JP4750680B2 - Disc brake - Google Patents

Description

  The present invention relates to a disc brake that is preferably used to give a braking force to a vehicle or the like, for example.

  In general, as a disc brake configured to apply a braking force to a vehicle by supplying brake fluid pressure accompanying a depression operation of a brake pedal or the like, for example, a collet type caliper is used (see, for example, Patent Document 1) or a reverse pin Various types of disc brakes are known, such as those using a mold caliper (see, for example, Patent Document 2).

  Of this type of prior art, for example, a disc brake using a collet-type caliper has a pair of arms spaced apart in the circumferential direction of the disc and straddling the outer circumference of the disc, and is attached to a non-rotating portion of the vehicle A caliper that is slidably supported on each arm portion of the mounting member via a slide pin and straddles both sides of the disc between the arm portions, and is located on both sides of the disc A pair of friction pads and the like are movably mounted between the arm portions of the mounting member and pressed against both sides of the disk by the caliper.

  Here, each arm portion of the mounting member is provided with a pin fitting hole extending in the axial direction of the disk, and the base end side of the slide pin is fixedly mounted on the caliper. The slide pin is slidably inserted into the pin fitting hole of the arm portion so that the caliper is slidably assembled to the arm portion of the mounting member. It is something to support.

  On the other hand, in the disc brake using the reverse pin type caliper, a slide pin is fixedly provided on an attachment member attached to a non-rotating portion of the vehicle, and a pin fitting hole into which the slide pin is inserted is provided with a counterpart. It is set as the structure provided in a caliper.

JP 11-108089 A Japanese Patent Laid-Open No. 54-111058

  By the way, in the prior art by the above-mentioned patent document 1, each arm part of the attachment member attached to the non-rotating part of the vehicle has a structure straddling the outer peripheral side of the disk, and a slide pin on the caliper side is provided on these arm parts. It is set as the structure which provides the pin fitting hole inserted so that sliding is possible. For this reason, it is difficult to increase the heat capacity of the disk for the following reasons, which is a problem in improving the braking performance.

  That is, there is a demand for increasing the heat capacity of the disk as an evaluation of the braking performance. In order to increase the heat capacity of the disk, it is conceivable to increase its outer diameter or increase the thickness of the disk. However, in order to avoid interference with wheels, suspensions, etc., it is not practical to increase the disk thickness.

  On the other hand, with regard to the outer diameter of the disc, assuming that the arm portion of the mounting member and the like are placed inside the wheel (tire wheel) together with the disc, the outer diameter of the disc is equal to the thickness of the arm portion in the radial direction of the disc. The diameter will be constrained. However, the pin fitting hole is formed in the arm portion of the mounting member as described above.

  For this reason, if it is going to form the arm part of an attachment member in a sturdy structure by ensuring sufficient thickness in the surrounding wall part of the said pin fitting hole, the thickness of the whole arm part must be enlarged. If the thickness of the arm portion is to be ensured in this way, the outer diameter of the disk needs to be formed with a smaller diameter by the thickness of the arm portion.

  In particular, a vehicle such as a commercial vehicle has a configuration in which the wheel diameter (tire wheel diameter) is reduced for reasons such as economy even though the total weight itself is heavy. For this reason, the outer diameter size of the disk is restricted to be small by being affected by the wheel diameter and the thickness of the arm portion, and there is a problem that it is difficult to ensure the heat capacity of the disk.

  In addition, if wear of the friction pad progresses while the brake operation of the vehicle is repeated, the center of gravity position of the entire caliper deviates from the range of the slide pin fitting length with respect to the pin fitting hole, and the caliper supported by the mounting member Inclination or the like may easily occur. In such a case, since the slide pin is inclined in the pin fitting hole and the sliding resistance increases, the caliper cannot be smoothly displaced in the axial direction of the disk, and the drag torque There is a problem that causes it to occur.

  Therefore, measures such as increasing the number of slide pins provided in the caliper have been studied. However, in this case, for example, each slide pin needs to be slidably inserted into three pin fitting holes, and the caliper is supported at three points on the mounting member. High machining accuracy is required for each point. In addition, the number of bolts for fixing the slide pins also increases, leading to an increase in the number of parts and the number of assembly steps, and there is a problem that workability at the time of assembly is lowered.

  On the other hand, for example, in the prior art disclosed in Patent Document 2, since the slide pin is provided on the side of the mounting member attached to the non-rotating portion, the thickness of the portion of the mounting member that straddles the outer peripheral side of the disk is reduced. Thus, the outer diameter of the disk can be increased. However, in this case, there is a problem peculiar to the reverse pin type caliper, and it is difficult to increase the workability at the time of assembly due to an increase in the number of parts, and there is a problem that the manufacturing cost increases.

  Even in the case of a reverse pin type caliper, if wear of the friction pad progresses, the position of the center of gravity of the entire caliper moves toward the inner side in the axial direction of the disk, so the caliper supported by the mounting member In addition, there is a problem that a tilt or the like tends to occur, and the caliper cannot be smoothly displaced in the axial direction of the disk, which causes drag torque and the like.

  The present invention has been made in view of the above-described problems of the prior art, and an object of the present invention is to increase the outer capacity of the disk to increase the heat capacity, and to ensure a stable braking effect even during so-called fade. Another object of the present invention is to provide a disc brake that can stabilize the caliper posture over a long period of time and can improve the brake performance.

  Another object of the present invention is to reduce the thickness of the portion of the mounting member that straddles the outer peripheral side of the disk even when a collet caliper is used, and to improve workability during assembly. It is to provide a disc brake that can be used.

In order to solve the above-described problems, the present invention provides a mounting member that is disposed across a disk and is attached to a non-rotating portion of a vehicle at a position on the inner side, and an axial direction of the disk while being supported by the mounting member. and a caliper displaced, before Symbol mounting member provided with a pin fitting hole extending in the axial direction of the disc, provided with a slide pin slidably fitted in the pin fitting hole in the caliper Applies to disc brakes.

The feature of the configuration invention of claim 1 is employed, the pin fitting hole, the provided on the mounting member at a position where the inner side of the disk, before kissing Raidopin is base end the mounting is a stationary end fixed to the caliper located on the inner side of the member, slidably be fitted to Ru configured on the tip side in the pin fitting hole as a free end, said mounting member and the caliper The slide pin fitting length with respect to the pin fitting hole is located within the axial range of the disc and faces in the radial direction of the disc, and the caliper is placed between the opposing surface portions of the disc. The biasing means for biasing radially outward is provided.

According to the invention of claim 2, wherein the biasing means are configured so as to place the axial position overlapping with the center of gravity of the caliper in the axial direction of the disk.

According to a third aspect of the present invention, the urging means is provided at positions spaced apart from each other in the circumferential direction of the disk together with the pin fitting hole and the slide pin, and the respective urging members are attached to the vehicle. while biasing member located on the lower side of the member, it is as configuration than the other biasing member located on the upper side is set to an urging force larger becomes.

According to a fourth aspect of the present invention, the pin fitting hole and the slide pin are provided at positions separated from each other in the circumferential direction of the disk, and the pin fitting hole and the slide pin are mounted in a state where the attachment member is attached to the vehicle. one pin fitting hole located on the lower side of, are be provided with a biasing member only with respect to the slide pin.

As described above, according to the invention described in claim 1, pin fitting hole is provided in the mounting member at a position where the inner side of the disk, the scan Raidopin is base end on the inner side of the mounting member position to become a fixed end fixed to the caliper, the a structure in which the distal end side is slidably inserted into the pin fitting hole as a free end, to said mounting member and the caliper, before Symbol pin fitting located within the axial extent of the disk of engagement length of the slide pin relative to the hole is formed face to face in the radial direction of the disk, urges the caliper radially outwardly of the disc between the counter surface since the configuration in which the biasing means for, for example, it is not necessary to provide a pin fitting hole in a portion across the outer periphery of the disc out of the mounting member, both can be reduced the thickness of this portion, dimension of which corresponds to this Only It is possible to increase the outer diameter of the disk. By increasing the outer diameter of the disk, the heat capacity can be increased, and a stable braking effect can be ensured even during so-called fade.

The biasing means provided between the facing surface portions of the mounting member and the caliper biases the caliper outward in the radial direction of the disk at a position within the range of the slide pin fitting length with respect to the pin fitting hole. Therefore, the sliding resistance added between the slide pin and the pin fitting hole due to the weight of the caliper can be reduced by the biasing force of the biasing means, and the sliding resistance between the two can be kept small. . The entire caliper can be maintained in a stable support state by a slide pin inserted into the pin fitting hole, and the caliper posture can be maintained for a long time while restraining the caliper from tilting with respect to the mounting member by the biasing means. And the generation of drag torque can be suppressed, and the braking performance can be improved.

Further, provided on the mounting member pin fitting hole at a position where the inner side of the disc, the slide pin has a configuration in which fixed to the caliper, the disk against the disk brake using a so-called collet type caliper The heat capacity can be increased by increasing the outer diameter dimension of the motor, and a stable braking effect can be ensured even during so-called fading. The entire disc brake can be reduced in size by taking advantage of the collet type caliper, and the weight can be reduced.

  In particular, in the case of a collet type caliper, unlike the reverse pin type caliper, the position where the slide pin is fixed to the caliper by the bolt is greatly separated from the torque receiving portion of the mounting member. The acting bending moment can be kept small, and the bolt can be easily loosened. Further, by providing the pin fitting hole at a position near the torque receiving portion, it is possible to efficiently reduce the weight of the entire brake while ensuring the rigidity of the mounting member in the vicinity of the torque receiving portion.

The key Yaripa, in which case the center of gravity is a configuration located within the engagement length of the slide pin relative to the pin fitting hole, the support state in which the entire caliper stable by slide pins which are inserted into the pin fitting hole Thus, the sliding resistance between the slide pin and the pin fitting hole can be kept small, and the braking performance can be improved.

When the biasing means is arranged at an axial position that overlaps the center of gravity of the caliper in the axial direction of the disk, the caliper is placed at the position of the center of gravity so that the sliding resistance between the slide pin and the pin fitting hole is reduced. The urging means can continue to urge the disk radially outward, thereby stabilizing the caliper posture and supporting the entire caliper with a slide pin inserted into the pin fitting hole. Meanwhile, smooth sliding displacement of the slide pin can be ensured.

The pre-Symbol biasing means, when the friction pad has a structure in which the center of gravity of the caliper over until reaching the replacement time from new state placed within the movement track moving repeats the braking operation of the vehicle Even if the friction pad wears out, the caliper is positioned at its center of gravity so that the sliding resistance between the slide pin and the pin fitting hole is reduced until the friction pad reaches a predetermined replacement time. Thus, the urging means can continue to be urged outward in the radial direction of the disk, and the entire caliper can be maintained in a stable support state over a long period of time. And the drag of the brake accompanying abrasion of a friction pad can be reduced, and the judder-proof performance at the time of deterioration can also be improved.

Biasing means in the case where the structure is a pad spring formed as a separate body, together with the urging means can be formed by using a different thickness (or different materials) and pad spring, for biasing the caliper The biasing means can be manufactured by selecting a suitable dedicated spring material, plate thickness or the like. Thereby, the yield of materials and the like can be improved, and inexpensive manufacturing becomes possible.

The case where the structure forms a biasing means integral with the pad spring may both be formed of a material of a single (identical) achieve reduction of number of parts, improve the workability during assembly can do.

When the biasing means is fixed to the caliper, the biasing means can be fixedly provided at the position of the center of gravity of the caliper, and the caliper posture is always kept stable even when the friction pad is worn. be able to.

The biasing means, when said pin fitting hole and the direction perpendicular to the axial direction of the slide pin and configured to urge the mounting member and the caliper opposite to each other, and the slide pin biasing force of the biasing means It is possible to transmit in the orthogonal direction, and the sliding property of the slide pin with respect to the pin fitting hole can be improved while maintaining the posture of the slide pin in a stable state.

Member and any one of the caliper Mounting, in the case of the configuration where the biasing means to form a guide groove forming a concave shape in a portion abutting the by the braking torque when pressed friction pads to the disc of the caliper Even if the caliper is slightly elastically deformed due to the rotational moment acting on the inner side, the urging means can be elastically deformed in the same direction by the guide groove at this time, and when the braking is released, the urging means is restored. The caliper can be immediately returned to the state before braking by force. For this reason, it is possible to stabilize the caliper posture with respect to the mounting member, to reduce the drag of the brake accompanying wear of the friction pad, and to improve the anti-judder performance at the time of deterioration over time.

One biasing member located on the lower side of the two biasing members members Mounting in a state attached to the vehicle, and than the other biasing member on the upper side is configured to be set to the biasing force larger becomes In this case, it is possible to effectively prevent the slide pin from rattling within the pin fitting hole located on the lower side of both sides in the circumferential direction of the disk, while maintaining the posture of the slide pin in a stable state, The slide pin can be smoothly slid with respect to the pin fitting hole.

Each pin fitting holes of the member Mounting in a state attached to the vehicle, one of the pin fitting hole located on the lower side of the slide pins, the case of the configuration in which the biasing member only with respect to the slide pin By simply using a single biasing means, it is possible to prevent the slide pin from rattling within the pin fitting hole located on the lower side of both sides in the circumferential direction of the disk. Can be smoothly slid and displaced. In this case, the number of parts can be reduced to improve workability during assembly.

When the clearance between each pin fitting hole and each slide pin is larger on the one side in the circumferential direction of the disc than on the other side, the two biasing means are biased on the one side in the circumferential direction where the clearance is larger than the other side. in case of the configuration to increase the forces, that the slide pin or backlash in the pin fitting hole at one side of the large circumferential direction of the clearance can be suppressed by the biasing force of the biasing means, each slide The pin can be smoothly slid and displaced with respect to the pin fitting hole.

Each pin fitting holes and spaced apart from each other in the circumferential direction of the disk, the pin fitting hole towards clearance greater of the slide pins, the case of the configuration in which the biasing member only with respect to the slide pin, single By simply using the biasing means, it is possible to prevent the slide pin from rattling in the pin fitting hole with the larger clearance on both sides in the circumferential direction of the disk. Smooth sliding displacement is possible. In this case, the number of parts can be reduced to improve workability during assembly.

An abutment surface of the biasing means, in the case of forming a sliding surface frictional coefficient is small, the sliding characteristics of the caliper relative to the mount member is being reduced been influenced by contact with or contact portions between the biasing means The slide pin can be smoothly slid with respect to the pin fitting hole, and the caliper can be stabilized. Further, the contact surface of the urging means is provided with an inclusion such as a lubricant to make it a sliding surface, thereby preventing the contact surface of the urging means from being affected by rust due to change over time. The sliding characteristics on the contact surface of the urging means can be kept good.

  Hereinafter, a case where the disc brake according to the embodiment of the present invention is applied to a vehicle such as a four-wheel automobile will be described in detail with reference to the accompanying drawings.

  Here, FIG. 1 to FIG. 21 show a first embodiment of the present invention. In the figure, reference numeral 1 denotes a disk that rotates together with the wheels of the vehicle. The disk 1 is formed as a rotating disk having an outer diameter R, as illustrated by a two-dot chain line in FIGS. Is.

  An attachment member 2 is attached to a non-rotating part of the vehicle. The attachment member 2 is made of a metal material having high rigidity, such as steel or aluminum alloy, and is formed into an elongated, substantially rectangular frame shape as shown in FIGS. It is integrally formed as a body. And the attachment member 2 is shape | molded from the below-mentioned one side frame board 3, the other side frame board 5, and the left and right joint frame boards 6 and 6 as a highly rigid integral (cast product). .

  Reference numeral 3 denotes one side frame plate of the mounting member 2, and the one side frame plate 3 extends in the circumferential direction of the disk 1 at a position radially inward of the disk 1 with respect to a friction pad 16 described later, for example, as shown in FIG. The mounting plate portion 3A and a pair of left and right protruding plate portions 3B and 3B protruding from both sides in the length direction of the mounting plate portion 3A toward the outer side in the radial direction of the disk 1. Then, the mounting plate portion 3A and each protruding plate portion 3B of the one-side frame plate 3 are located on one side (inner side) of the disk 1 as shown in FIG. It extends.

  Further, each protruding plate portion 3B of the one side frame plate 3 is disposed at a position sandwiching an inner friction pad 16 described later from both sides in the circumferential direction of the disk 1 as shown in FIGS. A joint frame plate 6 to be described later is integrally formed on the projecting end side of the projecting plate portion 3B, and a flat surface portion 3C having a substantially horizontal surface is formed between the pad guide portion 3D and the joint frame plate 6 to be described later. It has become.

  Here, on both sides in the length direction of the mounting plate portion 3A, as shown in FIGS. 8 and 12, the left and right positions are located on the radially inner side of the disk 1 with respect to the pad guide portion 3D and pin fitting hole 4A described later. A pair of screw holes 3A1, 3A1 is formed. A fixing bolt (not shown) is screwed into these screw holes 3A1, and the mounting plate portion 3A of the mounting member 2 is a knuckle portion (not shown) which becomes a non-rotating portion of the vehicle by the fixing bolt. It is attached in a fixed state.

  Further, the left and right protruding plate portions 3B and 3B are provided with inner side pad guide portions 3D and 3D at positions on the inner side in the radial direction of the disc 1 with respect to the flat surface portion 3C. As shown in FIG. 21, it is formed as a U-shaped notch having a notch width W. And in this pad guide part 3D, the ear | edge part 17A of the friction pad 16 (back metal 17) mentioned later is slidably inserted via the pad spring 19, respectively.

  Further, the bottom side of each pad guide portion 3D constitutes an inner side torque receiving portion 3E, and these inner side torque receiving portions 3E send braking torque from the friction pad 16 via a pad spring 19 described later. It will be accepted.

  Reference numerals 4 and 4 are pin guide cylindrical protrusions integrally formed on the projecting plate portions 3B and 3B of the mounting member 2 (one side frame plate 3). Each cylindrical protrusion 4 is shown in FIGS. As shown in FIG. 15, it is formed as a stepped cylindrical body projecting from each projecting plate portion 3B of the one side frame plate 3 toward the outer side in the axial direction of the disk 1, and its inner peripheral side is the thickness of the projecting plate portion 3B It is a bottomed pin fitting hole 4A extending in the direction (the axial direction of the disk 1). A slide pin 13 described later is slidably inserted into the pin fitting hole 4A.

  Here, these pin fitting holes 4A are arranged at positions where the overall length is closer to the inner side than the disk 1 as shown in FIGS. 5 and 7, and against the left and right torque receiving portions 3E and 3E. Are arranged at positions adjacent to each other in the circumferential direction of the disk 1 as shown in FIGS. Moreover, 4A of pin fitting holes are arrange | positioned in the position which becomes in the range of the notch width W (refer FIG. 21) with respect to pad guide part 3D. The center of the pin fitting hole 4A is preferably arranged at a position that coincides with the width center of the notch width W. Further, it is preferable to secure a thickness of a dimension T (for example, about T = 2 to 6 mm) shown in FIGS. 5, 7, and 15 on the bottom side of the pin fitting hole 4A.

  Further, the outer peripheral side of the cylindrical protrusion 4 is a latching portion 4B to which a later-described cylinder spring 20 is attached with a tightening margin as shown in FIG. 21, and the upper surface thereof (the surface on the radially outer side of the disk 1) A shallow concave groove portion 4C to which the cylinder spring 20 is engaged in the retaining state is formed (see FIGS. 14 and 15).

  Reference numeral 5 denotes the other side frame plate of the attachment member 2, and the other side frame plate 5 is disposed at a position facing the one side frame plate 3 with the disk 1 interposed therebetween as shown in FIGS. 10 and 11. The other side frame plate 5 extends substantially in parallel along the other side surface of the disc 1 so as to integrally connect between the below-described joint frame plates 6 and 6 on the outer side (other side) of the disc 1. . Here, the other side frame plate 5 has an elongated bar-like connecting beam portion 5A that extends in the left and right directions (circumferential direction of the disk 1) as shown in FIGS. 1 and 9, and the connecting beam portion. It is composed of a pair of left and right protruding plate portions 5B, 5B protruding from both sides in the length direction of 5A toward the radially outer side of the disk 1.

  As shown in FIGS. 1 and 9, the connecting beam portion 5A of the other side frame plate 5 extends in the circumferential direction of the disk 1 at a position radially inward of the disk 1 with respect to a friction pad 16, which will be described later. The right protruding plate portions 5B and 5B are integrally connected with rigidity. In addition, each protruding plate portion 5B of the other side frame plate 5 has a flat surface portion 5C, an outer side pad guide portion 5D, and an outer side torque, respectively, in substantially the same manner as the protruding plate portion 3B of the one side frame plate 3 described above. A receiving portion 5E and the like are formed.

  6 and 6 are a pair of left and right joint frame plates extending in the axial direction of the disc 1 so as to straddle the outer periphery of the disc 1, and the joint plate plates 6 and 6 are as shown in FIGS. The one side frame plate 3 and the other side frame plate 5 which are disposed in a position straddling the outer periphery of the disk 1 and extend in parallel with each other along both surfaces of the disk 1 are arranged on both sides in the length direction (the circumferential direction of the disk 1). Are connected together.

  Here, each joint frame plate 6 is formed as a thin plate body slightly curved along the outer periphery of the disk 1 as shown in FIG. 8, and the plate thickness t is the thickness of the arm portion described in the prior art. The thickness is set to 1/2 or less (for example, t = about 5 to 10 mm). As a result, the outer diameter R of the disk 1 can be increased by, for example, about 8 to 15 mm as compared with the current product, and the heat capacity of the disk 1 can be increased.

  A caliper 7 is slidably supported by the mounting member 2, and the caliper 7 includes a bridge portion 8 extending in the axial direction across the outer peripheral side of the disk 1 as shown in FIGS. 1 to 8, and the bridge portion 8. Is formed integrally on one side of the disk 1 and is disposed on the inner side of the disk 1 as an inner leg, and is formed on the other side of the bridge part 8 and is disposed on the outer side of the disk 1. The outer leg portion 10 includes claws 10A and 10A having a bifurcated shape as shown in FIG.

  On the other hand, a cylinder bore 9A is formed in the cylinder portion 9 of the caliper 7, as shown in FIG. 6, and a piston 12 is slidably inserted into the cylinder bore 9A. The cylinder bore 9A is configured to drive the piston 12 toward a friction pad 16, which will be described later, by supplying brake fluid pressure from a master cylinder (not shown) of the vehicle, for example.

  As shown in FIGS. 2 and 3, the caliper 7 is integrally provided with a pair of mounting portions 11 and 11 that project in a substantially L shape from both the left and right sides of the cylinder portion 9 and extend in the circumferential direction of the disk 1. It has been. Further, as shown in FIGS. 5 and 7, slide pins 13 described later are fixedly attached to these attachment portions 11 by fastening bolts 14. In this case, the attachment portion 11 of the caliper 7 extends to a position that is closer to the inner side than the cylindrical protrusion 4 of the attachment member 2, and is disposed opposite to the cylindrical protrusion 4 in the axial direction of the disk 1. .

  Further, as shown in FIGS. 1 and 8, flat slidable contact surface portions 9 </ b> B and 9 </ b> B are formed in the cylinder portion 9 of the caliper 7 at positions facing a cylinder spring 20 (described later) in the radial direction of the disk 1. An urging plate portion 22 of a cylinder spring 20 described later elastically abuts on these sliding contact surface portions 9B, and the cylinder portion 9 which is an inner leg portion of the caliper 7 is connected to the disk 1 by the urging plate portion 22. It is always urged toward the radially outer side.

  Here, the caliper 7 is arranged at a position where the entire center of gravity G including the piston 12 and the slide pin 13 described later is a dimension La from the tip of the slide pin 13 as shown in FIG. G is accommodated within a range of a fitting length Lt of a slide pin 13 described later with respect to the pin fitting hole 4A. That is, the shape of the caliper 7 is designed and formed so as to satisfy the condition of the gravity center position G.

  13 and 13 are slide pins provided on each mounting portion 11 of the caliper 7. Each slide pin 13 has a base end side on the cylinder portion 9 side through fastening bolts 14 and 14 as shown in FIGS. These are fixed ends fixed to the respective attachment portions 11, and the distal end side is a free end and is slidably inserted into the pin fitting hole 4 </ b> A of the attachment member 2. Accordingly, the caliper 7 is slidably supported by the mounting member 2 via the slide pin 13.

  Here, the slide pin 13 is set such that the fitting length Lt of the mounting member 2 to the pin fitting hole 4A is as shown in FIG. 7, and the center of gravity position G of the caliper 7 including the piston 12 and the slide pin 13 is It is within the range of this fitting length Lt. The center-of-gravity position G is within the range of the fitting length Lt until a friction pad 16 described later reaches a replacement time from a new state.

  Reference numerals 15 and 15 denote protective boots for protecting the slide pins 13 from the outside. The protective boots 15 are formed in an accordion shape using, for example, an elastic resin material, and the cylindrical protrusions 4 of the mounting member 2 and the slide pins. 13 is attached. The protective boot 15 covers the periphery of the proximal end side of the slide pin 13 to prevent foreign matters such as rainwater and dust from entering between the slide pin 13 and the pin fitting hole 4A.

  Reference numerals 16 and 16 denote inner and outer friction pads disposed on both sides of the disk 1. Each of the friction pads 16 is a back metal 17 formed in a substantially fan shape as shown in FIGS. And a lining 18 made of a friction material fixedly provided so as to be superposed on the surface side of the back metal 17. Further, as shown in FIGS. 1 and 8, ears 17A and 17A having convex shapes corresponding to the inner side and outer side pad guide portions 3D and 5D project from the both ends of the back metal 17 in the length direction. Has been.

  Here, the inner side friction pad 16 is slidably inserted into the inner side pad guide part 3D via a pad spring 19 described later, as shown in FIG. . Further, the outer side friction pad 16 is slidably inserted into the outer side pad guide part 5D via a pad spring 19 described later, as shown in FIG.

  As shown in FIG. 6, the friction pads 16 are arranged opposite to both sides of the disk 1, and the piston 12 is pushed by the brake hydraulic pressure in accordance with the brake operation of the vehicle, so that the claw portion of the caliper 7. The disk 1 is pressed between 10A and the piston 12 so as to sandwich the disk 1 from both sides, thereby applying a braking force to the disk 1.

  In this case, braking torque when each friction pad 16 is pressed against the disk 1 by the caliper 7 is transmitted from the ear portion 17A of the friction pad 16 (back metal 17) to the torque receiving portions 3E and 5E of the mounting member 2, and the mounting member. The two projecting plate portions 3B, 5B and the like receive the rotational torque (braking torque) from the disk 1.

  19 and 19 are a pair of left and right pad springs provided on the mounting member 2 so as to be spaced apart from each other in the circumferential direction of the disk 1. Each pad spring 19 is a stainless steel plate having a spring property (for example, a plate thickness of 0.1 mm). 16 mm) is integrally formed by bending as shown in FIG. 16 using means such as press working.

  The pad spring 19 includes a pair of guide plate portions 19A and 19A that are spaced apart from each other on the inner side and the outer side, a connecting plate portion 19B that integrally connects the guide plate portions 19A, and each guide plate portion 19A. The inner side and outer side pad urging portions 19C, 19C and the like are arranged at positions on the inner side in the radial direction.

  Here, the guide plate portion 19A of the pad spring 19 is fitted and mounted in the pad guide portions 3D and 5D of the mounting member 2 as shown in FIGS. 9 to 13, and the inner side and outer side friction pads are fitted. 16 is slidably guided in the axial direction of the disk 1 through the respective ear portions 17A of the back metal 17.

  Each pad urging portion 19 </ b> C elastically urges the inner and outer friction pads 16 from the radially inner side to the outer side of the disk 1. As a result, the pad spring 19 stabilizes and smoothes the movement (sliding displacement) of the friction pad 16 in the axial direction of the disk 1.

  Reference numerals 20 and 20 denote cylinder springs constituting the urging means of the caliper 7, and each cylinder spring 20 is separated from the pad spring 19 by using a stainless steel plate having a spring property (for example, a plate thickness of about 1.2 mm). It is formed on the body and is formed by bending as shown in FIGS. The cylinder spring 20 includes a sandwiching plate portion 21 that is bent into a substantially U-shape, and an urging plate portion 22 that is formed by folding the sandwiching plate portion 21 obliquely upward.

  Here, the sandwiching plate portion 21 of the cylinder spring 20 has a flat surface portion 21A on the upper side (a portion on the outer side in the radial direction of the disk 1), and between the side plate portions 21B and 21C located on both sides of the flat surface portion 21A. Thus, the latching portion 4B of the cylindrical projection 4 is clamped with a tightening margin as shown in FIG. The flat surface portion 21 </ b> A of the sandwiching plate portion 21 is brought into contact with the concave groove portion 4 </ b> C of the cylindrical protrusion 4 with a wide contact area.

  Further, the urging plate portion 22 of the cylinder spring 20 is formed so as to be folded diagonally upward in a substantially U shape from the side plate portion 21 </ b> B of the clamping plate portion 21. As shown in FIG. 8, the urging plate portion 22 of the cylinder spring 20 is in elastic contact with the sliding contact surface portion 9B of the caliper 7 (cylinder portion 9) from below, and the cylinder portion 9 of the caliper 7 is indicated by an arrow. It is urged toward the outer side in the radial direction of the disk 1 in the B direction.

  In this case, the urging plate portion 22 of the cylinder spring 20 is located within the range of the fitting length Lt of the slide pin 13 with respect to the pin fitting hole 4A and at a position overlapping the center of gravity G of the caliper 7 in the axial direction of the disk 1. Has been placed. Even when the center of gravity position G of the caliper 7 moves from the new state to the replacement time, the urging plate portion 22 of the cylinder spring 20 moves its movement locus (FIG. 5, FIG. 5). It is arranged within the range of dimension Lb) shown in FIG.

  The urging plate portion 22 of the cylinder spring 20 has a sliding surface 22A made of a self-lubricating material such as polytetrafluoroethylene at a portion (contacting surface) that contacts the sliding contact surface portion 9B of the cylinder portion 9. For example, it is formed using means such as coating. The cylinder spring 20 is not limited to the contact portion of the urging plate portion 22, and a lubricating film may be formed over the entire surface of the clamping plate portion 21 and the urging plate portion 22.

  The disc brake according to the present embodiment has the above-described configuration, and the operation thereof will be described next.

  First, when the brake fluid pressure from a master cylinder (not shown) is supplied into the cylinder portion 9 (cylinder bore 9A shown in FIG. 6) of the caliper 7 in accordance with the brake operation of the vehicle, the piston 12 in the cylinder portion 9 is The brake fluid pressure at this time slides and displaces in the axial direction of the disk 1 and presses the friction pad 16 on the inner side (cylinder portion 9 side) toward one side of the disk 1.

  At this time, the entire caliper 7 is attached to the mounting member 2 so that the slide pin 13 is displaced relative to the pin fitting hole 4A in the direction indicated by the arrow A in FIGS. On the other hand, the disc 1 is slid and displaced in the axial direction of the disc 1 (arrow A direction), whereby each claw portion 10A of the outer leg 10 presses the outer friction pad 16 toward the other side of the disc 1.

  For this reason, the disk 1 is strongly sandwiched by the inner friction pad 16 and the outer friction pad 16 from both sides, and applies a braking force to a running vehicle, for example. Further, when the brake operation is released, the friction pads 16 are separated from both sides of the disc 1 and the braking force on the vehicle is released.

  By the way, when the inner and outer friction pads 16 are pressed against both surfaces of the disk 1 in order to apply braking force to the vehicle, the rotational torque (braking torque) from the disk 1 becomes the ears 17A of the friction pads 16 and the like. Are added to the torque receiving portions 3E and 5E of the mounting member 2 and are also added to the cylinder portion 9 and the outer leg portion 10 of the caliper 7.

  However, the braking torque applied to the cylinder portion 9 side of the caliper 7 is received between the pin fitting hole 4 </ b> A of the cylindrical protrusion 4 provided on the one side frame plate 3 of the mounting member 2 and the slide pin 13. Thus, the deformation of the cylinder portion 9 and the like of the caliper 7 due to the influence of the braking torque can be suppressed by the slide pin 13 and the like inserted into the pin fitting hole 4A.

  Further, the attachment member 2 includes a side frame plate 3 and another side frame plate 5 extending in parallel with each other along both surfaces of the disk 1, and both ends in the length direction of the one side frame plate 3 and the other side frame plate 5. The left and right joint frame plates 6 and 6 connected across the outer periphery of the disk 1 are integrally formed as an elongated, substantially rectangular frame (see FIG. 11) having high rigidity. Therefore, the mounting member 2 can be formed in a sturdy structure while being reduced in size and weight, and the braking torque received by the torque receiving portions 3E and 5E on the inner side and the outer side of the disk 1 is applied to the entire mounting member 2. Can be supported stably.

  In addition, a cylinder spring 20 is provided between the cylindrical protrusion 4 of the mounting member 2 and the cylinder portion 9 of the caliper 7 to urge the cylinder portion 9 outward in the radial direction of the disk 1. 20 is arranged at a position that falls within the range of the fitting length Lt of the slide pin 13 with respect to the pin fitting hole 4A. For this reason, the sliding resistance added between the slide pin 13 and the pin fitting hole 4A due to the weight of the entire caliper 7 including the piston 12 and the like can be reduced by the urging force of the cylinder spring 20. The sliding resistance can be kept small.

  On the other hand, the lining 18 of the friction pad 16 is gradually worn while the brake operation as described above is repeated. When the wear of the lining 18 is increased and the replacement time of the friction pad 16 is reached, the slide pin 13 is pulled out from the pin fitting hole 4A of the cylindrical protrusion 4 (the direction indicated by the arrow A in FIGS. 5 and 7). ), The fitting length Lt of the slide pin 13 with respect to the pin fitting hole 4A is shortened by the thickness corresponding to the wear allowance of the lining 18.

  However, even in this case, since the cylinder portion 9 of the caliper 7 is urged toward the radially outer side of the disk 1 by the cylinder spring 20, the caliper 7 together with the slide pin 13 inserted into the pin fitting hole 4A is used. The whole can be maintained in a stable support state, and the caliper 7 can be prevented from being inclined with respect to the mounting member 2 by the cylinder spring 20.

  Thus, according to the present embodiment, the cylindrical protrusion 4 protruding in the axial direction of the disk 1 is integrally formed on the one side frame plate 3 of the mounting member 2, and one side is formed in the cylindrical protrusion 4. A bottomed pin fitting hole 4A extending in the thickness direction of the frame plate 3 is provided, and the pin fitting hole 4A is disposed at a position on the inner side of the disk 1 over the entire length (full length). The caliper 7 is formed so that its center of gravity G exists within the range of the fitting length Lt of the slide pin 13 with respect to the pin fitting hole 4A.

  For this reason, it is not necessary to provide the pin fitting hole in the portion (for example, the portion corresponding to the joint frame plate 6) straddling the outer peripheral side of the disk 1 in the mounting member 2, and the thickness t of the joint frame plate 6 is illustrated. As shown in FIG. 8, the thickness can be reduced to about 5 to 10 mm, for example, and the thickness can be reduced to, for example, 1/2 or less compared to the thickness of the arm described in the related art.

  As a result, the outer diameter R of the disk 1 can be increased to, for example, about 8 to 15 mm as compared with the current product, and the heat capacity is increased by increasing the outer diameter R of the disk 1. Therefore, a stable braking effect can be ensured even during so-called fading.

  Further, the cylindrical projection 4 of the mounting member 2 is provided with the clamping plate portion 21 of the cylinder spring 20 fitted in the latching portion 4B in a retaining state, and the urging plate portion 22 of the cylinder spring 20 is provided with the caliper 7. The caliper 7 is placed on the disk 1 at a position within the range of the fitting length Lt of the slide pin 13 with respect to the pin fitting hole 4A by elastically contacting the flat sliding contact surface portion 9B of the (cylinder portion 9). It is set as the structure urged | biased to radial direction outward (arrow B direction in FIG. 8).

  For this reason, the sliding resistance acting between the slide pin 13 and the pin fitting hole 4A due to the weight (self-weight) of the caliper 7 can be reduced by the urging force of the cylinder spring 20, and the sliding resistance between the two can be reduced. It can be kept small. The entire caliper 7 can be maintained in a stable support state by the slide pin 13 inserted into the pin fitting hole 4A, the posture of the caliper 7 can be stabilized over a long period of time, and drag torque can be generated. Thus, the braking performance can be improved.

  Further, since the center of gravity G of the caliper 7 exists within the range of the fitting length Lt of the slide pin 13 with respect to the pin fitting hole 4A, the cylindrical protrusion on the one side frame plate 3 side of the mounting member 2 The slide pin 13 and the cylinder spring 20 that are inserted into the 4 pin fitting hole 4A can maintain the caliper 7 in a stable support state, and the caliper 7 is inclined with respect to the mounting member 2. Can be lost.

  Moreover, even when the gravity center position G of the caliper 7 moves in the direction indicated by the arrow A in FIGS. 5 and 7 until the friction pad 16 reaches the replacement time from the new state, the urging plate portion 22 of the cylinder spring 20 is used. Are arranged within the range of the movement locus (dimension Lb shown in FIGS. 5 and 7).

  For this reason, the entire caliper 7 can be maintained in a stable support state by the slide pin 13 inserted into the pin fitting hole 4A until the friction pad 16 reaches the replacement time from the new state. On the other hand, problems such as the caliper 7 tilting can be eliminated.

  In particular, the position of the center of gravity G of the entire caliper 7 including the slide pin 13 is kept within the range of the fitting length Lt from the time when the friction pad 16 reaches the replacement time from the new state, so that the brake operation of the vehicle can be performed. Even if wear of the friction pad 16 progresses repeatedly, the center of gravity position of the entire caliper 7 remains within the range of the fitting length Lt of the slide pin 13 with respect to the pin fitting hole 4A until the friction pad 16 reaches the replacement time. The entire caliper 7 can be kept in a stable support state for a long time.

  Therefore, according to the present embodiment, so-called brake drag and the like can be satisfactorily suppressed, the judder resistance against deterioration with time can be improved, and the brake performance can be improved. Moreover, the entire disc brake can be reduced in size by taking advantage of the so-called collet type caliper, and the weight can be reduced.

  Further, the pin fitting hole 4 </ b> A of the mounting member 2 is configured to be disposed at a position adjacent to the inner side torque receiving portion 3 </ b> E in the circumferential direction of the disk 1. For this reason, when the braking torque via the friction pad 16 is received by the inner torque receiving portion 3E, the bending moment acting between the pin fitting hole 4A and the slide pin 13 can be suppressed to a small level. The advantage of the so-called collet type caliper can be utilized.

  That is, when a collet-type caliper is employed as in the present embodiment, unlike the reverse pin-type caliper, the position where the slide pin 13 is fixed to the mounting portion 11 of the caliper 7 with the fastening bolt 14 is the torque receiving position. Since the position is far away from the portion 3E, the bending moment acting on the screwed portion of the fastening bolt 14 can be kept small, and the fastening bolt 14 can be easily loosened.

  Further, a pin fitting hole 4A is formed as a bottomed hole in a position close to the torque receiving portion 3E in the one side frame plate 3 of the mounting member 2, and a slide pin 13 is inserted into the pin fitting hole 4A. Therefore, it is easy to ensure the rigidity of the mounting member 2 in the vicinity of the torque receiving portion 3E, and the entire mounting member 2 can be reduced in size and efficiently reduced in weight.

  Further, in the present embodiment, the cylinder spring 20 is formed separately from the pad spring 19, so that the cylinder spring 20 is formed using a plate thickness (or a different spring material or the like) different from that of the pad spring 19. Can be formed. The cylinder spring 20 can be manufactured by selecting a dedicated spring material suitable for biasing the caliper 7, the plate thickness, etc., thereby improving the yield of the material and the like. Manufacture is possible.

  In the first embodiment, as shown in FIGS. 1 and 8, the cylinder portion 9 of the caliper 7 has flat sliding contact portions 9B and 9B at positions facing the cylinder spring 20 and the disk 1 in the radial direction. The case of forming is described as an example. However, the present invention is not limited to this. For example, as in the first modification shown in FIGS. 22 to 24, the guide groove portions 9B ′ and 9B ′ having a concave curved shape are formed in the cylinder portion 9 of the caliper 7. It is good.

  Here, the concave guide groove portions 9B 'and 9B' are formed on the back side of the cylinder portion 9 and the bridge portion 8 of the caliper 7 as shown in FIG. It extends along the axial direction. Then, as shown in FIG. 22, the urging plate portion 22 of the cylinder spring 20 abuts against the guide groove portion 9B ′ having the concave curved shape, so that the cylinder portion 9 of the caliper 7 is attached to the disk 1. Can always be urged toward the radially outer side (in the direction of arrow B).

  In this case, a rotational moment acts in the direction indicated by arrow C in FIG. 22 on the inner side (cylinder portion 9) of the caliper 7 by the braking torque when the friction pad 16 is pressed against the disk 1, and the caliper 7 is slightly elastic. Even if it is deformed, at this time, the urging plate portion 22 of the cylinder spring 20 can be elastically deformed in the same direction by the guide groove portion 9B ′. When the braking is released, the caliper 7 can be immediately returned to the state before the braking by the restoring force of the cylinder spring 20.

  For this reason, according to the disc brake according to the first modification, the guide groove portions 9B 'and 9B' having a concave curved shape are formed in the cylinder portion 9 of the caliper 7, thereby stabilizing the posture of the caliper 7 with respect to the mounting member 2. Thus, the drag of the brake accompanying the wear of the friction pad 16 can be reduced, and the anti-judder performance at the time of deterioration with time can be improved.

  Next, FIGS. 25 to 32 show a second embodiment of the present invention. The feature of this embodiment is that a cylinder spring as an urging means is formed integrally with a pad spring. . In the present embodiment, the same components as those in the first embodiment described above are denoted by the same reference numerals, and the description thereof is omitted.

  In the figure, 31 and 31 are pad springs employed in the present embodiment, and each pad spring 31 is formed in substantially the same manner as the pad spring 19 described in the first embodiment, for example, FIG. 26 to FIG. As also shown, a pair of guide plate portions 31A and 31A spaced apart from each other on the inner side and the outer side, a connecting plate portion 31B integrally connecting the guide plate portions 31A, and a guide plate portion 31A The inner side and outer side pad urging portions 31C, 31C and the like are arranged at positions on the radially inner side.

  However, the pad spring 31 in this case is different from the pad spring 19 according to the first embodiment in that it is integrally formed with a cylinder spring 32 described later. The pad spring 31 is formed by bending a stainless steel plate having a spring property (for example, a plate thickness of about 0.6 mm) as shown in FIG. It is integrally formed.

  Reference numeral 32 denotes a cylinder spring that constitutes an urging means for the caliper 7. The cylinder spring 32 has the same function as the cylinder spring 20 described in the first embodiment, but is formed integrally with the pad spring 31. Is different. As shown in FIG. 28, the cylinder spring 32 is composed of a base plate portion 32A and an urging plate portion 32B formed by folding the base plate portion 32A obliquely upward in a substantially U shape. Yes.

  Here, the base plate portion 32A of the cylinder spring 32 is integrally connected to the guide plate portion 31A on the inner side of the pad spring 31, and as shown in FIGS. 27 and 32, the mounting member 2 (one side frame plate 3) is connected. It is placed with a wide contact area on the flat surface portion 3C, the upper side surface of the cylindrical projection 4 (the portion that is the radially outer side of the disk 1), and the like.

  Further, the urging plate portion 32B of the cylinder spring 32 is formed such that the base end side is folded back from the base plate portion 32A into a substantially U shape, and the distal end side extends from the outer side in the circumferential direction of the disc 1 to the inner side. The urging plate portion 32 </ b> B of the cylinder spring 32 elastically abuts against the cylinder portion 9 side of the caliper 7 from below, and urges the cylinder portion 9 of the caliper 7 toward the radially outer side of the disk 1. It is.

  Further, the urging plate portion 32B of the cylinder spring 32 has a portion (contact surface) in contact with the back surface side of the cylinder portion 9 (for example, the sliding contact surface portion 9B illustrated in FIG. 8) such as polytetrafluoroethylene. A sliding surface 32C made of a self-lubricating material is formed using a means such as coating. The cylinder spring 32 is not limited to the contact portion of the urging plate portion 32B, and a lubricating film may be formed over the entire surface of the urging plate portion 32B, for example.

  Thus, even in the present embodiment configured as described above, the cylinder portion 9 of the caliper 7 can always be urged toward the radially outer side of the disk 1 by the cylinder spring 32, which is almost the same as the first embodiment. Similar effects can be obtained. In particular, in the present embodiment, since the cylinder spring 32 is formed integrally with the pad spring 31, the following effects can be obtained.

  That is, when the pad spring 31 integral with the cylinder spring 32 is assembled to the mounting member 2, the guide plate portion 31A of the pad spring 31 is placed in the pad guide portions 3D and 5D of the mounting member 2 as shown in FIG. At the same time, they are mounted on the flat surface portions 3C and 5C. When the pad spring 31 is assembled to the attachment member 2 in this manner, the base plate portion 32A side of the cylinder spring 32 is automatically positioned on the flat surface portion 3C of the attachment member 2 (one side frame plate 3). Therefore, the workability when the cylinder spring 32 is attached can be improved.

  Moreover, by forming the cylinder spring 32 integrally with the pad spring 31, both can be formed using a single material, so that the material cost can be reduced and the number of parts can be reduced. This makes it possible to easily manage components and the like.

Next, FIGS. 33 to 41 show a reference example of the present invention, wherein the reference example is that where the structure provided by fixing the cylinder spring as an urging means to the caliper. In the reference example , the same components as those in the first embodiment described above are denoted by the same reference numerals, and the description thereof is omitted.

In the figure, reference numerals 41 and 41 denote cylinder springs as urging means employed in the reference example . Each of the cylinder springs 41 is a stainless steel having a spring property substantially similar to the cylinder spring 20 described in the first embodiment. It is formed using a steel plate (for example, a plate thickness of about 1.2 mm), and is configured separately from a pad spring (not shown).

  However, the cylinder spring 41 in this case is different from the first embodiment in that the cylinder spring 41 is fixed to the cylinder portion 9 of the caliper 7. That is, the cylinder spring 41 includes a substantially rectangular fixing plate portion 41A that is fixed to the back surface side of the cylinder portion 9 using a fixing tool 42 such as a bolt, a screw, or a rivet, as shown in FIGS. The urging plate 41 </ b> B extends obliquely downward with respect to the plate 41 </ b> A, and the tip side is convexly curved in an arc shape.

  Here, the fixed plate portion 41 </ b> A of the cylinder spring 41 is arranged so that the urging plate portion 41 </ b> B is disposed at a position where the center of gravity position G (see FIGS. 34 and 35) of the caliper 7 overlaps with the axial direction of the disk 1. It is fixed to the back side of the part 9 using a fixing tool 42. The urging plate 41B of the cylinder spring 41 elastically contacts the cylindrical projection 4 side (a guide groove 43 described later) of the mounting member 2 from above, and the cylinder of the caliper 7 is caused by the elastic reaction force at this time. The portion 9 is urged toward the outer side in the radial direction of the disk 1 (the direction indicated by the arrow B in FIG. 33).

  Further, on the urging plate portion 41B of the cylinder spring 41, a sliding surface 41C made of a self-lubricating material such as polytetrafluoroethylene is coated on a portion (contact surface) that contacts a guide groove portion 43 described later. It is formed using means. The cylinder spring 41 is not limited to the contact portion of the urging plate portion 41B, and a lubricating film may be formed over the entire surface of the fixed plate portion 41A and the urging plate portion 41B.

  Reference numerals 43 and 43 are concave curved guide groove portions formed on the side of each cylindrical protrusion 4 of the attachment member 2, and each guide groove portion 43 is provided on the attachment member 2 (one side frame plate as shown in FIGS. 34 and 40). 3) extending from the flat surface portion 3C to the upper surface of the cylindrical projection 4 in the axial direction of the disk 1. The urging plate 41B of the cylinder spring 41 is elastically brought into contact with the guide groove 43 having a concave curved shape, and the cylinder portion 9 of the caliper 7 is moved radially outward of the disk 1 by the elastic reaction force at this time. It is always biased toward (in the direction of arrow B in FIG. 33).

Thus, even in the reference example configured as described above, the cylinder portion 9 of the caliper 7 can be urged toward the radially outer side of the disk 1 by the cylinder spring 41, and the operation is almost the same as that of the first embodiment. An effect can be obtained. In particular, in the reference example , since the cylinder spring 41 is fixed to the cylinder portion 9 of the caliper 7, the following operational effects can be achieved.

  That is, by fixing the cylinder spring 41 to the cylinder portion 9 of the caliper 7, the position of the cylinder spring 41 with respect to the center of gravity position G of the caliper 7 can be fixed. Can be urged radially outward. As a result, the posture of the caliper 7 can always be kept stable by the cylinder spring 41 even when the friction pad 16 is worn.

  Further, since the concave groove guide groove 43 is formed in the contact portion of the cylinder spring 41 in the mounting member 2, the following effects can be obtained. That is, a rotational moment acts in the direction of arrow C in FIG. 33 on the inner side (cylinder portion 9) of the caliper 7 by the braking torque when the friction pad 16 is pressed against the disk 1, and the caliper 7 is slightly elastically deformed. Even at this time, the urging plate 41B of the cylinder spring 41 can be elastically deformed in the same direction by the guide groove 43 at this time. When the braking is released, the caliper 7 can be immediately returned to the state before the braking by the restoring force of the cylinder spring 41.

For this reason, according to the disc brake according to the reference example , the guide groove portion 43 having a concave curve is formed in a portion extending from the flat surface portion 3C of the mounting member 2 (one side frame plate 3) to the upper surface of the cylindrical protrusion 4. In addition, the posture of the caliper 7 with respect to the mounting member 2 can be stabilized, the dragging of the brake accompanying the wear of the friction pad 16 can be reduced, and the anti-judder performance at the time of deterioration with time can be improved.

In the reference example , the case where the guide groove 43 having a concave curve is formed on the cylindrical protrusion 4 side of the mounting member 2 with which the cylinder spring 41 abuts has been described as an example. However, not limited to this, for example, a cylinder spring 41 is one that the site of contact with the mounting member may be formed as a flat sliding contact surface.

Next, FIGS. 42 and 43 show a third embodiment of the present invention. The feature of the present embodiment is that the urging force of the urging means located on the upper side with the disc brake attached to the vehicle is reduced. The load is set to be larger than the biasing means located on the side. In the present embodiment, the same components as those in the first embodiment described above are denoted by the same reference numerals, and the description thereof is omitted.

  In the figure, 51 and 52 are slide pins employed in the present embodiment, and the slide pins 51 and 52 are configured in the same manner as the slide pin 13 described in the first embodiment, and the base end side thereof is the caliper 7. Are fixed to the mounting portions 11, 11 using fastening bolts 14, 14, and the distal end side which is a free end is slidably inserted into the pin fitting holes 4 A, 4 A of the mounting member 2.

  However, in this case, the slide pins 51 and 52 are formed so that the slide pin 51 located on the upper side is slightly larger in diameter than the slide pin 52 located on the lower side when attached to the vehicle. The clearance S1 between the pin fitting hole 4A and the slide pin 51 is formed small, and the clearance S2 between the pin fitting hole 4A and the slide pin 52 is larger than the clearance S1 as shown in FIG. > S1).

  Reference numerals 53 and 54 denote cylinder springs as urging means employed in the present embodiment. The cylinder springs 53 and 54 are formed in substantially the same manner as the cylinder spring 20 described in the first embodiment. Thus, the pad springs 19 that are spaced apart above and below the friction pad 16 are configured as separate members (separate bodies).

  However, the cylinder springs 53 and 54 in this case have different urging forces F1 and F2, respectively, by changing their plate thickness or material. The cylinder spring 54 positioned on the lower side is set to have a larger urging force than the cylinder spring 53 positioned on the upper side in the mounting state on the vehicle. That is, the urging force F2 of the cylinder spring 54 located on the lower side in FIG. 42 is set to a load (F2> F1) larger than the urging force F1 of the cylinder spring 53 located on the upper side.

  Thus, also in the present embodiment configured as described above, the cylinder portion 9 of the caliper 7 can be urged toward the radially outer side of the disk 1 by the cylinder springs 53 and 54. Almost the same effect can be obtained.

  In particular, in the present embodiment, the biasing force F2 of the lower cylinder spring 54 is set to a load (F2> F1) larger than the biasing force F1 of the upper cylinder spring 53. Therefore, the following effects can be obtained.

  That is, when the disc brake is attached to the vehicle as shown in FIG. 42 and a braking operation is performed on the disc 1 rotating in the direction of arrow C, for example, the caliper 7 moves the slide pin 51 located on the upper side. It is known to receive a rotational moment in the direction of arrow D as the center. For this reason, the slide pin 52 located on the lower side of the friction pad 16 in FIG. 42 is likely to be loose in the pin fitting hole 4A.

  Therefore, in this embodiment, the urging force F2 of the cylinder spring 54 located on the lower side in FIG. 42 is set to a load larger than the urging force F1 of the cylinder spring 53 located on the upper side. As a result, it is possible to effectively suppress the slide pin 52 located on the lower side from rattling in the pin fitting hole 4A by the cylinder spring 54 having a large urging force F2, and the posture of the slide pin 52 can be reduced. Both slide pins 51, 52 can be smoothly slid and displaced with respect to the respective pin fitting holes 4A while maintaining a stable state.

In the third embodiment, when the disc brake is mounted in the vehicle, as shown in FIG. 42, one slide pin 51 is disposed on the upper side and the other slide pin 52 is disposed on the lower side. Explained with an example. However, the present invention is not limited to this. For example, the two slide pins 51 and 52 may be arranged at substantially the same height.

  In such a case, the clearance S2 between the pin fitting hole 4A and the slide pin 52 is larger than the clearance S1 between the pin fitting hole 4A and the slide pin 51 as shown in FIG. > S1), the biasing force F2 of the cylinder spring 54 disposed on the larger clearance S2 side may be set to a biasing force (F2> F1) larger than that of the other cylinder spring 53. .

  Even in such a case, it is possible to prevent the slide pin 52 from rattling in the pin fitting hole 4A on one side in the circumferential direction where the clearance S2 is large, by the urging force F2 of the cylinder spring 54. The slide pins 51, 52 can be smoothly slid and displaced with respect to the respective pin fitting holes 4A.

Next, FIG. 44 shows a fourth embodiment of the present invention. The feature of this embodiment is that an urging means is provided at a position above the friction pad with the disc brake attached to the vehicle. In this case, the urging means is provided only at a position below the friction pad. In the present embodiment, the same components as those in the third embodiment described above are denoted by the same reference numerals, and the description thereof is omitted.

  In the figure, reference numeral 61 denotes a cylinder spring as an urging means employed in the present embodiment. The cylinder spring 61 is formed in substantially the same manner as the cylinder spring 20 described in the first embodiment. However, in the present embodiment, the cylinder spring 61 is provided only at a position below the friction pad 16 in the state of being attached to the vehicle, and the cylinder spring itself is attached at a position above the friction pad 16. The configuration is to be abolished.

  Thus, also in the present embodiment configured as described above, the cylinder portion 9 of the caliper 7 can be urged toward the radially outer side of the disk 1 by the cylinder spring 61, which is the same as the fourth embodiment described above. Almost the same effect can be obtained.

  That is, in the present embodiment, the pin fitting hole 4A and the slide pin 52 located on the lower side of the pin fitting holes 4A and the slide pins 51 and 52 in a state where the attachment member 2 is attached to the vehicle. Since only the single cylinder spring 61 is used, the slide pin 52 is rattled within the pin fitting hole 4A located on the lower side of both sides in the circumferential direction of the disk 1 because the cylinder spring 61 is provided only for the cylinder spring 61. The slide pins 51 and 52 can be smoothly slid and displaced with respect to the respective pin fitting holes 4A. In this case, the number of parts can be reduced to improve workability during assembly.

In the fourth embodiment, when the disc brake is mounted on the vehicle, as shown in FIG. 44, one slide pin 51 is disposed on the upper side and the other slide pin 52 is disposed on the lower side. Explained with an example. However, the present invention is not limited to this. For example, the two slide pins 51 and 52 may be arranged at substantially the same height.

  In such a case, the clearance S2 between the pin fitting hole 4A and the slide pin 52 is larger than the clearance S1 between the pin fitting hole 4A and the slide pin 51 as illustrated in FIG. If S2> S1), the cylinder spring 61 may be provided only on the slide pin 52 side having a large clearance.

  In the first embodiment, the sliding surface 22A made of a self-lubricating material such as polytetrafluoroethylene is formed on the biasing plate portion 22 of the cylinder spring 20 by means such as coating. And explained. However, the present invention is not limited to this. For example, a lubricant such as grease may be applied to a contact portion of the biasing plate portion 22 (for example, a contact surface that contacts the sliding contact surface portion 9B of the cylinder portion 9). It is good also as a structure which forms a sliding surface by making it adhere. This also applies to the second to fifth embodiments.

  On the other hand, in each of the embodiments described above, the pad guide portions 3D and 5D of the mounting member 2 are formed as U-shaped notches, and the torque receiving portions 3E and 5E are formed on the bottom side of the notches as an example. I gave it as an explanation. However, the present invention is not limited to this. For example, the torque receiving portion may be provided at a position spaced from the pad guide portion on the inner side or the outer side in the radial direction of the disc.

  Moreover, in each said embodiment, pad guide part 3D, 5D of the attachment member 2 is formed as a U-shaped notch, and the back metal 17 of each friction pad 16 is movable to pad guide part 3D, 5D. The case where the convex-shaped ear | edge part 17A to fit is formed as an example was demonstrated. However, the present invention is not limited to this. For example, the pad guide portion is formed in a convex shape, and a concave fitting recess that is movably fitted to the convex pad guide portion is provided on the back plate of the friction pad. It is good also as a structure to provide.

  Further, in each of the above embodiments, the case where a single cylinder bore 9A (piston 12) is provided in the cylinder portion 9 of the caliper 7 has been described as an example. However, the present invention is not limited to this, and can be widely applied to, for example, a collet-type caliper or a reverse pin-type caliper having two or more pistons provided in the caliper.

1 is a front view showing a disc brake according to a first embodiment of the present invention. It is the top view which looked at the disk brake of FIG. 1 from upper direction. It is the rear view which looked at the disc brake from the opposite side to FIG. It is the right view which looked at the disc brake of FIG. 1 from the right side. It is sectional drawing which expanded the pin fitting hole of a disc brake, a slide pin, etc. from the arrow V-V direction in FIG. It is sectional drawing which expanded the disc brake from the arrow VI-VI direction in FIG. It is sectional drawing which looked at the pin fitting hole of a disc brake, a slide pin, etc. from the arrow VII-VII direction in FIG. It is sectional drawing which looked at the attachment member, the caliper, the friction pad of the inner side, etc. from the arrow VIII-VIII direction in FIG. It is a front view which shows the attachment member in FIG. 1 with a pad spring and a cylinder spring in the state which removed the caliper. FIG. 10 is a plan view of the mounting member, pad spring, and cylinder spring of FIG. 9 as viewed from above. It is a top view which shows the attachment member in FIG. 10 as a single unit. FIG. 10 is a rear view of the mounting member, the pad spring, and the cylinder spring as viewed from the opposite side to FIG. 9. It is the elements on larger scale which expand and show the left side part of an attachment member with a pad spring in the state which removed the cylinder spring in FIG. It is the elements on larger scale which expand and show the cylindrical protrusion etc. of the attachment member located in the right side of FIG. It is sectional drawing which looked at the cylindrical protrusion part and pin fitting hole of the attachment member from the arrow XV-XV direction in FIG. It is a perspective view which shows the pad spring in FIG. 13 as a single unit. It is a perspective view which shows the cylinder spring in FIG. 12 as a single unit. It is the front view which looked at the cylinder spring in FIG. 17 from the front. It is a top view of the cylinder spring shown in FIG. It is a right view of the cylinder spring shown in FIG. It is an assembly state explanatory view showing the state of assembling the cylinder spring to the cylindrical projection of the mounting member. It is a front view which shows the disc brake by the 1st modification of this invention. It is a front view which shows the caliper in FIG. 22 as a single unit. It is the bottom view which looked at the caliper of FIG. 23 from the downward direction. It is a top view which shows the disc brake by 2nd Embodiment. It is a top view which shows the attachment member, pad spring, and cylinder spring in FIG. 25 in the state which removed the caliper etc. It is the rear view which looked at the attachment member, the pad spring, and the cylinder spring from the rear side of FIG. It is a perspective view which shows the pad spring and cylinder spring in FIG. FIG. 29 is a view of the pad spring and the cylinder spring as seen from the direction of arrows XXIX-XXIX in FIG. 28. It is the top view which looked at the pad spring and cylinder spring of FIG. 29 from upper direction. It is a left view of the pad spring and cylinder spring which are shown in FIG. It is an assembly state explanatory view showing a state in which the pad spring and the cylinder spring are assembled to the mounting member. It is a front view which shows the disc brake by the reference example of this invention . It is the top view which looked at the disk brake of FIG. 33 from upper direction. It is sectional drawing which shows the caliper in FIG. 34 as a single body from arrow XXXV-XXXV directions. FIG. 36 is a partial bottom view of the caliper of FIG. 35 viewed from below. It is a top view which expands and shows the cylinder spring in FIG. It is the front view which looked at the cylinder spring of FIG. 37 from the front. It is a right view of the cylinder spring shown in FIG. It is a fragmentary top view which shows the attachment member in FIG. 33 as a single-piece | unit. It is the partial rear view which looked at the attachment member of FIG. 40 from the back side. It is a front view which shows the disc brake by 3rd Embodiment. FIG. 43 is a partially cutaway side view of the disc brake as seen from the direction of arrows XXXXIII-XXXXIII in FIG. It is a front view which shows the disc brake by 4th Embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Disc 2 Mounting member 3 One side frame board 3A Mounting plate part 3B, 5B Projection board part 3D Inner side pad guide part 3E Inner side torque receiving part 4 Cylindrical protrusion 4A Pin fitting hole 5 Other side frame board 5A Connecting beam part 5D Outer side pad guide part 5E Outer side torque receiving part 6 Joint frame plate (part straddling the outer peripheral side of the disk)
7 Caliper 8 Bridge 9 Cylinder (Inner Leg)
9A Cylinder bore 9B ', 43 Guide groove portion 10 Outer leg portion 11 Mounting portion 12 Piston 13, 51, 52 Slide pin 14 Fastening bolt 16 Friction pad 17 Back metal 18 Lining 19, 31 Pad spring 20, 32, 41, 53, 54, 61 Cylinder spring (biasing means)
22A, 32C, 41C Sliding surface G Center of gravity position Lb dimension (range of movement trajectory where the center of gravity of the caliper moves)
Lt mating length

Claims (4)

It includes a mounting member attached to a non-rotating portion of the vehicle arranged the inner side position across the disk, and a caliper which is displaced in the axial direction of the disc while being supported by the member with said mounting, before Symbol mounting portion In the disc brake formed by providing a pin fitting hole extending in the axial direction of the disc in the material and providing a slide pin slidably fitted in the pin fitting hole in the caliper ,
Said pin fitting hole, the provided on the mounting member at a position where the inner side of the disk, before kissing Raidopin is fixed to the caliper located on the inner side than the base end the mounting member a stationary end, slidably be fitted to Ru configured on the tip side in the pin fitting hole as a free end,
To said mounting member and the caliper, surface that faces located within the axial extent of said disc engagement length of the slide pin relative to the pin fitting hole in the radial direction of the disk is formed, between the counter surface disc brake, characterized in that the caliper has a configuration in which the biasing means for urging the radially outer side of the disk. 2. The disc brake according to claim 1, wherein the urging means is arranged at an axial position that overlaps a center of gravity of the caliper in the axial direction of the disc. The biasing means are provided at positions spaced apart from each other in the circumferential direction of the disk together with the pin fitting hole and the slide pin, and are positioned on the lower side of the biasing members in a state where the mounting member is mounted on a vehicle. 3. The disc brake according to claim 1, wherein one of the urging members is configured to have a larger urging force than the other urging member positioned on the upper side. The pin fitting hole and the slide pin are respectively provided at positions separated from each other in the circumferential direction of the disk, and one of the pin fitting hole and the slide pin located on the lower side with the attachment member attached to the vehicle The disc brake according to claim 1 or 2, wherein the biasing member is provided only for the pin fitting hole and the slide pin.

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