JP2017061976A - Disc brake and railway vehicle disc brake - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a disc brake in which both a piston-side brake pad assembly and an anti-piston side brake pad assembly can obtain the substantially-same clearances from a disc rotor face at the release of a brake, and which are eliminated in drag at normal traveling.SOLUTION: A disc brake 100 comprises: a floating caliper 21 having a base part 15 which is slidably pivoted to a support 13, and a pair of pressing arms which are extended from the base part 15; brake pad assemblies which are arranged at tips of the pair of the pressing arms, respectively, so as to oppose a side face of the disc rotor 23; a drive piston 29 which is arranged at one pressing arm for driving one brake pad assembly toward the side face of the disc rotor 23; and a caliper return mechanism 11 which is interposed between the one brake pad assembly and the support 13 so that a prescribed amount of a displacement amount of the one brake pad assembly reaches a displacement amount of the floating caliper 21.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a disk brake and a railway vehicle disk brake.

In a railway vehicle or the like, a disc brake device is provided for each wheel, and a braking force is generated by friction when the control member is pressed against the disc (see, for example, Patent Document 1).
As shown in FIGS. 23 and 24, the disc brake device 501 is provided with a pair of restrictors 505 on both sides of a disc 503 that rotates integrally with a wheel with a predetermined clearance from the disc surface. These control elements 505 are supported by a caliper 507. Either one (upper part in FIG. 23) of the control device 505 is supported via a piston 509 provided in the caliper 507, and supplies the pressure fluid to the oil supply port 511 of the piston 509 toward the disc 503. Can be pushed out.

  On the other hand, the caliper 507 is connected to the support frame 517 by two parallel support pins 515 that are parallel to the rotation shaft 513 of the disk 503 and equidistant from the rotation shaft 513. Therefore, the caliper 507 is movable in the support pin axis direction with respect to the support frame 517. The support frame 517 is fixed at a predetermined position of the carriage with a plurality of bolts.

  With such a configuration, when a pressure fluid is supplied from the oil supply port 511, the piston 509 is operated to the extension side, and the control member 505 is pushed out toward the disk 503. At the same time, the reaction force attracts the brake 505 disposed on the opposite side across the disk 503. As a result, the pair of restrictors 505 sandwich the disc 503 from both sides, and a braking force is generated by friction at that time.

  Further, as shown in FIG. 25, the disc brake device 501 includes two sleeves 519 in which two parallel support pins 515 that connect the caliper 507 and the support frame 517 are slidably fitted, and the sleeves. And an anti-vibration rubber 521 provided on the outer periphery of 519. The two sleeves 519 are supported by mounting holes 523 formed in the support frame 517 via vibration-proof rubber 521, respectively. According to the disc brake device 501, during braking, the caliper 507 appropriately moves in the direction of the support pin shaft, and prevents the brake control member 505 from coming into contact with one another. Further, since the support structure of the support pins 515 is the same both in the upper and lower directions, the followability of the caliper 507 is stabilized, and uneven wear of the restrictor 505 is minimized.

JP 11-141579 A

  However, the conventional disc brake device 501 described above has a problem that the pad clearance on the anti-piston side is not forcibly opened after the brake is released, and the pad clearance on the anti-piston side is opened only by disturbance such as wheel movement. For this reason, the anti-piston-side restrictor 505 (brake pad) is likely to be dragged, which may cause uneven wear. In addition, when the disc brake device 501 is employed in a railway vehicle disc brake, there is a possibility that the starting torque of the vehicle may increase due to dragging of the anti-piston side brake 505.

  Due to these problems, there has been a request for the development of a disc brake that can forcibly open the pad clearance on the anti-piston side when the brake is released. In this case, it is more preferable that the pad clearances on the piston side and the anti-piston side in the floating caliper are evenly allocated in order to prevent dragging.

  As described above, especially in a disc brake used in a railway vehicle or the like, it is desirable to provide a gap so that the lining surface and the disc rotor surface do not come into contact with each other when the brake is released because the vehicle runs at high speed. On the other hand, the caliper attached to the bogie frame that suspends the wheel is structurally mounted with the caliper on the spring and the disc rotor under the spring. For this reason, the relative movement amount is larger than the clearance obtained when the brake is released. As a result, especially in the case of a floating caliper, drag resistance may increase.

  The present invention has been made in view of the above situation, and the object thereof is a floating caliper. When the brake is released, the piston-side brake pad assembly and the anti-piston-side brake pad assembly have substantially the same clearance from the disk rotor surface. Another object of the present invention is to provide a disc brake and a railcar disc brake that can eliminate dragging during normal running.

The above object of the present invention is achieved by the following configuration.
(1) A base portion slidably supported via a guide pin with respect to a cylindrical support portion of the support, and a pair of pressing arms extended from the base portion to a position sandwiching the disk rotor from both sides in the axial direction. A floating caliper having a pair of brake pad assemblies respectively provided at the front ends of the pair of pressing arms so as to face the side surfaces of the disk rotor, and one of the brake pad assemblies facing the side surface of the disk rotor The drive piston provided on one of the pair of pressing arms for driving and the one brake pad so that a predetermined amount of displacement of the one brake pad assembly is the displacement of the floating caliper And a caliper return mechanism interposed between the assembly and the support. Brakes.

  According to the disc brake having the configuration (1), the movement amount of one brake pad assembly (piston side brake pad assembly) is detected by the sensor lever, and the movement amount of about half of the movement amount is set as a relative position to the support. The other brake pad assembly (the anti-piston side brake pad assembly) is moved by a predetermined amount in the direction (disc rotor approaching direction) opposite to the moving direction of the brake pad assembly (disc rotor separating direction). For this reason, although it is a Fiss caliper type caliper mechanism, a substantially equivalent gap is obtained from the rotor surface for one brake pad assembly and the other brake pad assembly when the brake is released, and dragging during normal travel is eliminated.

(2) The disc brake configured as described in (1) above, wherein the caliper return mechanism is centered on an intermediate portion by a sensor lever support member fixed to the one pressing arm and a fulcrum pin of the sensor lever support member. A sensor lever that is pivotally supported by one of its pivot ends and contacts the one brake pad assembly, a transmission lever support member fixed to the one pressing arm, and a fulcrum pin of the transmission lever support member And a transmission lever that is rotatably supported around the intermediate portion and whose one rotation end abuts the support, and one end that is pivotally connected to the other rotation end of the sensor lever, and the transmission lever And a first link mechanism having the other end pivotably connected to the other pivot end of the disc brake.

  According to the disc brake having the configuration (2), when the release of the brake is started, the drive piston is retracted, and one brake pad assembly is separated from the disc rotor. A pad clearance is formed between one brake pad assembly and the disc rotor. At this time, one rotation end of the sensor lever is biased by one brake pad assembly, and the sensor lever is rotated in a direction in which one brake pad assembly retreats around the fulcrum pin of the sensor lever support member. That is, the displacement amount of one brake pad assembly is detected. At the same time, the transmission lever connected via the first link mechanism is rotated in the opposite direction to the sensor lever around the fulcrum pin of the transmission lever support member. Therefore, the transmission lever displaces the transmission lever support member (floating caliper) by the reaction force of one rotating end in contact with the support, so that the displacement amount is approximately half of the displacement amount of one brake pad assembly. Pull the other brake pad assembly away from the disc rotor. As a result, a predetermined amount of pad clearance, which is approximately half the amount of displacement of one brake pad assembly (piston side brake pad assembly), is ensured on the piston side and the anti-piston side.

(3) The disc brake having the configuration of (2), wherein one rotation end of the transmission lever is elastically urged in a direction in which it abuts against the support by a spring mechanism. brake.

  According to the disc brake having the configuration (3), one rotation end of the transmission lever is elastically biased in a direction in which it abuts against the support by the spring mechanism. Since the sensor lever is connected to the transmission lever via the first link mechanism, one rotating end is elastically biased in a direction to drive one brake pad assembly toward the side surface of the disk rotor. The When the drive piston is driven, one brake pad assembly (piston side brake pad assembly) is displaced in a direction away from the sensor lever. At this time, since the sensor lever is elastically biased by the spring mechanism, the sensor lever rotates in a direction in contact with one brake pad assembly. As a result, the sensor lever is always kept in contact with one brake pad assembly.

(4) The disc brake having the configuration of (3), wherein the spring mechanism is capable of relatively moving a fulcrum pin at the other rotation end of the sensor lever and a fulcrum pin at the other rotation end of the transmission lever. A first holding spring, a first compression spring interposed in a compressed state between a fulcrum pin at the other rotation end of the sensor lever and a fulcrum pin at the other rotation end of the transmission lever, and the transmission lever And a fixing member fixed to the support, and a second compression spring interposed in a compressed state.

  According to the disc brake having the configuration of (4) above, the second compression spring or the first compression is used for the relative movement between the sprung and unsprung in the vehicle such as when traveling on a curve due to the configuration on the brake mounting mechanism. The compression spring is compressed. That is, when the relative movement amount becomes larger than the clearance at the time of releasing the brake (when any brake pad assembly is pressed and displaced by the disc rotor), the displacement is absorbed by the spring mechanism. This prevents one brake pad assembly or the other brake pad assembly from being strongly pressed against the rotor surface during curve running. Further, when the vehicle returns to straight running, a clearance is again secured between the disc rotor and one brake pad assembly and the other brake pad assembly, and abnormal lining wear can be avoided.

(5) The disc brake having the configuration of (1), wherein the caliper return mechanism is centered on an intermediate portion by a sensor lever support member fixed to the one pressing arm and a fulcrum pin of the sensor lever support member. A sensor lever that is pivotally supported by one of its pivot ends and contacts the one brake pad assembly, a transmission lever support member fixed to the one pressing arm, and a fulcrum pin of the transmission lever support member A transmission lever that is rotatably supported around an intermediate portion, a coupling member that couples the other rotation end of the sensor lever and the other rotation end of the transmission lever so as to be relatively rotatable, and A fixing member fixed to the support, and a second link mechanism having one end rotatably connected to one rotation end of the transmission lever and the other end connected to the fixing member. Disc brake according to claim.

  According to the disc brake having the configuration (5), when release of the brake is started, the drive piston is retracted, and one brake pad assembly is separated from the disc rotor. A pad clearance is formed between one brake pad assembly and the disc rotor. At this time, one rotation end of the sensor lever is biased by one brake pad assembly, and the sensor lever is rotated in a direction in which one brake pad assembly retreats around the fulcrum pin of the sensor lever support member. That is, the displacement amount of one brake pad assembly is detected. At the same time, the transmission lever connected so as to be relatively rotatable via the connection member is rotated in the opposite direction to the sensor lever around the fulcrum pin of the transmission lever support member. Therefore, the transmission lever displaces the transmission lever support member (floating caliper) by the reaction force of the one rotation end that presses the support via the second link mechanism and the fixing member, so that one brake pad assembly The other brake pad assembly is pulled away from the disc rotor with a displacement amount that is approximately half of the displacement amount. As a result, a predetermined amount of pad clearance, which is approximately half the amount of displacement of one brake pad assembly (piston side brake pad assembly), is ensured on the piston side and the anti-piston side.

(6) The disc brake having the configuration of (5), wherein one rotation end of the transmission lever is elastically urged so as to be relatively movable with respect to the fixed member by a spring mechanism. Disc brake.

  According to the disc brake having the configuration (6) above, the spring mechanism absorbs the relative movement with respect to the relative movement between the sprung and unsprung parts of the vehicle when traveling on a curve because of the structure on the brake mounting mechanism. To do. That is, when the relative movement amount becomes larger than the clearance at the time of releasing the brake (when any brake pad assembly is pressed and displaced by the disc rotor), the displacement is absorbed by the spring mechanism. Thus, one brake pad assembly or the other brake pad assembly is not strongly pressed against the rotor surface. Further, when the vehicle returns to straight running, a clearance is again secured between the disc rotor and one brake pad assembly and the other brake pad assembly, and abnormal lining wear can be avoided.

(7) In the disc brake having the configuration of (6), the spring mechanism is connected to the fixing member so as to be relatively movable, and holds a fulcrum pin at one rotation end of the transmission lever so as to be relatively movable. And a third compression spring interposed in a compressed state between a fulcrum pin at one rotation end of the transmission lever and a spring receiver as the other end of the second link mechanism, and the transmission lever And a fourth compression spring interposed in a compressed state between the spring receiver supported at the tip of a support pin that penetrates the spring receiver and the through hole of the fixing member from the side, and the fixing member. Disc brake.

  According to the disc brake having the configuration (7), the one rotation end of the transmission lever is configured not to move further relative to the fixed member while being elastically biased by the third compression spring and the fourth compression spring. Become. Therefore, the transmission lever presses and biases the support via the fixing member when one of the rotation ends rotates in a direction of relative movement with respect to the fixing member. And since one rotation end of a transmission lever does not move relatively with respect to a fixed member by the pressurization force of a 3rd compression spring and a 4th compression spring, as a result, a transmission lever support member (floating) by reaction force from a fixed member Caliper) moves. Furthermore, when the relative movement amount between the sprung and unsprung portions becomes larger than the clearance when the brake is released, the displacement is absorbed by the third compression spring and the fourth compression spring.

(8) In the disc brake having the configuration of (1), the caliper return mechanism is rotatably supported by the rotating shaft fixing member fixed to the one pressing arm and the rotating shaft fixing member. A lever rotating shaft, a sensor lever fixed to one end of the lever rotating shaft and having a rotating tip abutting against the one brake pad assembly, and a rotating tip fixed to the other end of the lever rotating shaft to the support A disc brake comprising: a transmission lever that is maintained at a predetermined interval with respect to the disc brake.

  According to the disc brake having the configuration (8), when release of the brake is started, the drive piston is retracted, and one brake pad assembly is separated from the disc rotor. A pad clearance is formed between one brake pad assembly and the disc rotor. At this time, the sensor lever is rotated in a direction in which one brake pad assembly moves backward. That is, the displacement amount of one brake pad assembly is detected. At the same time, the transmission lever fixed to the other end of the lever rotation shaft is rotated in the same direction. Therefore, the transmission lever becomes approximately half of the displacement amount of one brake pad assembly by displacing the rotating shaft fixing member (floating caliper) by the reaction force of the rotating tip maintained at a predetermined interval with respect to the support. With the amount of displacement, pull the other brake pad assembly away from the disc rotor. As a result, a predetermined amount of pad clearance, which is approximately half the amount of displacement of one brake pad assembly (piston side brake pad assembly), is ensured on the piston side and the anti-piston side.

(9) The disc brake having the configuration according to (8), wherein the rotation tip of the transmission lever is elastically biased in a direction facing the support by a spring mechanism.

  According to the disc brake having the configuration (9), the rotation tip of the transmission lever is elastically biased in the direction facing the support by the spring mechanism. Since the sensor lever rotates integrally via the transmission lever and the lever rotation shaft, the rotation tip is elastically biased in the same direction (direction in which one brake pad assembly is driven toward the side surface of the disk rotor). The When the drive piston is driven, one brake pad assembly (piston side brake pad assembly) is displaced in a direction away from the sensor lever. At this time, since the sensor lever is elastically biased in a direction facing the support, the sensor lever rotates in a direction in contact with one brake pad assembly. As a result, the sensor lever is always kept in contact with the one-side brake pad assembly.

(10) The disc brake having the configuration according to (9), wherein the spring mechanism includes a spring receiving plate fixed to the support, and a tip that penetrates the through hole of the spring receiving plate is a rotating tip of the transmission lever. In a tension state between a support pin that contacts the compression pin, a compression spring interposed in a compressed state between the intermediate support portion of the support pin and the spring receiving plate, and a rotation tip of the support pin and the transmission lever A disc brake comprising: a tension spring interposed therein.

  According to the disc brake having the structure of (10) above, is the compression spring compressed due to the relative movement between the sprung and unsprung parts of the vehicle when traveling on a curve because of the structure on the brake mounting mechanism? The tension spring is pulled. That is, when the relative movement amount becomes larger than the clearance at the time of releasing the brake (when any brake pad assembly is pressed and displaced by the disc rotor), the displacement is absorbed by the spring mechanism. This prevents one brake pad assembly or the other brake pad assembly from being strongly pressed against the rotor surface during curve running. Further, when the vehicle returns to straight running, a clearance is again secured between the disc rotor and one brake pad assembly and the other brake pad assembly, and abnormal lining wear can be avoided.

(11) A disc brake for a railway vehicle comprising the disc brake of any one of (1) to (10) above.

  According to the railway vehicle disc brake having the above configuration (11), when the brake is pressed by the brake pads against the disc rotors attached to both side surfaces of the railcar wheel, braking is performed. In addition, the pad clearance between the brake pad and the disc rotor can be maintained constant. As a result, uneven wear and drag of the brake pad can be prevented, and an increase in the starting torque of the railway vehicle can be suppressed.

  According to the disc brake according to the present invention, the piston side brake pad assembly and the anti-piston side brake pad assembly have substantially the same clearance from the disc rotor surface at the time of releasing the brake while being a floating caliper. Can be resolved.

  According to the railway vehicle disc brake of the present invention, it is possible to prevent uneven wear and drag of the brake pads and to suppress an increase in starting torque of the railway vehicle.

  The present invention has been briefly described above. Further, the details of the present invention will be further clarified by reading through a mode for carrying out the invention described below (hereinafter referred to as “embodiment”) with reference to the accompanying drawings. .

It is the perspective view which looked at the disc brake concerning a 1st embodiment of the present invention from the lower side of one press arm. FIG. 2 is a side view of the disc brake shown in FIG. 1. FIG. 3 is a front view of the disc brake shown in FIG. 2 as viewed from the brake pad assembly side. FIG. 4 is a sectional view taken along the line IV-IV in FIG. 2. 5A is a front view, FIG. 5B is a bottom view, and FIG. 5C is a right side view of the caliper return mechanism shown in FIG. 4. FIG. 5 is a perspective view of the caliper return mechanism shown in FIG. 4. It is the figure which notched a part of disc brake concerning a 2nd embodiment of the present invention, and was seen from the lower side. 8A is a front view, FIG. 8B is a bottom view, and FIG. 8C is a right side view of the caliper return mechanism shown in FIG. 7. FIG. 8 is a perspective view of the caliper return mechanism shown in FIG. 7. FIG. 10 is an exploded perspective view of the caliper return mechanism shown in FIG. 9. It is the figure which notched a part of disc brake concerning a 3rd embodiment of the present invention, and was seen from the lower side. FIG. 12A is a left side view, FIG. 12B is a front view, and FIG. 12C is a bottom view of the caliper returning mechanism shown in FIG. 11. FIG. 12 is a perspective view of the caliper return mechanism shown in FIG. 11. FIG. 14 is an exploded perspective view of the caliper return mechanism shown in FIG. 13. It is the perspective view which looked at the disc brake concerning a 4th embodiment of the present invention from the one press arm side. It is the perspective view which looked at the disc brake shown in FIG. 15 from the other pressing arm side. It is the figure which notched the disk brake shown in FIG. 15 in the surface containing the axis line of a lever rotating shaft, and was seen from the lower side. FIG. 16 is a perspective view of the caliper return mechanism shown in FIG. 15. It is a disassembled perspective view of the caliper returning mechanism shown in FIG. (A) is an operation explanatory diagram before the brake braking of the disc brake shown in FIG. 17, (b) is an operation explanatory diagram during the brake braking, and (c) is an operation explanatory diagram when the brake braking is completed. (A) is an operation explanatory view before the brake release of the disc brake shown in FIG. 17, (b) is an operation explanatory view during the brake release, and (c) is an operation explanatory view when the brake release is completed. (A) is operation | movement explanatory drawing when a wheel moves to the piston side, (b) is operation | movement explanatory drawing when a wheel moves to the anti-piston side. It is a top view of the conventional floating type caliper brake device. It is a front view of FIG. It is sectional drawing which shows the conventional support structure.

Embodiments according to the present invention will be described below with reference to the drawings.
As shown in FIGS. 1-4, the disc brake 100 which concerns on 1st Embodiment of this invention is used for the disc brake for rail vehicles. In addition, the disc brake 100 can also be suitably used for various industrial drive device brake devices that generate a braking force on a rotating member such as an elevator.

  The floating caliper type disc brake 100 according to the first embodiment is a piston-side pressing which is a pair of pressing arms extending from a base 15 slidably supported on a support 13 coupled to a cart frame (not shown). The floating caliper 21 having the arm 17 and the anti-piston side pressing arm 19, and the piston side pressing arm 17 and the anti-piston side pressing arm so as to face the side surfaces of the disk rotor 23 (see FIG. 4) attached to both side surfaces of the wheel 39. A piston-side brake pad assembly 25 and an anti-piston-side brake pad assembly 27, which are a pair of brake pad assemblies provided at the respective front end portions of 19, and the piston-side brake pad assembly 25 are driven toward the side surface of the disk rotor 23. A drive piston 29 provided on the piston-side pressing arm 17 for Comprising Yaripa a return mechanism 11, the.

  An upper guide pin 35 that is a guide pin with respect to an upper cylindrical support portion 31 and a lower cylindrical support portion 33 that are a pair of upper and lower cylindrical support portions of the support 13 are provided at an upper portion and a lower portion of the base portion 15 in the floating caliper 21. Lower guide pins 37 are spanned respectively. The base portion 15 of the floating caliper 21 is slidably supported by the upper cylindrical support portion 31 and the lower cylindrical support portion 33 via the upper guide pin 35 and the lower guide pin 37. On the base 15 of the floating caliper 21, the piston side pressing arm 17 and the anti-piston side pressing arm 19 are extended to a position where the disk rotor 23 attached to both side surfaces of the wheel 39 is sandwiched from both sides in the axial direction. Note that the piston-side pressing arm 17 and the anti-piston-side pressing arm 19 in the present embodiment are each composed of a bifurcated arm portion.

  The piston side brake pad assembly 25 and the anti-piston side brake pad assembly 27 are configured by attaching a brake pad 41 to an anchor plate 43. The drive piston 29 presses the brake pad 41 against the disc rotor 23 by pressing the anchor plate 43. The piston-side brake pad assembly 25 and the anti-piston-side brake pad assembly 27 are arranged at the tips of the piston-side pressing arm 17 and the anti-piston-side pressing arm 19 so as to face the outer surfaces of the disk rotor 23 attached to both side surfaces of the wheel 39. Provided in each part. In the present embodiment, a structure in which the lining surfaces of the piston-side brake pad assembly 25 and the anti-piston-side brake pad assembly 27 press the disc rotor 23 to perform a braking operation will be described as an example. Of course, the disc brake 100 may be configured to brake by directly pressing both side surfaces of the wheel 39.

  In this embodiment, the drive piston 29 is provided on the piston-side pressing arm 17 which is one of a pair of pressing arms in order to drive the piston-side brake pad assembly 25 toward the side surface of the disk rotor 23.

  A pair of friction rubber rings (not shown) are fitted inside the upper cylindrical support portion 31 of the support 13. A friction rubber ring having a shape and material having a high elastic range (deformation amount) and a return force (retraction effect) is selected. The pair of friction rubber rings are fitted into the upper cylindrical support portion 31 and elastically support the upper guide pin 35 slidably.

  A centering bearing (not shown) is fixed at the center of the inner peripheral surface of the upper cylindrical support portion 31 surrounding the upper guide pin 35. The aligning bearing supports the upper guide pin 35 in a swingable manner. In the aligning bearing, the upper guide pin 35 and the upper cylindrical support portion 31 of the support 13 are not parallel because the wheel 39 elastically supported by the carriage frame is displaced (swings) relative to the carriage frame. Even in this case, the sliding surfaces of the brake pad 41 and the disk rotor 23 can be brought into close contact with each other during braking.

  Although not shown, a rubber bush and a sleeve are interposed between the lower guide pin 37 and the lower cylindrical support portion 33. The lower guide pin 37 is slidably supported in the axial direction with respect to the lower cylindrical support portion 33 via these rubber bushes and sleeves instead of the aligning bearing.

  In the disc brake 100 according to the first embodiment, the caliper returning mechanism 11 is arranged so that the predetermined amount of displacement of the piston side brake pad assembly 25 which is one brake pad assembly becomes the displacement amount of the floating caliper 21. It is interposed between the brake pad assembly 25 and the support 13.

  As shown in FIGS. 4 to 6, the caliper return mechanism 11 includes a sensor lever support member 45, a sensor lever 47, a transmission lever support member 49, a transmission lever 51, a fixing member 53, and a first link mechanism. 55.

  The sensor lever support member 45 is fixed to the piston side pressing arm 17. The sensor lever 47 is supported by a fulcrum pin 57 of the sensor lever support member 45 so as to be rotatable about an intermediate portion, and one rotation end (sensor lever pad end 59) abuts on the piston side brake pad assembly 25. .

  The transmission lever support member 49 is fixed to the piston side pressing arm 17. The transmission lever 51 is supported by a fulcrum pin 61 of the transmission lever support member 49 so as to be rotatable about an intermediate portion, and one rotation end (transmission lever support end 63) abuts the support 13.

  The fixing member 53 is formed by bending a band plate into a crank shape. The fixing member 53 is fixed to the support 13 at the base end side in the longitudinal direction. The distal end side in the longitudinal direction of the fixing member 53 supports the second compression spring 67 of the spring mechanism 65.

  One end (spring receiver 71) of the first link mechanism 55 is rotatably connected to the other rotation end (sensor lever link end 69) of the sensor lever 47. In the first link mechanism 55, the other end (holder transmission lever end 75) is rotatably connected to the other rotation end (transmission lever link end 73) of the transmission lever 51.

  The transmission lever 51 is elastically biased in a direction in which the transmission lever support end 63 abuts against the support 13 by a spring mechanism 65.

  The spring mechanism 65 includes a spring holder 77, a first compression spring 79, and a second compression spring 67. The spring holder 77 holds the fulcrum pin 81 of the sensor lever link end 69 and the fulcrum pin 83 of the transmission lever link end 73 so that they can move relative to each other.

  The first compression spring 79 is interposed between the fulcrum pin 81 of the sensor lever link end 69 and the fulcrum pin 83 of the transmission lever link end 73 in a compressed state. The second compression spring 67 is interposed between the transmission lever 51 and the fixing member 53 in a compressed state. More specifically, one end of the second compression spring 67 contacts the fixing member 53. The other end of the second compression spring 67 abuts between the fulcrum pin 61 of the transmission lever support member 49 in the transmission lever 51 and the fulcrum pin 83 of the transmission lever link end 73. That is, the second compression spring 67 presses and urges the transmission lever 51 with the counterclockwise moment of FIG.

Next, the operation of the disc brake 100 described above will be described.
In the disc brake 100 according to the present embodiment, the movement amount of the piston-side brake pad assembly 25 is detected by the sensor lever 47, and the movement amount of the piston-side brake pad assembly 25 is set with the movement amount of the substantially half as a relative position to the support 13. The anti-piston side brake pad assembly 27 is configured to move by a predetermined amount in a direction opposite to the direction (the disc rotor separating direction) (the disc rotor approaching direction). For this reason, although it is a Fiss caliper type caliper mechanism, when the brake is released, the piston side brake pad assembly 25 and the anti-piston side brake pad assembly 27 both have substantially the same clearance from the rotor surface of the disc rotor 23, and dragging in normal running is performed. Is resolved.

  Further, in the disc brake 100 of the first embodiment, when the release of the brake is started, the drive piston 29 is retracted, and the piston side brake pad assembly 25 is separated from the disc rotor 23. A pad clearance is formed between the piston side brake pad assembly 25 and the disk rotor 23. At this time, the sensor lever 47 is urged at the sensor lever pad end 59 by the piston side brake pad assembly 25 and rotates in a direction in which the piston side brake pad assembly 25 moves backward about the fulcrum pin 57 of the sensor lever support member 45. Be made. That is, the displacement amount of the piston side brake pad assembly 25 is detected. At the same time, the transmission lever 51 connected via the first link mechanism 55 is rotated in the direction opposite to the sensor lever 47 around the fulcrum pin 61 of the transmission lever support member 49. Therefore, the transmission lever 51 displaces the transmission lever support member 49 (floating caliper 21) by the reaction force of the transmission lever support end 63 that is in contact with the support 13, so that the displacement amount of the piston-side brake pad assembly 25 is substantially half. The anti-piston side brake pad assembly 27 is pulled away from the disc rotor 23 by the amount of displacement. As a result, a predetermined amount of pad clearance, which is substantially half the displacement of the piston-side brake pad assembly 25, is ensured on the piston side and the anti-piston side.

  Further, in the disc brake 100 of the first embodiment, the transmission lever support end 63 is elastically biased in the direction in which the transmission lever support end 63 abuts against the support 13 by the spring mechanism 65. Since the sensor lever 47 is connected to the transmission lever 51 via the first link mechanism 55, the transmission lever support end 63 drives the piston side brake pad assembly 25 toward the side surface of the disc rotor 23. Is elastically biased. When the drive piston 29 is driven, the piston-side brake pad assembly 25 is displaced in a direction away from the sensor lever 47. At this time, since the sensor lever 47 is elastically biased by the spring mechanism 65, the sensor lever 47 rotates in a direction in which the sensor lever 47 contacts the piston-side brake pad assembly 25. As a result, the sensor lever 47 is always kept in contact with the piston-side brake pad assembly 25.

  Further, in the disc brake 100 according to the first embodiment, the second compression spring 67 or the second compression spring 67 or the second spring is used for the relative movement between the sprung and unsprung parts of the vehicle when traveling on a curve because of the configuration on the brake mounting mechanism. 1 compression spring 79 is compressed. That is, when the relative movement amount is larger than the clearance at the time of releasing the brake (when any brake pad assembly is pressed and displaced by the disc rotor 23), the displacement is absorbed by the spring mechanism 65. For example, if the transmission lever 51 that receives the reaction force from the support 13 rotates clockwise in FIG. 4 due to relative movement between the sprung and unsprung parts, the second compression spring 67 is compressed. Further, when the transmission lever 51 receiving the reaction force from the support 13 rotates counterclockwise in FIG. 4 due to the relative movement between the sprung and unsprung parts, the first compression spring 79 is compressed. As a result, the piston-side brake pad assembly 25 or the anti-piston-side brake pad assembly 27 is not strongly pressed against the rotor surface of the disk rotor 23. Further, when the vehicle returns to the straight running, the clearance between the disc rotor 23 and the piston side brake pad assembly 25 and the anti-piston side brake pad assembly 27 is secured again, so that the lining is prevented from being worn abnormally.

Next, a disc brake 200 according to a second embodiment of the present invention will be described.
As shown in FIGS. 7 to 10, the disc brake 200 according to the second embodiment of the present invention includes the first link mechanism 87 of the caliper return mechanism 85 and the spring mechanism 89, and the disc according to the first embodiment. Different from the configuration of the brake 100. Note that in the disc brake 200 of the second embodiment, the same reference numerals are given to the same components as those of the disc brake 100 of the first embodiment, and duplicate descriptions are omitted.

  In the caliper return mechanism 85 according to the second embodiment, the sensor lever 47 is supported by the piston-side pressing arm 17 by the sensor lever support member 45. As shown in FIG. 10, the sensor lever support member 45 includes a fulcrum pin 57, a fulcrum pin support 91, a fulcrum pin fixture 93, and a nut 95.

  One end (spring receiver 99) of the first link mechanism 87 in the caliper return mechanism 85 is rotatably connected to the other rotation end (sensor lever link end 69) of the sensor lever 47. In the first link mechanism 87, the other rotation end (holder transmission lever end 75) is rotatably connected to the other rotation end (transmission lever link end 108) of the transmission lever 107.

  The sensor lever link end 69 is inserted into the spring holder 77. The sensor lever link end 69 is in contact with a contact bolt 97 fixed to the upper end of the spring holder 77 of the spring mechanism 89. The contact bolt 97 is restricted from being detached from the spring holder 77 by the nut 95. Further, a fulcrum pin 81 is inserted into the sensor lever link end 69. A spring receiver 99 that is rotatably supported by the fulcrum pin 81 is in contact with one end of the first compression spring 79. The other end of the first compression spring 79 contacts the spring receiver 101. The spring receiver 101 is rotatably supported by a fulcrum pin 83 of the transmission lever link end 73 in the transmission lever 107. The other rotation end (transmission lever link end 108) of the transmission lever 107 is supported by a slider 105 that slides with the engagement pin 106 engaged with the slide hole 103 of the spring holder 77.

  The transmission lever 107 is rotatably supported by the transmission lever support member 49 by a fulcrum pin 61. The transmission lever 107 abuts the swing lever 111 at the transmission lever support end 109. One end of the swing member 111 is swingably supported by the fulcrum pin 61 of the transmission lever support member 49, and the other end abuts on one end of the second compression spring 67. The other end of the second compression spring 67 is in contact with the support 13 via a spring receiver 115 which is a fixing member fixed to the support 13 with a fixing bolt 113. That is, the second compression spring 67 is interposed between the transmission lever 107 and the spring receiver 115 fixed to the support 13 in a compressed state.

  The caliper return mechanism 85 is not limited to the fulcrum pin 57, the fulcrum pin 61, the fulcrum pin 81, and the fulcrum pin 83 for operating the transmission mechanism. It is configured so that it can be securely retained by the components. As a result, in the disc brake 200, each fulcrum pin of the transmission mechanism does not need to be provided with a dedicated retaining prevention means, and the ease of assembly is improved. This configuration is the same for the disc brake 100 according to the first embodiment.

Next, the operation of the disc brake 200 according to the second embodiment will be described.
Also in the disc brake 200 of the second embodiment, as in the disc brake 100 of the first embodiment, the sensor lever 47 detects the displacement amount of the piston-side brake pad assembly 25 and the piston-side brake pad assembly 25 is detected. A predetermined amount of pad clearance, which is approximately half of the displacement amount, is ensured on the piston side and the non-piston side.

  Further, when the relative movement amount becomes larger than the clearance when the brake is released (when any brake pad assembly is pressed and displaced by the disc rotor 23), the first compression spring 79 or the second compression spring 79 in the spring mechanism 89 is used. The displacement is absorbed by the compression spring 67. That is, if the piston side brake pad assembly 25 receives a reaction force due to relative movement, the first compression spring 79 is compressed. If the anti-piston brake pad assembly 27 receives a reaction force due to the relative movement, the second compression spring 67 is compressed. This prevents the piston-side brake pad assembly 25 or the anti-piston-side brake pad assembly 27 from being strongly pressed against the rotor surface of the disc rotor 23 during curve traveling. Further, when the vehicle returns to the straight running, the clearance between the disc rotor 23 and the piston side brake pad assembly 25 and the anti-piston side brake pad assembly 27 is secured again, so that the lining is prevented from being worn abnormally.

Next, a disc brake 300 according to a third embodiment of the present invention will be described.
As shown in FIGS. 11 to 14, the disc brake 300 according to the third embodiment of the present invention includes a caliper return mechanism 117, a second link mechanism 119, and a spring mechanism 121. Different from the configuration of the brake 100. Note that in the disc brake 300 of the third embodiment, the same components as those of the disc brake 100 of the first embodiment are denoted by the same reference numerals, and redundant description is omitted.

The caliper return mechanism 117 according to the third embodiment includes a sensor lever support member 123, a sensor lever 125, a transmission lever support member 127, a transmission lever 129, a connecting member 131, a second link mechanism 119, And a spring mechanism 121.
The sensor lever support member 123 is fixed to the piston side pressing arm 17. The sensor lever 125 is supported by a fulcrum pin 57 of the sensor lever support member 123 so as to be rotatable about an intermediate portion, and one rotation end (sensor lever pad end 59) abuts on the piston side brake pad assembly 25. . The transmission lever support member 127 is fixed to the piston side pressing arm 17. The transmission lever 129 is supported by a fulcrum pin 61 of the transmission lever support member 127 so as to be rotatable around an intermediate portion.

  The connecting member 131 connects the other rotation end (sensor lever transmission end 133) of the sensor lever 125 and the other rotation end (transmission lever sensor end 135) of the transmission lever 129 so that they can rotate relative to each other. The second link mechanism 119 has a fixing member 137 fixed to the support 13 and one rotation end (transmission lever link end 139) of the transmission lever 129 having one end (spring receiver 141) rotatably connected thereto. The other end (spring receiver 143) is connected to the fixing member 137.

In the caliper return mechanism 117 according to the third embodiment, the transmission lever link end 139 of the transmission lever 129 is elastically urged so as to be relatively movable with respect to the fixed member 53 by the spring mechanism 121.
The spring mechanism 121 includes a spring holder 145, a third compression spring 147, and a fourth compression spring 149. The spring holder 145 is connected to the fixing member 137 so as to be relatively movable, and holds the fulcrum pin 83 at the transmission lever link end 139 of the transmission lever 129 so as to be relatively movable. The third compression spring 147 is interposed between the spring receiver 141 that engages the fulcrum pin 83 at the transmission lever link end 139 of the transmission lever 129 and the spring receiver 143 that is the other end of the second link mechanism 119 in a compressed state. Be dressed. The fourth compression spring 149 is provided between the fixing member 137 and the spring receiving member 155 supported by the tip of the support pin 153 passing through the through hole 151 of the spring receiver 143, the spring holder 145 and the fixing member 137 from the transmission lever 129 side. It is inserted in a compressed state. A spring receiver 157 is disposed between the fourth compression spring 149 and the fixing member 137.

  The connecting member 131 is fixed to the sensor lever transmission end 133 by a bolt 159. The connecting member 131 supports the transmission lever sensor end 135 of the transmission lever 129 via the swing shaft 161 so as to be swingable. That is, the connecting member 131 connects the sensor lever transmission end 133 and the transmission lever sensor end 135 so that they can rotate relative to each other.

Next, the operation of the disc brake 300 according to the third embodiment will be described.
In the disc brake 300 according to the third embodiment, when the release of the brake is started, the drive piston 29 is retracted, and the piston-side brake pad assembly 25 is separated from the disc rotor 23. A pad clearance is formed between the piston side brake pad assembly 25 and the disk rotor 23. At this time, the sensor lever 125 is urged at the sensor lever pad end 59 by the piston side brake pad assembly 25 and rotates in a direction in which the piston side brake pad assembly 25 moves backward about the fulcrum pin 57 of the sensor lever support member 123. Be made. That is, the displacement amount of the piston side brake pad assembly 25 is detected. At the same time, the transmission lever 129 coupled so as to be relatively rotatable via the coupling member 131 is rotated in the direction opposite to the sensor lever 125 around the fulcrum pin 61 of the transmission lever support member 127. Therefore, the transmission lever 129 displaces the transmission lever support member 127 (floating caliper 21) by the reaction force of the transmission lever link end 139 that presses the support 13 via the second link mechanism 119 and the fixing member 137. The anti-piston side brake pad assembly 27 is pulled away from the disc rotor 23 with a displacement amount that is substantially half of the displacement amount of the piston side brake pad assembly 25. As a result, a predetermined amount of pad clearance, which is substantially half the displacement of the piston-side brake pad assembly 25, is ensured on the piston side and the anti-piston side.

  In the disc brake 300 of the third embodiment, the transmission lever link end 139 of the transmission lever 129 is elastically urged relative to the fixing member 137 by the spring mechanism 121. In view of this, in the disc brake 300, the third compression spring 147 or the fourth compression spring 149 is compressed with respect to the relative movement between the sprung and unsprung during the curve traveling due to the configuration on the brake mounting mechanism. . That is, when the relative movement amount becomes larger than the clearance at the time of releasing the brake (when any brake pad assembly is pressed and displaced by the disc rotor 23), the displacement is absorbed by the spring mechanism 121. As a result, the piston-side brake pad assembly 25 or the anti-piston-side brake pad assembly 27 is not strongly pressed against the rotor surface. Further, when the vehicle returns to the straight running, the clearance between the disc rotor 23 and the piston side brake pad assembly 25 and the anti-piston side brake pad assembly 27 is secured again, so that the lining is prevented from being worn abnormally.

  Further, in the disc brake 300 according to the third embodiment, the transmission lever link end 139 of the transmission lever 129 is more than the fixed member 137 relative to the fixed member 137 while being elastically biased by the third compression spring 147 and the fourth compression spring 149. It becomes the structure which does not move. Therefore, the transmission lever 129 presses and biases the support 13 via the fixing member 137 when the transmission lever link end 139 rotates in the direction of relative movement with respect to the fixing member 137. The transmission lever link end 139 of the transmission lever 129 does not move relative to the fixed member 137 due to the pressing force of the third compression spring 147 and the fourth compression spring 149, and as a result, the transmission lever link 139 is transmitted by the reaction force from the fixed member 137. The lever support member 127 (floating caliper 21) moves. Further, when the relative movement amount between the sprung and unsprung portions becomes larger than the clearance at the time of releasing the brake, the displacement is absorbed by the third compression spring 147 and the fourth compression spring 149.

Next, a disc brake 400 according to a fourth embodiment of the present invention will be described.
As shown in FIGS. 15 to 17, in the disc brake 400 according to the fourth embodiment of the present invention, a caliper return mechanism 165 includes a rotating shaft fixing member 167 fixed to the piston-side pressing arm 17, and a rotating shaft fixing member. A lever rotation shaft 163 rotatably supported by 167, a sensor lever 169 fixed to one end of the lever rotation shaft 163 and having a rotating tip abutting against the piston side brake pad assembly 25, and the other end of the lever rotation shaft 163 And a transmission lever 171 that is fixed to the support 13 so that the rotation tip is maintained at a predetermined interval with respect to the support 13. Note that in the disc brake 400 of the fourth embodiment, the same components as those of the disc brake 100 of the first embodiment are denoted by the same reference numerals, and redundant description is omitted.

  In the disc brake 400 according to the fourth embodiment, the rotating tip of the transmission lever 171 is elastically biased in the direction facing the support 13 by the spring mechanism 173.

  As shown in FIGS. 18 and 19, in the disc brake 400, the spring mechanism 173 has a spring receiving plate 175 fixed to the support 13, and the tip of the spring receiving plate 175 passing through the through hole 177 rotates the transmission lever 171. A support pin 179 contacting the tip, a compression spring 181 interposed between the intermediate support portion of the support pin 179 and the spring receiving plate 175, and a rotation tip of the support pin 179 and the transmission lever 171. A tension spring 183 interposed therebetween in a tension state.

  The rotating shaft fixing member 167 includes a strip-shaped fixed base 185 and a pair of parallel bearing upright plates 187 suspended from both ends of the fixed base 185. The fixed base 185 is fixed to the piston side pressing arm 17 by a body mounting bolt 189. In the present embodiment, the piston-side pressing arm 17 is formed to be bifurcated up and down. The fixed base 185 is fixed to the upper arm surface on the lower side. The pair of bearing upright plates 187 are provided on the upper surfaces of both ends of the fixed base 185 so as to be separated from each other in the extending direction of the piston-side pressing arm 17. A friction reducing bush 193 is fitted in the bearing hole 191 of each bearing upright plate 187.

  The lever rotation shaft 163 is rotatably supported by the bearing hole 191 of the bearing upright plate 187 via the bush 193. That is, the axis of the lever rotation shaft 163 extends along the extending direction of the piston-side pressing arm 17. A nut 95 is screwed onto the protruding end of the lever rotation shaft 163 protruding from the pair of bearing upright plates 187. The nut 95 restricts the detachment of the lever rotating shaft 163 from the bearing upright plate 187.

  The sensor lever 169 is fixed to one end of the lever rotation shaft 163 protruding from the bearing upright plate 187 on the piston side brake pad assembly 25 side by shrink fitting or screwing. The sensor lever 169 is formed in an arm shape protruding outward in the radial direction of the lever rotation shaft 163. The sensor lever 169 has a base end fixed to the lever rotation shaft 163 and a rotating tip abutting against the anchor plate 43 of the piston side brake pad assembly 25. That is, the sensor lever 169 is disposed on the anchor plate 43 side.

The transmission lever 171 is fixed to the other end of the lever rotation shaft 163 protruding from the bearing upright plate 187 on the support 13 side by shrink fitting or screwing. The transmission lever 171 is also formed in an arm shape protruding outward in the radial direction of the lever rotation shaft 163. Here, as shown in FIG. 15, the transmission lever 171 is formed shorter than the sensor lever 169 so as to have a length ratio of 2: 1 with the sensor lever 169. The transmission lever 171 has a proximal end fixed to the lever rotation shaft 163 and a rotating distal end maintained at a predetermined interval with respect to the support 13. The maintenance of the predetermined interval is realized by the rotation tip of the transmission lever 171 contacting the opposite head end 195 of the support pin 179. The transmission lever 171 is disposed on the support 13 side.
As a result, the caliper return mechanism 165 is configured to be able to transmit to the support 13 a predetermined amount that is half the amount of movement of the piston-side brake pad assembly 25. A spring locking lever side hole 197 is formed on the rotation tip side of the transmission lever 171.

In the disc brake 400 according to the fourth embodiment, the caliper return mechanism 165 interposed between the piston side brake pad assembly 25 and the support 13 causes half of the displacement amount of the piston side brake pad assembly 25 to be equal to that of the floating caliper 21. Displacement amount.
The rotating tip of the transmission lever 171 is elastically biased in a direction facing the support 13 by a spring mechanism 173.

The spring mechanism 173 includes a spring receiving plate 175, a support pin 179, a compression spring 181, and a tension spring 183.
The spring receiving plate 175 is formed in a strip shape, and one end in the longitudinal direction is fixed to the support 13 by a plurality of (two in the illustrated example) support mounting bolts 199. A through hole 177 is formed at the other end of the spring receiving plate 175 in the longitudinal direction.

  One end of the support pin 179 is a large-diameter head 201, and the other end is a counter-head end 195 having a smaller diameter than the head 201. The support pin 179 is inserted into the through hole 177 of the spring receiving plate 175 from the support 13 side toward the piston side pressing arm 17. That is, the support pin 179 is disposed in parallel with the upper guide pin 35 and the lower guide pin 37. The support pin 179 is restricted from coming off toward the piston-side pressing arm 17 when the head 201 comes into contact with the spring receiving plate 175. The support pin 179 has a stepped shape with a large diameter on the head 201 side and a small diameter on the opposite head end 195 side, with a substantially central portion in the longitudinal direction as a boundary. Therefore, a stepped portion 203 is formed at the center of the support pin 179 at the boundary between the large diameter side and the small diameter side. Further, the support pin 179 has a spring locking shaft-side hole 205 penetrating in the diametrical direction on the opposite head end 195 side of the stepped portion 203. In the support pin 179, the rotating tip of the transmission lever 171 contacts the opposite head end 195 that penetrates the spring receiving plate 175.

  The compression spring 181 is externally inserted on the large diameter side of the support pin 179 penetrating the spring receiving plate 175. A spring seat 207 as an intermediate support portion is fixed to the step portion 203 of the support pin 179 to which the compression spring 181 is attached. One end of the compression spring 181 contacts the spring receiving plate 175 and the other end contacts the spring seat 207 and is attached to the support pin 179. That is, the compression spring 181 is interposed between the spring seat 207 of the support pin 179 and the spring receiving plate 175 in a compressed state. The compression spring 181 is compressed and deformed when a load larger than the set compression load is applied to the opposite head end 195, and allows the support pin 179 to move toward the support 13.

  The tension spring 183 has locking hooks 209 at both ends. The tension spring 183 is extrapolated to the small diameter side of the support pin 179. The tension spring 183 has a locking hook 209 at one end locked in the spring locking shaft side hole 205, and a locking hook 209 at the other end locked in the spring locking lever side hole 197 of the transmission lever 171. . That is, the tension spring 183 is interposed between the support pin 179 and the rotation tip of the transmission lever 171 in a tension state. As a result, the caliper return mechanism 165 is elastically biased in a direction in which the rotation tip of the transmission lever 171 faces (approaches) the support 13.

Next, the operation of the disc brake 400 according to the fourth embodiment will be described.
In the disc brake 400 of the fourth embodiment, the lever rotation shaft 163 is rotatably fixed to the piston-side pressing arm 17 by the rotation shaft fixing member 167. A sensor lever 169 that contacts the piston brake pad assembly 25 is fixed to one end of the lever rotation shaft 163. A transmission lever 171 that is maintained at a predetermined interval with respect to the support 13 is fixed to the other end of the lever rotation shaft 163. Here, the rotating tip of the transmission lever 171 is elastically biased in a direction facing the support 13 by the spring mechanism 173. And since the sensor lever 169 rotates integrally via the transmission lever 171 and the lever rotating shaft 163, the rotation front end is the same direction (direction which drives the piston side brake pad assembly 25 toward the side surface of the disk rotor 23). Is elastically biased. When the drive piston 29 is driven, the piston-side brake pad assembly 25 is displaced in a direction away from the sensor lever 169. At this time, the sensor lever 169 is elastically biased in a direction facing the support 13, and thus rotates in a direction in which the sensor lever 169 contacts the piston-side brake pad assembly 25. Thereby, the sensor lever 169 is always maintained in contact with the piston-side brake pad assembly 25.

Next, the operation of the disc brake 400 will be described with reference to FIGS.
In the disc brake 400 according to the fourth embodiment, as shown in FIG. 20A, a pad clearance C is set between each brake pad 41 and the disc rotor 23 when the brake is released. . In this state, it is assumed that the drive piston 29 has advanced by the initial stroke S0.

When braking of the brake is started, the drive piston 29 is driven, and first, the piston side brake pad assembly 25 approaches the disc rotor 23. At this time, the sensor lever 169 in contact with the piston-side brake pad assembly 25 rotates following this rotation, and this rotation is transmitted to the transmission lever 171. The transmission lever 171 presses the opposite head end 195 of the support pin 179. If the compression spring 181 is not compressed by this pressing force, the transmission lever 171 receives a reaction force from the support 13 via the support pin 179.
The reaction force from the support 13 is transmitted from the lever rotation shaft 163 to which the transmission lever 171 is fixed to the rotation shaft fixing member 167, and the anti-piston side brake pad assembly 27 is moved to the disc rotor as shown in FIG. The floating caliper 21 is moved in a direction to approach the 23. As a result, when the drive piston 29 has a stroke S0 + C, a pad clearance C / 2 is vacated between each brake pad 41 and the disk rotor 23.
When the brake braking is completed, as shown in FIG. 20C, the piston-side brake pad assembly 25 and the anti-piston-side brake pad assembly 27 hold the disc rotor 23 at the same time.

  The compression spring 181 may be compressed by a pressing force with which the transmission lever 171 presses the opposite head end 195 of the support pin 179. In this case, when the transmission lever 171 presses the counter head end 195 of the support pin 179, the compression spring 181 is compressed, and the head 201 of the support pin 179 protrudes from the counter piston side of the spring receiving plate 175. Therefore, the floating caliper 21 is not moved until the piston side brake pad assembly 25 contacts the disk rotor 23 and receives a reaction force from the disk rotor 23. After the piston side brake pad assembly 25 receives the reaction force from the disk rotor 23, the floating caliper 21 is moved in a direction in which the anti-piston side brake pad assembly 27 approaches the disk rotor 23. At the same time, the protruding head 201 of the support pin 179 is also drawn into the spring receiving plate 175, and a normal state is obtained. In this manner, the spring mechanism 173 can change the behavior of the floating caliper 21 until after the brake braking is completed, depending on the setting of the compression load of the compression spring 181.

  On the other hand, as shown in FIG. 21A, the brake pad 41 and the disc rotor 23 are in contact with each other in the disc brake 400 during brake braking (C = 0). In this state, it is assumed that the drive piston 29 has advanced by the stroke S0 + 2C.

  As shown in FIG. 21 (b), when the release of the brake is started, the drive piston 29 is retracted, and the piston-side brake pad assembly 25 is separated from the disc rotor 23. A pad clearance is formed between the piston side brake pad assembly 25 and the disk rotor 23. At this time, the sensor lever 169 in contact with the piston-side brake pad assembly 25 is pressed, and the sensor lever 169 is rotated in the direction in which the piston-side brake pad assembly 25 moves backward. That is, the displacement amount of the piston side brake pad assembly 25 is detected.

  At the same time, rotation of the sensor lever 169 causes the transmission lever 171 to rotate in the same direction via the lever rotation shaft 163. Therefore, the transmission lever 171 displaces the rotating shaft fixing member 167 (floating caliper 21) by the reaction force of the rotating tip maintained at a predetermined interval with respect to the support 13, thereby the displacement amount of the piston side brake pad assembly 25. The anti-piston side brake pad assembly 27 is pulled away from the disc rotor 23 with a displacement amount that is approximately half of the displacement. As a result, when the drive piston 29 has a stroke S0 + C, a pad clearance C / 2 is vacated between each brake pad 41 and the disk rotor 23.

  Then, as shown in FIG. 21 (c), when the brake release is completed, half (C) of the retracted distance (2C) of the piston side brake pad assembly 25 corresponds to the anti-piston side brake pad assembly 27 and the disc rotor 23. Is assigned as pad clearance C. As a result, a pad clearance C that is half the amount of displacement of the piston-side brake pad assembly 25 is ensured on the piston side and the anti-piston side.

  By the way, in the disc brake 400 according to the fourth embodiment, due to the configuration on the brake mounting mechanism, the wheel 39 is moved by the relative movement between the sprung and the unsprung state in the vehicle during curve traveling or the like, so There is a case where it moves in a direction along the pin 37. For example, as shown in FIG. 22A, when the wheel 39 moves to the drive piston 29 side, the floating caliper 21 also moves in the same direction with respect to the support 13. Then, the distance between the spring receiving plate 175 and the rotation shaft fixing member 167 supporting the lever rotation shaft 163 increases, and the rotation tip of the transmission lever 171 moves away from the opposite head end 195 of the support pin 179. At this time, the spring mechanism 173 has one end locked by the support pin 179 and the extension spring 183 whose other end is locked by the transmission lever 171 extends to absorb the increase in distance.

  Further, when the wheel 39 moves to the opposite piston side, the floating caliper 21 also moves in the same direction with respect to the support 13. Then, the distance between the spring receiving plate 175 and the rotation shaft fixing member 167 supporting the lever rotation shaft 163 is reduced, and the rotation tip of the transmission lever 171 presses the opposite head end 195 of the support pin 179. At this time, the spring mechanism 173 has one end abutting against the spring receiving plate 175 and the other end abutting against the intermediate support portion of the support pin 179 is contracted, so that the reduction in distance is absorbed. . Thus, the caliper return mechanism 165 can absorb the displacement between the floating caliper 21 and the support 13 due to the movement of the wheel 39.

  That is, if the caliper return mechanism 165 is connected only by the link mechanism without using the spring mechanism 173, there is a possibility that the caliper return mechanism 165 may be damaged due to such movement of the wheel 39. That is, the caliper return mechanism 165 includes the spring mechanism 173, thereby realizing an even allocation of pad clearances with high reliability.

  As described above, in the disc brake 400 according to the fourth embodiment, the compression spring 181 is provided for the relative movement between the sprung and the unsprung state in the vehicle such as when traveling on a curve due to the configuration on the brake mounting mechanism. It is compressed or the tension spring 183 is pulled. That is, when the relative movement amount becomes larger than the clearance (clearance C) when the brake is released (when any brake pad assembly is pressed and displaced by the disc rotor 23), the displacement is absorbed by the spring mechanism 173. Is done. This prevents the piston-side brake pad assembly 25 or the anti-piston-side brake pad assembly 27 from being strongly pressed against the rotor surface during curve traveling. Further, when the vehicle returns to the straight running, a clearance (clearance C) between the disc rotor 23 and the piston-side brake pad assembly 25 and the anti-piston-side brake pad assembly 27 is secured again, and abnormal lining wear can be avoided.

  In the railway vehicle disc brake according to the above-described embodiment, the brake pad 41 is pressed against the disc rotor 23 attached to both side surfaces of the railway vehicle wheel 39 to perform braking by providing the above-described disc brake configuration. At this time, the pad clearance C between the brake pad 41 and the disk rotor 23 can be kept constant. Thereby, it is possible to prevent uneven wear and drag of the brake pad 41 and to suppress an increase in the starting torque of the railway vehicle.

  Therefore, according to the disc brakes 100, 200, 300, and 400 according to the present embodiment, the piston-side brake pad assembly 25 and the anti-piston-side brake pad assembly 27 are both rotors of the disc rotor 23 when the brake is released, although the floating caliper 21 is used. A substantially equivalent gap (clearance C) is obtained from the surface, and dragging during normal running can be eliminated.

  Moreover, according to the railway vehicle disc brake according to the present embodiment, it is possible to prevent uneven wear and drag of the brake pad 41 and to suppress an increase in starting torque of the railway vehicle.

  In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably. In addition, the material, shape, dimensions, number, arrangement location, and the like of each component in the above-described embodiment are arbitrary and are not limited as long as the present invention can be achieved.

11 ... caliper return mechanism 13 ... support 15 ... base 17 ... piston side pressing arm (one pressing arm)
19: Anti-piston side pressing arm (the other pressing arm)
21 ... Floating caliper 23 ... Disc rotor 25 ... Piston side brake pad assembly (one brake pad assembly)
27 ... Anti-piston brake pad assembly (the other brake pad assembly)
29 ... Drive piston 45 ... Sensor lever support member 47 ... Sensor lever 49 ... Transmission lever support member 51 ... Transmission lever 53 ... Fixing member 55 ... First link mechanism 57 ... fulcrum pin (fulcrum pin of sensor lever support member)
59 ... Sensor lever pad end (one rotation end of the sensor lever)
61 ... fulcrum pin (fulcrum pin of transmission lever support member)
63 ... Transmission lever support end (one rotation end of the transmission lever)
65 ... Spring mechanism 67 ... Second compression spring 69 ... Sensor lever link end (the other rotation end of the sensor lever)
73 ... transmission lever link end (the other rotation end of the transmission lever)
75: Holder transmission lever end (the other end of the first link mechanism)
77 ... Spring holder 79 ... First compression spring 81 ... Supporting pin (supporting pin at the end of the sensor lever link)
83 ... fulcrum pin (fulcrum pin at the end of transmission lever link)
100: Disc brake

Claims (11)

A floating caliper having a base slidably supported via a guide pin with respect to a cylindrical support portion of the support, and a pair of pressing arms extending from the base to a position sandwiching the disk rotor from both axial sides When,
A pair of brake pad assemblies respectively provided at the tip portions of the pair of pressing arms so as to face the side surfaces of the disk rotor;
A drive piston provided on one pressing arm of the pair of pressing arms to drive one of the brake pad assemblies toward the side surface of the disk rotor;
A caliper return mechanism interposed between the one brake pad assembly and the support so that a predetermined amount of the displacement amount of the one brake pad assembly becomes the displacement amount of the floating caliper;
A disc brake comprising: The disc brake according to claim 1,
The caliper return mechanism is
A sensor lever support member fixed to the one pressing arm;
A sensor lever that is rotatably supported around an intermediate portion by a fulcrum pin of the sensor lever support member, and whose one rotation end is in contact with the one brake pad assembly;
A transmission lever support member fixed to the one pressing arm;
A transmission lever that is rotatably supported around an intermediate portion by a fulcrum pin of the transmission lever support member, and whose one rotation end abuts on the support;
A first link mechanism in which one end is rotatably connected to the other rotation end of the sensor lever and the other end is rotatably connected to the other rotation end of the transmission lever;
A disc brake comprising: The disc brake according to claim 2, wherein
One rotating end of the transmission lever is
A disc brake, wherein the disc brake is elastically biased in a direction in which it abuts against the support by a spring mechanism. The disc brake according to claim 3, wherein
The spring mechanism is
A spring holder for holding the fulcrum pin of the other rotation end of the sensor lever and the fulcrum pin of the other rotation end of the transmission lever so as to be movable relative to each other;
A first compression spring interposed in a compressed state between a fulcrum pin at the other rotation end of the sensor lever and a fulcrum pin at the other rotation end of the transmission lever;
A second compression spring interposed in a compressed state between the transmission lever and a fixing member fixed to the support;
A disc brake comprising: The disc brake according to claim 1,
The caliper return mechanism is
A sensor lever support member fixed to the one pressing arm;
A sensor lever that is rotatably supported around an intermediate portion by a fulcrum pin of the sensor lever support member, and whose one rotation end is in contact with the one brake pad assembly;
A transmission lever support member fixed to the one pressing arm;
A transmission lever supported by a fulcrum pin of the transmission lever support member so as to be rotatable about an intermediate portion;
A connecting member that connects the other rotation end of the sensor lever and the other rotation end of the transmission lever so as to be relatively rotatable with each other;
A fixing member fixed to the support;
A second link mechanism having one end rotatably connected to one rotation end of the transmission lever and the other end connected to the fixing member;
A disc brake comprising: The disc brake according to claim 5, wherein
One rotating end of the transmission lever is
A disc brake, wherein the disc brake is elastically urged relative to the fixed member by a spring mechanism. The disc brake according to claim 6, wherein
The spring mechanism is
A spring holder connected to the fixing member so as to be relatively movable, and holding a fulcrum pin at one rotation end of the transmission lever so as to be relatively movable;
A third compression spring interposed in a compressed state between a fulcrum pin at one rotation end of the transmission lever and a spring receiver as the other end of the second link mechanism;
A fourth compression spring interposed in a compressed state between a spring receiver supported at the tip of a support pin that has passed through the through hole of the spring receiver and the fixing member from the transmission lever side, and the fixing member;
A disc brake comprising: The disc brake according to claim 1,
The caliper return mechanism is
A rotating shaft fixing member fixed to the one pressing arm;
A lever rotating shaft rotatably supported by the rotating shaft fixing member;
A sensor lever fixed to one end of the lever rotation shaft and having a rotating tip abutting against the one brake pad assembly;
A transmission lever which is fixed to the other end of the lever rotation shaft and whose rotation tip is maintained at a predetermined interval with respect to the support;
A disc brake comprising: The disc brake according to claim 8, wherein
The rotating tip of the transmission lever is
A disc brake, wherein the disc brake is elastically biased in a direction facing the support by a spring mechanism. The disc brake according to claim 9, wherein
The spring mechanism is
A spring backing plate fixed to the support;
A support pin in which a tip penetrating the through hole of the spring receiving plate comes into contact with a rotating tip of the transmission lever;
A compression spring interposed in a compressed state between the intermediate support portion of the support pin and the spring receiving plate;
A tension spring interposed in a tension state between the support pin and the rotation tip of the transmission lever;
A disc brake comprising:   A disc brake for railway vehicles, comprising the disc brake according to any one of claims 1 to 10.

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