、前記支持プレート２６と前記押圧プレート４１との間で弾性的に圧縮している。前記各押圧ユニット３９、３９の押圧プレート４１を前記両プレッシャプレート２０ａ、２０ｂの裏面に突き当てる位置は、前述した実施の形態の第２例で、前記各曲げ起こし部３２ｃ、３２ｄの先端部を両プレッシャプレート２０ａ、２０ｂの裏面に当接させる場合と同様に、各セグメント３４ａ〜３４ｄの径方向両端部の、ほぼ円周方向中央部としている。 [Fifth Example of Embodiment]
23 to 28 also show a fourth example of the embodiment of the invention corresponding to claims 1 to 3, 5, 6, 8, and 9. In the case of this example, as the elastic members for pressing the radially outer end and inner end of the pair of pads 19a, 19b, press units 39, 39 incorporating disc springs 38, 38 are used. Yes. Each of these pressing units 39, 39 is formed by fitting a pressing plate 41 and the disc spring 38 to a guide pin 40. Of these, the guide pin 40 is fitted in a guide hole 42 formed in the support plate 26 so as to be axially displaceable, and the pressing plate 41 is attached to the pressure plates 20a, 20b constituting both pads 19a, 19b. It is abutting against the back of the. In this state, the disc spring 38 is elastically compressed between the support plate 26 and the pressing plate 41. The position where the pressing plate 41 of each pressing unit 39, 39 abuts against the back surface of each of the pressure plates 20a, 20b is the second example of the above-described embodiment, and the tip of each bending raising portion 32c, 32d is Similarly to the case where the pressure plates 20a and 20b are brought into contact with the back surfaces of the pressure plates 20a and 20b, the central portions of the segments 34a to 34d are substantially circumferentially located at both ends in the radial direction.

又、本例の場合には、図２６に示したアクチュエータ２３ａの構造を、前述の図６に示した第１例の構造の場合と異ならせている。このアクチュエータ２３ａに関しても、圧力流体の送り込みによりピストン２５ａを突出させ、パッド１９ｂをディスク２（図２９参照）に押し付ける様にしている。但し、このアクチュエータ２３ａの構造に関しては、従来から知られており、又、本発明の要旨とも関係しないので、詳しい説明は省略する。尚、本例の構造を有するアクチュエータ２３ａを他の実施の形態の構造に組み込む事もできるし、他の実施の形態の構造に組み込んだアクチュエータ２３（例えば図６参照）を本例の構造に組み込む事もできる。
その他、弾性部材を板ばねから皿板ばね３８に変更した以外の部分の構成及び作用は、上述した実施の形態の第２例と同様であるから、同等部分には同一符号を付して、重複する説明は省略する。 In the case of this example, the structure of the actuator 23a shown in FIG. 26 is different from the structure of the first example shown in FIG. With respect to the actuator 23a as well, the piston 25a is protruded by sending in the pressure fluid, and the pad 19b is pressed against the disk 2 (see FIG. 29). However, the structure of the actuator 23a has been known in the art and is not related to the gist of the present invention, so a detailed description is omitted. The actuator 23a having the structure of this example can be incorporated in the structure of another embodiment, and the actuator 23 (see, for example, FIG. 6) incorporated in the structure of another embodiment is incorporated in the structure of this example. You can also do things.
In addition, since the configuration and operation of the portion other than changing the elastic member from the leaf spring to the disc leaf spring 38 are the same as those in the second example of the embodiment described above, the same reference numerals are given to the equivalent portions, A duplicate description is omitted.

図示の例では、固定フレームに対してキャリパを、軸方向の変位を可能に支持すると共に、一対のパッド支持部のうちの一方のパッド支持部にのみアクチュエータを組み込んだ、フローティングキャリパ型の構造に就いて説明した。但し、本発明は、固定フレームに対してキャリパを、軸方向の変位を阻止した状態で支持する代わりに、一対のパッド支持部の両方に、それぞれアクチュエータを組み込んだ構造で実施する事もできる。この場合には、前記固定フレームと前記キャリパとを一体に構成する事もできる。或いは、特許文献８に記載されている構造の様に、アクチュエータをパッド支持部以外の部分に設置する構造を採用する事もできる。この場合に、アクチュエータが収縮する際に制動力を発生させる構造も、採用可能である。 In the example shown in the drawing, the caliper is supported with respect to the fixed frame so as to be capable of displacement in the axial direction, and the floating caliper type structure in which the actuator is incorporated only in one of the pad support portions of the pair of pad support portions. I explained. However, the present invention can be implemented with a structure in which actuators are incorporated in both of the pair of pad support portions instead of supporting the caliper with respect to the fixed frame in a state in which axial displacement is prevented. In this case, the fixed frame and the caliper can be integrally formed. Or the structure which installs an actuator in parts other than a pad support part like the structure described in patent document 8 is also employable. In this case, a structure that generates a braking force when the actuator contracts can be employed.

又、本発明を実施する場合に、請求項２に記載した発明の様に、各弾性部材を両パッド支持部と両プレッシャプレートとの間に挟持して、これら両パッド支持部に支持されたパッドを当該パッド支持部に対し揺動変位を可能に支持する事が好ましい。但し、キャリパを固定支持部に対し若干の揺動変位を可能に支持する構造を採用すれば、一方のパッドのみを、本発明の構造により、パッド支持部に対して揺動変位可能に支持し、他方のパッドに関しては、パッド支持部に対し変位不能に支持する事もできる。この場合に於いて、前記固定支持部に対する前記キャリパの揺動支持部には、ブレーキトルクが加わるが、このブレーキトルクは、何れにしても固定支持部に対するキャリパの支持部に加わる。従って、前述の特許文献３に記載された発明の構造に比べれば、コスト上昇を低く抑えられる。又、キャリパを固定支持部に対し揺動変位を不能に支持する代わりに、前記他方のパッドを前記パッド支持部に、例えば円筒状の凸面と円筒状の凹面との係合により、揺動変位を可能に支持する事もできる。この様な凸面と凹面との係合により揺動変位を許容する構造は、本発明の構造に比べてコストが嵩むが、片側のみであれば、コスト上昇を少なく抑えられる。
更に、各弾性部材として、硬質ゴムの如きエラストマーを使用する事もできる。 In carrying out the present invention, as in the invention described in claim 2, each elastic member is sandwiched between both pad support portions and both pressure plates, and supported by these both pad support portions. It is preferable to support the pad so that the pad can be oscillated and displaced with respect to the pad support portion. However, if a structure that supports the caliper with respect to the fixed support portion so as to be able to be slightly swung is adopted, only one pad is supported so as to be able to be swung with respect to the pad support portion by the structure of the present invention. The other pad can be supported so as not to be displaced with respect to the pad support portion. In this case, a brake torque is applied to the caliper support portion of the caliper relative to the fixed support portion, and this brake torque is applied to the caliper support portion relative to the fixed support portion in any case. Therefore, compared with the structure of the invention described in Patent Document 3, the cost increase can be suppressed to a low level. Further, instead of supporting the caliper with respect to the fixed support portion so that the rocking displacement is impossible, the other pad is swung to the pad support portion by, for example, engagement of a cylindrical convex surface and a cylindrical concave surface. Can also be supported. Such a structure that allows the oscillating displacement by engagement between the convex surface and the concave surface is more costly than the structure of the present invention, but if only one side is used, an increase in cost can be suppressed to a small extent.
Furthermore, an elastomer such as hard rubber can be used as each elastic member.

１ディスク付車輪
２ディスク
３車輪
４スプリングピン
５ボルト
６ナット
７被制動側摩擦面
８固定フレーム
９取付部
１０垂下部
１１支持軸
１２キャリパ
１３基部
１４支持板部
１５ガイド筒部
１６ベローズ
１７ａ、１７ｂ押圧腕
１８ａ、１８ｂパッド支持部
１９ａ、１９ｂパッド
２０ａ、２０ｂプレッシャプレート
２１ａ、２１ｂライニング
２２制動側摩擦面
２３、２３ａアクチュエータ
２４シリンダ孔
２５、２５ａピストン
２６支持プレート
２７アンカピン
２８係止突条
２９係止凸部
３０ａ、３０ｂ、３０ｃ、３０ｄ板ばね
３１ａ、３１ｂ、３１ｃ、３１ｄ基板部
３２ａ、３２ｂ、３２ｃ、３２ｄ曲げ起し部
３３ねじ
３４ａ、３４ｂ、３４ｃ、３４ｄセグメント
３５、３５ａ圧縮コイルばね
３６保持凹部
３７鍔部
３８皿板ばね
３９押圧ユニット
４０ガイドピン
４１押圧プレート
４２ガイド孔 DESCRIPTION OF SYMBOLS 1 Wheel with disk 2 Disk 3 Wheel 4 Spring pin 5 Bolt 6 Nut 7 Braking side frictional surface 8 Fixed frame 9 Mounting part 10 Hanging part 11 Support shaft 12 Caliper 13 Base 14 Support plate part 15 Guide cylinder part 16 Bellows 17a, 17b Pressing arm 18a, 18b Pad support portion 19a, 19b Pad 20a, 20b Pressure plate 21a, 21b Lining 22 Braking side friction surface 23, 23a Actuator 24 Cylinder hole 25, 25a Piston 26 Support plate 27 Anchor pin 28 Locking protrusion 29 Locking Convex part 30a, 30b, 30c, 30d Leaf spring 31a, 31b, 31c, 31d Substrate part 32a, 32b, 32c, 32d Bending part 33 Screw 34a, 34b, 34c, 34d Segment 35, 35a Compression coil spring 3 6 Holding recess 37 Hook 38 Disc spring 39 Press unit 40 Guide pin 41 Press plate 42 Guide hole

Claims

A pair of discs that are supported and fixed concentrically with the wheel on both side surfaces of the wheel, and each outer surface is a braking side friction surface in a direction orthogonal to the rotation center axis of the wheel, and a peripheral portion of the wheel A caliper having a fixed support portion provided on the base, a base portion supported by the fixed support portion, and a pair of pressing arms extending from the base portion to a position sandwiching the both disks from both sides in the axial direction, and a pressure plate And a lining attached to a surface of the pressure plate facing the outer surface of the two discs, and the pressure plate of the pressure plate at a tip portion of the pressing arms at a portion facing the outer surfaces of the two discs. A pair of pads supported by the pair of pad support portions provided, and an actuator for moving the two pads far and away. In a disc brake device for braking by pressing a braking side friction surface of a pad lining against both of the braked friction surfaces, at least one of the pad support portions, and the pad support portion By sandwiching a plurality of elastic members between the pressure plate and the supported pressure plate while being displaced inward and outward with respect to the radial direction, the pad supported by the at least one pad support portion is A disc brake device characterized by supporting swinging displacement.

By sandwiching each of the elastic members in a state of being displaced inward and outward with respect to the radial direction, a plurality of each between the two pad support portions and the two pressure plates, the two pads with respect to the two pad support portions, The disc brake device according to claim 1, wherein each disc brake device is supported so as to be capable of swinging displacement.

A base portion of the caliper is supported on the fixed support portion so as to be able to be displaced along a support shaft parallel to the rotation center axis of the wheel, and is provided at the tip portions of the both pressing arms, respectively. The disc brake device according to any one of claims 1 to 2, wherein the actuator is provided only in one of the pad support portions.

The base part of the caliper is supported by the fixed support part in a state in which the displacement of the wheel in the rotational direction is prevented, and the pad support parts provided at the tip parts of the pressing arms are respectively provided on the pad support parts. The disc brake device according to claim 1, wherein an actuator is provided.

Among the linings constituting the two pads, a circumferential concave groove or a circumferential discontinuity that is continuous from one end edge to the other end edge in the circumferential direction is present in a radially intermediate portion of the lining constituting the both pads. The disc brake device described in any one of the above.

A part of the lining that constitutes both the pads has a radially concave groove or a radially discontinuous portion that is continuous from the inner peripheral edge to the outer peripheral edge in a plurality of portions of the intermediate portion in the circumferential direction, each being long in the radial direction The disc brake device according to any one of claims 1 to 5.

Each said elastic member is a leaf | plate spring long installed in the direction along these both pad support parts installed in the width direction both ends part of the said both pad support parts. Disc brake device described in 1.

Each of the elastic members is any one selected from a compression coil spring, a disc spring, and an elastomer block, and a plurality of elastic members are arranged on each of the radially outer side and the radially inner side. The disc brake device according to any one of claims 1 to 6, wherein the disc brake device is sandwiched between a support portion and the pressure plate.

A plurality of linings of the pads are formed by a circumferential groove or circumferential discontinuity continuous from one edge to the other edge in the circumferential direction, and a radial groove or radial discontinuity that is long in the radial direction. And is attached to the inner surface of the pressure plate in a state of being divided into a plurality of portions, and the elastic members are positioned so as to overlap the respective portions in the axial direction between the pad support portion and the pressure plate. The disc brake device according to claim 8, which is sandwiched between the disc brake devices.