JPH1122764A - Adjuster for disc brake device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an adjuster suppressing the size in the axial direction of a rotor, eliminating a need to locate a load plate between a piston and a friction pad, and suitable for reduction of size and weight. SOLUTION: A mechanism to rotate a latched member 32 by an adjuster lever 38 on an eccentric cam shaft 34 is incorporated between a pair of pistons 15 and 16 to press a friction pad against a rotor. By threadedly joining rotation of an adjuster gear 30, formed integrally, with a latched member 32, to an adjuster screw 21 through a transmission gear 27 engaged with the adjuster gear 30, the pistons 15 and 16 threadedly engaging with the adjuster screw 21 are unthreaded to the rotor side. Further, an adjuster lever 38 is provided with a protrusion part 82 forming an oscillation fulcrum during release operation.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an adjuster of a disc brake device for adjusting a clearance between a friction pad and a rotor, and more particularly, to an air adjuster using air pressure as a drive source of the friction pad during a braking operation. The present invention relates to an adjuster suitable for a drive type disk brake device.

[0002]

2. Description of the Related Art Heretofore, as an adjuster used in an air-driven disc brake device, a feed mechanism using a rotationally driven screw has been provided behind a pair of pressing pieces abutting against a back plate of a friction pad. An adjusting spindle that pushes the pressure piece toward the rotor through the control lever, an operating lever for rotating each adjusting spindle, a synchronizing device for synchronizing the rotation of each adjusting spindle, and adjusting a rotating torque acting on each adjusting spindle. A configuration incorporating a post-adjustment device has been proposed (see Japanese Patent Application Laid-Open No. 8-508080).

A pair of pistons are provided on the outer periphery and are provided so as to be movable in the axial direction of the rotor with their tips directed toward the rotor and press the friction pads, and a pair of pistons are provided on the outer periphery of each piston. A pair of sleeves are formed on the inner periphery of the female screw portion to be screwed with the male screw portion and are driven to rotate and reciprocate the piston along the rotor shaft. The sleeves are connected to the ends of each sleeve and rotate integrally with the sleeve. A pair of transmission gears, an adjuster gear provided between the pair of transmission gears so as to mesh with the pair of transmission gears, a camshaft that rotates by rotating the operation lever, and a camshaft of the camshaft. An adjuster having a transmission mechanism for rotating the adjuster gear by rotation has also been proposed (European Patent EP 0703379 A1).
reference).

[0004]

However, in the case of the former adjuster, since the various mechanisms including the adjusting spindle are connected in the axial direction of the rotor, the size is increased in the axial direction of the rotor, and the size is large in the axial direction of the rotor. There is a problem that it is necessary to secure a storage space, and it is difficult to mount it on a small vehicle or the like.

In the case of the latter adjuster, the outer diameter of the piston is reduced because a pair of pistons for pressing the friction pad are screwed into the sleeve. Therefore, in order to stabilize the contact with the friction pad, it is necessary to interpose a load plate having a large contact area with the friction pad. Occurs. Further, a transmission mechanism for rotating the adjuster gear by rotation of the camshaft is provided, but this also requires a one-way clutch mechanism to be provided in the axial direction of the rotor, which increases the dimension in the rotor axial direction. Further, no manual release is disclosed for releasing the adjustment by replacing the friction pad.

SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to solve the above-mentioned problems, and it is possible to suppress the dimension in the rotor axial direction, to easily mount it on a small vehicle, etc. An object of the present invention is to provide an adjuster for a disc brake device capable of performing a release.

[0007]

SUMMARY OF THE INVENTION In order to achieve the above object, the present invention relates to an adjuster mechanism of a disc brake device for adjusting a clearance between a friction pad and a rotor, wherein the adjuster mechanism includes a pair of friction pads for pressing the friction pad against the rotor. Piston, a pair of adjuster screw members for screwing the piston in the rotor axis direction, a ratchet member held by a caliper between the pistons to rotate the adjuster screw member, and a cam supported by the caliper between the pistons A shaft portion, a ring portion held while providing a desired gap in the camshaft, and an arm portion extending from the ring portion and having a tip engaged with a pawl of the ratchet member, the ratchet member being integrally formed with the rotation of the camshaft. An adjuster lever to be rotated, and an operation lever connected to the end of the camshaft to rotate the camshaft, A gear for manual release that pulls up the arm of the adjuster lever to disengage the arm from the ratchet member, and the adjuster lever is assembled to the camshaft on a part of the lower surface of the ring. When a lifting force is applied to the arm by a manual release gear, the arm is moved from the ratchet member by a swinging operation in which the projection serves as a swing fulcrum. It is configured to deviate.

According to the above configuration, when the operating lever disposed between the rotors is rotated, the cam shaft is rotated integrally with the operating lever, and the adjuster lever provided on the cam shaft is The ratchet member is rotated by a fixed amount. As a result, the adjuster gear, which is a component gear of the ratchet member, rotates, and rotates the adjuster screw screwed to each piston via each transmission gear included in the adjuster screw member meshing with the adjuster gear. Then, each piston is screwed out to the rotor side with respect to the caliper, and the friction pad with which these pistons are in contact moves to the rotor side.

In the above configuration, the ratchet mechanism or the like for transmitting the rotation of the operation lever to the transmission gear is disposed in the space between the pair of pistons and does not affect the dimension in the rotor axial direction. That is, since there are few components connected in the rotor axis direction, the dimension in the rotor axis direction can be suppressed.

[0010] Further, the piston for pressing the friction pad is fitted (screw-fit) to the outer periphery of the adjuster screw, so that the piston diameter can be maximized within the dimensional restrictions on the caliper. it can. Since the diameter of the piston can be increased, the contact between the piston and the friction pad is stabilized, and it is not necessary to interpose a load plate between the piston and the friction pad to stabilize the contact.

The adjuster lever engaged with the ratchet member is provided with a positioning projection on a ring portion fitted to the camshaft. The arm portion side engaged with the ratchet member swings by a swing operation in which the portion serves as a swing fulcrum, and the engagement with the ratchet member is released. Therefore, for example, when compared with a configuration in which the ring portion and the arm portion are slid together on the camshaft to release the engagement at the time of the release operation, the fitting between the camshaft and the ring portion is defined as a clearance fit having a large dimensional tolerance. In addition, there is no inconvenience that the inner peripheral edge of the ring portion is caught by the camshaft due to the bending moment acting during the release operation and the release operation is hindered, and a smooth release operation can be ensured. In addition, if the adjuster lever is attached to the camshaft so that it can swing, even if a bending moment acts on the adjuster lever due to vibration applied during braking, etc., the load will be reduced by a minute swing operation. The deformation and breakage of the adjuster lever caused by vibrations and the like can be prevented, and the vibration resistance and operation reliability of the adjuster lever can be improved. The eccentric camshaft can amplify the boosting action.

[0012]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to the illustrated embodiments. 1 to 9 show one embodiment of an adjuster of a disc brake device according to the present invention.
1 is an exploded perspective view of an adjuster 1 according to an embodiment, FIG. 2 is a plan view of a part of a disk brake device 2 incorporating the adjuster 1, and FIG. 3 is a sectional view taken along line AA of FIG. 4 is a sectional view taken along the line BB of FIG. 2, and FIG.
FIG. 6 is a view of the adjuster lever shown in FIG.
7, FIG. 7 is a view taken in the direction of arrow E in FIG. 6, and FIG. 8 is an explanatory view of the operation of the adjuster lever at the time of manual release (adjustment MAX) in one embodiment. FIG. 9 is a view of the adjuster lever of one embodiment. It is explanatory drawing of operation | movement in a free state.

As shown in FIG. 2, a disc brake device 2 equipped with the adjuster 1 of this embodiment has a disk-shaped rotor 4 that rotates integrally with wheels, and a pair of disks 4 that are opposed to each other with the rotor 4 interposed therebetween. Frictional pads 6 and 7 and a drive mechanism accommodating portion 11c serving as an accommodating portion of a piston for pressing one of the frictional pads 6 toward the rotor 4 are provided at one end of a bridge portion 11a straddling the rotor 4.
A caliper 11 having a claw portion 11b for pressing the back surface of the other friction pad 7 on the other end side of the a and a support 10 fixed to the vehicle body and supporting the caliper 11 (see FIGS. 3 and 4). It is a configuration provided. The above-described adjuster 1 has a suitable configuration for use in a pneumatically-driven disc brake device used in a motorcycle. However, the adjuster 1 is suitable for a hydraulically-driven disc brake device that is widely used in passenger cars and the like. Needless to say, it can also be mounted.

Each of the friction pads 6 and 7 is pressed against the surface of the rotor 4 to generate a predetermined frictional force.
2 and a back plate 13 fixedly mounted on the back side of the lining 12 and functioning as a mounting bracket or the like.

The adjuster 1 of one embodiment includes a caliper 1
One friction pad 6 is separated from the rotor 4 by a pair of pistons 15 and 16 incorporated in one drive mechanism accommodating portion 11c.
To adjust the clearance between each of the friction pads 6 and 7 and the rotor 4.

Specifically, as shown in FIGS. 1 and 2, the adjuster 1 is provided with a driving mechanism accommodating portion 11c of the caliper 11.
A piston support case 18 slidably held in the direction of the rotor 4 in the inside, and a pair of pistons 1 movably supported in the axial direction of the rotor by the piston support case 18
5, 16 are provided. A pair of adjuster screws 21, 22 having screw portions 21 a, 22 a screwed to female screws on the inner periphery of the pistons 15, 16 are formed on the outer periphery on the distal end side, and a screw portion 19 for fastening is formed on the inner periphery on the proximal end side. 22, a pair of transmission gears 27 and 28 having a screw portion 24 screwed to the screw portion 19 at the base end of the adjuster screws 21 and 22 and integrally rotating with the pair of adjuster screws 21 and 22; An adjuster gear 3 provided between the pair of transmission gears 27 and 28 so as to mesh with the pair of transmission gears 27 and 28.
0 and a ratchet member 32 provided coaxially with the adjuster gear 30 and rotatable integrally with the adjuster gear 30.
Are respectively supported by the piston support case 18. Further, an eccentric camshaft 34 rotatably mounted between the pair of pistons 15 and 16 with the axis thereof oriented in the radial direction of the rotor 4, and an eccentric camshaft 34 connected to and mounted on an end of the eccentric camshaft 34. An operation lever 36 for rotating the camshaft 34, a ring portion 52 fitted to the eccentric camshaft 34, and an arm portion 53 extending from the ring portion 52 and having a tip engaged with a pawl of the ratchet member 32. An adjuster lever 38 that rotates together with the eccentric camshaft 34 to rotate the ratchet member 32 in accordance with the rotation of the eccentric camshaft 34, and an arm 53 of the adjuster lever 38 is pulled upward to ratchet the arm 53. And a manual release gear 60 for disengaging from the member 32.

The piston support case 18 includes the piston 1
Between a pair of cylindrical portions 18a, 18a accommodating 5 and 16;
The configuration is such that a shaft insertion hole 18b corresponding to the eccentric cam portion of the eccentric camshaft 34 is formed. A gear support hole 18c that rotatably supports the adjuster gear 30 and the ratchet member 32 is provided so as to pass through the center of the shaft insertion hole 18b.

The pair of pistons 15 and 16 have a headed cylindrical shape with one end opened, and the closed other end is connected to the rotor 4.
It is slidably fitted to the cylindrical portion 18a of the piston support case 18 toward the side. And these pistons 1
The engagement grooves 40 are formed on the front end surfaces of the friction pads 6 that abut against the back plate 13 so that the rotation movements in the piston support case 18 are restricted. Have been. The engagement of the engagement grooves 40 with the projections formed on the back plate 13 restricts the rotation of the pistons 15 and 16.

As shown in FIGS. 1 and 2, the adjuster screws 21 and 22 have a substantially cylindrical shape, and are screwed to the screw portions (male screws) 24 of the transmission gears 27 and 28 described above. The female screw 19 is engraved on the inner periphery of the base end. The screw portion 19 is provided with the adjuster screws 21 and 22 respectively.
Are oppositely threaded with respect to the threaded portions 21a and 22a formed on the outer periphery on the distal end side of. In addition, each adjuster screw 21,
A flange 42 is formed on the outer peripheral portion of the base 22 near the base end. The flanges 42 are in contact with the end surfaces of the pistons 15 and 16, and the initial positions of the pistons 15 and 16 are set.

A pair of transmission gears 27, 28 are connected to adjuster screws 2 screwed to these transmission gears 27, 28.
The piston support case 1 is formed in cooperation with
The cylindrical portion 18a is rotatably supported by the piston support case 18 by sandwiching a protruding portion protruding toward the inner diameter side of the base end of the cylindrical portion 18a.

When the transmission gears 27 and 28 are driven to rotate,
Each adjuster screw 21, 22 is connected to these transmission gears 27,
As a result, the pistons 15 and 16 advance and retreat in the rotor axial direction. An opening is provided at the center of each of the transmission gears 27 and 28 for inserting a return spring 44 that urges the pistons 15 and 16 away from the friction pad 6.

The return spring 44 is connected to the transmission gear 2.
The spring receiving sleeve 46 has a cylindrical portion 46a that penetrates through the inside of the adjuster screws 21 and 22 and positioning members 46b that protrude from the base end of the cylindrical portion 46a and abut on the end faces of the transmission gears 27 and 28. Will be accommodated. The return spring 44 is compressed by a spring receiving washer 49 provided at the other end of a bolt 48 which is inserted through the center of the spring receiving sleeve 46 and one end of which is screwed to the pistons 15, 16. Act on the pistons 15 and 16. Therefore, the return spring 44 is connected to the piston 1
5 and 16 are stabilized by the urging force, and centering is also performed. Positioning piece 46b of spring receiving sleeve 46
The drive mechanism housing 1 from outside the spring receiving sleeve 46.
1c and the transmission gear 2
7 and 28 and are fixed.

In the case of this embodiment, the adjuster lever 38 includes a ring 52 and an arm 53 which are separate from each other.
As shown in (1), the arm portion 53 has a curved portion 53a wound around the outer periphery of the ring portion 52 on the base end side. The arm portion 53 is mounted on the eccentric camshaft 34 together with the ring portion 52 in a state where the curved portion 53a is wound around the outer periphery of the ring portion 52, and the eccentric camshaft 34 is inserted through the ring portion 52 and the arm portion 53. Is fixed to the eccentric camshaft 34 together with the ring portion 52 by a screw member 56 screwed into the camshaft 34. Also, as shown in FIG.
There is a gap between the ring portion 52 and the protruding portion 34a of the camshaft 34, and by providing a non-adjustment range of a fixed amount Δx, dragging is prevented.

Further, in the case of this embodiment, when the adjuster lever 38 is assembled to the eccentric camshaft 34 on a part of the lower surface of the ring portion 52 as shown in FIGS. Is provided with a projection 82 which abuts on the upper surface of the cam portion to perform positioning in the height direction.
When the lifting force is applied to 3, the arrow (b) in FIG.
As shown in the figure, the arm portion 53 is attached to the eccentric camshaft 34 such that the arm portion 53 is disengaged from the ratchet member 32 by a swinging operation in which the projection 82 serves as a swing fulcrum. Further, the support by the projection 82 is effective even when a downward load is applied due to the vibration of the vehicle during braking or the force in the return direction of the ratchet member 32. In this case, an arrow (c) in FIG. As described above, the arm portion 53 swings downward by the swinging operation in which the projection 82 serves as the swing fulcrum.

When the adjuster lever 38 is set on the eccentric camshaft 34, the arm 53 is easily positioned in a horizontal state as shown in FIG. In order to prevent the posture from becoming unstable and further restrict the swinging direction, the projecting portion 82 is designed so that the tip surface 82a is finished flat and a certain contact area is obtained. As shown in 7,
It is elongated.

The upper end of the eccentric cam shaft 34
As shown in FIG. 1 and FIG. 4, it is rotatably supported by a retainer 54 screwed into a shaft insertion hole 11d opened at an upper portion of the drive mechanism accommodating portion 11c. A spring 58 for biasing the adjuster lever 38 is provided between the retainer 54 and the ring portion 52 so that the end of the adjuster lever 38 is kept engaged with the ratchet member 32. As shown in FIG. 1, a manual release gear 60 is provided on the body cover 50.
1, so that it can be rotated. The gear 60 rotates when the lever 61 is rotated, and pulls up the adjuster lever 38 to move the adjuster lever 3 upward.
The engagement between the ratchet member 8 and the ratchet member 32 is released, and the gap adjustment is returned to the initial state.

The adjuster 1 of one embodiment described above
Then, when the operation lever 36 is rotated, the operation lever 36
The eccentric camshaft 34 rotates integrally with the eccentric camshaft 34, and the adjuster lever 38 mounted on the eccentric camshaft 34 moves in the direction of the arrow (a) in FIG. 3 to rotate the ratchet member 32 by a fixed amount. As a result, the adjuster gear 30 integrated with the ratchet member 32 rotates, and the rotation of the adjuster gear 30 is controlled by the inner circumferences of the pistons 15 and 16 via the transmission gears 27 and 28 meshing with the adjuster gear 30. Rotate the adjuster screws 21 and 22 screwed into
The rotation of the adjuster screws 21 and 22 causes the pistons 15 and 16 to be screwed out to the rotor side, and the friction pad 6 with which the pistons 15 and 16 are in contact is moved to the rotor 4 side so that the rotor 4 and the The gap between the friction pads 6 and 7 is reduced.

In the above adjuster 1, the components connected in the rotor axial direction to move the pistons 15 and 16 toward the rotor 4 are adjuster screws 21 and 22.
A ratchet mechanism or the like for transmitting the rotation of the operation lever 36 to the transmission gears 27 and 28 with the transmission gears 27 and 28 connected to the ends of the adjuster screws 21 and 22 includes:
It is arranged in the space between the pair of pistons 15 and 16,
Does not affect the dimension in the rotor axis direction. That is, since there are few components connected in the rotor axis direction, the dimension in the rotor axis direction can be suppressed, the size can be reduced, and the mounting on a small vehicle or the like becomes easy.

The piston 1 for pressing the friction pad 6
5 and 16 fit (screw-fit) to the outer circumferences of the adjuster screws 21 and 22, and are compared with a conventional one in which a pair of pistons pressing a friction pad are screwed into a sleeve. The piston diameter can be maximized within the dimensional restrictions on the caliper. And
Because the piston diameter can be increased, the piston 1
The contact between the friction pads 6, 5 and the friction pad 6 is stabilized, and there is no need to interpose a load plate between the pistons 15, 16 and the friction pad 6 to stabilize the contact. Therefore, as compared with the structure having a load plate, the weight can be reduced, and the return movement of the pistons 15 and 16 at the time of braking release can be performed quickly to prevent inconvenience such as dragging. can do.

As shown in FIGS. 10 and 11, the adjuster lever 38 finishes the entire lower end surface of the ring portion 52 to make the entire lower end surface thereof flat against the upper surface of the cam of the eccentric cam shaft 34. The contact makes it possible to perform positioning when assembled to the eccentric camshaft 34 and to slide the entire adjuster lever 38 on the eccentric camshaft 34 during a release operation by the manual release gear 60. However, in such an assembling structure, a large force is required to operate the manual release gear 60. Further, in order to facilitate the sliding, the fitting between the eccentric camshaft 34 and the ring portion 52 must be performed. If a clearance fit with a large dimensional tolerance is used, the inner peripheral edge of the ring portion 52 inclined at the time of the sliding operation may be caught on the eccentric camshaft 34, and a smooth release operation may not be performed.

Therefore, the adjuster lever 38 of the adjuster 1 is configured such that a positioning projection 82 is provided on the ring portion 52 fitted to the eccentric camshaft 34. As a result, the gear 6 for manual release
At the time of the release operation, the arm portion 53 engaged with the ratchet 32 swings due to the swinging operation in which the protrusion 82 becomes a swing fulcrum, and the engagement with the ratchet 32 is released. Compared to the conventional case in which the ring portion 52 and the arm portion 53 are disengaged by sliding on the eccentric camshaft 34 integrally, the fitting between the eccentric camshaft 34 and the ring portion 52 is a clearance fit having a large dimensional tolerance. However, the inner peripheral edge of the ring portion 52 may be bent by the bending moment acting during the release operation.
No inconvenience such that the release operation is hindered by being caught by the step No. 4 does not occur, and a smooth release operation can be ensured.

If the adjuster lever 38 is swingably attached to the eccentric camshaft 34 in this manner, the adjuster lever 3 may be vibrated during a braking operation or the like.
Even if a bending moment acts on the load 8, the load can be reduced by a minute swinging operation, the deformation and breakage of the adjuster lever 38 caused by vibrations and the like can be prevented, and the vibration resistance and operation reliability of the adjuster lever 38 can be reduced. Performance can be improved.

The adjuster 1 according to the embodiment described above
Is a forward operation type that operates at the time of forward movement when the operation lever 36 is rotated. When changing to a return operation type that operates at the time of return operation of the operation lever 36, the two-dot chain line in FIG. It is sufficient to replace the component 64 enclosed by the circle with the component 66 enclosed by the broken line.

The adjuster 1 according to the above-described embodiment is
Is a positive type, but a negative type can be used by changing the direction of the pawl of the ratchet member 32 and changing the contact direction of the adjuster lever 38.

Further, in this embodiment, the adjuster lever 38 has the ring portion 52 and the arm portion 53 as separate bodies, but the ring portion 52 and the arm portion 53 may be formed integrally.

[0036]

According to the adjuster of the disk brake device of the present invention, the ratchet mechanism for transmitting the rotation of the operation lever to the transmission gear is disposed in the space between the pair of pistons, and affects the dimension in the rotor axial direction. Do not give. That is, since there are few components connected in the rotor axial direction, the dimension in the rotor axial direction can be suppressed, and the size can be reduced. Compared to a structure having a load plate, the weight can be reduced, and the return operation of the piston at the time of braking release can be made smooth to prevent inconvenience such as dragging.
Further, it is possible to provide a configuration having a manual release when releasing the adjustment by replacing the friction pad or the like, and at the time of this release operation, the protrusion is engaged with the ratchet member by a swinging operation serving as a swing fulcrum. The arm part side swings to disengage from the ratchet member, and the bending moment acting during the release operation does not cause inconvenience such that the inner peripheral edge of the ring part is caught on the eccentric cam shaft and the release operation is hindered. , Smooth release operation can be ensured. Also, even when a bending moment acts on the adjuster lever due to vibration or the like applied during a braking operation, etc., the load can be reduced by a minute swing operation,
It is possible to prevent the adjuster lever from being deformed or damaged due to vibration or the like, and to improve the vibration resistance and operation reliability of the adjuster lever.

[Brief description of the drawings]

FIG. 1 is an exploded perspective view of an embodiment of an adjuster of a disc brake device according to the present invention.

FIG. 2 is a cross-sectional plan view of a part of a disk brake device incorporating an adjuster according to an embodiment of the present invention.

FIG. 3 is a sectional view taken along line AA of FIG. 2;

FIG. 4 is a sectional view taken along line BB of FIG. 2;

FIG. 5 is a view of the adjuster lever shown in FIG.

FIG. 6 is a view as viewed in the direction of arrow D in FIG. 5;

FIG. 7 is a view as seen from an arrow E in FIG. 6;

FIG. 8 is an explanatory diagram of an operation of the adjuster lever according to the embodiment of the present invention at the time of manual release (at the time of an adjustment MAX).

FIG. 9 is an explanatory diagram of an operation of the adjuster lever in a free state according to the embodiment of the present invention.

FIG. 10 is a plan view showing a conventional adjuster lever mounting structure.

11 is a view as viewed from the direction of the arrow F in FIG. 10;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Adjuster 2 Disc brake device 4 Rotor 6,7 Friction pad 11 Caliper 11c Drive mechanism accommodation part 15,16 Piston 18 Piston support case 19 Screw part 21,22 Adjuster screw 21a, 22a Screw part 24,25 Screw part 27,28 Transmission Gear 30 Adjuster gear 32 Ratchet member 34 Eccentric camshaft 34a Projection 36 Control lever 38 Adjuster lever 40 Engagement groove 44 Return spring 46 Spring receiving sleeve 48 Bolt 52 Ring part 53 Arm part 54 Retainer 58 Spring 60 Gear for manual release 61 Lever 82 Projection

Claims (1)

[Claims] 1. An adjuster of a disc brake device for adjusting a clearance between a friction pad and a rotor, comprising: a pair of pistons pressing the friction pad against the rotor; and screwing and rotating with the piston. A pair of adjuster screw members for causing the piston to screw out in the rotor axial direction, a ratchet member held between the pistons by a caliper to rotate the adjuster screw members, and supported by the caliper between the pistons A camshaft; a ring portion held while providing a desired gap in the camshaft; and an arm portion extending from the ring portion and having a tip engaged with a pawl of the ratchet member. An adjuster lever for integrally rotating the ratchet member; and a camshaft connected to an end portion of the camshaft. An operating lever for rotating the shaft, and a gear for manual release for lifting the arm of the adjuster lever upward to disengage the arm from the ratchet member, wherein the adjuster lever has a ring. A projection is provided on a part of the lower surface of the section for positioning in the height direction when assembled to the camshaft. When a pulling force is applied to the arm by the gear for manual release, the projection swings. An adjuster for a disc brake device, characterized in that the arm portion is disengaged from the ratchet member by a swinging operation as a fulcrum.