JP5087645B2 - Disc brake with pin rail caliper - Google Patents

Description

  The present invention relates to an improved brake system, and more particularly to an improved brake system including a sliding mechanism for slidably engaging a disc brake member along a slide pin.

  Current brake systems are usually equipped with calipers. This is to apply a braking force by temporarily fixing the friction pads arranged opposite to an annular braking surface on the rotor.

  A braking load (for example, a braking torque) generated thereby is brought into contact by interaction (supporting or the like) with a plurality of disk brake constituent members slidably engaged along the slide pin. In one particular configuration, the slide pin is heavily loaded. In the said form, there exists a possibility that a pin may deform | transform or a pin may be distorted by heavy load, or there exists a possibility of causing the defect of the slide pin which may arise. In order to solve such problems, the prior art provides a thicker slide pin to cope with the increasing load, or against the disc brake support bracket to partially release the slide pin from the load. The brake shoe is in contact. However, providing a thicker sliding member requires additional costs and / or manufacturing costs associated with machining (such as broaching or milling) to bring the brake shoe into contact with the support bracket. In addition, if a thicker sliding member is used, the necessary distance between the brake rotor and the wheel increases, thereby reducing the size of the brake rotor.

  In another particular form, the disc brake with the sliding mechanism is in a “lock-up” state, so that the disc brake component cannot slide substantially freely along the slide pin. There is a risk that. In the above configuration, the sliding mechanism is in the “lock-up state” because contaminants interacting with a plurality of disk brake components slidably engaged along the slide pin (for example, This is because of particles such as dust, debris, and debris. To solve this problem, prior art uses sliding mechanism sealing, booting and / or grease to protect the disc brake components from the surrounding environment. Inevitably adding higher component costs and manufacturing costs associated with the formation, installation and maintenance of these additional components. In another particular form, the disc brake, when temporarily fixing the opposing friction pads, largely does not all of the braking load (eg braking torque), if one slide In addition to the pins, the other slide pin serves to simply maintain the relative position of each brake shoe. In the prior art, attempts have been made to solve this problem using various disc brake structures, but only a few have been successful and the manufacturing costs have increased.

  Incorporating both “pull” and “push” type contact modes while receiving braking loads in contact, usually in a lighter disc brake, NVH (Noise, Vibration, Harshness), taper wear and / or Or it would be particularly important to provide an improved pin rail caliper with slide pins that would improve operational performance. Examples of disc brake assemblies are US Pat. Nos. 4,144,952, 4,279,331, 4,319,668, 4,344,551, 4,351,421, 4,418,797, 5,094,323, 5,111,915, and 5,860,496, US Patent Application No. 20080029356, which is incorporated herein by reference. It has been incorporated. As shown and described herein, the present invention improves these disc brake assemblies.

  An object of the present invention is to improve the conventional disc brake system, and specifically, to improve the attachment of the disc brake component. In one aspect, the present invention provides a disc operable to apply a clamping force to a rotating disc having a support bracket, two opposed and spaced slide pins, an inner brake shoe and an outer brake shoe, and a caliper body. A brake is provided. The support bracket includes a pair of spaced frame members at opposite ends thereof. Each frame member has a surface from which at least three arms extend. The at least three arms include a first arm, a second arm, and a third arm. Each arm has an opening, and the arms are sequentially provided with a space therebetween. The two opposed and spaced slide pins are arranged in such a manner that at least one of the first, second and third arms supports, supports or supports the slide pin. And is engaged with the opening of the third arm. The caliper body is slidably supported by a slide pin. The caliper body includes a slidable piston operable to bring the inner brake shoe and the outer brake shoe close to each other. Each of the slide pins is supported by the first, second, and third arms of the support bracket, thereby allowing for pin deformation and pin distortion over conventional calipers with pins to which a braking load is applied, or Both of these are mitigated.

  In another aspect, the present invention provides a disc operable to apply a clamping force to a rotating disc having a support bracket, two opposed and spaced slide pins, an inner brake shoe and an outer brake shoe, and a caliper body. Provide brakes. The support bracket includes a pair of spaced frame members at opposite ends thereof. Each frame member has a surface from which at least one arm extends. The at least one arm includes an opening. The two opposed and spaced slide pins are engaged with at least one opening of each frame member such that at least one of the at least one arm bears the slide pin. The caliper body includes a slidable piston operable to bring the inner brake shoe and the outer brake shoe closer to each other and to be slidably supported by at least a pair of spaced boss portions by a slide pin. Each of the bosses is a polymer having a plurality of grooves that define openings (e.g., bearing the slide pins) to receive the respective slide pins such that the respective slide pins are slidably engaged. Includes bushings.

  In another aspect, the present invention provides a disc brake operable to apply a clamping force to a rotating disc having a support bracket, two oppositely spaced slide pins, an inner brake shoe and an outer brake shoe, and a caliper body. I will provide a. The support bracket includes a pair of spaced frame members at opposite ends thereof. Each frame member has a surface from which at least two arms extend. The at least two arms include a first arm and a second arm, each arm having an opening, and each arm is sequentially provided with a gap therebetween. This spacing is defined by the side walls of the first and second arms and the face of the frame member therebetween. The two opposed and spaced slide pins are engaged with the openings of the first and second arms such that at least one of the first and second arms supports the slide pins.

  The inner brake shoe and the outer brake shoe have protrusions extending from opposite ends thereof. The protrusions of the inner brake shoe and the outer brake shoe include respective openings for receiving slide pins for assisting the support of these shoes. The protrusions of the inner brake shoe and the outer brake shoe are provided in the interval between the first arm and the second arm so as not to substantially contact the surface of the frame member. The caliper body is provided with a slidable piston operable to bring the inner brake shoe and the outer brake shoe closer to each other, and a first pair of spaced bosses extending from opposite ends of the inner side of the caliper body. ing. Each boss has a plurality of grooves defining an opening in each polymeric bushing to receive each slide pin to slidably engage each slide pin.

  The plurality of grooves in the above description may assist in the removal of debris and debris exiting each slide pin while the polymer bushing slides along each slide pin, or the depth is about the inner diameter of the polymer bushing. Values range from 5% to about 20%, or about 5 to about 15 arcuate grooves extending longitudinally with a plurality of grooves, or any combination of the above configurations. The outer brake shoe has a protruding portion along its outer surface, and the caliper body usually has an outer portion that extends parallel to the outer surface of the outer brake shoe. Therefore, the outer portion of the caliper body is The outer brake shoe includes an opening for engaging the protrusion of the outer brake shoe so that the outer portion of the caliper body is fixed and supported by the outer brake shoe.

In yet another aspect, any aspect of the invention is further characterized by one or any combination of the features described below.
Such features include:
The slide pin has a first, second and third frame member so that the diameter of the slide pin can be reduced from about 20% to about 40% compared to a conventional caliper having a pin to which a braking load is applied. It is supported by the arm, which reduces pin deformation, pin distortion, or both,
At least one of the inner brake shoe and the outer brake shoe is provided with a protrusion extending from at least one opposing end of the brake shoes, and the protrusions support the inner and outer brake shoes. An opening for receiving the slide pin is provided to assist
The slide pin is in contact with the brake on position so that a substantially or completely tangential braking load is applied,
The interval includes a first interval and a second arm provided between the first arm and the second arm defined by the side walls of the first arm and the second arm and the surface of the frame member therebetween. A second space provided between the second arm and the third arm defined by the side wall of the third arm and the surface of the frame member is included, and the inner brake shoe and the outer brake shoe have these A protrusion extending from the opposite end of the brake shoe is provided, and this protrusion is provided with an opening for receiving a slide pin so as to assist the support of each inner and outer brake shoe, For this purpose, each protrusion of the outer brake shoe is provided within a first interval between the first arm and the second arm, and each protrusion of the inner brake shoe Provided in the second gap between the arm and the third arm,
The protrusions of the inner brake shoe and outer brake shoe do not substantially contact the surface of the frame member,
At least one of the inner brake shoe and the outer brake shoe has a first engagement portion along the outer surface of each brake shoe for fixing and supporting the second engagement portion of the caliper body,
The first engagement portion includes at least one protrusion along the outer surface of the outer brake shoe, and the at least one protrusion engages with the at least one opening so that the outer portion of the caliper body is supported by the outer brake shoe. The second engagement portion comprises at least one opening along the outer portion of the caliper body,
The caliper body includes at least a pair of spaced bosses that are slidably supported by the slide pins, each of the bosses having a respective slidable engagement with each slide pin. Comprising a polymeric bushing having a plurality of grooves defining an opening for receiving;
The plurality of grooves assists in removing debris exiting each slide pin while the polymer bushing slides along each slide pin, or the depth of the plurality of grooves is about 5 times the inner diameter of the polymer bushing. % To about 20%, or a plurality of grooves extending in the longitudinal direction to form about 5 to 15 arched grooves, or any combination of the above ,
The boss part is a support bracket, one or both of an inner brake shoe and an outer brake shoe, a caliper body, or any combination thereof, usually along the slide pin in the same direction with respect to the engaging surface of the rotating disk. The two slide pins can be individually deformed so as to assist the alignment of the two slide pins.
Each boss part is formed separately from the polymer bushing and then integrated or formed with the polymer bushing as an integral polymer boss component,
The at least one pair of spaced bosses includes a first pair of spaced bosses extending from opposite ends of the inner side of the caliper body;
The boss part is a support pin, one or both of an inner brake shoe and an outer brake shoe, a caliper body, or any combination thereof, which is usually a slide pin in the same direction with respect to the engaging surface of the rotating disk. Individually deformable to assist in the alignment of the two slide pins so that they slide substantially freely along
Each boss part is formed separately from the polymer bushing and then integrated or formed with the polymer bushing as an integral polymer boss component,
The inner brake shoe and the outer brake shoe have protrusions including openings for receiving slide pins so as to support the support between the inner brake shoe and the outer brake shoe, extending from the opposite ends of these shoes.
At least one of the inner brake shoe and the outer brake shoe has a first engagement portion along the outer surface of each brake shoe, and is fixedly supported on the second engagement portion of the caliper body. The engagement portion includes at least one protrusion along the outer surface of the outer brake shoe, and the second engagement portion has at least one protrusion so that the outer portion of the caliper body is supported by the outer brake shoe. At least one opening along the outside of the caliper body to engage the two openings, or any combination of the above.

  It will be appreciated that the aspects and examples referred to above are not limiting and may take other forms, as described and illustrated herein. For example, as described in the text and shown in the drawings, other unique structures can be formed by arbitrarily combining the above-described aspects and features of the present invention.

1 is an exploded perspective view of a disc brake assembly including a first embodiment of the present invention. FIG. 2 is a perspective view of the disc brake assembly and embodiment shown in FIG. 1. FIG. 3 is another perspective view of the disc brake assembly and embodiment illustrated in FIGS. 1 and 2. FIG. 4 is an enlarged perspective view of the disc brake assembly and the embodiment illustrated in FIGS. 1 is a perspective view of one embodiment in accordance with the teachings of the present invention. FIG. FIG. 6 is a perspective view of a second embodiment in accordance with the teachings of the present invention. FIG. 6 is another perspective view of the disc brake assembly and the second embodiment shown in FIG. 5. FIG. 7 is an exploded perspective view of the disc brake assembly and the second embodiment illustrated in FIG. 6. FIG. 6 is a perspective view of another embodiment in accordance with the teachings of the present invention. FIG. 6 is a perspective view of another embodiment in accordance with the teachings of the present invention. FIG. 8 is an enlarged perspective view of the disc brake assembly and embodiment illustrated in FIGS.

  The present invention broadly relates to an improved braking system for overcoming problems associated with taper wear and operational performance. In one aspect, the invention relates to an improved disc brake 10 operable to apply a clamping force to a rotating disc 12 of an automobile vehicle. In general, the disc brake 10 associated with FIGS. 1-4B includes a support bracket 14, an inner brake shoe 16 and an outer brake shoe 18, a piston 20, a caliper body 22, and two opposed slide pins 30. However, the number of constituent members is not limited. Typically, the disc brake 10 includes a support bracket 14. The support bracket has a pair of spaced frame members 34 at opposite ends thereof. Each frame member 34 has an inner wall surface 36 from which at least one arm extends. The arm may be provided with an opening 40 for receiving the slide pin 30.

  It will be appreciated that where more than one arm is included, there is a gap defined by the side walls of the two or more arms and the inner wall surface 36 of each frame member 34 therebetween. In general, the same number of arms may extend from both frame members of the support bracket, but this is not necessary. For example, one, two, or more arms may extend from each opposed frame member. Alternatively, the number of arms extending from one frame member may be larger or smaller than the number of arms extending from the other frame member. Further, the size of the arms (eg, the thickness with respect to the radial axis of the rotating disk) is such that one or more arms can cover a wider portion of each slide pin 30 than the other arm. It will be appreciated that it may vary.

  As shown in FIG. 2, in one preferred embodiment, the frame member 34 includes a first arm 42 provided outside the disc brake 10, a second arm 44 provided at the center of the disc brake 10, and a disc brake. 10 includes a third arm 46 provided in the interior of 10. The opening 40 may extend through one or more of the first arm 42, the second arm 44, and the third arm 46 to engage the slide pin 30. It will be appreciated that the first, second and third arms can be arranged in sequence with spacings 48, 50 therebetween so that the openings 40 are substantially aligned and maintained in alignment. In one aspect, the first interval 48 and the second interval 50 may be cited as the interval. The first interval 48 may be provided between the first arm 42 and the second arm 44. The first interval 48 is defined by the side wall 52 of the first arm 42 and the side wall 54 of the second arm 44, and the inner wall surface 36 of the frame member 34 therebetween. The second interval 50 can be provided between the second arm 44 and the third arm 46. The second interval 50 is defined by the side wall 56 of the second arm 44, the side wall 58 of the third arm 46, and the inner wall surface 36 of the frame member 34. When the first, second and third arms are provided, the slide pins 30 are fully supported by these arms, so that conventional calipers (e.g., current calipers that use pins to carry braking loads). , Pin deformation, pin distortion, etc., and any combination thereof.

  As such, the diameter of the disc brake slide pin 30 having a frame member with at least three arms can be reduced from about 20% to about 40%, and preferably about It can be shortened from 25% to about 35%. For example, it is estimated that the load capacity of a 10 mm pin that is supported at least in triple is equivalent to the load capacity of a 14 mm slide pin that is supported only at the end of the frame member of the support bracket, but is not limited thereto. Absent. As such, by reducing the diameter of the slide pin 30, the mounting space required for the disc brake 10, the so-called package space, is reduced, thereby providing a larger rotating disc 12 in a given package. Can be provided.

  The disc brake 10 includes an inner brake shoe 16 and an outer brake shoe 18, each of which includes a pressure plate 60 and a brake pad 62 (for example, a friction material). The inner brake shoe 16 and the outer brake shoe 18 are positioned so that each brake pad 62 faces the surface of the rotating disk 12. It will be appreciated that at least one of the inner brake shoe 16 and the outer brake shoe 18 may be provided with a protrusion 64 extending from the opposite end of each brake shoe 16, 18. When the protrusion 64 is provided, it may be provided around the opposing end of the pressure plate 60. The protrusion may be provided with an opening 66 for receiving and slidingly engaging the slide pin 30 so as to assist the support of each inner brake shoe 16 and outer brake shoe 18.

  In one preferred embodiment, both the inner brake shoe 16 and the outer brake shoe 18 may be provided with a protrusion 64 provided with an opening 66 for receiving and supporting the slide pin 30. Typically, the inner brake shoe 16 and the outer brake shoe 18 can be provided within an interval. For example, the protrusion 64 of the outer brake shoe 18 may be provided in the first interval 48 between the first arm 42 and the second arm 44. Furthermore, the protrusion 64 of the inner brake shoe may be provided in the second interval 50 between the second arm 44 and the third arm 46. Advantageously, the projection 64 provided with the opening 66 may accommodate the slide pin 30 during assembly of the disc brake 10, and is slidably engaged with the inner brake shoe 16 and the outer brake. It will be appreciated that the shoe 18 is normally secured to the disc brake 10 so that it does not substantially or completely disengage from the disc brake 10 while assembling the rest.

  It is considered that the inner brake shoe 16, the outer brake shoe 18, or both of them are supported at least partially in contact with the inner wall surface 36 of the frame member 34. However, it is preferable that the inner brake shoe 16 and the outer brake shoe 18 do not substantially or completely contact the inner wall surface 36 of the frame member 34. In the latter arrangement, the inner brake shoe 16 and the outer brake shoe 18 are supported substantially or completely by the slide pin 30. It is considered that a contact part (abutment) can be used as a description of the design element that resists the load. For example, the braking load is generated by friction between the rotary disk 12 and the inner brake shoe 16 and the outer brake shoe 18, and both slide pins 30 (for example, leading as described later) are used as contact portions for the braking load. Slide pins and trailing slide pins) may be used.

  This braking load is transmitted to the slide pin through the brake shoe, and then transmitted from the slide pin to the support bracket. Furthermore, in conventional designs, it is believed that the braking load may be transmitted directly from the brake shoe to the support bracket (eg, a slide pin becomes an abutment). In this way, when the inner brake shoe 16 and the outer brake shoe 18 are substantially or completely supported by the slide pin 30, the slide pin 30 is in contact with the abutment (for example, The tangential braking load caused by the disc brake 10 while in the brake-on position is transmitted substantially or completely by the slide pin 30).

  The disc brake 10 further includes a biasing member 114 (e.g., for assisting in holding each inner brake shoe 16 and outer brake shoe 18 in place (e.g., a brake-on position, a brake-off position, or both). Springs, clips, etc.). In one exemplary embodiment, such as shown in FIGS. 2 and 3, the end of the bias member 114 is aligned with the inner brake shoe and outer brake while the center of the bias member 114 engages the second arm of the frame member 34. Engage with the corresponding end of the shoe. The bias member 114 assists in maintaining a gap 112 (eg, not in contact and / or abutment) between the inner brake shoe 16 and the outer brake shoe 18 and the inner side wall 36 of the frame member 34. Is desirable. Accordingly, the inner brake shoe 16 and the outer brake shoe 18 provide a pull-push arrangement for the disc brake 10 as discussed herein, while not in contact and / or abutment. It may be an assist.

  In the pull push mode, in a state where the load is relatively low and the deformation is small, first, the braking load reacts at the tip of the brake shoe (for example, the brake pad), while the pressure plate is pulled ( For example, it can be referred to as a concept of being in a tensioned state. Then, at low load, the brake shoe pulls the leading pin in the direction of rotation of the tire so that the leading pin transmits the load to the support bracket. As the load increases, the trailing end of the brake shoe contacts the abutment (eg, a slide pin) due to deformation, the pressure plate load transitions from tension to compression (eg, pressing), and the leading abutment The load between the trailing abutments is shared.

  In the present invention, this push-pull function is realized by controlling the distance between the pins relative to the pressure plate of the brake shoe and the distance between the pins relative to the support bracket with respect to the deformation of the support bracket. At almost the same time, the trailing pin is pressed in the direction of rotation of the tire by the brake shoe. Once the load has increased sufficiently, the deformation (e.g., between the slide pin and the opening) eliminates the spacing substantially or completely, and the trailing end pin then transmits the load to the support bracket. In this mode (eg, pull-push mode), the leading pin load is considered to be greater (eg, in contact) than the trailing pin load. As discussed below, the caliper can be arranged to operate in the opposite manner, referred to as push-pull.

  At least one of the inner brake shoe 16 and the outer brake shoe 18 may include a first engagement portion for fixing to the caliper body 22 and / or the second engagement portion of the support bracket 14. The first and second engaging portions may be fixed by fasteners (eg, clips, bolts, hooks, pins, etc.) or any attachment component. In one aspect, the first engaging portion is a protrusion 72 (for example, a nub nub), and the second engaging portion is an opening 74 for receiving the protrusion 72, but the opposite configuration. Can also be engaged. The first engagement portion, the second engagement portion, or both may be formed integrally with each inner brake shoe 16 and / or outer brake shoe 18 and / or caliper body 22, It will be appreciated that the components may be added separately. In a preferred embodiment, the outer brake shoe 18 may include a first engagement portion having a pair of protrusions 72 provided on the outer surface 76 of the pressure plate 60. Further, the caliper body 22 may include a second engagement portion having a pair of openings 74 for engaging the pair of protrusions 72. It will be appreciated that the protrusion 72 may be provided at the opposite end of the outer brake shoe 18 along the outer surface 76 of the pressure plate 60.

  The disc brake 10 is slidable by a slide pin 30 having a piston 20 operable to bring the inner brake shoe 16 and the outer brake shoe 18 closer to each other in order to engage the opposite side of the rotating disc 12. A caliper body 22 is further included. The caliper body 22 includes a finger portion 80 provided outside the disc brake 10, a bridge portion 82 provided at the center portion of the disc brake 10, and a piston portion 84 provided inside the disc brake 10. It may be. The caliper body 22 may further include at least a pair of spaced boss portions 78. The boss 78 may be provided at the opposite end of the caliper body 22, and an opening 86 for accommodating the slide pin 30 may be provided. It will be appreciated that the slide pin 30 may support the caliper body 22 such that the caliper body 22 is partially, substantially, or completely supported by the slide pin 30.

  The boss part 78 may further include a bushing 88. The bushing 88 may be formed in a state of being integrated with the boss portion 78 or may be a separate component member integrated with the boss portion 78. 1-4B, in one embodiment, the boss 78 of the caliper body 22 is formed separately from the bushing 88 and then integrated. The bushing 88 formed separately may use a polymer material substantially or completely. Examples of the polymer material include, but are not limited to, nylon, polyester, polycarbonate, and the like, or any combination thereof. Examples of the polymer material include a filler (for example, glass). An amount of filler of at least 20%, at least 40%, or at least 60% of the polymeric material may be included. However, it will be appreciated that less filler may be included. Preferably, the melting point (eg, crystalline melting point) of the polymeric material is at least 150 degrees, more preferably at least 200 degrees.

Bushing 88 includes an opening 90 for receiving slide pin 30 to slidably engage the slide pin. It will be appreciated that the bushing 88 provides a low friction sliding mechanism for the caliper body 22. If a sliding mechanism is provided, it will be appreciated that the mechanism is not sealed, boot (eg, boot seal), cap, greased, or a combination thereof. In one preferred embodiment, the bushing 88 includes a plurality of grooves 92 that define an opening 90. Groove depth D _G of the groove 92 takes a value in the range of from about 5% to about 20% of the inner diameter of the bushing 88, preferably can take a value in the range of from about 10% to about 15% . It will be appreciated that the inner diameter of the bushing 88 can be obtained from the deepest portion of the groove 92.

  The groove 92 may be a longitudinally extending groove having a contour. The contour shape and size of the groove 92 may vary. The number of grooves is about 5-15, more preferably about 8-12. It will be appreciated that some of the grooves are considered for the size of the disc brake. Illustratively, in FIG. 4B, the contour of the groove 92 may be a plurality of round (eg, arched) groove contours. Other contours are considered, such as square or triangular contours, stepped contours, multiple grooves with similar or different contours, or any combination thereof. The contour may further include a flat side wall, an arched side wall, a flat bottom, an arched bottom, a substantially U-shaped part, a substantially V-shaped part, or any of these. Combinations can be mentioned.

  Further, the groove 92 assists in removing debris from the slide pin 30 while the bushing 88 slides along the slide pin 30. For example, while driving an automobile, particles and others (dust, debris, contaminants, contaminants, etc.) may adhere to and / or be embedded within the bushing 88. Normally, the particles are positioned in the groove 92 so that the caliper body 22 continues to operate and can slide along the slide pin 30. As the caliper body 22 slides along the slide pin 30, particles may pass from the bushing 88 through the opening 90, or more specifically, by the sliding mechanism of the slide pin 30 passing through the bushing 88. The particles are removed from the grooves 92 such that the particles are substantially removed or eliminated through the grooves 92. Normally, the structure of the groove 92 as described above reduces the caliper body lock-up along the slide pin 30 due to the accumulation of particles as compared with the conventional bushing without the groove, and thus the operation of the caliper body. Life span is extended.

  In another embodiment with respect to FIGS. 5-8C, the boss portion 78 may be formed integrally with the bushing 88 as one component (eg, an integral boss component 96). Preferably, this integral boss component 96 may be substantially or completely polymeric. It will be appreciated that the integrated boss component 96 may be formed separately from the caliper body 22 or may be fixed to the caliper body 22. As illustrated in FIGS. 8A and 8B, the integrated boss component 96 includes a groove 92 that defines an opening 90 that functions in a manner similar to that described above. The integrated boss component 96 further includes a first attachment portion for fixing the member to the caliper body 22. The caliper body 22 includes a second attachment portion for engaging and fixing the first attachment portion of the integrated boss portion 96. For example, as illustrated in FIG. 7, the first attachment portion of the integral component member 96 may include a protrusion 102 for engaging the second attachment portion of the caliper body 22. Further, the second attachment portion of the caliper body 22 may be provided with an opening 104 for accommodating the protruding portion 102 of the integrated boss constituting member 96. It will be appreciated that other securing means may be utilized to secure the integrated boss component 96 to the caliper body 22.

  Disc brakes have defects such as fluctuations (for example, displacement and bending) in the opening and slide pins, and / or fluctuations caused by the surrounding environment such as temperature changes (distortion, wear, etc.) It is considered that the disc brake is formed in a state where there is a defect. Such fluctuations may affect the sliding mechanism of the disc brake 10. As such, it is understood that the integral boss component 96 is normally individually deformable (eg, rotatable, bendable, etc.) to assist in the self-alignment of the disc brake 10. Will be done.

  More specifically, the integrated boss component 96 may be individually deformed as necessary to align the two slide pins, so that the support bracket, inner brake shoe and One or both of the outer brake shoes, the caliper body, etc., or any combination thereof that slidably engages with the slide pin 30 can be freely slid along the slide pin. The polymer bushing 88 and / or the integrated boss component 96 can be designed to be self-aligned with the general position of the slide pin 30, so-called self-alignment, so that the sliding force of the disc brake component along the slide pin 30 And / or drag torque is believed to be reduced. As such, the self-aligning feature of the integral boss component 96 positions the slide pin 30 in the same direction, usually in the same direction relative to the rotational axis of the rotating disk 12, and / or the sliding force of the slide pin 30 and / or The drag torque may be reduced.

  It will be appreciated that a plurality of round groove profiles desirably substantially reduce or eliminate stress concentrated around the polymeric bushing 88. Furthermore, the use of the polymer bushing 88 and / or the integrated boss component 96 can reduce the possibility of rattling noises under vibration conditions.

  In one preferred embodiment, the caliper body 22 is in the vicinity of the piston portion 84 (eg, a support bracket such as the third arm 46 of the support bracket 14) for receiving the slide pin 30 to support at least a portion thereof. 1) provided with a single pair of boss portions (the boss portion 78 with the polymer bushing 88 of FIGS. 1 to 3 or the boss portion 96 of FIGS. 5 to 7). As described above, the caliper body may be further supported through the second engaging portion. It is desirable that the first engagement portion of the outer brake shoe 18 is provided with a pair of protrusions 72 that are usually provided at opposite ends of the outer surface of the brake shoe 18 (for example, the pressure plate 60). Furthermore, a pair of openings 74 that are normally provided at opposite ends of the finger portions 80 of the caliper body 22 may be provided in the second engagement portion of the caliper body 22.

  The finger portion 80 normally extends perpendicularly from the bridge portion 82 of the caliper body 22, and thus the inner surface of the finger portion 80 extends parallel to the outer brake shoe 18 (for example, the pressure plate 60). . As such, the pair of protrusions 72 along the outer surface of the outer brake shoe 18 are normally aligned with and engaged with the pair of openings along the finger portion 80 of the caliper body 22. Accordingly, the caliper body 22 is fixed to the outer brake shoe 18 or at least a part thereof is supported by the outer brake shoe 18. In such a structure, disc brakes are used regardless of whether self-aligning (eg, integral boss component 96) or fixed bushing (eg, boss portion 78 with polymeric bushing 88) is used. A sliding arrangement is provided by the bearing arrangement. The sliding load of this mechanism is relatively unaffected by deformation of the caliper body 22, the support bracket 14, the slide pin 30, the inner brake shoe, and the outer brake shoe.

  As described above, the disc brake 10 further includes two opposingly spaced slide pins 30 that are removably attached to the brake. The slide pin 30 engages with an opening of one or more disc brake components (eg, support bracket 14, inner brake shoe 16, outer brake shoe 18, caliper body 22, or any combination thereof). So that at least one disc brake component engaged with the slide pin 30 is configured to slide, support, etc., or any combination thereof along the pin. Also good. The slide pin 30 may be formed of a metal material, a polymer material, a composite material, or the like. The slide pin 30 is usually a member that is parallel to the other and extends in the longitudinal direction, which is the same direction as the rotation axis of the rotary disk 12. The outline of the slide pin 30 may vary in shape and size. The outline, size, weight, and the like of each slide pin 30 may be the same or different. Preferably, the slide pin 30 is typically similar and typically includes an arcuate contour, but is not necessarily required.

  Typically, the slide pin 30 includes a retention feature for securing the slide pin 30 to the disc brake 10. In one aspect, the slide pin 30 may be provided with a flange portion 106. The flange portion is slidably engaged with one or more openings along the slide pin 30 (for example, the support bracket 14, the inner brake shoe 16, the outer brake shoe 18, the caliper body 22, or the slide pin 30). The slide pin 30 is prevented from sliding substantially or completely through the opening) of the others. The flange 106 is preferably provided at the end of the slide pin 30 as shown in FIGS. As an alternative or as another form, in another aspect, the slide pin 30 may be provided with a depression (recess) 108 for accommodating the retention clip 10 (for example, a bias member).

  This depletion prevents (eg, holds) the slide pin from moving substantially or completely axially relative to the support bracket (eg, through one or more openings in the disc brake component). Is for. It will be appreciated that the retention clip 110 may be a metal such as stainless steel, plastic, or both. In one exemplary embodiment illustrated in FIGS. 2 and 3, the depression 108 is typically positioned between the bosses 78, 96 and the third arm 46 of the frame member 34 to accommodate the retention clip 110. Like that. The retention clip 110 is one or more of, for example, a support bracket 14, an inner brake shoe 16, an outer brake shoe 18, a caliper body 22, or any other that slidably engages a slide pin 30. It will be appreciated that a biasing mechanism may be further provided to assist the sliding mechanism (such as sliding).

  As noted above, there is a particular need to provide an improved pin rail caliper having slide pins that provide a braking load abutment while incorporating “pull” and “push” type abutment modes. There will be. In one aspect, the disc is configured to operate in a “pull” abutment mode (ie, the brake shoe pressure plate is pulled) in a low deceleration state where squeal noise occurs and a lot of wear occurs. A brake may be configured. Due to the axial distance from the rotating disc to the brake shoe abutment, in the “pull” mode, the brake shoe moment causes the brake shoe “self-apply” (for example, the brake off position when the vehicle driver is away from the brake pedal). In this state, the tendency of the brake shoe to partially engage with the rotating disk surface is reduced. It is believed that squeal noise and / or taper wear is usually reduced by reducing the “self-apply” tendency.

  In another aspect, the “pull push” is used at high deceleration to share the braking load between the leading (rear) and trailing (front) protrusions of the inner and outer brake shoes (eg, pressure plate). The disc brake can be designed to transition to the abutment mode. As a result, it is possible to substantially reduce or eliminate the need for an outer support tie bar (for example, usually provided on the outer portion of the support bracket), thereby reducing the weight.

  In order to proceed with the discussion in one exemplary embodiment, it is assumed that the rotating disk 12 rotates in a counterclockwise direction (eg, facing the outside of the caliper, such as the finger portion 80 of the caliper body 22). According to the present invention, the braking torque generated by the engagement surfaces of the rotating disks and the engagement of the brake pads 62 may be transmitted to both slide pins by the method described below.

  For reference, the slide pin 30 includes a rear pin 130 (for example, a leading pin), a front pin 132 (for example, a trailing pin), and a protrusion 64 including a rear protrusion 116 and a front protrusion 118. ing. It will be appreciated that in the counterclockwise direction of the rotating disk 12, the rear protrusions 116 of the inner brake shoe 16 and the outer brake shoe 18 respectively engage with the rear pin 130 first. The front protrusion 118 is engaged with the front pin 132 by the deformation of the associated rear protrusion 116. More specifically, when the brake is applied (for example, the brake-on position), the rear pin 130 is acted on by the rear protrusion 116 of the inner brake shoe 16 and the outer brake shoe 18. The rear projection 116 is elastically distorted by the frictional force of the brake shoe, whereby the rear pin 130 and the rear projection 116 are engaged, and the inner brake shoe 16 and the front pin 132 of the outer brake shoe 18 are engaged. And the front protrusion 118 are engaged with each other.

  Thus, in the desired pull-push brake shoe engagement mode, the inner brake shoe 16 and the outer brake shoe 18 pull the rear pin 130 (eg, usually with a low braking load) and against the front pin 132 (eg, usually The result is pressing (with high braking load). The engagement of the rear protrusion 116 first stabilizes the brake engagement, and as a result, wear of uneven friction material (such as a pad) and engagement noise can be minimized. In this specification, the “leading pin” means that when the rotation direction of the rotary disk 12 is given, the slide pin is associated with the end that leads the remaining portion of the brake shoe. Means. 2 and 3, to rotate the rotating disk 12 counterclockwise, the rear pin 130 becomes a leading pin and the front pin 132 becomes a trailing pin. Therefore, when the rotating disk 12 is clockwise, the front pin 12 is a leading pin and the rear pin 130 is a trailing pin.

  It will be appreciated that if the rotating disk 12 rotates clockwise rather than counterclockwise, the engagement pattern will in principle be the opposite of the pattern described above. For example, the front protrusions 118 of the inner brake shoe 16 and the outer brake shoe 18 each first engage with a front pin 132 (for example, a leading pin). As the associated front protrusion 118 is deformed, the rear protrusion 116 engages with the rear pin 130 (for example, a trailing pin).

  In the present invention, the inner brake shoe and the outer brake shoe are first engaged with the leading pin, and swinging so as to engage the trailing pin to realize the pull push engagement. By distributing the braking load transmitted to the rotating disc relatively evenly, the vibration of the disc brake system, often associated with prior art push or pull brake systems, is reduced.

  Unless otherwise stated, the dimensions and geometry of the various structures illustrated herein are not intended to be limited to the present invention, and other dimensions and geometries are possible. A plurality of structural components may be provided by a single built-in structure. In another form, one built-in structure can be divided into another plurality of constituent members. In addition, while features of the present invention have been described in the context of one exemplary embodiment, such features may be combined with one or more other features of other embodiments for any given application. Good. It will be further understood from the above description that the manufacture of the unique structure and its operation constitute the method according to the invention.

  Preferred embodiments of the invention are disclosed. However, one of ordinary skill in the art appreciates that certain modifications are within the scope of the teachings of the invention. Accordingly, the following claims should be studied to determine the true scope and content of this invention.

  In summary, according to the present invention, the present invention is a disc brake operable to apply a clamping force to a rotating disc, comprising a support bracket having a pair of spaced frame members provided at opposite ends, The frame member has a surface from which at least three arms extend, and the at least three arms include a first arm, a third arm, and a third arm, each arm having an opening and spaced apart from each other. Two oppositely engaged with the openings of the first, second and third arms such that at least one of the first, second and third arms bears the slide pin. Includes spaced apart slide pins, inner brake shoes and outer brake shoes. With operable slidable piston so as to approach, structure comprising a caliper body that is supported slidably by the sliding pin is provided.

DESCRIPTION OF SYMBOLS 10 Disc brake 12 Rotating disc 14 Support bracket 16 Inner brake shoe 18 Outer brake shoe 20 Piston 22 Caliper body 30 Slide pin 34 Frame member 36 Inner wall surface 40 Opening part 42, 44, 46, 48 Arm 60 Pressure plate 62 Brake pad 64 Protrusion Part 66 opening 72 pair of protrusions

Claims (15)

a) having a support bracket, which is
1. A pair of spaced apart frame members are provided at opposite ends;
2. At least two arms extend from the frame member; and
3. Each of the arms is provided with an opening,
b) having an inner brake shoe in which a leading projection provided with an opening and a trailing projection provided with an opening are provided at opposite ends;
c) having an outer brake shoe in which a leading protrusion provided with an opening and a trailing protrusion provided with an opening are provided at opposite ends;
d) has a reading slide pin;
e) having a trailing slide pin;
f) the leading slide pin and the tray so that the two opposed slide pins support the brake shoe and the at least two arms support the two opposed slide pins. The ring slide pins are arranged to face each other, and are engaged with the openings of the at least two arms and the openings of the protrusions of the brake shoe,
g) a caliper body including a pair of spaced bosses provided with openings having bushings for accommodating the slide pins;
h) having a slidable piston operable to bring the inner brake shoe and outer brake shoe closer to each other ;
The inner brake shoe, the outer brake shoe, or both include a first engagement portion, the caliper body further includes a second engagement portion, and the first engagement portion further includes the second engagement portion. A disc brake having a clip for fixing to an engaging portion .   One or more brake shoe tips are pulled in contact with the slide pin to deform the leading slide pin or the frame member with which the leading slide pin engages, or to deform both, The disc brake of claim 1, wherein the trailing end of one or more of the brake shoes is pressed into contact with the trailing slide pin. Wherein the bushing is provided with a groove, a disc brake according to claim 1, wherein.   The disc brake is configured to operate in a pull abutment mode, thus reducing a self-applied tendency and reducing the self-applying tendency to reduce squeal noise, taper wear, or both. Item 2. The disc brake according to item 2. The disc brake is configured to operate in a pull abutment mode, thus reducing a self-applied tendency and reducing the self-applying tendency to reduce squeal noise, taper wear, or both. Item 4. The disc brake according to item 3 .   The disc brake according to claim 1, wherein the brake is not provided with an outer support tie bar.   The disc brake according to claim 1, wherein the pair of spaced boss portions are separately formed and fixed to the caliper body.   The disc brake according to claim 1, wherein the bushing can make the sliding mechanism self-alignable. a) having a support bracket, which is
1. A pair of spaced apart frame members are provided at opposite ends;
2. At least three arms extend from the frame member; and
3. Each of the arms is provided with an opening,
b) having an inner brake shoe in which a leading projection provided with an opening and a trailing projection provided with an opening are provided at opposite ends;
c) having an outer brake shoe in which a leading protrusion provided with an opening and a trailing protrusion provided with an opening are provided at opposite ends;
d) has a reading slide pin;
e) having a trailing slide pin;
f) the leading slide pin and the tray so that the two opposed slide pins support the brake shoe and the at least three arms support the two opposed slide pins. The ring slide pins are arranged so as to face each other, and are engaged with the openings of the three arms and the openings of the protrusions of the brake shoe,
g) a caliper body including a pair of spaced bosses provided with openings having bushings for accommodating the slide pins;
h) A disc brake including a slidable piston operable to bring the inner brake shoe and the outer brake shoe closer to each other. One or more brake shoe tips are pulled into contact with the slide pin to deform the leading slide pin, the frame member with which the leading slide pin engages, or both, The disc brake according to claim 9 , wherein the trailing end of one or more of the brake shoes is pressed to come into contact with the trailing slide pin. The inner brake shoe, the outer brake shoe, or both include a first engagement portion, the caliper body includes a second engagement portion, and the first engagement portion is connected to the second engagement portion. further comprising a clip for securing the engagement portion, claim 1 0 disk brake according. Wherein the bushing is provided with a groove, claim 1 0 Disk brake according. The disc brake is configured to operate in a pull abutment mode, thus reducing a self-applied tendency and reducing the self-applying tendency to reduce squeal noise, taper wear, or both. claim 1 1 disk brake according. The disc brake according to claim 1, wherein the caliper body is supported only by the slide pin at the pair of spaced boss portions. Each of the at least two arms extending from the frame member is
a) an outer arm provided outside the disc brake;
b) an inner arm provided inside the disc brake;
The disc brake according to claim 1, wherein the outer arm and the inner arm are disposed with a space therebetween.

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