JP2012193802A - Electric brake device with parking mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a structure which can improve durability and can prevent the generation of a colliding sound when applied with an impact by absorbing the impact when locking an output shaft of an electric motor.SOLUTION: A parking lock device is constituted of: a rotation-side engagement member 27 fixed to a part of a rotating shaft 35 which rotates accompanied by electricity carrying to the electric motor 8a; a deterrence-side engagement member 28 which is supported in a state that the member is inhibited in rotation with the rotating shaft 35 as a center so as to be displaceable in a direction in which the member approximates and separates from the rotation-side engagement member 27; and an elastic member 29 arranged at a part of the deterrence-side engagement member 28. The elastic member 29 and the rotation-side engagement member 27 are made to abut on each other before the deterrence-side engagement member 28 and the rotation-side engagement member 27 are engaged with each other at the operation of a parking brake.

Description

  The present invention relates to an improvement of an electric brake device with a parking mechanism that generates a braking force using an electric motor as a drive source and can maintain the braking force even after energization of the electric motor is stopped. . Specifically, in order to maintain the braking force of the parking brake, it is intended to realize a structure capable of reducing impact and noise when locking the rotation of the output shaft of the electric motor. .

  Electric disc brakes that use an electric motor as a drive source eliminate the need for piping compared to the hydraulic disc brakes that have been widely used in the past, making manufacturing easier and lowering costs. There are many advantages such as reduced brake load and less environmental load, and improved response due to the absence of brake fluid movement. As such an electric disc brake, the output of the electric motor is input to a force-increasing mechanism, and this force-increasing mechanism converts the rotary motion of this electric motor into a linear motion while increasing the force, and a pair of pads is placed on both sides of the rotor. Various types of structures that strongly press have been proposed. In addition, an electric brake device with a parking mechanism that can maintain a braking force even after the energization of the electric motor is stopped has been conventionally known, for example, as described in Patent Documents 1 to 3. Yes. Each of these inventions described in each of the patent documents presses a pair of pads, each of which is a braking friction member, against both side surfaces in the axial direction of a brake rotor that is a rotating body for braking, which rotates with a wheel. Intended for brakes.

  For this reason, any of the electric brake devices with a parking mechanism described in each of the above-mentioned patent documents converts the rotary motion of the output shaft of the electric motor into a linear motion and presses both pads against the brake rotor. And a parking lock device for maintaining the two pads pressed against the brake rotor even after the energization of the electric motor is stopped. Of these, the parking lock device is required to have a function of continuously pressing both pads against the brake rotor even after the electric power supply to the electric motor is stopped.

11 and 12 show the structure of an electric disc brake device with a parking mechanism provided with a parking lock device described in Patent Document 4. FIG.
This electric disc brake device 1 with a parking brake is to electrically exhibit both functions of a service brake and a parking brake.
The electric disc brake device 1 includes a caliper 2, a support 3 that is a support member, a piston 4, a brake rotor 5 that is a rotating rotating body that rotates together with wheels, and the brake rotor 5 that is sandwiched from both sides in the axial direction. A pair of pads 6 a and 6 b provided in a state, a ball ramp mechanism 7 that is an electric pressing device, an electric motor 8, a speed reduction mechanism 9, and a lock mechanism 12 are provided. Of these, the lock mechanism 12 includes a solenoid 13 (see FIG. 12), an engaging claw member 14, and a claw wheel 15. The claw wheel 15 includes an inner member 16 and an outer member 17 provided concentrically with each other, and an elastic member 18 provided between the peripheral surfaces of the members 16 and 17. The inner member 16 is externally fitted and fixed to the rear end portion of the motor rotor 10 of the electric motor 8.

When operating the service brake device with such an electric disc brake device 1, a predetermined current is supplied to the electric motor 8 based on the driver's brake operation, and the motor rotor 10 of the electric motor 8 is turned on. Rotate in the braking direction. The rotation of the motor rotor 10 is decelerated at a predetermined reduction ratio by the reduction mechanism 9 and the torque is increased, and then converted into a linear motion by the ball ramp mechanism 7 to move the piston 4 to the brake rotor 5 side. Displace. Then, the inner pad 6 a of the pair of brake pads 6 a and 6 b is pressed against the inner side surface of the brake rotor 5. Then, as a reaction of the pressing force, the caliper claw 11 of the caliper 2 presses the outer side pad 6 b against the outer side surface of the brake rotor 5.
When releasing the brake, the motor rotor 10 is rotated in the reverse direction to displace the piston 4 in a direction away from the brake rotor 5, thereby releasing the both brake pads 6 a and 6 b from the brake rotor 5.

  When the parking brake device of the electric disk brake device 1 is operated, the motor rotor 10 is rotated in the braking direction based on the operation of the driver's switch and the like, and the brake pads 6a and 6b are moved to the brake rotor. Press to 5 In this state, a claw portion 20 formed on the outer peripheral surface of the claw wheel 15 so that the engagement claw portion 19 of the claw wheel 15 is formed by operating the solenoid 13 constituting the lock mechanism 12. Engage. In this way, by restricting the rotation of the motor rotor 10 of the electric motor 8, the braking state is maintained in a state where energization of the electric motor 8 and the solenoid 13 is stopped.

  In the case of the parking brake device that operates in this way, when the claw portion 20 of the claw wheel 15 and the engagement claw portion 19 of the engagement claw member 14 are engaged, it is generated due to the inertia of the motor rotor 10 or the like. The impact to be absorbed can be absorbed by the elastic member 18 provided between the inner member 16 and the outer member 17 of the claw wheel 15. However, when the elastic member 18 is damaged or deteriorated, the inner member 16 and the outer member 17 may be loosely engaged with each other, and the axial force for maintaining the braking state may be reduced. Conceivable. Further, since the claw portion 20 of the claw wheel 15 and the engagement claw portion 19 of the engagement claw member 14 are directly engaged, it is conceivable that a collision sound is generated during the engagement.

  Patent Document 2 also absorbs the residual rotational energy of the electric motor by providing an elastic member between a flange portion formed on the rotating shaft of the electric motor and a claw wheel engaged with the flange portion. The structure to be described is described. However, even in this structure, the same problem as in Patent Document 1 can be considered.

  In view of the circumstances as described above, the present invention absorbs an impact when the output shaft of an electric motor is locked, thereby improving durability and preventing a collision sound at the time of impact. The present invention has been invented to realize an attached electric brake device.

The electric brake device with a parking mechanism of the present invention is similar to a conventionally known electric brake device with a parking mechanism, and includes a braking rotator, a support member, a braking friction member, and an electric pressing device. And a parking lock device.
Of these, the braking rotator rotates with the wheel, and corresponds to a brake rotor constituting a disc brake device or a drum constituting a drum brake device.
The support member is supported by a non-rotating portion in a state adjacent to the braking rotator, and supports (in the case of a floating caliper type disc brake) or a caliper (opposing piston) constituting a disc brake device. Type disc brake device) or a back plate constituting a drum brake device.
Further, the braking friction member is configured such that a part of the support member is opposed to a part of the braking rotating body (both axial side surfaces of the brake rotor, an inner peripheral surface of the drum). It is supported so that it can move with respect to the body.
The electric pressing device uses an electric motor as a drive source and moves the braking friction member in a direction approaching the braking rotating body via a speed reducer.
Further, the parking lock device keeps the braking friction member pressed against the braking rotator even after the energization of the electric motor is stopped.

In particular, in the electric brake device with a parking mechanism of the present invention, the parking lock device includes a rotation side engagement member, a suppression side engagement member, an electric actuator, and a buffer mechanism.
Of these, the rotation-side engagement member is fixed to a part of the rotation shaft that rotates when the electric motor is energized, and has a rotation-side engagement surface concentric with the rotation shaft. The rotation-side engaging member is moved in a predetermined direction based on a reaction of the braking force in a state in which the braking force is generated by pressing the braking friction member against the braking rotating body by the electric pressing device. Torque to rotate is applied.
In addition, the restraining side engaging member rotates around the rotating shaft so as to be able to be displaced in the direction of moving toward and away from the rotating side engaging surface directly or via another member with respect to the support member. It is supported in a blocked state, and has a shape that can be engaged with and disengaged from the rotation-side engagement surface.
Further, the electric actuator is for applying a force in the direction of moving toward and away from the rotating side engaging member to the deterring side engaging member based on energization, for example, a direct acting solenoid Etc. can be used.
Further, the buffer mechanism is provided on at least one of the inhibition-side engagement member and the rotation-side engagement member or a part of the member displaced in synchronization with the one engagement member. The engaging member is provided between the opposing member that moves far and away, and before the restraining side engaging member and the rotating side engaging member are engaged with each other, By acting to slow down the displacement speed, the impact during this engagement is mitigated.

When the electric brake device with a parking mechanism of the present invention as described above is implemented, for example, as in the invention described in claim 2, the rotating shaft to which the rotating side engaging member is fixed is connected to the electric motor. Output shaft.
Moreover, as a specific structure when implementing the electric brake device with a parking mechanism of the present invention as described above, for example, the structure as in the invention described in claims 3 to 6 can be adopted.

In the case of the structure according to the third aspect of the present invention, the restraining side engaging member is concentrically provided so as to be axially displaceable and non-rotatable with respect to the rotating side engaging member. .
Further, the buffer mechanism is constituted by an elastic member provided in a portion facing at least one member of at least one of the restraining side engaging member and the rotating side engaging member.
The elastic member is brought into contact with a part of the mating member before the restraining side engaging member and the rotating side engaging member are engaged.

Further, in the case of the structure of the invention described in claim 4, the restraining side engaging member can be displaced in the axial direction with respect to the rotating side engaging member and cannot rotate. Provided concentrically with the engaging member.
In addition, the shock absorbing mechanism is an air damper mechanism configured by a concave portion provided in one of the restraining side engaging member or the rotating side engaging member and a convex portion provided in the other member. And
Then, before the restraining side engaging member and the rotating side engaging member are engaged, the convex portion and the concave portion are engaged to confine air in the concave portion.

Further, in the case of the structure according to the fifth aspect of the present invention, a helical gear-like uneven portion is formed on the entire outer peripheral surface of the rotating side engaging member.
The restraining side engaging member includes an engaging convex portion that engages with a concave portion of the concave and convex portions of the rotating side engaging member, and is present in a direction perpendicular to the central axis of the rotating side engaging member. Provide on a virtual plane.
Moreover, the said buffer mechanism is comprised with the elastic member provided in at least one of the front-end | tip part of the engagement convex part of the said suppression side engagement member, and the bottom part of the recessed part of the said uneven part.
Then, before the engagement convex portion of the restraining side engaging member engages with the concave portion of the concave and convex portion of the rotation side engaging member, the elastic member is moved between the concave portion and the tip of the engaging convex portion. Hold between.

Furthermore, in the case of the structure according to the sixth aspect of the present invention, the actuator is a solenoid that linearly moves the actuator based on energization.
The solenoid includes a coil, a case, and a plunger.
Of these, the plunger is supported by the case so as to be axially displaceable and non-rotatable. Further, one end and the other end are projected to the outside of the case from a pair of through holes provided concentrically with each other at both ends of the case. The intermediate portion is disposed inside the case, and a part of the intermediate portion is a large diameter portion having an outer diameter larger than the inner diameter of the through hole.
Further, the restraining side engaging member is provided at one end of the plunger so as not to rotate and to be displaced in the axial direction together with the plunger.
An elastic member constituting the buffer mechanism is provided at the other end of the plunger.
And before the said suppression side engaging member and the said rotation side engaging member engage, this elastic member is made to contact | abut to the outer surface of the edge part of this case which is a receiving surface.

Further, when the electric brake device with a parking mechanism as described in claims 1 to 6 described above is implemented, preferably, as described in claim 7, the actuator is linearly moved to the plunger based on energization. The solenoid to be used.
The solenoid includes a coil, a case, and a plunger.
Of these, the plunger is supported by the case so as to be axially displaceable and non-rotatable. Further, one end and the other end are projected to the outside of the case from a pair of through holes provided concentrically with each other at both ends of the case. And the intermediate part is arrange | positioned inside a case and a part of this intermediate part is made into the large diameter part which has an outer diameter larger than the internal diameter of the said through-hole.
Further, the restraining side engaging member is provided at one end of the plunger so as not to rotate and to be displaced in the axial direction together with the plunger.
An elastic member is provided at the other end of the plunger.
And before the other end edge of the said large diameter part contact | abuts to the inner surface of the said case, this elastic member is made to contact | abut to the 2nd receiving surface which exists in the part facing this case.

In the case of the disc-type electric parking brake device of the present invention as described above, the inhibition-side engagement member and the rotation-side engagement member are engaged between the inhibition-side engagement member and the rotation-side engagement member. Before the operation, a buffer mechanism is provided to reduce the impact during the engagement. For this reason, the impact at the time of this engagement is relieved, durability of the said restraining side engaging member and a rotation side engaging member is aimed at, and generation | occurrence | production of an impact sound can be prevented.
Further, even when the elastic member is deteriorated, the deterioration of the elastic member does not affect the engagement between the restraining side engaging member and the rotating side engaging member with respect to the rotating direction. There is no play.

Further, if the restraining side engaging member and the rotating side engaging member are arranged concentrically as in the inventions described in claims 3 to 4 and 6, the rotating side engaging member can be downsized in the radial direction. Can be planned.
Further, as in the invention described in claim 5, if the restraining side engaging member is disposed on a virtual plane that exists in a direction perpendicular to the central axis of the rotating side engaging member, the rotating side engaging member is provided. The size can be reduced with respect to the axial direction of the member.
As described above, the structure of the invention described in claims 3 to 4 or 6 or the structure of the invention described in claim 5 is appropriately selected according to the conditions such as the design of the electric brake with a parking mechanism as a whole. By selecting, the degree of freedom of design can be improved.

  According to the seventh aspect of the present invention, when the elastic member is provided at the other end of the plunger constituting the solenoid as the actuator, the rotation-side engagement member is locked by the inhibition-side engagement member. When the plunger is displaced in the direction in which the elastic member is released, the elastic member is placed on the portion facing the case before the large diameter portion formed in the intermediate portion of the plunger contacts the inner surface of the case of the solenoid. Abutting against the existing second receiving surface, the plunger reduces the impact when contacting the inner surface of the solenoid case. For this reason, durability of these plungers and solenoids can be improved, and the generation of impact sound at the time of contact can be suppressed.

The schematic diagram which shows the 1st example of embodiment of this invention. Similarly, the lower left part shows the II cross section of FIG. 3 and the upper right part shows the same cross section, showing the specific structure. FIG. 3 is a cross-sectional view of FIG. FIG. 3 is an enlarged view of a portion X in FIG. 2, (A) shows a state when the parking lock mechanism is not operated, and (B) shows a state when the parking lock mechanism is operated. FIG. 3 is an enlarged view of a Y portion in FIG. 2, (A) shows a state before the second elastic member contacts the second receiving surface, and (B) shows a state where the second elastic member contacts the second receiving surface. (C) shows a state where the second elastic member is elastically deformed and absorbs an impact after the contact, respectively. Sectional drawing (A) shown in the state which took out the unit which combined the power increasing mechanism and the axial force sensor, and was assembled | attached to the caliper, and sectional drawing (B) shown in the state before assembling. It is sectional drawing which shows the 2nd example of embodiment of this invention, (A) has shown the state when an air damper mechanism is non-operating, (B) has shown the state at the time of an operation | movement similarly, respectively. The schematic diagram which shows the 3rd example of embodiment of this invention. Similarly, the knee sectional view of FIG. In the fourth example of the embodiment of the present invention, (A) shows a state before the elastic member contacts the receiving surface, (B) shows a state where the elastic member contacts the receiving surface, and (C) shows this state. It is sectional drawing which each shows the state which an elastic member elastically deforms after contact | abutting and absorbs an impact. Sectional drawing of a disk-type electric parking brake which shows an example of a conventional structure. FIG. 12 is a sectional view of the hoe of FIG.

[First example of embodiment]
FIGS. 1-6 has shown the 1st example of embodiment of this invention corresponding to Claims 1-3, 7. FIG. The structure of this example shows the case where the present invention is applied to a floating type disc brake.
This electric brake device with a parking mechanism includes a brake rotor 5 that is a braking rotator, a support (not shown) that is a support member, an inner pad 6a and an outer pad 6b that are brake friction members, and an electric motor. A type pressing device 21 and a parking lock device 22 are provided.
Among these, the brake rotor 5 is fixed concentrically with a wheel (not shown) and rotates together with the wheel.
The support is provided adjacent to the brake rotor 5 so as to straddle a part of the brake rotor 5 in the circumferential direction, and is supported and fixed to a non-rotating part such as a knuckle constituting a suspension device. . Since the structure and function of the support constituting such a floating type disc brake are well known in the conventional hydraulic disc brakes, illustration and detailed description thereof are omitted.

  Further, the inner and outer pads 6a and 6b are opposed to the both sides in the axial direction of the brake rotor 5 at a part of the support that sandwiches a part of the circumferential direction of the brake rotor 5 from both sides in the axial direction. In this state, the brake rotor 5 is supported so as to be able to move far and near, that is, to allow the brake rotor 5 to be displaced in the axial direction.

The electric pressing device 21 includes an electric motor 8a that is a drive source, a speed reducer 9a that is reversible in the direction of power transmission, such as a gear speed reducer, a feed screw mechanism 23, and a ball ramp mechanism 24. And a thrust generation mechanism 25 that converts rotational motion into linear motion. Such an electric pressing device 21 can be configured to be installed in the caliper 2a as shown in FIG. 1 or to be stored in a casing 26 fixed to the caliper 2a as shown in FIG. .
The caliper 2a is supported with respect to the support so that the brake rotor 5 can be displaced in the axial direction. In the case of this example, the thrust generating mechanism 25 presses the inner pad 6 a against the inner side surface of the brake rotor 5. The thrust generating mechanism 25 is also reversible with respect to the direction of force transmission. Then, as a reaction of pressing by the thrust generating mechanism 25, the caliper 2a is displaced to the inner side with respect to the support, and a caliper claw 11a provided at an outer side end portion of the caliper 2a connects the outer pad 6b to the brake rotor. Press against the outer side of 5. In this state, the brake rotor 5 is strongly clamped by the outer pad 6b and the inner pad 6a from both sides in the axial direction, and braking is performed.
In the case of this example, the thrust generating mechanism 25 is constituted by a combination of a feed screw mechanism 23 and a ball ramp mechanism 24. The structure and operation of such a thrust generating mechanism 25 are basically the same as the conventional structure described in Patent Document 6. However, when the present invention is carried out, the thrust generating mechanism 25 is not limited to a structure in which the feed screw mechanism 23 and the ball / ramp mechanism 24 are combined as shown in the figure, and a force in the rotational direction such as a cam / roller mechanism is increased. However, various mechanical force-increasing mechanisms that convert to axial force can be adopted.

  Further, the parking lock device 22 maintains the inner and outer pads 6a and 6b pressed against the both sides in the axial direction of the brake rotor 5 even after the energization of the electric motor 8a is stopped. Provided. The parking lock device 22 having such a role includes a solenoid 13a which is an electric actuator, a rotation side engagement member 27, a suppression side engagement member 28, a first elastic member 29, and a second. The elastic member 30 is provided.

Among these, the solenoid 13a includes a coil (not shown), a case 31 (see FIG. 5), and a plunger 32. The plunger 32 has an intermediate portion disposed inside the case. Further, one end portion and the other end portion are axially displaceable and non-rotatable in a state of projecting out of the case 31 from a pair of through holes 33, 33 provided concentrically at both end portions of the case. I support it. For this purpose, for example, a part of the plunger 32 and a part of the case 31 are spline-engaged or key-engaged. An intermediate portion of the plunger 32 is a large-diameter portion 34 that can be displaced in the axial direction together with the plunger 32 and has an outer diameter larger than the inner diameters of the through holes 33 and 33.
The restraining side engaging member 28 is fixed to one end of the plunger 32 of the solenoid 13a. The second elastic member 30 is attached to the other end of the plunger 32.

Further, the rotating side engaging member 27 is connected to the output portion 35 of the output shaft 35 of the electric motor 8a at the tip of the portion protruding to the side opposite to the speed reducer 9a (the left side in FIGS. 1, 2, and 4). It is fixed in a state of rotating together with the shaft 35.
Such a rotation-side engagement member 27 has a bevel gear shape, and a front end surface of the rotation-side engagement member 27 (on the surface opposite to the main body portion of the electric motor 8a on the left side in FIGS. A portion closer to the outer diameter of the surface) is a rotation side engaging portion 36 concentric with the output shaft 35. Further, on the outer peripheral surface of the rotation side engaging portion 36, a rotation side uneven portion 37 having a gear shape is formed on the entire periphery.

  Further, the restraining side engaging member 28 is formed with a restraining side engaging concave portion 38 for engaging with the rotating side engaging portion 36 of the rotating side engaging member 27 at the tip portion. Further, on the inner peripheral surface of the restraining side engaging recess 38, a restraining side uneven portion 39 that can be engaged with the rotating side uneven portion 37 formed on the outer peripheral surface of the rotating side engaging member 28 is formed. . The material of such a restraining side engaging member 28 is not particularly limited as long as sufficient strength and rigidity can be ensured, such as metal and synthetic resin. Such a restraining side engaging member 28 is in a state of being prevented from rotating, and is moved in the direction of moving relative to the rotating side engaging member 27 by the solenoid 13a, that is, the output shaft 35 of the electric motor 8a. Axial displacement is supported.

  The first elastic member 29 has a locking recess 40 formed at the center of the bottom surface of the restraining side engaging recess 38 of the restraining side engaging member 28, and a distal end portion from the bottom surface to the rotation side engaging member. It is mounted in a state protruding in the direction of the combined member 27. Such a first elastic member 29 can be a spring or an elastomer such as rubber.

  Further, the second elastic member 30 is integrally formed of an elastomer such as rubber and has an H shape including a pair of side plates 41 and 41 and a connecting plate 42. Among these, the pair of side plates 41, 41 are arranged in parallel with the central axis of the plunger 32 with the other end of the plunger 32 being sandwiched therebetween. The connecting plate 42 is provided on a virtual plane that exists in a direction orthogonal to the central axis of the plunger 32 and connects the side plates 41 and 41 to each other. Further, a through hole (not shown) for fixing the connecting plate to the outer peripheral surface of the other end of the plunger 32 is formed in the central portion of the connecting plate 42. The connecting plate 42 is fixed to the plunger 32 by, for example, forming a locking groove over the entire outer peripheral surface of the other end of the plunger 32 and fixing the inner peripheral surface of the through hole to the locking surface. Fix externally in the groove. In addition, it can also be fixed by bonding or the like.

Further, the second elastic member 30 has the other end edge of the second elastic member 30 (the other end edge of the pair of side plates 41 and 41) and the second receiving surface 43 of the claims. The distance L ₄₃ (see FIG. 5) between the caliper 2a facing the other end edge or the inner surface of the casing 26 (see FIG. 2) or the like is set to the other end surface (see FIG. 5) of the large-diameter portion 34. a left end surface) of, among the inner surface of the casing 31, are arranged smaller (L ₄₃ <the L ₃₁₎ made as than the distance L ₃₁ between the second end surface opposite to the surface of the large-diameter portion 34 .
The solenoid 13a employs a 2-way solenoid or the like that can change the operating direction based on a signal from a control device or the like.

  In the case of the disc brake device with a parking mechanism of this example, as described above, as shown in FIG. 1, the electric motor 8a, the speed reducer 9a, and the parking lock device 22 are housed in the caliper 2a. Alternatively, as shown in FIG. 2, the electric motor 8a, the speed reducer 9a, and the parking lock device 22 can be housed in a casing 26 fixed in the caliper 2a. A specific structure, operation, and effect of a disc brake device with a parking mechanism to which the present invention is applied will be described below with reference to FIG.

  In the case of the disc brake device with a parking mechanism shown in FIG. 2, a reduction gear 44 is fixedly fitted on the tip of the output shaft 35 (the right end in FIG. 2) of the electric motor 8a and concentrically fitted with the output shaft 35. (Spline engagement). Further, the speed reducer 9a is shown in FIG. 3 between the speed reduction small gear 44 and the speed reduction large gear 46 fitted and fixed to the base end portion of the drive spindle 45 provided at the center of the thrust generating mechanism 25. By arranging a plurality of gears as shown, the rotation of the output shaft 35 is increased (torque is increased) and transmitted to the drive spindle 45, and the drive spindle 45 is driven to rotate with a large torque. I have to.

  In order to constitute the thrust generating mechanism 25, a flange 47 having an outward flange shape is formed at an axially intermediate portion of the drive spindle 45, and an inner side surface of the flange 47 is supported by a thrust rolling bearing 48. With this configuration, the drive spindle 45 can be rotationally driven while supporting a thrust load directed toward the inner side. In the case of this example, the flange 47 and the thrust rolling bearing 48 are connected to an axial force sensor 49 and an elastic member 50 that is elastically deformable in the axial direction, such as a wave plate spring, a compression coil spring, and rubber. At the same time, it is housed in the case unit 51. The case unit 51 is formed by combining an inner side case 52 and an outer side case 53. The case unit 51 is formed by combining the inner and outer cases 52 and 53 in a non-separable manner so that they can be slightly displaced in the axial direction.

  Among these, the inner side case 52 is provided with a cylindrical fixed side peripheral wall portion 56 from the outer peripheral edge of the annular bottom plate portion 55 having a circular through hole 54 in the center portion toward the outer side. An extraction hole 58 for exposing the end of the connector 57 for extracting the measurement signal of the axial force sensor 49 is formed at one position in the circumferential direction of the base side portion (inner portion) of the fixed side peripheral wall portion 56. is doing. In addition, a long locking hole 59 in the axial direction at a plurality of circumferential positions (for example, two to three positions at equal intervals in the circumferential direction) of the first half-side portion (outer-side portion) of the fixed-side peripheral wall portion 56; 59 is formed. The structure for exposing the end portion of the connector 57 may be a notch that opens at the front end edge (outer side end edge) of the fixed-side peripheral wall portion 56 instead of the take-out hole 58. In this case, however, the phase in the circumferential direction between this notch and each of the locking holes 59, 59 is shifted (a notch is provided between the locking holes 59, 59 adjacent in the circumferential direction). ).

  On the other hand, the outer side case 53 is provided with a cylindrical displacement side peripheral wall portion 62 from the outer peripheral edge of the annular bottom plate portion 61 having a circular through hole 60 in the center portion toward the inner side. Then, the engagement pieces 63, 63 formed at the circumferential positions of the distal end edge (inner side end edge) of the displacement side peripheral wall portion 62 are moved to the respective locking holes 59, 59 in the axial direction. The case unit 51 is configured to be engaged with each other. The axial dimension of the case unit 51 can be expanded and contracted within a range in which the engagement pieces 63 and 63 can be displaced in the engagement holes 59 and 59. Further, the case unit 51 is arranged radially outward from the outer peripheral surface of the displacement side peripheral wall 62 at a plurality of locations in the circumferential direction of the displacement side peripheral wall 62 (for example, two to three positions at equal intervals in the circumferential direction). The locking pieces 64 and 64 are formed to protrude in a state of protruding in the direction.

  In such a case unit 51, a flange portion 47 provided at an intermediate portion of the drive spindle 45, the axial force sensor 49, the thrust rolling bearing 48, and the elastic member 50 are incorporated, and FIG. The axial force measuring unit 65 is as shown. Then, as shown in FIG. 2, the axial force measuring unit 65 is assembled to the inner end of the cylinder space 66 provided in the inner side portion of the caliper 2a. A concave groove 67 that opens to the inner diameter side and the outer side of the cylinder space 66 is formed in a portion of the rear end portion of the cylinder space 66 that is aligned with the end portion of the connector 57. To prevent interference with the parts. In addition, a locking recess 68 is formed in the cylinder space 66 near the back end of the middle portion, except for the recess 67 portion, over substantially the entire circumference.

  The axial force measuring unit 65 pushes the elastic member 50 in the axial direction and the locking pieces 64 and 64 radially inward while being elastically compressed into the inner end of the cylinder space 66. Then, in the state after the completion of pushing, the leading edge of each of the locking pieces 64, 64 is abutted against the inner side surface of the locking recess 68 by the elasticity of the elastic member 50. In this state, the outer side case 53 is not displaced in the direction (outer side) of coming out of the cylinder space 66, and the axial force sensor 49 is provided with a sufficient preload to ensure measurement accuracy. It becomes. Therefore, the plug 71 provided at the end of the harness 70 is inserted into the cylinder space 66 through the connection hole 69 formed in the caliper 2a, the plug 71 and the connector 57 are connected, and the axial force sensor 49 is connected. The measurement signal can be extracted.

  In this way, the thrust generation is performed by combining the feed screw mechanism 23 and the ball ramp mechanism 24 between the axial force measuring unit 65 and the inner pad 6a assembled at the inner end of the cylinder space 66. A mechanism 25 is provided. Of these, the feed screw mechanism 23 is screwed into a male screw portion 72 provided in the outer half portion (left half portion in FIG. 2) of the drive spindle 45 with a screw hole 74 provided in the center portion of the drive side rotor 73. It is composed by letting. The ball ramp mechanism 24 includes the driving side rotor 73, the driven side rotor 75, and a plurality of balls 76. Drive-side lamps having a plurality of locations (for example, 3 to 4 locations) in the circumferential direction of the mutually opposing surfaces of the rotors 73 and 75, each having a circular shape when viewed in the axial direction. Portions 77 and 77 and driven side lamp portions 78 and 78 are provided.

  The depth of each of the lamp portions 77 and 78 in the axial direction is gradually changed with respect to the circumferential direction, but the direction of the change is the drive side lamp portions 77 and 77 and the driven side lamp portions 78 and 78. 78 are opposite to each other. Accordingly, when the rotors 73 and 75 are rotated relative to each other and the balls 76 and 76 roll along the ramp portions 77 and 77, the distance between the rotors 73 and 75 is expanded and contracted with a large force. The A spacer 79 that is spherically engaged with the driven-side rotor 75 is sandwiched between the driven-side rotor 75 and the inner pad 6a. Further, a part of the engaging protrusion 80 projecting from the outer peripheral edge of the driven-side rotor 75 and a part of the concave groove 67 are engaged via a sleeve 92, and the driven-side rotor 75 is driven. An axial displacement is supported around the tip of the spindle 45 while preventing rotation.

  At the time of braking by the electric brake device with a parking mechanism of this example configured as described above, the output shaft 35 is rotated by energizing the electric motor 8a, and the thrust generating mechanism 25 is transmitted via the speed reducer 9a. The drive spindle 45 is rotated. At the initial stage of this rotational drive, the drive-side rotor 73 does not rotate due to the resistance of the biasing spring 81 or the like, and the front end side of the drive spindle 45 is based on the threaded engagement between the male screw portion 72 and the screw hole 74. In parallel (moves toward the brake rotor 5 without rotating). By this parallel movement, a gap between the both side surfaces in the axial direction of the brake rotor 5 and the inner pad 6a and the outer pad 6b is closed. During such parallel movement, the balls 76 and 76 are located at the end of the ramp portions 77 and 78 on the deepest side.

As a result of the parallel movement, gaps between the respective parts are lost, and when the resistance of the drive side rotor 73 to move further toward the brake rotor 5 increases, the drive side rotor 73 rotates together with the drive spindle 45. Then, the drive side rotor 73 and the driven side rotor 78 rotate relative to each other. Then, the balls 76 and 76 move to the shallower side of the ramp portions 77 and 78 while rolling, and the distance between the rotors 73 and 78 increases. Since the ramp angles of the ramp portions 77 and 78 are loose, the force for expanding the distance between the rotors 73 and 78 is increased, and the inner and outer pads 6a and 6b are placed on both side surfaces of the brake rotor 5 on the both sides. The spacer 79 and the caliper claw 11a can be pressed with a large force to perform braking.
The magnitude of the braking force is adjusted by regulating the amount of current supplied to the electric motor 8a and adjusting the torque input from the output shaft 35 to the thrust generating mechanism 25 via the speed reducer 9a. When such a service brake is operated, the tip side of the restraining side engaging member 28 is retracted from the rotating side engaging member 27 as shown in FIG. Therefore, the restraining side engaging member 28 does not affect the operation of the electric pressing device 21 including the electric motor 8a.
Further, in order to perform braking in this way, adjustment of the magnitude of the force for pressing the inner and outer pads 6a, 6b against both side surfaces of the brake rotor 5 is a feed that adjusts the amount of current supplied to the electric motor 8a. In addition to forward control, feedback control based on the measurement signal of the axial force sensor 49 can also be used.

  Further, when the parking mechanism for maintaining the vehicle in a stopped state is operated, the electric pressing device 21 presses the inner and outer pads 6a and 6b against both side surfaces of the brake rotor 5 to generate a braking force. In this state, the solenoid 13a is energized. Based on this energization, the restraining side engaging member 28 is displaced in a direction approaching the rotating side engaging member 27. Then, as shown in FIG. 4B, the inhibition-side uneven portion 39 of the inhibition-side engagement recess 38 of the inhibition-side engagement member 28 and the rotation-side engagement portion 36 of the rotation-side engagement member 27. The rotation-side uneven portion 37 is engaged with the rotation-side engagement member 27 in the rotation direction.

In the case of this example, the tip of the locking recess 40 formed in the center of the bottom surface of the suppression side engagement recess 38 of the suppression side engagement member 28 protrudes from the bottom surface toward the rotation side engagement member 27. In this state, the first elastic member 29 is attached. For this reason, before the inhibition side uneven part 39 and the rotation side uneven part 37 are engaged, the front end surface of the first elastic member 29 and the rotation side engagement part of the inhibition side engagement member 28 are engaged. The front end surface of 36 abuts. Further, when the restraining side engaging member 28 is displaced in the direction, the first elastic member 29 is elastically deformed as shown in FIG. 4B to absorb the impact during the engagement. Then, while preventing the occurrence of a collision sound, the concave and convex portions 39 and 37 are engaged with each other. For this purpose, the elasticity of the first elastic member 29 is made smaller than the thrust of the solenoid 13a.
When the first elastic member 29 is deteriorated, the effect of suppressing the collision noise is deteriorated. Even in this case, the deterioration of the first elastic member 29 is caused by the inhibition side engaging member 28 and the rotation. There is no influence on the engagement of the side engaging member 27 in the rotational direction. For this reason, backlash does not occur in this rotational direction, and the original performance of the parking mechanism does not deteriorate.

  When the parking mechanism is operated, energization to the electric motor 8a constituting the electric pressing device 21 is stopped while the solenoid 13a is energized. Based on the rotation of the output shaft 35 of the electric motor 8a, the thrust generating mechanism 25 and the inner and outer pads 6a and 6b are pressed against the both side surfaces of the brake rotor 5 to generate a braking force. As described above, the speed reducer 9a has reversibility with respect to force transmission. Therefore, when the energization to the electric motor 8a is stopped, the rotation side engaging member is based on the reaction of the braking force. 27 tends to rotate in a predetermined direction. As described above, when the restraining side uneven portion 39 and the rotating side uneven portion 37 are engaged, the rotating side engaging member 27 reduces the braking force. There is no rotation in the direction to make it. Then, the energization to the solenoid 13a is stopped in a state where the inhibition side uneven portion 39 and the rotation side uneven portion 37 are engaged. In a state where the energization to the solenoid 13a is stopped, the restraining side engagement member 28 stops at the position as it is (the state shown in FIG. 4B) without being displaced in the axial direction. Accordingly, the concave and convex portions 39 and 37 on the inhibition side and the rotation side remain engaged.

In this way, in a state where the restraining side uneven part 39 and the rotation side uneven part 37 are engaged, the inner and outer pads 6a and 6b are connected to the brake rotor 5 without energizing any part. Since it can be kept pressed against both sides in the axial direction, the braking force can be ensured without consuming battery power.
In order to release the operation of the parking brake, the solenoid 13a is energized to move the restraining side engaging member 28 away from the rotating side engaging member 27 as shown in FIG. Displace to. Then, the engagement between the restraining side and the rotation side uneven portions 39 and 37 is released, and the rotation side engaging member 27 can be rotated, so that both the pads 6a and 6b are disposed on both side surfaces of the brake rotor 5 in the axial direction. The pressing force is lost.

In the case of this example, an H-shaped second elastic member 30 is provided at the other end of the plunger 32 of the solenoid 13a. The second elastic member 30 is opposed to the other end edge of the second elastic member 30 (the other end edge of the pair of side plates 41, 41 constituting the second elastic member 30) and the other end edge. The distance L ₄₃ (see FIG. 5) from the second receiving surface 43 that is the inner surface of the casing 26 is set to the other end surface (the left end surface in FIG. 5) of the large-diameter portion 34 of the plunger 32 and the inner surface of the case. Of these, the arrangement is restricted so that the distance L ₃₁ is smaller than the distance L ₃₁ between the other end surface of the large-diameter portion 34 and the surface facing the other end surface (L ₄₃ <L ₃₁ ). For this reason, the plunger 32 is displaced in the direction in accordance with the displacement of the restraining side engaging member 28, and before the other end surface of the large diameter portion 34 comes into contact with the inner surface of the case 31, FIG. 2, the other end edges of the pair of side plates 41, 41 constituting the second elastic member 30 abut against the second receiving surface 43. When the plunger 32 is further displaced in this direction from this state, the connecting plate 42 constituting the second elastic member 30 is elastically deformed as shown in FIG. In this way, the impact at the time of collision between the large-diameter portion 34 of the plunger 32 and the inner surface of the case 31 is absorbed, and the occurrence of collision noise when the parking mechanism is released is suppressed.

[Second Example of Embodiment]
FIG. 7 shows a second example of an embodiment of the present invention corresponding to claims 1, 2, and 4.
In the case of this example, the restraining side engaging member 28a is provided concentrically with the rotating side engaging member 27a in a state where it can be displaced in the axial direction with respect to the rotating side engaging member 27a and cannot rotate. Moreover, the latching recessed part 40a is formed in the bottom face of the inhibition side engaging recessed part 38a of the inhibition side engaging member 28a.
Further, a locking convex portion 82 is formed at the center of the distal end surface of the rotation side engagement portion 36a of the rotation side engagement member 27a. The outer diameter D ₈₂ of the locking projections 82, the same as the inner diameter D _40a of the locking recess 40a, are slightly smaller (D ₈₂ ≦ D _40a) than the inner diameter D _40a. And the air damper mechanism 83 which confine | air-closes air in this latching recessed part 40a is comprised by fitting with the latching recessed part 40a and the latching convex part 82. As shown in FIG.

  When the parking mechanism for maintaining the vehicle in a stopped state is operated, the inner and outer pads 6a and 6b are pressed against both side surfaces of the brake rotor 5 by the electric pressing device 21 (see FIG. 2) to generate a braking force. In this state, the solenoid 13a (see FIG. 2) is energized. Based on this energization, the restraining side engaging member 28a is displaced in a direction approaching the rotating side engaging member 27a. Then, the inhibition-side uneven portion 39a of the inhibition-side engagement recess 38a of the inhibition-side engagement member 28a and the rotation-side uneven portion 37a of the rotation-side engagement portion 36a of the rotation-side engagement member 27a are connected to this rotation side. The engagement member 27a is engaged in the rotation direction.

In the case of this example, a locking recess 40a formed at the center of the bottom surface of the restraining side engaging recess 38a of the restraining side engaging member 28a, and a distal end surface of the rotating side engaging portion 36a of the rotating side engaging member 27a An air damper mechanism 83 is constituted by the locking projection 82 provided at the center of the air damper. In the air damper mechanism 83, the inhibition side uneven portion 39a of the inhibition side engagement recess 38a of the inhibition side engagement member 28a and the rotation side uneven portion 37a of the rotation side engagement portion 36a of the rotation side engagement member 27a are provided. Before the engagement, as shown in FIG. 7B, the tip of the locking projection 82 is inserted into the locking recess 40a. Then, air is trapped in the locking recess 40a. Further, when the restraining side engaging member 28a is displaced in the above direction, air is little by little in the locking recess 40a, and between the inner peripheral surface of the locking recess 40a and the outer peripheral surface of the locking projection 82. Leak through the gap. For this reason, the engagement between the concave and convex portions 39a and 37a on the restraining side and the rotation side is performed slowly, and the impact at the time of the engagement can be absorbed and the generation of the collision sound can be prevented.
Except for the differences in the shape and structure of both the rotation-side and restraining-side engagement members 27a, 28a, the present embodiment is the same as the first example of the above-described embodiment, and therefore illustrations and explanations regarding equivalent parts are omitted.

[Third example of embodiment]
8 and 9 show a third example of an embodiment of the present invention corresponding to claims 1, 2, 5 and 7. FIG. In the case of this example, a gear-shaped uneven portion 84 is formed on the outer peripheral surface of the rotation-side engaging member 27b over the entire periphery.
Further, the restraining side engaging member 28b is provided on a virtual plane that exists in a direction perpendicular to the central axis of the rotating side engaging member 27b so that the rotating side engaging member 27b can be displaced in the radial direction. . Further, the restraining side engaging member 28b engages with the recesses 85, 85 of the concavo-convex part 84 of the rotating side engaging member 27b at the tip part (can enter into any of the concave parts 85). A convex portion 86 is provided. Further, an elastic member 87 is provided at the tip of the engaging convex portion 86. The elastic member 87 can also be provided at the bottom of each of the recesses 85 and 85 constituting the uneven portion 84.

  When the parking brake for maintaining the vehicle in a stopped state is operated, the inner and outer pads 6a and 6b are pressed against both side surfaces of the brake rotor 5 (see FIG. 2) by the electric pressing device 21 to generate a braking force. In this state, the solenoid 13a is energized. Based on this energization, the restraining side engaging member 28b is displaced in a direction approaching the rotating side engaging member 27b (downward direction in FIGS. 8 and 9). And the engagement convex part 86 of the said suppression side engaging member 28b and the any recessed part 85 which comprises the uneven | corrugated | grooved part 84 of the said rotation side engaging member 27b engage.

In the case of this example, an elastic member 87 is provided at the tip of the engaging convex portion 86 of the restraining side engaging member 28b. For this reason, before the engagement convex part 86 of the said restraining side engaging member 28b and the recessed part 85 of the uneven | corrugated | grooved part 84 of the said rotation side engaging member 27b engage, the front end surface of the said elastic member 87 And the bottom of the recess 85 abut. Furthermore, the elastic member 87 is elastically deformed in the process in which the restraining side engaging member 28b enters the concave portion 85, so that the impact at the time of the engagement can be absorbed and the generation of the collision sound can be prevented.
If the restraining side engaging member 28b is disposed on a virtual plane that exists in a direction orthogonal to the central axis of the rotating side engaging member 27b as in this example, the axis of the rotating side engaging member Space in the direction can be reduced.
Except for the differences in the shape, structure, and arrangement of both the rotation side and restraining side engaging members 27b, 28a, they are the same as in the first and second examples of the above-described embodiment, and therefore, illustrations and descriptions regarding equivalent parts are omitted. .

[Fourth Example of Embodiment]
FIG. 10 shows a fourth example of the embodiment of the invention corresponding to claims 1, 2, 6, and 7. In this example, an elastic member 88 is attached to the other end of the plunger 32 constituting the solenoid 13a. The elastic member 88 has the same structure as that of the second elastic member 30 shown in FIG. 5. The functions of the first elastic member 29 and the second elastic member 30 shown in FIG. The arrangement of the elastic member 88 is devised so as to have both.
Such an elastic member 88 is a receiving end which is one end edge of the elastic member 88 (one end edge of the pair of side plates 90 and 90 constituting the elastic member 88) and the outer surface of the case 31 of the solenoid 13a facing the one end edge. the distance L ₈₉ between the surface 89, smaller than the stroke L ₂₇ up to the restraining side engaging recess 38c of the restraining side engaging member 28c and the rotating side engaging member 27c Kiru engaged (L ₈₉ <L ₂₇₎ is doing.

  When the parking brake for maintaining the vehicle in a stopped state is operated, the electric pressing device 21 presses the inner and outer pads 6a and 6b against both side surfaces of the brake rotor 5 (see FIG. 2) to generate a braking force. In this state, the solenoid 13a is energized. Based on this energization, the restraining side engaging member 28c is displaced in a direction approaching the rotating side engaging member 27c (right direction in FIG. 10). Then, the inhibition-side uneven portion 39c of the inhibition-side engagement recess 38c of the inhibition-side engagement member 28c and the rotation-side uneven portion 37c of the rotation-side engagement portion 36c of the rotation-side engagement member 27c are connected to this rotation side. The engagement member 27c is engaged in the rotation direction.

In the case of this example, a distance L ₈₉ between one end edge of the pair of side plates 90, 90 constituting the elastic member 88 and the receiving surface 89 which is the outer surface of the case 31 of the solenoid 13 a facing the one end edge is set as a deterrent side The stroke is smaller than the stroke L ₂₇ (L ₈₉ <L ₂₇ ) until the restraining side engaging recess 38 c of the engaging member 28 c and the rotating side engaging member 27 c are completely engaged. For this reason, before the restraining side uneven part 39c of the restraining side engaging recessed part 38c of the restraining side engaging member 28c contacts with the rotating side uneven part 37c of the rotating side engaging member 27c rotating side engaging part 36c. As shown in FIG. 10B, one end edge of the side plate of the elastic member 88 (one end edge of the pair of side plates 90, 90) contacts the receiving surface 89. Further, the connecting plate constituting the elastic member 88 in a process in which the restraining side engaging member 28c and the plunger 32 are displaced until the restraining side and rotating side uneven portions 39c and 37c are completely engaged. 91 is elastically deformed as shown in FIG. As a result, the concave and convex portions 39c and 37c are slowly engaged with each other to absorb the impact when the concave and convex portions 39c and 37c are engaged with each other, thereby preventing the occurrence of collision noise.

In the case of this example, similarly to the structure shown in FIG. 5, the other end edge of the elastic member 88 (the other end edge of the pair of side plates 90, 90) and the second receiver of the claims. The distance L ₄₃ between the caliper 2a facing the other end edge or the inner surface of the casing 26 or the like is the surface ₄₃ , and the other end surface (the left end surface in FIG. 10) of the large-diameter portion 34 of the plunger 32. , of the inner surface of the case 31 of the solenoid 13a, and regulates as smaller (L ₄₃ <L ₃₁₎ than the distance L ₃₁ between the other end surface opposite to the surface of the large diameter portion 34. For this reason, the impact at the time of a collision with the large diameter part 34 of the said plunger 32 and the inner surface of the said case 31 is absorbed, and generation | occurrence | production of a collision sound can also be prevented.

  The structure of each of the above embodiments is a structure in which the present invention is applied to a disk-type electric parking mechanism, but can also be applied to a drum-type electric parking mechanism. That is, the present invention can be applied to various structures that generate a braking force using an electric motor as a drive source and lock the rotation of the output shaft of the electric motor in order to maintain the braking force.

DESCRIPTION OF SYMBOLS 1 Electric disc brake 2, 2a Caliper 3 Support 4 Piston 5 Brake rotor 6a, 6b Pad 7 Ball ramp mechanism 8, 8a Electric motor 9, 9a Deceleration mechanism 10 Motor rotor 11, 11a Caliper claw 12 Lock mechanism 13, 13a Solenoid 14 Engagement Claw material
15 Claw wheel 16 Inner member 17 Outer member 18 Elastic member 19 Engaging claw portion 20 Claw portion 21 Electric pressing device 22 Locking device for parking 23 Feed screw mechanism 24 Ball ramp mechanism 25 Thrust generating mechanism 26 Casings 27, 27a, 27b, 27c Rotating side engaging members 28, 28a, 28b, 28c Deterring side engaging member 29 First elastic member 30 Second elastic member 31 Case 32 Plunger 33 Through hole 34 Large diameter portion 35 Output shafts 36, 36a, 36b, 36c Rotating side engaging portions 37, 37a, 37b, 37c Rotating side uneven portions 38, 38a, 38b, 38c Deterring side engaging concave portions 39, 39a, 39b, 39c Depressing side uneven portions 40, 40a Locking concave portion 41 Side plate 42 Connection Plate 43 Second receiving surface 44 Reduction small gear 45 Drive spindle 46 Reduction large gear 47 Hook 48 Thrust rolling bearing 49 Axle Sensor 50 Elastic member 51 Case unit 52 Inner side case 53 Outer side case 54 Through hole 55 Bottom plate part 56 Fixed side peripheral wall part 57 Connector 58 Extraction hole 59 Locking hole 60 Through hole 61 Bottom plate part 62 Displacement side peripheral wall part 63 Engagement piece 64 Locking piece 65 Axial force measuring unit 66 Cylinder space 67 Groove groove 68 Locking recess 69 Connection hole 70 Harness 71 Plug 72 Male thread part 73 Drive side rotor 74 Screw hole 75 Driven side rotor 76 Ball 77 Drive side lamp part 78 Covered Driving side lamp portion 79 Spacer 80 Engaging protrusion 81 Energizing spring 82 Engaging spring 83 Locking protrusion 83 Air damper mechanism 84 Concavity and convexity 85 Concavity 86 Engaging protrusion 87

JP 2003-307240 A JP 2008-275053 A JP 2001-524647 A JP 2007-321862 A JP 2003-104179 A JP 2004-169729 A

Claims (7)

A braking rotator that rotates together with the wheels, a support member that is supported by a non-rotating portion in a state adjacent to the braking rotator, and a part of the support member that faces a part of the braking rotator. In this state, the braking friction member supported so as to be able to move to and from the braking rotator and an electric motor as a drive source, and the braking friction member is brought closer to the braking rotator via a reduction gear. Equipped with a parking mechanism comprising: an electric pressing device to be moved; and a parking lock device for maintaining the braking friction member pressed against the braking rotator even after energization of the electric motor is stopped In the electric brake device,
The parking lock device includes a rotation-side engagement member having a rotation-side engagement surface concentric with the rotation shaft, which is fixed to a part of a rotation shaft that rotates in response to energization of the electric motor, and the support member. The rotation-side engagement is supported in a state in which rotation about the rotation axis is prevented so that displacement in the direction of moving toward and away from the rotation-side engagement surface can be performed directly or via another member. A restraining side engaging member that can be engaged with and disengaged from the mating surface, and an electric actuator that applies a force in a direction approaching the rotating side engaging member to the restraining side engaging member based on energization. It is equipped with
At least one of the restraining side engaging member and the rotating side engaging member, or a member that displaces the member in synchronism with the one engaging member. By acting to slow the relative displacement speed between the member and the mating member before the restraining side engaging member and the rotating side engaging member are engaged, An electric brake device with a parking mechanism, characterized in that a shock-absorbing mechanism for reducing the impact force during the engagement is provided.   The electric brake device with a parking mechanism according to claim 1, wherein a rotation shaft to which the rotation-side engagement member is fixed is an output shaft of the electric motor.   The restraining side engaging member is concentrically provided so as to be axially displaceable and non-rotatable with respect to the rotating side engaging member, and the buffer mechanism includes the restraining side engaging member and the A part of at least one of the rotation-side engaging members, which is constituted by an elastic member provided at a portion facing the counterpart member, the restraining-side engagement member and the rotation-side engagement member The electric brake device with a parking mechanism according to any one of claims 1 and 2, wherein the elastic member comes into contact with a part of the counterpart member before engaging with each other.   The restraining side engaging member is provided concentrically with the rotating side engaging member in a state in which the inhibiting side engaging member is axially displaceable and non-rotatable with respect to the rotating side engaging member. An air damper mechanism comprising a concave portion provided in one of the restraining side engaging member or the rotating side engaging member and a convex portion provided in the other member, the restraining side engaging member 3. The method according to claim 1, wherein the convex portion and the concave portion are engaged to confine air in the concave portion before the combined member and the rotating side engaging member are engaged with each other. Electric brake device with parking mechanism.   The rotation-side engagement member is formed with a gear-shaped uneven portion on the entire circumference of the outer peripheral surface, and the suppression-side engagement member is engaged with a recess in the uneven portion of the rotation-side engagement member. An engaging convex portion that is provided on a virtual plane that exists in a direction perpendicular to the central axis of the rotating side engaging member, and the buffer mechanism is provided on the engaging convex portion of the inhibiting side engaging member. It is composed of an elastic member provided on at least one of the tip and the bottom of the concave portion of the concave and convex portion, and the engaging convex portion of the restraining side engaging member and the concave and convex portion of the rotating side engaging member. The parking mechanism attached according to any one of claims 1 to 2, wherein the elastic member is sandwiched between the concave portion and the tip of the engaging convex portion before the concave portion is engaged. Electric brake device. The actuator is a solenoid that causes the plunger to linearly move when energized. The solenoid includes a coil, a case, and a plunger, and the plunger is axially displaceable and non-rotatable in the case. One end portion and the other end portion projecting from a pair of through holes provided concentrically to both end portions of the case to the outside of the case, and a part of the intermediate portion is an inner diameter of the through hole. It has a large diameter part with a larger outer diameter,
The restraining side engaging member is provided at one end portion of the plunger so as not to rotate and to be axially displaceable together with the plunger, and at the other end portion of the plunger, an elastic member constituting the buffer mechanism. A member is provided, and before the restraining side engaging member and the rotating side engaging member are engaged, the elastic member comes into contact with the outer surface of the end portion of the case as a receiving surface. The electric brake device with a parking mechanism according to any one of 2. The actuator is a solenoid that causes the plunger to linearly move when energized. The solenoid includes a coil, a case, and a plunger, and the plunger is axially displaceable and non-rotatable in the case. One end portion and the other end portion projecting from a pair of through holes provided concentrically to both end portions of the case to the outside of the case, and a part of the intermediate portion is an inner diameter of the through hole. It has a large diameter part with a larger outer diameter,
The restraining side engaging member is provided at one end of the plunger so as not to rotate and to be able to be displaced in the axial direction together with the plunger, and an elastic member is provided at the other end of the plunger. The elastic member abuts on a second receiving surface existing in a portion facing the case before the other end edge of the large diameter portion abuts on the inner surface of the other end of the case. The electric brake device with a parking mechanism described in any one of the above.

Images