JP5260616B2 - Adjuster mechanism in link type booster - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an adjuster mechanism in a link-type booster capable of securing high adjusting precision without unreasonable force acting on an adjusting section. <P>SOLUTION: The adjustment of the adjuster mechanism 6 can be performed without being affected by the oscillation of links 7 and the oscillation of brake arms and the high adjusting precision can be secured without being affected by the rigidity of the adjusting section, because the oscillation supporting shafts of the adjuster levers 10 substantially coinside with output shaft supporting points 8 in the substantially center parts of the links 7 less affected by the movement from the proximal ends of the brake arms while adopting a simply structured link-type booster, by making the oscillation supporting shafts of the adjuster levers 10 rotating each of adjuster gears along with excessive stroke of each of the brake arms coincide with the output shaft supporting points 8 in the substantially center parts of each of the links 7. <P>COPYRIGHT: (C)2012,JPO&amp;INPIT

Description

  According to the present invention, an output shaft fulcrum and a base end portion of each brake arm at a substantially intermediate portion of a pair of links that are expanded and swung by an axial movement of an actuator are separated from each other by a relative rotation between an adjuster gear and an adjuster nut. The present invention relates to an adjuster mechanism in a link type booster connected via an adjuster mechanism that adjusts the angle.

  Conventionally, in a vehicle equipped with a brake, particularly a disc brake for a railway vehicle, a base end portion of a pair of brake arms is expanded and a pad assembly provided at the open end portion is clamped from both sides of the brake rotor. An insulator-type caliper brake that performs a brake operation is known. In these lever-type caliper brakes, when the pad assembly is worn, the time when the brake starts to work is delayed and the braking distance becomes long. Therefore, an adjuster mechanism, which is a gap adjusting mechanism, is usually disposed between the actuator and the base end portion of the brake arm so that an excessive stroke does not occur in the brake arm. As such an adjuster mechanism, for example, there is a brake cylinder described in Patent Document 1 below.

JP 2008-164159 A (refer to the gazette abstract)

  As shown in FIG. 7, the brake cylinder disclosed in Patent Document 1 is attached to the piston 103 that moves relative to the cylinder body 102, the shaft rod 104 that moves together with the piston 103, and the shaft rod 104. A push rod 105 and a projection length adjusting means 106 for adjusting a projection length of the push rod 105 from the cylinder main body 102 when the brake is operated. The push rod 105 is parallel to the moving direction of the piston 103. And a female screw 151 is screwed into at least a part of the inner surface of the shaft hole, and the shaft rod 104 is screwed with the female screw 151 into at least a part of the outer surface. The mating male screw 141 is threaded and inserted into the shaft hole, and the engaging portion 142 is engageable with a rotational force applying means for applying a rotational force around the shaft from the outside. Those having.

  In the brake cylinder 101 provided with such a protrusion length adjusting means 106, the piston 103 is connected via the shaft rods 104 and 105 as shown in FIG. 7 (B) by supplying the pressure into the pressure chamber 102b. The member 107 is moved in the expanding direction with respect to the first casing 121 in the cylinder body 102. As a result, a brake arm (not shown) connected to each of the connecting member 107 and the first casing 121 is swung to perform a braking operation. When wear occurs in the pad assembly, the cover 108 is removed, and a socket such as a handle wrench is externally engaged with the engaging portion 142 of the shaft rod 104 to rotate the female screw 151 of the push rod 105. By moving the male screw 141 of the shaft rod 104 into engagement with the shaft rod 104 to increase the axial distance between the shaft rod 104 and the push rod 105, it is possible to adjust the clearance to suppress the overstroke of the brake arm.

  However, in such a conventional adjuster mechanism, the adjustment work is performed manually using an external handle wrench or the like, and the work is troublesome. Therefore, an automatic gap adjustment mechanism that eliminates the hassle of manual adjustment is also used, but there is an unavoidable tendency for over adjustment and pad clearance adjustment width to increase due to the effect of body rigidity. In addition, the adjusting unit may be damaged due to excessive force from the brake arm.

  SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to solve the problems in the conventional adjuster mechanism and to provide an adjuster mechanism in a link type booster capable of ensuring high adjustment accuracy without applying an excessive force to the adjusting portion. And

Therefore, the problem solving means adopted by the present invention is:
An adjuster that adjusts the inter-shaft distance between the output shaft fulcrum and the base end of each brake arm at the substantially middle part of the pair of links that are expanded and oscillated by the axial movement of the actuator by relative rotation between the adjuster gear and the adjuster nut. In the adjuster mechanism in the link type booster connected via the mechanism, the swing support shaft of each adjuster lever that rotates each adjuster gear in accordance with the overstroke of each brake arm is arranged at a substantially intermediate portion of each link. An output shaft fulcrum that substantially matches the output shaft fulcrum and prevents rotation of the adjuster mechanism in the shortening direction by the adjuster gears, and the support shaft of the check claw is an output shaft fulcrum at a substantially intermediate portion of each link The adjuster mechanism in the link type booster is characterized in that it is arranged so as to substantially match .
It is also adjuster mechanism in link-type booster, characterized in that pre-Symbol linked by balance spring between the adjuster levers.

  According to the present invention, the output shaft fulcrum and the base end portion of each brake arm at the substantially intermediate portion of the pair of links that are expanded and swung by the axial movement of the actuator are respectively rotated by the relative rotation of the adjuster gear and the adjuster nut. In the adjuster mechanism in the link type booster connected via an adjuster mechanism that adjusts the distance between the links, the swing support shafts of the adjuster levers that rotate the adjuster gears when the brake arms are overstroked are connected to the links. It is almost the middle of the link that is less affected by the behavior from the base end of the brake arm while adopting a link type booster with a simple structure by making it substantially coincide with the output shaft fulcrum in the middle part of Since the pivot shaft of the adjuster lever is approximately aligned with the output shaft fulcrum at the shaft, the link swing and brake arm Without being affected by the movement, and can adjust the adjuster mechanism, without being affected by rigidity of the adjusting unit, high adjustment accuracy can be ensured.

  Further, when the adjuster levers are connected by balance springs, the balance spring connected between the adjuster levers is extended even if the adjuster gear is difficult to rotate due to the axial force acting on the adjuster mechanism. Shows a behavior of parallel movement rather than rotational movement, and the adjuster gear is not rotated with a force more than necessary, so that the adjuster gear is prevented from being damaged. Further, when a check claw for preventing the adjuster mechanism from rotating in the shortening direction by the adjuster gears is provided, the adjuster mechanism can be reliably adjusted in the expansion direction to complement the pad assembly wear, and the adjuster mechanism goes back in the shortening direction. Therefore, high adjustment accuracy can be ensured, and when the adjuster is returned when the pad assembly is replaced, the adjuster gear does not reversely rotate. Therefore, only the adjuster nut can be rotated to reduce the adjuster mechanism to the position before replacement.

  Furthermore, when the support shaft of the check pawl is substantially coincident with the output shaft fulcrum at the substantially intermediate portion of each link, the malfunction does not occur due to the swinging of the link, as in the behavior of the adjuster lever. , It is possible to always keep the check function at the same position.

It is a principal part front view of one Example of the adjuster mechanism in the link type booster of this invention. It is the principal part rear view and side view same as the above. FIG. 3 is an enlarged view of the main part of FIG. It is a partially exploded perspective view of the principal part. FIG. 2 is an overall plan view of the brake device in which the adjuster mechanism is employed in the link type booster of the present invention. FIG. 2 is an overall front view of the brake device. It is explanatory drawing of the brake cylinder by which the conventional adjustment means was employ | adopted.

  Hereinafter, a preferred embodiment for carrying out an adjuster mechanism in a link type booster of the present invention will be described with reference to the drawings. As shown in FIG. 1, the adjuster mechanism in the link type booster of the present invention includes an output shaft fulcrum 8 at a substantially intermediate portion of the pair of links 7, 7 that swings and expands by the axial movement of the actuator, and each brake arm. In the adjuster mechanism in the link type booster in which the base end portion is connected via the adjuster mechanism 6 that adjusts the distance between the shafts by the relative rotation of the adjuster gear and the adjuster nut, respectively, with the overstroke of each brake arm. The swing support shaft of the adjuster lever 10 for rotating the adjuster gears is made substantially coincident with the output shaft support point 8 at the substantially intermediate portion of each link.

  Hereinafter, an embodiment of an adjuster mechanism in the link type booster of the present invention will be described. As shown in FIGS. 5 and 6, the body 2 is fixed to the vehicle body stationary part via an appropriate support 1, and intermediate parts of a pair of brake arms 3 and 3 are disposed on both sides of the lower part of the body 2. 23. A brake holder 4 is supported at each open end of the brake arms 3, 3, and a pad assembly 5 is attached to the brake holder 4. And the outer end 13A of the adjuster nut 13 which comprises the output shaft of the adjuster mechanism 6 in the link type booster mentioned later is connected with each base end part of the brake arms 3 and 3. As shown in FIG.

  As shown in FIG. 1, the axial movement of the actuator (in addition to the axial movement of the wedge 15 that is axially moved by an actuator such as a separate fluid pressure or an electric motor, the wedge 15 itself is axially moved by the hydraulic pressure or the electric motor, etc. The output shaft fulcrum 8 and the base end portion of each brake arm 3 (FIGS. 5 and 6) at the substantially intermediate portion of the pair of links 7 and 7 that swing and expand by the adjuster gears may be respectively provided. They are connected via an adjuster mechanism 6 that adjusts the distance between the shafts by relative rotation with the adjuster nut. The pivots 18 for swinging the pair of links 7 and 7 are disposed at both ends of a strut 17 disposed at the lower end. A roller 16 is supported by a roller shaft 19 at each swinging end of the upper ends of the links 7 and 7.

  As shown in FIGS. 1 and 2, when the slopes 15 </ b> A and 15 </ b> A on both sides of the wedge 15 expand the links 7 and 7 via the rollers 16 and 16 with the axial movement of the wedge 15, Is output from the output shaft fulcrum 8 to the base end portion of the brake arm 3 through the adjuster mechanism 6. An adjuster gear 12 of the adjuster mechanism 6 that adjusts the distance between the shafts by relative rotation between an adjuster gear and an adjuster nut, which will be described later, is rotated by an adjuster lever 10 that swings when the brake arm 3 is overstroked due to wear of the pad assembly 5. It is configured to be adjusted. In the present invention, the swing support shaft of the adjuster lever 10 is configured to be substantially coincident with the output shaft support point 8 at a substantially intermediate portion of each link 7. The base end portions of the adjuster levers 10 each having the output shaft fulcrum 8 at the substantially intermediate portion of each link 7 as a swinging support shaft are connected with a balance spring 9 stretched between them.

  Referring to FIG. 3, which is an enlarged view of the main part of FIG. 2B, in FIG. 1, when the brake arm 3 is overstroked due to wear of the pad assembly 5, the adjuster nut 13 in the adjuster mechanism 6 is also excessively moved outward. Move the stroke. At that time, the adjuster lever 10 swings about the output shaft fulcrum 8 on the upper side, which is the swing end, to the outside (the base end side of the brake arm 3). As shown in FIG. 2B, the adjuster gear 12 of the adjuster lever 10 is balanced by a balance between the return spring 20 that urges the adjuster lever 10 upward and the pressing spring 21 that urges the adjuster lever 10 toward the adjuster gear 12. Oscillation and return operations are performed for reliable engagement and adjustment.

  As shown in FIG. 3 and FIG. 4 which is a partially exploded perspective view, the adjuster lever 10 during an overstroke is adjusted when the upper end of the swing end portion swings outward (ie, the lower side) about the output shaft fulcrum 8. The gear 12 is rotated to the right in the drawing to feed one ratchet tooth. At that time, a check pawl 22 in the stopper 11 is engaged with the adjuster gear 12 on the opposite side of the adjuster lever 10. The check pawl 22 has a function of preventing the adjuster gear 12 from rotating in the shortening direction of the adjuster mechanism. The check pawl 22 is installed on the stopper 11 whose base end is supported by the output shaft fulcrum 8 in the substantially middle portion of the link 7, and the hole at the tip thereof is formed at the base of the adjuster gear 12 as shown in FIG. 4. The shaft portion is supported together with the shaft portion of the base portion of the adjuster gear 12 when the shaft portion is fitted into the adjuster socket 14 that is pivotally supported by the output shaft fulcrum 8.

  With this configuration, the arrangement of the check pawl 22 in the stopper 11 can reliably adjust the adjuster mechanism in the expansion direction that complements the pad assembly wear, and does not reverse in the shortening direction. Since the adjuster gear 12 does not reversely rotate when the adjuster is returned when the pad assembly is replaced, only the adjuster nut 13 can be rotated to reduce the adjuster mechanism 6 to the position before replacement. At this time, the support shaft of the stopper 11 provided with the check pawl 22 is made to substantially coincide with the output shaft support point 8 in the substantially middle portion of each link 7, and the swing of the link 7 is similar to the behavior of the adjuster lever 10. The check function can always be maintained at the same position without malfunction due to movement or the like.

  Thus, a link type booster having a simple structure is adopted by making the swinging support shaft of the adjuster lever 10 for rotating each adjuster gear 12 substantially coincide with the output shaft support point 8 in the substantially intermediate portion of each link 7. However, the adjuster mechanism can be adjusted at the output shaft fulcrum 8 at the substantially intermediate portion of the link 7 that is hardly influenced by the behavior from the base end portion of the brake arm 3 and is affected by the rigidity of the adjusting portion. And high adjustment accuracy can be secured. In addition, since the adjuster levers 10 and 10 are connected by the balance spring 9, the balance spring 9 is extended even if the adjuster gear 12 is difficult to rotate due to the axial force acting on the adjuster mechanism 6, and the adjuster lever 10. Shows the behavior of parallel movement instead of rotational movement, and the adjuster gear 12 is not rotated with an excessive force, so that the adjuster gear 12 is prevented from being damaged.

  The embodiments of the present invention have been described above. However, within the scope of the present invention, the brake actuator type (fluid type such as liquid pressure or air pressure, electric type such as electromagnetic or motor, or gear train is used. The wedge of the embodiment itself may constitute an actuator that is axially moved by fluid pressure, an electric motor or the like), the output shaft fulcrum in the link of the adjuster mechanism, and the base end of the brake arm. Related configuration of connecting part, position of output shaft fulcrum, that is, boost ratio in link type booster, adjustment form by relative rotation of adjuster gear and adjuster nut (screw engagement with screw, engagement of protrusion and inclined groove, etc. Can also be adopted), the form of shaft support to the output shaft fulcrum in the link of the adjuster lever, and the connection of the balance spring to each adjuster lever Form, installation mode of the check pawl in the stopper, the shape of the counter claw for supporting form such as to the output shaft fulcrum in the link of the stopper can be suitably selected. In addition, the specifications described in the examples are merely examples in all respects and should not be interpreted in a limited manner.

  The adjuster mechanism in the link type booster of the present invention is preferably applied to a caliper type disc brake of a railway vehicle, but can also be applied to a vehicle such as an automobile, an industrial disc brake and the like.

6 Adjuster mechanism 7 Link 8 Link output shaft fulcrum 9 Balance spring 10 Adjuster lever 13 Adjuster nut 15 Wedge 16 Roller 17 Strut 18 Support shaft 19 Roller shaft

Claims (2)

An adjuster that adjusts the inter-shaft distance between the output shaft fulcrum and the base end of each brake arm at the substantially middle part of the pair of links that are expanded and oscillated by the axial movement of the actuator by relative rotation between the adjuster gear and the adjuster nut. In the adjuster mechanism in the link type booster connected via the mechanism, the swing support shaft of each adjuster lever that rotates each adjuster gear in accordance with the overstroke of each brake arm is arranged at a substantially intermediate portion of each link. An output shaft fulcrum that substantially matches the output shaft fulcrum and prevents rotation of the adjuster mechanism in the shortening direction by the adjuster gears, and the support shaft of the check claw is an output shaft fulcrum at a substantially intermediate portion of each link An adjuster mechanism in a link type booster, characterized in that it is arranged substantially coincident with Adjuster mechanism in link-type booster according to claim 1, characterized in that pre-Symbol linked by balance spring between the adjuster levers.

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