JP6285056B2 - Disc brake device - Google Patents

Description

  The present invention relates to a floating disc brake device, and more particularly to a disc brake device capable of reducing drag torque.

About general floating disk caliper
As shown in FIG. 31, the caliper bracket 101 fixed to the knuckle 100 of the vehicle body is provided with a pair of bracket-side support arms 102, and these bracket-side support arms 102 straddle the outer edge of the disc rotor 103 in the axial direction. The caliper body 104 is supported. The bracket side support arms 102 are formed with rectangular grooves facing each other. A retainer that floats and supports the pads 105 and 106 and facilitates sliding of the pads 105 and 106 is provided in the rectangular groove of the bracket-side support arm 102. As the pads 105 and 106, a pair of pads 105 and 106 on the inboard side and the outboard side are provided so as to sandwich the disc rotor 103.

  The caliper body 104 has a pair of body side support arms 107. A pair of slide pins 108 are screwed onto the bracket side support arms 102, and the body side support arms 107 are supported by the slide pins 108 so as to be relatively movable. The caliper body 104 is floatingly supported with respect to the caliper bracket 101 by the slide pins 108 and the body side support arms 107. The slide pin 108 may be screwed by providing a nut on the bracket-side support arm 102. As shown in FIG. 32, the caliper body 104 also has a reaction force claw 109 that extends across the outer edge of the disk rotor 103 in the axial direction and supports the back surface of the pad 106 on the outboard side.

  When the brake is activated and the piston protrudes from the caliper body 104, the pad 105 on the inboard side is pressed by the piston to press the disc rotor 103. The reaction force generated thereby moves the caliper body 104 that is floatingly supported in the axial direction, and the reaction force claw 109 presses the pad 106 on the outboard side toward the disk rotor 103 side. Therefore, the braking operation is realized by sandwiching the disc rotor 103 between the pads 105 and 106 on the inboard side and the outboard side.

  When releasing the brake, the load on the reaction force claw 109 is released simultaneously with the release of the piston load. Normally, the piston is pulled away from the inboard side pad 105 by means such as an elastic ring fitted in a groove provided in the cylinder of the caliper body 104, and the inboard side pad 105 itself is held without restriction in the piston axial direction. Is done. At this time, if the pad 105 on the inboard side is repelled from the disk rotor 103 even under the influence of slight fluctuation of the disk rotor 103, the pad 105 is naturally separated from the disk rotor 103.

Japanese Utility Model Publication No. 6-32773 Japanese Utility Model Publication No. 6-80035 Japanese Utility Model Publication No. 3-41232 JP-A-8-200409 JP 2004-225726 A

  On the other hand, the reaction force claw 109 is floatingly supported as it is at the position where the load is removed. Moreover, because there is a sliding resistance of the slide pin 108 that supports the caliper body 104 and a reaction force due to the bending of the boot 110 that protects the slide pin 108, the pad 106 on the outboard side moves in a direction away from the disk rotor 103. Will be regulated. Even if the pad 106 on the outboard side is knocked back from the disk rotor 103, it is likely to come into contact with the disk rotor 103 due to this restriction. As a result, drag torque is generated when the pad 106 contacts the rotation of the disk rotor 103.

  At this time, the pad 106 is worn by contact with the disk rotor 103. If the posture of the caliper body 104 is inclined due to adhesion of foreign matter to the caliper body 104, the posture of the pad 106 on the outboard side is also inclined with respect to the disc rotor 103. In particular, in an electric brake, the caliper body 104 may be asymmetrical with respect to the radial direction of the disk rotor due to the mounting of a motor as a power source, and the caliper body 104 becomes more difficult to maintain its posture. As a result, the pad 106 on the outboard side in particular may cause uneven wear.

The following documents have been proposed as a technique for reducing drag torque.
1. Pads on the inboard side and outboard side are attached to the piston and reaction force claw respectively, and the slide pin is supported by a protrusion of elastic rubber with an H-shaped section, and the disk is released when braking is released using the repulsive force of rubber generated during braking The pad is pulled away from the rotor (Patent Document 1).
2. The back surface of the pad on the inboard side and the pad on the outboard side is spanned by a hanger pin straddling the disk rotor, and an elastic member is provided on the disk rotor side of both pads of the hanger pin. The reaction force of the elastic member at the time of braking widens the distance between both pads for releasing the brake (Patent Document 2).

3. The retainer is provided with a spring portion, and the pad ear piece is elastically biased by the first pressing piece of the spring so that the friction pad can be moved away from the disc rotor in the axial direction of the disc rotor.
In addition, unlike the first pressing piece, the retainer is provided with a second pressing piece located at an opposing position. The distance between the first pressing piece and the second pressing piece is inclined so as to be closer to the disc rotor, and the pad ear pieces are provided with tapered surfaces on the upper and lower edges on the disc rotor side (Patent Document). 3).

The retainer is provided with a first spring portion and is elastically brought into contact with the wear warning member of the pad. Further, an auxiliary spring is provided on the back surface of the pad, and is in contact with a second spring portion provided also on the caliper bracket (Patent Document 4).
A pair of spring portions provided on the retainer suppresses pad dragging, suppresses judder and brake noise, and further suppresses rattling of the pad. Further, the pad is prevented from falling off from the caliper bracket in the temporary assembly (Patent Document 5).

  When an elastic member is provided on the slide pin support part or the hanger pin as in Patent Document 1 or 2, the slide pin in contact with the elastic member needs to move relative to the pad without following the wear of the pad. Therefore, it is better that the sliding resistance between the elastic member and the slide pin is small. The repulsive force that is deformed and stored by the elastic member changes according to the amount of deformation. However, if the sliding resistance is small, the amount of deformation of the elastic member is small, so that it is difficult to generate a sufficient repulsive force.

When a spring provided on a retainer or caliper bracket as in Patent Document 3 or 4 is used, if a foreign object is caught in the spring portion, the movement of the pad may be restricted and the function may not be performed. In the case of providing a taper surface on the pad ear piece as in Patent Document 3, in addition to an increase in the processing cost of the pad, the pad is likely to drop off during caliper assembly or caliper attachment to the vehicle, which may lead to deterioration in workability. There is.
In Patent Document 5, the same problem as described in Patent Document 3 occurs.
As another method for reducing drag torque, for example, when an opposed brake caliper is used, the following problem occurs. Since a caliper body having a sufficient size to contain the stroked piston is required, the caliper size increases and the weight increases.

  The object of the present invention is to reliably release the state in which the pad on the outboard side is urged to the disc rotor when braking is released, to reduce drag torque, and to suppress uneven wear of the pad and to reduce man-hours. It is another object of the present invention to provide a disc brake device capable of reducing the weight.

In the disc brake device of the present invention, a caliper body is supported by a slide pin so as to be slidable in a direction parallel to the rotational axis of the disc rotor, with respect to a caliper bracket fixed to the vehicle body. In a floating disc brake device having a pair of pads that press against both the inboard side and the outboard side of the rotor to give a braking force,
A through hole is provided through each of the caliper bracket and the caliper body in a direction parallel to the rotation axis;
The other end of a shaft-like member comprising a shaft portion and a flange portion at one end of the shaft portion is coupled to the tip of the slide pin, and a collar is provided on the outer periphery of the slide pin. And the collar, the shaft portion of the shaft-shaped member is inserted into the through-hole of the caliper bracket, and the collar is inserted into the through-hole of the caliper body, so that the slide pin, the shaft-shaped And the member in which the collar is integrated penetrates the caliper bracket and the caliper body,
Thus before Symbol slide pin, with the shaft-like member and the collar, also configured to be relatively moved in the direction to any said caliper body of the caliper bracket,
The collar is restricted from moving in the axial direction toward the caliper bracket by having its end face hit the side of the caliper bracket,
A moving means for forcibly moving the slide pin relative to the caliper bracket at any time is provided, and a resistance member for generating a sliding resistance is provided between the slide pin and the caliper body. The sliding resistance by the member is greater than the force in the direction generated by the moving means.

  According to this configuration, during braking, the caliper body is supported by the slide pin with respect to the caliper bracket so that the pad on the outboard side is pressed against the disc rotor by the reaction force that presses the pad on the inboard side against the disc rotor. It slides relatively in a direction parallel to the rotation axis (hereinafter simply referred to as “axial direction”). Therefore, the disc brake device applies a braking force by pressing the pair of pads against both the inboard side and the outboard side of the disc rotor.

When shifting from the braking state to the braking release state, the pad on the inboard side separates from the disk rotor. At the same time, the moving means forcibly moves the slide pin relative to the caliper bracket so that the outboard pad moves away from the disk rotor. At this time, the pad on the inboard side may be biased toward the disc rotor, but by defining an appropriate position where the pad on the inboard side moves backward, the pad on the inboard side is attached to the disc rotor. Can be avoided.
Therefore, when braking is released, the state of biasing the pad on the outboard side to the disk rotor can be reliably released, the drag torque can be reduced, and uneven wear of the pad can be suppressed. In addition, there is no risk of the pad being dropped or the pad falling off when assembling the caliper. Therefore, the number of man-hours can be reduced as compared with the prior art. Further, the size can be reduced and the weight can be reduced as compared with the use of the opposed brake caliper.

A resistance member for generating a sliding resistance is provided between the slide pin and the caliper body, and the sliding resistance by the resistance member is made larger than the force in the direction generated by the moving means. In the brake release state, the moving means generates an axial force that forcibly moves the slide pin relative to the caliper bracket. At this time, since the sliding resistance by the resistance member is larger than the axial force by the moving means, the relative movement of the slide pin and the caliper body does not occur other than the relative movement by releasing the biasing force due to, for example, deformation of the resistance member. Therefore, at the time of braking, the caliper body is pulled toward the caliper bracket by the axial clearance between the slide pin and the caliper bracket.
A permanent magnet and an electromagnet may be used as the moving means.
As the moving means, fluid pressure may be used.
The resistance member may generate a force in the direction together with the moving means by elastic deformation.

A restoring force of an elastic member may be used as the moving means in the reference proposal example.
The elastic member may be a disc spring, a coil spring, or a resin member.
Since the moving means can be realized using inexpensive parts such as a disc spring, a coil spring, or a resin member, cost effectiveness can be enhanced.

As the moving means, a magnetic repulsive force or attractive force may be used.
As the moving means, fluid pressure control may be used.
An appropriate effect can be realized without causing unnecessary energy loss at the time of normal braking by using the magnetic force or the pressure of the fluid and linking the action with the operating state of the brake. The action time of magnetic force and fluid pressure is limited only when the brake is released. For this reason, the energy consumption of the system is very small compared to the case where the fluid pressure or the like is applied during braking.
Any so-called electric brake using an electric motor as a drive source for applying a braking force to the pad is still highly effective because it can be electronically controlled.

A plating film may be formed on the sliding surface of the moving means. In this case, the slide pin can be relatively moved relative to the caliper bracket and the caliper body.
The operating point of the moving means may be provided so as to be included in the caliper bracket.
One end of the action point of the moving means may be formed on the outer surface of the caliper bracket.
The sliding resistance may be realized by a member having a substantially U-shaped cross section (skirt shape) made of metal.
The resistance member that generates sliding resistance may be made of a resin member.
An electric motor may be used as a drive source for applying a braking force to the pad.

In the disc brake device of the present invention, a caliper body is supported by a slide pin so as to be slidable in a direction parallel to the rotational axis of the disc rotor, with respect to a caliper bracket fixed to the vehicle body. In the floating disc brake device having a pair of pads that press against both the inboard side and the outboard side of the rotor to give a braking force, the caliper bracket and the caliper body penetrate each of them in a direction parallel to the rotation axis A hole is provided, and the other end of a shaft-like member comprising a shaft portion and a flange portion at one end of the shaft portion is coupled to the tip of the slide pin, and a collar is provided on the outer periphery of the slide pin, and the slide The pin, shaft-shaped member, and collar are integrated into the caliper bracket through-hole. The shaft portion of the shaft-shaped member is inserted and the collar is inserted into the through-hole of the caliper body, and the slide pin, the shaft-shaped member, and the member in which the collar is integrated are the caliper. bracket and passes through the caliper body, thereby before Symbol slide pin, with the shaft-like member and said collar, said to any caliper body and the caliper bracket is configured to be relatively moved in the direction, said collar The end surface is in contact with the side surface of the caliper bracket, so that movement in the axial direction toward the caliper bracket side is restricted, and a moving means for forcibly moving the slide pin relative to the caliper bracket at any occasion is provided. A resistance member that generates a sliding resistance between the slide pin and the caliper body; Vignetting, sliding resistance due to the resistance member is greater than the force generated by the moving means. Therefore, when releasing the brake, the state of biasing the pad on the outboard side to the disc rotor is surely released, the drag torque is reduced, the uneven wear of the pad is suppressed, and the man-hours and weight are reduced. Can be achieved.

It is sectional drawing of the disc brake apparatus which concerns on a reference proposal example. It is the front view which looked at the disc brake device from the inboard side. It is the III-III sectional view taken on the line of FIG. It is a side view of the disc brake device. It is the VV line end view of FIG. It is an expanded sectional view of the important section of the initial state in the disc brake device. It is sectional drawing of the principal part at the time of braking in the disc brake device. It is sectional drawing of the principal part at the time of the brake release in the disc brake device. (A) is an expanded sectional view of the principal part at the time of braking in the disk brake device, and (B) is an enlarged sectional view of the essential part at the time of braking release in the disk brake device. It is sectional drawing of the principal part of the disc brake apparatus which concerns on the other reference proposal example. It is an AA line end view of the disk brake device. It is sectional drawing of the principal part of the disc brake apparatus which concerns on another reference proposal example. It is an AA line end view of the disk brake device. It is a BB line sectional view of the disc brake device. It is sectional drawing of the principal part of the disc brake apparatus which concerns on another reference proposal example. It is an AA line end view of the disk brake device. It is sectional drawing of the principal part of the disc brake apparatus which concerns on another reference proposal example. It is an AA line end view of the disk brake device. It is sectional drawing of the principal part of the disc brake apparatus which concerns on embodiment of this invention. It is an AA line end view of the disk brake device. It is a BB line sectional view of the disc brake device. It is sectional drawing of the principal part of the disc brake apparatus which concerns on another reference proposal example. It is an AA line end view of the disk brake device. It is sectional drawing of the principal part of the disc brake apparatus which concerns on other embodiment of this invention. It is an AA line sectional view of the disc brake device. It is a BB line end view of the disc brake device. It is sectional drawing of the principal part of the disc brake apparatus which concerns on further another embodiment of this invention. It is an AA line sectional view of the disc brake device. It is sectional drawing of the principal part of the disc brake apparatus which concerns on further another embodiment of this invention. It is an AA line end view of the disk brake device. It is sectional drawing of the disc brake apparatus of a prior art example. It is sectional drawing which cut | disconnected the disc brake device by another cut surface, and was seen.

  A disc brake device according to a reference proposal example will be described with reference to FIGS. In this example, a so-called electric brake device using an electric motor is applied to the disk brake device as a drive source for applying a braking force to the pad. However, it is not necessarily limited to the electric brake device. For example, a fluid pressure cylinder such as a hydraulic cylinder can be applied as the drive source. In this specification, the side closer to the center of the vehicle is referred to as the inboard side, and the side closer to the vehicle width direction outer side is referred to as the outboard side.

Fig. 1 shows a so-called horizontal cross-sectional view of this disc brake device (cross-sectional view taken along line I-I in Fig. 4).
FIG. 2 is a front view of the disc brake device as viewed from the inboard side. As shown in FIGS. 1 and 2, in the floating disc brake device, a caliper body 3 is supported on a caliper bracket 2 fixed to a knuckle 1 of a vehicle body so as to be slidable in an axial direction by a slide pin 4. . The caliper body 3 has a pair of pads 5 and 6, and these pads 5 and 6 are pressed against both the inboard side and the outboard side of the disc rotor 7 to give a braking force.

The caliper bracket 2 will be described.
The caliper bracket 2 has a pair of bracket-side support arms 8 and 8. These bracket-side support arms 8, 8 are arranged regardless of symmetry with respect to a plane parallel to the tangential direction of the outer edge of the rotor, and are provided apart from each other. Each bracket-side support arm 8 extends a predetermined distance in the tangential direction. 4 is a side view of the disc brake device, and FIG. 5 is an end view taken along the line VV of FIG.

  As shown in FIG. 5, rectangular grooves 8 a are formed on the surfaces of the pair of bracket-side support arms 8, 8 facing each other. Each rectangular groove 8a is recessed in the longitudinal direction from the opposing surface of each bracket-side support arm 8 and extends along the axial direction. A retainer 9 is provided in the rectangular groove 8a of the bracket-side support arm 8 to float and support a pad, which will be described later, and to facilitate sliding of the pad. In this example, the retainer 9 is provided, but the retainer 9 may be omitted and the pad may be floatingly supported (guided) in the rectangular groove 8 a of the bracket side support arm 8.

  As shown in FIG. 1, each bracket-side support arm 8 is formed with a through hole 8b penetrating in the axial direction, and a nut member 10 to be described later is inserted into each through hole 8b. The nut member 10 is screwed to the slide pin 4 and is provided integrally. Each nut member 10 and slide pin 4 are configured to be movable relative to each bracket-side support arm 8 in the axial direction in a state where each nut member 10 is inserted through the corresponding through hole 8b. A counterbore hole 8c concentric with the through-hole 8b is formed on the end surface on the outboard side of each bracket-side support arm 8. The counterbore 8c has a stepped hole shape. Each bracket-side support arm 8 is provided with a moving means described later.

The caliper body 3 and the slide pin 4 will be described.
The caliper body 3 has a pair of body-side support arms 11 and 11. These body-side support arms 11 and 11 extend away from the outer peripheral surface of the body and are disposed to face the bracket support arms. These body side support arms 11 and 11 are provided on the inboard side with respect to the bracket side support arm 8. Each body-side support arm 11 is formed with a through hole 11a penetrating in the axial direction, and the slide pin 4 is inserted into each through hole 11a. Each slide pin 4 is configured to be relatively movable in the axial direction with respect to each body-side support arm 11 in a state where each slide pin 4 is inserted through the corresponding through hole 11a.

  FIG. 6 is an enlarged view of a portion A in FIG. As shown in FIG. 6, the nut member 10 is inserted into the counterbore hole 8 c and the through hole 8 b in each bracket-side support arm 8. The nut member 10 includes a shaft portion 10a extending along the through hole 8b, and a flange portion 10b that is integrally connected to the shaft portion 10a and is inserted into the counterbore hole 8c so as to contact the shoulder 12 of the counterbore hole 8c. . The flange portion 10b is configured to be non-contact with the bottom surface of the sagittal hole 8c. A female thread 13 that opens to the inboard side and extends along the axial direction is formed on the shaft portion 10a of the nut member 10. The slide pin 4 is composed of, for example, a hexagonal bolt, and the tip end portion of the slide pin 4 is screwed to the female screw 13 of the shaft portion 10a of the nut member 10. A hole 14 that stops the nut member 10 when the screw is fastened is formed in the end face on the outboard side of the flange portion 10b.

  A cylindrical collar 15 is externally mounted on the outer peripheral surface of the slide pin 4. The collar 15 is provided integrally with the slide pin 4 and the nut member 10, and is movable relative to the body side support arm 11 and the bracket side support arm 8 in the axial direction. However, the collar 15 is interposed between the bolt head washer 4 a and the inboard side end face of the bracket side support arm 8 in the slide pin 4, and the movement in the axial direction is restricted. That is, the end surface on the outboard side of the collar 15 is configured to be able to contact and separate from the end surface on the inboard side of the bracket side support arm 8. As shown in FIG. 9A, during braking, the outboard side end surface of the collar 15 is separated via an axial clearance δ defined on the inboard side end surface of the bracket side support arm 8. As shown in FIG. 9B, the end face on the outboard side of the collar 15 abuts on the end face on the inboard side of the bracket side support arm 8 when the brake is released.

As shown in FIG. 6, an annular groove is formed on the inner peripheral surface of the through hole 11 a of the body side support arm 11. In this annular groove, for example, a resistance member 16 formed of a metal material in a substantially U-shaped cross section is provided. The resistance member 16 generates a sliding resistance between the collar 15 and the slide pin 4 and the body side support arm 11. Of the resistance member 16 provided in the annular groove of the body side support arm 11, the cylindrical portion exposed to the inner diameter side slides on the outer peripheral surface of the collar 15, thereby generating the sliding resistance. Yes. The sliding resistance by the resistance member 16 is defined to be larger than the axial force generated by the moving means described later.
Bellows-shaped boots 17 and 18 that protect the slide pin 4 and the collar 15 are provided on the outer peripheral surface of the collar 15. The boot 17 covers between the outboard side end of the outer peripheral surface of the collar 15 and the outboard side end of the body side support arm 11. The boot 18 covers between the inboard side end of the outer peripheral surface of the collar 15 and the inboard side end of the body side support arm 11.

  As described above, the flange portion 10b of the nut member 10 is configured to be able to contact the shoulder 12 of the counterbore hole 8c of the bracket-side support arm 8 and not to contact the bottom surface. Thereby, an annular space surrounded by the bottom surface, the inner circumferential surface of the sagittal hole, and the flange portion 10b is formed, and the moving means 19 made of an elastic member is provided in the annular space. In this example, a disc spring is applied as the elastic member. The moving means 19 forcibly moves the slide pin 4 relative to the caliper bracket 2 so that the pad 6 on the outboard side moves away from the disc rotor 7 when shifting from the braking state to the braking release state. It is a means to make.

  In the initial state shown in FIG. 6, that is, during non-braking, the disc spring as the moving means 19 is set in the annular space in a compressed state. In this initial state, an axial clearance δ is provided between the flange portion 10b of the nut member 10 and the shoulder 12 of the counterbore hole 8c. In this initial state, the end face on the outboard side of the collar 15 abuts on the end face on the inboard side of the bracket-side support arm 8, in other words, the collar 15 is in a state of receiving an axial force by the disc spring.

  At the time of braking shown in FIG. 7, the nut member 10 and the slide pin 4 move in one axial direction (inboard side) against the bracket-side support arm 8 against the restoring force of the disc spring. Therefore, a force to further compress the disc spring is applied from the nut member 10 until the shoulder 12 of the counterbore hole 8c and the flange portion 10b of the nut member 10 come into contact with each other. In the state where the shoulder 12 of the counterbore hole 8c and the flange portion 10b are in contact with each other, an axial clearance δ is generated between the collar 15 and the bracket side support arm 8. Since the body-side support arm 11 is restricted in relative movement with respect to the collar 15 by the resistance member 16, the restoring force of the disc spring is maintained until the flange portion 10b of the nut member 10 abuts against the shoulder 12 of the counterbore hole 8c. On the contrary, the nut member 10 is pulled in the axial direction by the slide pin 4. As a result, during braking, a larger reaction force is stored in the disc spring than during braking cancellation.

  When releasing the brake shown in FIG. 8, the tension force applied to the nut member 10 is released, so that the disc spring moves the nut member 10 to the other side (outboard side) in an attempt to restore. At this time, since the sliding resistance between the collar 15 and the resistance member 16 is defined to be larger than the axial force of the disc spring, the caliper body 3 is pulled by the nut member 10 following the collar 15. The nut member 10 moves until the collar 15 comes into contact with the bracket-side support arm 8, but at this time, the slide pin 4 is pulled toward the outboard side by the axial clearance δ.

A drive source, a linear motion mechanism, etc. are demonstrated.
As shown in FIG. 2, the caliper body 3 is provided with an electric motor 20 that applies a braking force to the pad, a speed reduction mechanism 21 that decelerates the rotation of the electric motor 20, and a linear motion mechanism 22 (FIG. 3). . The speed reduction mechanism 21 can sequentially reduce the rotation of the input gear attached to the rotor shaft of the electric motor 20 by a plurality of gear trains and transmit it to the output gear fixed to the end of the rotation shaft. As shown in FIG. 3, the linear motion mechanism 22 is a mechanism that applies a braking force to the disk rotor 7 by converting the rotary motion output from the speed reduction mechanism 21 into a linear motion to project the stroke portion 22 a. is there.

The effect will be described.
During braking, the reaction force claw 23 of the caliper body 3 presses the pad 6 on the outboard side against the disk rotor 7 by the reaction force of the stroke portion 22 a that presses the pad 5 on the inboard side against the disk rotor 7. The caliper body 3 is pulled away relative to the caliper bracket 2. The nut member 10, the slide pin 4, and the collar 15 move together with the caliper body 3 due to the sliding resistance of the resistance member 16 provided on the body side support arm 11. Accordingly, the nut member 10 is pulled toward the inboard side while the disc spring is elastically deformed by the flange portion 10b of the nut member 10.

  At this time, the nut member 10 moves relatively until the sum of the restoring force of the disc spring and the biasing force of the resistance member 16 balances the tensile force received from the caliper body 3. In particular, in this example, since the counterbore hole 8c is formed, the nut member 10 is relatively movable until the flange portion 10b of the nut member 10 contacts the shoulder 12 of the counterbore hole 8c. It should be noted that the disc spring remains elastically deformed to the extent that it does not exceed its stress limit.

  When the braking is released, the tensile force applied to the nut member 10 is released, so that the disc spring also releases its restoring force. At this time, since the sliding resistance of the resistance member 16 is larger than the restoring force of the disc spring, the body-side support arm 11 and the collar 15 are other than the relative movement due to the release of the urging force caused by the elastic deformation of the resistance member 16. Does not cause relative movement. Therefore, the caliper body 3 is pulled relatively to the caliper bracket 2 by the axial clearance δ between the collar 16 and the bracket-side support arm 8 during braking. Since the restoring force of the disc spring and the direction of the urging force of the resistance member 16 are the same, the force that pulls the caliper body 3 against the caliper bracket 2 is the sum of the restoring force and the urging force.

  Due to the above operation, the caliper bracket 2 and the disc rotor 7 do not move relative to the vehicle body in the axial direction. Therefore, when braking is released, the reaction force claw 23 of the caliper body 3 moves relatively away from the disc rotor 7. . Therefore, the reaction force claw 23 is pulled away from the pad 6 on the outboard side. At this time, the stroke portion 22a provided in the caliper body 3 approaches the disc rotor 7, and in some cases, the pad 5 on the inboard side may be urged toward the disc rotor 7. In the case of the electric brake device as in the embodiment, the urging of the pad 5 on the inboard side to the disk rotor 7 can be avoided by retracting the stroke portion 22a to an appropriate position in advance.

  Therefore, when the brake is released, the state where the pad 6 on the outboard side is urged to the disc rotor 7 can be reliably released, the drag torque can be reduced, and uneven wear of the pad 6 can be suppressed. In addition, there is no possibility that the pad 6 is additionally processed or the pads 5 and 6 are dropped when the caliper is assembled. Therefore, the number of steps can be reduced as compared with the conventional technique. Further, the size can be reduced and the weight can be reduced as compared with the use of the opposed brake caliper.

-By reducing the drag torque when the brake is released, it is possible to suppress energy loss during vehicle travel. For this reason, it is possible to improve the fuel consumption or power consumption of the vehicle and contribute to the extension of the travel distance of the vehicle.
-By reducing the drag torque when the brake is released, the wear of the pads 5, 6 and the disc rotor 7 can be suppressed. Therefore, the number of replacements and repairs of the pads 5 and 6 and the disk rotor 7 can be reduced.
-By reducing the drag torque when the brake is released, uneven wear of the pads 5 and 6 can be suppressed. For this reason, the frequency | count of replacement | exchange of the pads 5 and 6 can be reduced.
Further, since the moving means 19 can be realized by using an inexpensive part such as a disc spring, cost effectiveness can be improved.

Other reference proposal examples and embodiments will be described.
In the following description, the same reference numerals are given to the portions corresponding to the matters described in the preceding forms in each embodiment, and the overlapping description is omitted. When only a part of the configuration is described, the other parts of the configuration are the same as those described in advance unless otherwise specified. The same effect is obtained from the same configuration. Not only the combination of the parts specifically described in each embodiment, but also the embodiments can be partially combined as long as the combination does not hinder.

  In FIG. 10, a countersunk hole is not formed in the bracket-side support arm 8, and the disc spring as the moving means 19 is held using the outboard-side end face of the bracket-side support arm 8. The disc spring is designed to be below the stress limit even when it becomes completely flat during braking. FIG. 11 is an end view taken along line AA in FIG. As shown in FIGS. 10 and 11, a hexagon head 24 is provided on the outboard end face of the flange portion 10 b of the nut member 10 to stop the nut member 10 from rotating when the screw is fastened.

  As shown in FIG. 10, a boot 17A is provided on the outer peripheral surface of the collar 15, and each of the boots 17A has an accordion-shaped bellows portion 17Aa, 17Ab and a resistance portion 17Ac also serving as a resistance member, which are integrated along the axial direction. Is provided. The resistance portion 17Ac is inserted into an annular clearance between the middle portion in the longitudinal direction on the outer peripheral surface of the collar 15 and the through hole 11a of the body side support arm 11. A nut member seal 25 is provided on the flange portion 10 b of the nut member 10. The nut member seal 25 is provided so as to be elastically deformable across the outer peripheral surface of the flange portion 10b and the outboard side end surface of the bracket side support arm 8, and protects the space of the disc spring and the axial clearance δ generated when the brake is released. . A color seal 26 is provided on the inboard side end face of the bracket side support arm 8. The collar seal 26 protects the space of the axial clearance δ between the outboard side end surface of the collar 15 generated during braking and the inboard side end surface of the bracket side support arm 8.

  In this example, in addition to the slide pin 4 and the collar 15, a boot 17 </ b> A that protects them is inserted into the through hole 11 a of the body side support arm 11 to protect the entire collar. The boot 17A also serves to regulate relative movement between the collar 15 and the body side support arm 11 during braking. In this case, the number of parts can be reduced from that of the first embodiment, the structure can be simplified, and the manufacturing cost can be reduced. In addition, when the brake is released, the state where the pad on the outboard side is urged to the disc rotor can be reliably released, the drag torque can be reduced, and uneven wear of the pad can be suppressed.

  In the example of FIGS. 12 to 14, the through hole 8 b of the bracket-side support arm 8 is formed by expanding the diameter on the collar side, that is, the inboard side. The flange portion 10b of the nut member 10 is provided closer to the inboard side in the longitudinal direction. A first annular groove 27 is formed in the diameter-enlarged hole portion of the through-hole 8 b of the bracket side support arm 8, and a split ring 28 is fitted into the first annular groove 27. In this example, one end of the disc spring is brought into contact with the retaining ring 28 fitted in the first annular groove 27 instead of the surface of the bracket side support arm facing the flange portion 10b in the axial direction. A second annular groove 29 is formed in the vicinity of the inboard side end in the enlarged diameter hole portion of the bracket side support arm 8. One end of one boot 17 is fitted in the second annular groove 29. This prevents foreign matter from entering the vicinity of the disc spring or the boundary surface between the flange portion 10b of the nut member 10 and the counterbore.

  In the example of FIG. 15, a coil spring is applied as the elastic member instead of the disc spring. FIG. 16 is an end view taken along line AA in FIG. As shown in FIG. 16, in this example, as a rotation stop when the nut member 10 is screwed, the outer diameter surface of the flange portion 10b and the counterbored hole 8c of the bracket side support arm 8 through which the flange portion 10b is inserted are arcuate. A so-called D-cut process is performed in which a part thereof is cut parallel and flat to a plane including the axial direction. By this rotation prevention, a tool for holding the nut member 10 at the time of screw fastening is not required, the screw fastening of the nut member 10 can be simplified as compared with other embodiments, and the number of assembling steps can be reduced. As shown in FIG. 15, the collar seal 26 is integrally provided at one end of one boot 17. Thereby, a number of parts can be reduced rather than a separate color seal. The resistance member 16A has a ring shape having a rectangular cross section.

  In the example of FIG. 17, instead of a disc spring, a ring-shaped resin member 19A that generates a sufficient elastic force is provided as an elastic member. The body-side support arm 11 in this example has a bottomed cylindrical shape that opens to the outboard side. Most of the outer peripheral surface of the collar 15 is inserted into the cylindrical hole 11 b of the body side support arm 11. In other words, the outer peripheral surface of the collar 15 and the cylindrical hole 11b of the body side support arm 11 are in contact with each other with a sufficient length. An air hole 31 to which a rubber plug 30 is attached is formed in the bottom portion 11 c of the body side support arm 11.

  An annular rectangular groove 32 is formed in the through hole 8 b of the bracket side support arm 8, and an elastic ring 33 is provided in the rectangular groove 32. The elastic ring 33 is provided so that the inner peripheral surface of the elastic ring 33 abuts on the outer peripheral surface of the shaft portion 10 a of the nut member 10.

  At the time of braking, the nut member 10 moves in the axial direction, so that the elastic ring 33 in contact with the outer peripheral surface of the shaft portion 10a of the nut member 10 is elastically deformed. As a result, a repulsive force is stored in the elastic ring 33. When releasing the brake, the elastic force of the resin member 19A and the repulsive force of the elastic ring 33 cause the nut member 10 to move in the axial direction together with the resin member 19A. 18 is an end view taken along line AA in FIG. As shown in FIG. 18, a protrusion 34 protruding outward in the radial direction is provided on the outer peripheral surface of the flange portion 10 b of the nut member 10. In the counterbore 8c of the bracket-side support arm 8, a rectangular groove 35 that fits into the protrusion 34 is formed along the axial direction. These protrusions 34 and rectangular grooves 35 serve as a detent when the nut member 10 is screwed.

In the example of the embodiment of FIGS. 19 to 21, a permanent magnet 19B and an electromagnet 19C are provided as moving means instead of the disc spring. In this example, as shown in FIG. 19, an electromagnet 119 </ b> C having a cylindrical shape surrounding the outer peripheral surface of the shaft portion 10 a of the nut member 10 is provided on the bottom surface of the counterbore hole 8 c of the bracket-side support arm 8. An annular permanent magnet 19B is provided on the flange portion 10b facing the electromagnet 19C in the axial direction. The nut member 10 is made of, for example, stainless steel, which is a nonmagnetic material, and the bracket side support arm 8 is made of, for example, spheroidal graphite cast iron, which is also a nonmagnetic material. The coil 36 of the electromagnet 19C is electrically connected to a connector 37. The connector 37 is provided in a radial hole that communicates from the outer peripheral surface of the bracket-side support arm 8 to the through hole 8c. The connector 37 is connected to an external controller (not shown) and a power source via a cable 38.
An annular rectangular groove is formed on the peripheral surface of the sagittal hole 8c of the bracket-side support arm 8, and an elastic ring 39 having a rectangular cross section is provided in the rectangular groove to prevent foreign substances from entering from the outside. In the present embodiment, the resistance member 16 has a U-shaped cross section.

According to this configuration, the nut member 10 can be moved δ in the axial direction at any time, but only when the brake is released, the coil 36 is energized via the connector 37 from the controller to operate the moving means. By doing so, the drag torque can be reduced more effectively.
Since the resistance member 16 has a U-shaped cross section, the resistance member 16 can be easily inserted into the annular groove of the body side support arm 11.
Since the elastic ring 39 is provided in the rectangular groove of the bracket-side support arm 8, the repulsive force of the elastic ring 39 can be used when braking is released, as in the case of the elastic ring 33 in the example of FIG. The color seal 26 is integrally provided at one end of the boot 17 as in the example of FIG. However, the color seal 26 is brought into contact with the bracket side support arm 8 without providing a groove in which the color seal 26 is engaged.

  FIG. 22 shows an example in which a permanent magnet 19B is employed instead of the electromagnet 19C and the magnetic force between the permanent magnets 19B and 19B is used as the moving means. In this example, a permanent magnet 19B is provided on the bottom surface of the counterbore hole 8c, and an annular permanent magnet 19B is provided on the flange portion 10b facing the permanent magnet 19B in the axial direction. These permanent magnets 19B and 19B are attached to each other so as to attract each other, and the nut member 10 is attracted to the bottom surface side of the counterbored hole 8c until the flange portion 10b contacts the shoulder 12 of the counterbored hole 8c.

A retaining ring groove is formed at the end of the nut member 10 opposite to the flange portion 10b in the axial direction. By attaching the shaft retaining ring 40 to the retaining ring groove, the nut member 10 is prevented from falling off from the bracket side support arm 8. FIG. 23 is an end view taken along line AA in FIG. As shown in FIGS. 22 and 23, for example, an elastically deformable plastic cover 41 is attached to the end surface of the bracket side support arm 8 on the retaining ring side to prevent foreign matter from entering undesirably. ing.
Note that instead of the electromagnet of FIG. 19, a permanent magnet may be attached in a direction repelling the opposing permanent magnet to achieve the same action as in FIG. Moreover, the same effect | action as FIG. 22 may be implement | achieved by providing an electromagnet instead of one permanent magnet among the opposing permanent magnets of FIG.

  The example of embodiment of FIGS. 24-26 is another embodiment in case the permanent magnet 19B and the electromagnet 19C are used. In this example, an electromagnet 19C having a solid core parallel to the axial direction is provided on the bottom surface side of the sagittal hole in an annular space surrounded by the bottom surface and peripheral surface of the sagittal hole 8c and the flange portion 10b of the nut member 10. ing. For example, as shown in FIG. 25, the electromagnet 19 </ b> C is provided at a plurality of locations (three locations in this example) at an equal circumference when viewed from the axial direction. The coil 36 wound around each electromagnet 19C is formed of one copper wire. The flange portion 10b of the nut member 10 is provided with permanent magnets 19B at positions that are in phase with the electromagnets 19C and that are opposed in the axial direction. As shown in FIG. 26, the nut member 10 is provided with a protrusion 34 on the outer peripheral surface of the flange portion 10 b so that the nut member 10 is not always rotatable, and the nut member 10 is fitted into the protrusion 34 in the countersunk hole 8 c of the bracket side support arm 8. A rectangular groove 35 is formed.

  As shown in FIG. 24, an annular rectangular groove is formed on the peripheral surface of the sagittal hole 8 c of the bracket side support arm 8, and an O-ring 42 is provided in this rectangular groove. The O-ring 42 prevents entry of foreign matter from the outside. Although not shown, when a coil spring, a resin member, or an opposing permanent magnet is provided as the moving means, a plurality of them may be arranged on the circumference equally as in this embodiment. Further, instead of the O-ring 42, a ring-shaped member having a low X cross section or a low H cross section may be provided.

  In the example of the embodiment of FIGS. 27 and 28, fluid pressure control is used as the moving means. In this example, as shown in FIG. 27, a space surrounded by the flange portion 10 b of the nut member 10 and the bottom surface and the peripheral surface of the sagittal hole 8 c is used as the pressure chamber 43. The bracket-side support arm 8 is formed with a radial flow path 44 communicating with the pressure chamber 43. The pressure chamber 43 is filled with a specific fluid from the outside through the flow path 44, and the pressure chamber 43 is increased in pressure by an external pressure device (not shown). Thereby, the nut member 10 is moved by δ in the axial direction.

An annular groove is formed on the outer peripheral surface of the flange portion 10b, and an O-ring 45 is provided in the annular groove. An annular groove is formed on the inner peripheral surface of the bracket-side support arm 8 facing the outer peripheral surface of the shaft portion 10a, and an O-ring 46 is provided in the annular groove. These two O-rings 45 and 46 are arranged inside and outside in the axial direction so as to sandwich the pressure chamber 43 in the axial direction. These O-rings 45 and 46 prevent the fluid from undesirably leaking from the pressure chamber 43, and can control the pressure in the pressure chamber 43 with high accuracy.
According to this configuration, it is possible to move the nut member 10 in the axial direction at an arbitrary opportunity by controlling the pressure in the pressure chamber 43 with an external pressure device, but the pressure chamber 43 is only released when braking is released. By increasing the internal pressure, the drag torque can be reduced more effectively.

  29 and 30 also use fluid pressure control as the moving means. In this example, as shown in FIG. 29, the counterbore hole 8c of the bracket side support arm 8 is formed on the inboard side, and the flange portion 10b of the nut member 10 is disposed on the collar 15 side. Further, the nut member 10 can be moved in the axial direction by filling the pressure chamber 43 with a specific fluid and reducing the pressure in the pressure chamber 43 by pressure control. A retaining ring groove is formed in the vicinity of the counterbore hole entrance of the bracket side support arm 8, and a retaining ring 47 is attached to the retaining ring groove. As a result, the nut member 10 is prevented from falling off the bracket-side support arm 8, and the axial movement of the nut member 10 toward the collar 15 is restricted.

2 ... caliper bracket 3 ... caliper body 4 ... slide pins 5, 6 ... pad 7 ... disk rotor 16 ... resistance member 19 ... moving means 19B ... permanent magnet 19C ... electromagnet 20 ... electric motor

Claims (5)

With respect to the caliper bracket fixed to the vehicle body, the caliper body is supported by a slide pin so as to be slidable in a direction parallel to the rotational axis of the disc rotor, and the caliper body is inboard and outboard of the disc rotor. In a floating disc brake device having a pair of pads that press against both side surfaces to give a braking force,
A through hole is provided through each of the caliper bracket and the caliper body in a direction parallel to the rotation axis;
The other end of a shaft-like member comprising a shaft portion and a flange portion at one end of the shaft portion is coupled to the tip of the slide pin, and a collar is provided on the outer periphery of the slide pin. And the collar, the shaft portion of the shaft-shaped member is inserted into the through-hole of the caliper bracket, and the collar is inserted into the through-hole of the caliper body, so that the slide pin, the shaft-shaped And the member in which the collar is integrated penetrates the caliper bracket and the caliper body,
Thus before Symbol slide pin, with the shaft-like member and the collar, also configured to be relatively moved in the direction to any said caliper body of the caliper bracket,
The collar is restricted from moving in the axial direction toward the caliper bracket by having its end face hit the side of the caliper bracket,
A moving means for forcibly moving the slide pin relative to the caliper bracket at any time is provided, and a resistance member for generating a sliding resistance is provided between the slide pin and the caliper body. A disc brake device in which a sliding resistance by a member is larger than a force in the direction generated by the moving means.   2. The disc brake device according to claim 1, wherein a permanent magnet and an electromagnet are used as the moving means.   2. The disc brake device according to claim 1, wherein a fluid pressure is used as the moving means.   4. The disc brake device according to claim 1, wherein the resistance member generates a force in the direction together with the moving unit by elastic deformation. 5.   5. The disc brake device according to claim 1, wherein an electric motor is used as a drive source for applying a braking force to the pad.

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