JP6382116B2 - Brake actuator and brake device - Google Patents

Description

  The present invention relates to a brake actuator that is provided in a brake device and drives a piston that presses a pad.

  A vehicle such as an automobile is provided with a brake device corresponding to each wheel. A disc brake widely adopted as a brake device includes a rotor (disk) that rotates together with an axle, a pair of pads (friction materials) that are arranged to face each other with the rotor interposed therebetween, and a claw that presses one pad toward the rotor. And a piston for pressing the other pad toward the rotor. Then, when the driver operates the brake pedal, the brake fluid is supplied to the caliper and the piston moves toward the rotor. Accordingly, the pair of pads are pressed against each other so as to sandwich the rotor, and a braking force is generated.

  By the way, with the advancement of automobile technology, instead of the development of the mechanical brake device that operates by the hydraulic pressure of the brake fluid as described above, the development of an electric brake device having an actuator controlled by an electric signal has been developed. Progressing. This brake device eliminates the need for a master cylinder, hydraulic piping, a booster device, and the like, so that the entire device can be reduced in size and weight, and the braking force can be controlled with high accuracy. Therefore, for example, the present invention can be easily applied to a vehicle having an automatic tracking function that automatically controls acceleration force and braking force according to the behavior of another vehicle traveling ahead. Further, development of an electric parking brake having a function of a foot brake device capable of obtaining a braking force by a driver's brake pedal operation as a brake device is in progress.

  Such an electric brake device is described in Patent Document 1, for example. The brake device described in Patent Document 1 includes an electric parking brake device. The brake device of Patent Document 1 has a mounting (bracket) fixed to the vehicle body, and a brake housing (caliper) provided on the mounting via a pair of slide pins.

  The brake housing has a U-shaped cross section so as to straddle the disk rotor, and is movable in the axial direction of the disk rotor. The brake housing includes a claw portion that holds one pad and a piston that presses the other pad. The piston is driven by an electric motor that is operated by operating a parking brake switch provided in the passenger compartment.

  The electric motor is provided in parallel to the cylinder portion that movably accommodates the piston, and is accommodated in a gear body (case) formed in a substantially L shape. A reduction mechanism that reduces the rotation of the electric motor to increase the torque is housed in the gear body. This makes it possible to employ a small electric motor and suppresses an increase in the axial dimension of the cylinder portion, thereby improving the mounting property on the vehicle. As the gear body, resin is often used from the viewpoint of weight reduction and weather resistance of the vehicle's undercarriage.

JP 2012-229741 A

  In the brake device described in Patent Document 1 described above, a planetary gear speed reducer is adopted as the speed reduction mechanism, and a resin ring gear (internal gear) forming the planetary gear speed reducer is replaced with a separate resin gear body. It is trying to be attached to. Specifically, the jaws of the snap pieces provided on the ring gear are engaged with the engaging pieces provided on the lower body forming the gear body to connect the two.

  Thus, in patent document 1, the ring gear is attached to the gear body so as not to rotate by snap fitting. Therefore, the ring gear is likely to rattle with respect to the gear body, causing not only the generation of abnormal noise, but also the problem that the engaging portion between the ring gear and the gear body is likely to wear out. In particular, if the gear body is made of a material having excellent weather resistance and the ring gear is made of a material that is advantageous in terms of strength, and the two materials are made to be optimized, the above-mentioned problems become prominent.

  On the other hand, a means for fixing the ring gear and the gear body by bonding is also conceivable. In this case, however, it is necessary to fix the ring gear and the gear body until they are completely fixed, and there is a problem that the processing time increases.

  An object of the present invention is to provide a brake actuator and a brake device that can suppress rattling of the internal gear with respect to the case even when the material of the case and the material of the internal gear are different.

The brake actuator according to the present invention is a brake actuator that drives a piston that is movably held by a caliper, and includes an electric motor having a rotating shaft, and an output shaft that transmits the power of the electric motor to the piston. the provided rotational shaft and the input-side two-stage gear and the reduction mechanism is provided between the output shaft, the electric motor, and a case for accommodating the input-side two-stage gear and said speed reduction mechanism, the input-side The two-stage gear is rotatably supported by a rotation pin, the case is provided with a rotation pin fixing portion to which one end of the rotation pin is fixed, and the speed reduction mechanism is inserted into the case by insert molding. has an inner gear fixed on the outer peripheral surface of the internal gear, at least one detent projection projecting radially outward is provided, the detent projection, said pivot Is arranged at a position avoiding the emission fixing unit was different from the material of said the material of said gear case.

In the brake device according to the present invention, a rotor, a pad pressed against the rotor, a piston that presses the pad, a caliper that holds the piston movably, and an actuator that is provided in the caliper and drives the piston The actuator is provided between the rotary shaft and the output shaft, an electric motor having a rotary shaft, an output shaft that transmits the power of the electric motor to the piston, and an input-side two-stage gear and the reduction mechanism, the electric motor, accommodates the input-side two-stage gear and said speed reduction mechanism, and a case fixed to the caliper, the input-side two-stage gear, the rotary is rotatably supported by a pin, in the case, said pivot pin fixing portion to which one end of the pivot pin is fixed is provided, said reduction mechanism Has an inner gear which is fixed by insert molding on the case, on the outer circumferential surface of the internal gear, at least one detent projection projecting radially outward is provided, the detent projection, said pivot pin fixed parts are disposed at positions avoiding, with different and material of the the material in said gear case.

  In another aspect of the present invention, the internal gear is made of a polyamide resin.

  In another aspect of the present invention, the case is made of polybutylene terephthalate resin.

  In another aspect of the invention, the anti-rotation protrusion is disposed at a position avoiding the functional component in the case.

In another aspect of the present invention, the outer peripheral surface of said internal gear, said for performing retaining of the internal gear relative to the case, circumferentially extending annular retaining projection of the internal gear is provided, said stopper The protrusion is embedded in the case by insert molding and is not exposed to the outside .

  According to the present invention, even if the material of the internal gear and the material of the case are different, the internal gear is fixed to the case by insert molding, so that rattling of the internal gear with respect to the case can be easily suppressed. Therefore, wear of the speed reduction mechanism, generation of abnormal noise, and the like can be prevented. In addition, since a material suitable for the internal gear and a material suitable for the case can be arbitrarily selected, it is possible to construct a highly reliable brake device that is unlikely to fail.

It is a perspective view showing an outline of a brake device concerning the present invention. It is the top view which looked at the brake device (rotor abbreviation) of Drawing 1 from the direction of arrow A. It is a partial expanded sectional view which follows the BB line of FIG. It is a perspective view which shows an actuator single-piece | unit. It is sectional drawing which follows the CC line of FIG. It is an enlarged view of the broken-line circle | round | yen D part of FIG. It is a perspective view explaining the internal structure of a case single-piece | unit. (A), (b) is a perspective view explaining the detailed structure of an internal gear.

  Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings.

  1 is a perspective view showing an outline of a brake device according to the present invention, FIG. 2 is a plan view of the brake device (rotor omitted) of FIG. 1 viewed from the direction of arrow A, and FIG. 3 is a BB line of FIG. FIG. 4 is a perspective view showing the actuator alone, FIG. 5 is a sectional view taken along the line CC of FIG. 4, and FIG. 6 is an enlarged view of a broken line circle D part of FIG. FIG. 7 is a perspective view illustrating the internal structure of the case alone, and FIGS. 8A and 8B are perspective views illustrating the detailed structure of the internal gear.

  As shown in FIGS. 1 to 3, the brake device 10 includes an electric parking brake device (Electric Parking Brake) and is attached to a vehicle axle (not shown) so as to be integrally rotatable. It has. The rotor 11 includes a rotor main body 11a having a plurality of hub bolts 12 (four in the drawing) and a disk portion 11b provided integrally on the outer side in the radial direction of the rotor main body 11a. The disk part 11b forms a friction surface sandwiched between a pair of pads 13a and 13b. A wheel (not shown) is attached to the rotor body 11a, and a wheel nut (not shown) is screwed to each hub bolt 12.

  The brake device 10 includes a mounting bracket 14 that is fixed to a non-rotating portion (not shown) such as a knuckle of a vehicle. The mounting bracket 14 is formed in a predetermined shape by casting, and is integrally provided with a pair of pin mounting portions 14a to which the pair of slide pins 15 are slidably mounted. Each pin mounting portion 14 a extends in the axial direction of the rotor 11, and each slide pin 15 is movable in the axial direction of the rotor 11. A bridging portion 14 b is integrally provided between each pin mounting portion 14 a, and each pin mounting portion 14 a is arranged with a predetermined interval in the circumferential direction of the rotor 11.

  The brake device 10 includes a caliper 16 that is movably attached to the mounting bracket 14. The caliper 16 is formed into a predetermined shape by casting as with the mounting bracket 14, and includes a caliper body 16a and a pair of pin fixing portions 16b. The caliper body 16a has a substantially U-shaped cross section so as to straddle the disk portion 11b of the rotor 11, and includes a claw portion 16c, a cylinder portion 16d, and a connecting portion 16e. The connecting part 16e connects the claw part 16c and the cylinder part 16d.

  The claw portion 16 c is disposed on the hub bolt 12 side along the axial direction of the rotor 11, and the cylinder portion 16 d is disposed on the opposite side to the hub bolt 12 side along the axial direction of the rotor 11. Here, on the side opposite to the hub bolt 12 side along the axial direction of the rotor 11, a shock absorber (not shown) for attenuating the vibration of the vehicle is arranged. Therefore, the brake device 10 is fixed to the vehicle while avoiding the shock absorber.

  As shown in FIG. 3, the cylinder portion 16d is formed in a bottomed cylindrical shape, and a piston 17 is slidably provided inside the cylinder portion 16d. That is, the piston 17 is movably held by the caliper 16 and slides in the axial direction of the rotor 11. Here, the radially inner side of the cylinder portion 16d is cut so that the piston 17 can slide smoothly.

  Brake fluid (not shown) is supplied to the inside of the cylinder portion 16d and to the back side (right side in the drawing) of the piston 17 by operating a brake pedal (not shown). Yes. In other words, during normal braking by the driver's operation of the brake pedal, braking force is generated by supplying brake fluid.

  As shown in FIG. 1, the pair of pin fixing portions 16b are provided on the radially outer side of the cylinder portion 16d so as to protrude in opposite directions so as to face each other. Bolts 18 are respectively inserted into the distal end portions of the pin fixing portions 16b, and these bolts 18 are fixed to the slide pins 15, respectively. Thereby, the caliper 16 is movable in the axial direction of the rotor 11 with respect to the mounting bracket 14.

  As shown in FIG. 3, the claw portion 16c presses one pad (outer pad) 13a on the hub bolt 12 side of the disc portion 11b toward the disc portion 11b. Further, the piston 17 presses the other pad (inner pad) 13b on the side opposite to the hub bolt 12 side of the disk part 11b toward the disk part 11b.

  More specifically, when brake fluid is supplied to the back side of the piston 17 by the driver's brake pedal operation, the piston 17 is pushed out from the inside of the cylinder portion 16d and moves to the left in FIG. . As a result, the piston 17 presses the pad 13b toward the disk portion 11b. On the other hand, the caliper 16 moves to the right in FIG. 3 with respect to the mounting bracket 14 by the reaction force when the piston 17 presses the pad 13b. Thereby, the claw part 16c presses the pad 13a toward the disk part 11b.

  The piston 17 is hollow, and a feed screw mechanism 17a (not shown in detail) is accommodated therein. The feed screw mechanism 17 a includes a male screw member 17 b that is rotated forward and backward by the actuator 20. The feed screw mechanism 17a includes a female screw member (not shown) to which the male screw member 17b is screwed. Thus, when the driver operates a parking brake switch (not shown) in the passenger compartment, the male screw member 17b is rotationally driven in the forward and reverse directions by the actuator 20.

  As shown in FIGS. 1 to 3, the brake device 10 includes an actuator (brake actuator) 20 that drives a feed screw mechanism 17a. The actuator 20 is fixed to the bottom side of the cylinder portion 16d opposite to the rotor 11 side. Hereinafter, the structure of the actuator 20 that operates when the parking brake switch is operated will be described in detail with reference to the drawings.

  As shown in FIGS. 4 and 5, the actuator 20 includes a case 21 formed in a substantially L shape. The opening 21 a (see FIGS. 3 and 5) of the case 21 is sealed by the cover 22, thereby preventing rainwater, dust, and the like from entering the case 21. Both the case 21 and the cover 22 are formed in a predetermined shape by injection molding a resin material.

  Here, the case 21 occupies most of the outline of the actuator 20 and is exposed to a poor environment around the undercarriage of the vehicle. Therefore, the case 21 is formed of a polybutylene terephthalate resin (PBT resin) excellent in weather resistance. Examples of the characteristics of the PBT resin include excellent thermal stability, dimensional stability, chemical resistance, and the like. Thermal stability is a property that is not easily thermally deformed even when exposed to a high temperature environment for a long time. Dimensional stability is a characteristic that is difficult to change in dimensions because of its low water absorption even when exposed to a humid environment. Chemical resistance is a property that hardly changes in quality to organic solvents, gasoline, oil, and the like.

  Note that the material of the case 21 is not limited to the PBT resin, and other materials such as polyphenylene sulfide resin (PPS resin) may be used as long as the material has excellent weather resistance as described above. Further, since the cover 22 is also exposed to the same environment as the case 21, it may be formed of the same PBT resin as that of the case 21, or may be other materials (PPS resin or the like) having excellent weather resistance. good. Moreover, since it exists in the above environments, the case 21 and the cover 22 are fixed by the suitable welding means which fuses and fixes each resin material.

  Here, the electric motor 30 and the speed reduction mechanism 50 are accommodated in the case 21, and before the detailed structure of the case 21 is described, the structure of the electric motor 30 and the speed reduction mechanism 50 will be described.

  As shown in FIG. 5, the electric motor 30 includes a motor case 31. The motor case 31 is formed in a substantially cylindrical shape with a bottom by pressing a steel plate (magnetic material). Inside the motor case 31, a plurality of magnets 32 (only two are shown in the figure) having a substantially arc-shaped cross section are fixed. Inside these magnets 32, an armature 34 around which a coil 33 is wound is housed rotatably through a predetermined gap (air gap).

  A base end side of an armature shaft (rotation shaft) 35 is fixed to the rotation center of the armature 34. The distal end side of the armature shaft 35 extends to the outside of the motor case 31, and a pinion gear 36 is fixed to the distal end portion of the armature shaft 35. A commutator 37 to which an end portion of the coil 33 is electrically connected is fixed between the armature 34 and the pinion gear 36 along the axial direction of the armature shaft 35. A pair of brushes 38 is in sliding contact with the outer peripheral portion of the commutator 37. Note that the commutator 37 and the brushes 38 are also accommodated in the motor case 31, respectively.

  A drive current is supplied to each brush 38 by operating the parking brake switch when the vehicle is stopped. Then, a drive current is supplied to the coil 33 through the brushes 38 and the commutator 37, thereby generating an electromagnetic force in the armature 34. Therefore, the armature shaft 35 (pinion gear 36) is rotationally driven in a predetermined direction at a predetermined rotational speed. Here, the drive current supplied to each brush 38 is supplied from a vehicle-side connector (not shown) connected to the connector connecting portion 25 provided in the case 21.

  As shown in FIG. 5, the case 21 is provided with an output shaft 39 that is coupled to the male screw member 17 b (see FIG. 3) so as to be integrally rotatable and transmits the power of the electric motor 30 to the piston 17. The output shaft 39 is provided integrally with the planetary carrier 56 that forms the speed reduction mechanism 50, and transmits the torque increased in torque to the male screw member 17b. The armature shaft 35 and the output shaft 39 are provided in the case 21 side by side in parallel, and the speed reduction mechanism 50 is provided between the armature shaft 35 and the output shaft 39.

  In addition, an input-side two-stage gear 40 for transmitting power to an output shaft 39 arranged in parallel with the armature shaft 35 is provided between the speed reduction mechanism 50 and the pinion gear 36. The input-side two-stage gear 40 includes a large-diameter gear 41 that meshes with the pinion gear 36 and a small-diameter gear 42 that meshes with the large-diameter gear 52 of the output-side two-stage gear 51 that forms the reduction mechanism 50. .

  The reduction mechanism 50 is a planetary gear reduction mechanism and has an output-side two-stage gear 51. The output-side two-stage gear 51 includes a large-diameter gear 52 that meshes with the small-diameter gear 42 of the input-side two-stage gear 40 and a small-diameter gear 53 that functions as a sun gear (sun gear). The speed reduction mechanism 50 includes four planetary gears (planetary gears) 54 (only two are shown in the figure). These planetary gears 54 are meshed with both the small-diameter gear 53 and the internal gear 55, respectively.

  Each planetary gear 54 is rotatably supported by a planetary carrier 56 via a support pin 57. The internal gear 55 is fixed to the case 21 by insert molding, and the planetary carrier 56 is rotatable relative to the internal gear 55. Thereby, the rotation of the armature shaft 35 is transmitted to the speed reduction mechanism 50 via the input side two-stage gear 40 and the output side two-stage gear 51, and is decelerated by the speed reduction mechanism 50. Thereafter, the rotational force decelerated by the reduction mechanism 50 and increased in torque is transmitted from the output shaft 39 to the male screw member 17b (see FIG. 3), and the piston 17 is moved with a large force. Therefore, an electric parking brake device can be constructed using the small electric motor 30.

  As shown in FIGS. 5 to 7, the internal gear (internal gear) 55 is fixed to the axial base end side of the cylindrical fixing portion 23 a forming the caliper fixing portion 23 by insert molding. That is, the internal gear 55 is disposed coaxially with the output shaft 39. Since the internal gear 55 is provided in a space sealed by the case 21 and the cover 22, there is no weather resistance requirement unlike the case 21 and the cover 22. On the other hand, since the internal gear 55 is a power transmission element that forms the speed reduction mechanism 50, there are requirements for mechanical strength and durability. Therefore, in the present embodiment, the internal gear 55 is formed of PA66 resin (polyamide 66) which is a polyamide resin. Thereby, sufficient intensity | strength is acquired, realizing the weight reduction of the internal gear 55. FIG. Here, the polyamide-based resin has excellent characteristics in mechanical strength and also has excellent characteristics in chemical resistance as described above.

  However, the material of the internal gear 55 is not limited to PA66 resin, and other materials may be used as long as the material can provide strength suitable for the power transmission element. Here, since the internal gear 55 is fixed to the base end side of the cylindrical fixing portion 23a by insert molding, it is not a component that moves by itself. Therefore, for example, the internal gear 55 may be formed of a metal such as an aluminum material having higher strength. As described above, in the present embodiment, the material of the case 21 and the material of the internal gear 55 are made different from each other, and each is formed of an optimal material, thereby realizing the actuator 20 that is hard to fail and has high reliability. Yes.

  As shown in FIG. 8, the internal gear 55 has an annular gear body 55a. A tooth portion 55b having a predetermined pitch is formed on the inner peripheral surface of the gear body 55a. Four planetary gears 54 (see FIG. 5) are meshed with the tooth portion 55b. In addition, an annular support collar 55c formed in a step shape is provided on the tip end side in the axial direction of the gear body 55a, that is, on the output shaft 39 side in the state shown in FIG. The support collar portion 55c protrudes radially inward from the tooth tip of the tooth portion 55b, thereby rotatably supporting the outer peripheral portion of the planet carrier 56 (see FIG. 5).

  On the outer peripheral surface of the gear body 55a, four detent projections 55d that protrude outward in the radial direction of the internal gear 55 are integrally provided. These anti-rotation protrusions 55d are provided at equal intervals (for example, at 90 ° intervals) along the circumferential direction of the gear body 55a, and the cross-sectional shape is formed in a substantially rectangular shape. As shown in FIG. 7, each rotation prevention protrusion 55 d is fixed to the axially proximal end side of the cylindrical fixing portion 23 a by insert molding, whereby the rotation of the internal gear 55 with respect to the case 21 is made. In other words, each rotation stop projection 55d restricts relative rotation of the internal gear 55 with respect to the case 21. The axial base end side of the gear main body 55a is exposed to the outside as shown in FIG. 7, and the axial base end side of the gear main body 55a in each of the anti-rotation projections 55d is thereby exposed to the outside. Yes.

  As shown in FIG. 7, each anti-rotation protrusion 55 d is arranged at a position avoiding the rotation pin fixing portion PF provided inside the case 21. Thereby, it is suppressed that the thickness of case 21 around the rotation pin fixing | fixed part PF becomes thin, and it suppresses that the rigidity of the rotation pin fixing | fixed part PF falls. Therefore, the fall of the rotation pin P (refer FIG. 5) fixed to the rotation pin fixing | fixed part PF is prevented. Here, the rotation pin P supports the input side two-stage gear 40 (see FIG. 5) in a freely rotatable manner. In this way, by arranging each rotation stop projection 55d at a position avoiding the rotation pin P as a functional component accommodated in the case 21, the internal gear 55 and the rotation can be rotated without increasing the size of the case 21. The fixing strength of the pin P with respect to the case 21 is sufficiently secured. Further, each of the anti-rotation projections 55d is disposed at a position avoiding a screw hole (functional part) of a pair of screw insertion portions 23c described later, and thereby the rigidity of the pair of screw insertion portions 23c is reduced in the same manner as described above. Is suppressed.

  As shown in FIG. 8, an annular retaining protrusion 55e extending along the circumferential direction of the internal gear 55 is integrally provided on the outer peripheral surface of the gear body 55a. The retaining protrusion 55e is provided so as to protrude outward in the radial direction of the internal gear 55, and is disposed closer to the proximal end side in the axial direction of the internal gear 55 (lower side in FIG. 5). The retaining protrusion 55e is embedded in the axial base end side of the cylindrical fixing portion 23a (see FIG. 5) by insert molding, and the opening 21a side of the retaining protrusion 55e is formed so as not to be exposed to the outside. Thereby, the internal gear 55 is prevented from coming off from the case 21 in the axial direction. Here, as shown in FIG. 8, the protrusion height of the retaining protrusion 55e toward the outside in the radial direction is set to be lower than the protrusion height of each of the rotation prevention protrusions 55d toward the radially outer side. This is based on the fact that the load applied in the axial direction of the internal gear 55 is smaller than the load applied in the circumferential direction of the internal gear 55.

  The protrusion height of the retaining protrusion 55e outward in the radial direction does not cause any problem as shown in FIG. 8. For example, the height of the protrusion of the retaining protrusion 55e outward in the radial direction is different from each other. The following problems may occur if the height of the stop protrusion 55d is equal to the protruding height to the outside in the radial direction. That is, since the retaining protrusion 55e is disposed close to the rotating pin fixing portion PF, the rigidity of the opening of the rotating pin fixing portion PF may be reduced.

  As shown in FIG. 7, a pair of power supply terminals TM is provided by insert molding on the side opposite to the internal gear 55 side along the longitudinal direction of the case 21 (right side in the figure). One end side of these power supply terminals TM is exposed near the electric motor 30 in the case 21, and the other end side of each power supply terminal TM is exposed in the connector connecting portion 25. Each power supply terminal TM and the internal gear 55 are fixed to the case 21 by insert molding when the case 21 is injection-molded. Here, in FIG. 7, each power supply terminal TM and the internal gear 55 are shaded to make it easy to understand the parts to be inserted.

  Specifically, the power supply terminals TM, the internal gear 55, and the like manufactured in advance in another manufacturing process are prepared, and these are arranged at predetermined positions of a fixed mold (not shown). Next, a movable mold (not shown) is abutted against the fixed mold, and a molten resin (in this embodiment) is dispensed from a dispenser into a cavity (not shown) formed between the fixed mold and the movable mold. PBT resin) is supplied. Thereby, the periphery of each power supply terminal TM and the internal gear 55 is filled with the molten resin, and as a result, the case 21 in which each power supply terminal TM, the internal gear 55 and the like are fixed is completed.

  Thus, since each power supply terminal TM and the internal gear 55 are fixed to the case 21 by insert molding, the axis of the cylindrical fixing portion 23a and the axis of the internal gear 55 can be made to coincide with each other with high accuracy. Therefore, it becomes possible to operate the electric motor 30 and the speed reduction mechanism 50 more smoothly. Further, since the positional accuracy between each power supply terminal TM and the connector connecting portion 25 can be improved, the connection of the vehicle side connector (not shown) to the connector connecting portion 25 can be performed smoothly.

  As shown in FIGS. 4 and 5, the case 21 includes a caliper fixing portion 23 that is fixed to the cylinder portion 16 d (see FIG. 3) of the caliper 16 and a motor housing portion 24 that houses the electric motor 30 (see FIG. 5). And. The caliper fixing portion 23 is provided at a portion where the output shaft 39 of the case 21 is disposed, and is disposed coaxially with the output shaft 39 and the speed reduction mechanism 50. A cylindrical fixing portion 23a is provided on the radially inner side of the caliper fixing portion 23, and the bottom side of the cylinder portion 16d is fitted and fixed to the axial front end side of the cylindrical fixing portion 23a. Further, an outer peripheral wall portion 23 b that forms a part of the outer case of the case 21 is provided on the radially outer side of the caliper fixing portion 23.

  On the other hand, the motor housing portion 24 is provided at a portion of the case 21 where the electric motor 30 is disposed, and is disposed coaxially with the armature shaft 35 (see FIG. 5). The motor accommodating portion 24 includes a cylindrical main body portion 24a extending in the axial direction of the armature shaft 35, and a stepped bottom wall portion 24b on the opposite side to the cover 22 side along the axial direction of the cylindrical main body portion 24a. ing. The electric motor 30 is inserted into the motor housing 24 and is firmly fixed to the motor housing 24 by fastening means (not shown) so as not to rotate relative to the motor housing 24.

  As shown in FIG. 4, the axial length L1 of the motor accommodating portion 24 is longer than the axial length L2 of the caliper fixing portion 23 (L1> L2). Here, the axial length L1 of the motor accommodating portion 24 is a length dimension from the opening 21a (see FIG. 5) of the case 21 to the bottom wall portion 24b of the motor accommodating portion 24, and the axis of the caliper fixing portion 23 is The direction length L2 is a length dimension from the opening 21a of the case 21 to the tip of the cylindrical fixing portion 23a of the caliper fixing portion 23. Further, the axial length L1 is approximately twice the axial length L2.

  Thus, when the actuator 20 is fixed to the caliper 16, the electric motor 30 can be disposed directly beside the cylinder portion 16d as shown in FIG. 2 so that the armature shaft 35 and the output shaft 39 are parallel to each other. . Therefore, it can suppress that the axial direction dimension of the cylinder part 16d increases, and it can avoid that the brake device 10 contacts a shock absorber etc. FIG.

  Here, as shown in FIG. 5, a vehicle-side connector is electrically connected to the side opposite to the caliper fixing portion 23 side that sandwiches the motor accommodating portion 24 along the longitudinal direction of the case 21 (left-right direction in the drawing). The connector connecting portion 25 is integrally provided. Inside the connector connecting portion 25, the other end side of the power supply terminal TM (see FIG. 7) for supplying the drive current from the vehicle side connector to each brush 38 is provided. As shown in FIG. 2, the connector connecting portion 25 is directed to the side opposite to the cylinder portion 16 d side in a state where the actuator 20 is fixed to the caliper 16. Thus, the vehicle-side connector can be easily and reliably connected to the connector connecting portion 25 with the brake device 10 attached to the vehicle.

  As shown in FIGS. 4, 5, and 7, the caliper fixing portion 23 includes a cylindrical fixing portion 23a and an outer peripheral wall portion 23b. A pair of screw insertion portions 23c are integrally provided on the outer peripheral wall portion 23b so as to partially protrude radially outward. That is, each screw insertion portion 23 c is disposed on the radially outer side of the caliper fixing portion 23. A fixing screw S (see FIGS. 1 and 2) for fixing the actuator 20 to the caliper 16 (see FIG. 2) is inserted into each screw insertion portion 23c, and each screw insertion portion 23c is fixed to the caliper 16. It is like that.

  The screw insertion portions 23c are arranged to face each other with the cylindrical fixing portion 23a as a center, and as a result, as shown in FIG. 3, the shaft center of the output shaft 39 is not displaced from the shaft center of the piston 17. The actuator 20 is fixed to the caliper 16 with an equal fixing force. Each screw insertion portion 23 c is arranged at a predetermined interval across the output shaft 39 in the short direction of the case 21 intersecting the longitudinal direction of the case 21.

  As shown in FIGS. 2, 4, and 7, between the screw insertion portions 23 c and the outer peripheral wall portion 23 b, the fixing portion reinforcement for increasing the fixing strength of the screw insertion portions 23 c with respect to the outer peripheral wall portion 23 b. Ribs 23d are provided integrally. Thereby, the twist and rattling with respect to the caliper 16 of the case 21 at the time of the action | operation of the actuator 20 are suppressed.

  A pair of reinforcing ribs 24 d are integrally provided on the outer side in the radial direction of the motor housing portion 24. As shown in FIG. 4, these reinforcing ribs 24 d are arranged such that the motor accommodating portion 24 having an axial length L <b> 1 inclines toward the caliper fixing portion 23 side with respect to the caliper fixing portion 23 having an axial length L <b> 2. It is provided in order to suppress (falling) or twisting. Further, since the case 21 is formed by injection molding a resin material (PBT resin), the resin shrinks and sinks when cured. Each reinforcing rib 24d also suppresses inclination and distortion of the motor housing portion 24 with respect to the caliper fixing portion 23 due to the occurrence of sink marks when the case 21 is cured.

  Each reinforcing rib 24d is provided from one axial end (upper in FIG. 4) of the motor housing 24 to the other axial end (lower in FIG. 4) of the motor housing 24. Each reinforcing rib 24d has a substantially triangular cross section, and the amount of protrusion of each reinforcing rib 24d to the radially outer side of the motor housing portion 24 is from the one axial end side of the motor housing portion 24 to the other axial end side. It gradually gets bigger as you go to.

  Further, each reinforcing rib 24d is arranged on the side where the caliper fixing portion 23 of the motor accommodating portion 24 is located, and the protruding direction of each reinforcing rib 24d is the caliper when the motor accommodating portion 24 is viewed from its axial direction. It is directed to each screw insertion portion 23 c of the fixing portion 23. Thereby, the reinforcing ribs 24 d are arranged in the dead space of the case 21. Therefore, each reinforcing rib 24d can be formed relatively large to increase the rigidity of each reinforcing rib 24d itself.

  Further, by arranging the reinforcing ribs 24d in the dead space of the case 21, the cylinder portion 16d and the motor housing portion 24 do not interfere with each other while suppressing the inclination toward the caliper fixing portion 23 side of the motor housing portion 24, that is, It can be arranged close to each other at a position avoiding the cylinder portion 16d. That is, the location of each reinforcing rib 24d is an advantageous location for reducing the size and weight of the brake device 10.

  As shown in FIG. 4, the other axial end side of the motor accommodating portion 24 in each reinforcing rib 24 d is provided toward the outer peripheral wall portion 23 b of the caliper fixing portion 23. Thereby, the stress applied to each reinforcing rib 24d is released to the outer peripheral wall portion 23b through the screw insertion portion 23c. Therefore, the inclination and the twist with respect to the caliper fixing | fixed part 23 of the motor accommodating part 24 are suppressed more reliably. Here, the thickness of the outer peripheral wall portion 23 b along the axial direction of the output shaft 39 is thick, and the rigidity of the outer peripheral wall portion 23 b along the axial direction of the output shaft 39 is high. Moreover, the outer peripheral wall part 23b is connected with the screw insertion part 23c. Therefore, the outer peripheral wall portion 23b is suppressed from being deformed by the stress applied from each reinforcing rib 24d.

  As shown in FIG. 4, the caliper fixing portion 23 is provided with a plurality of meat stealing portions 23 e. These meat stealing portions 23e are provided on the cylinder portion 16d side (the upper side in the drawing) of the caliper fixing portion 23 and around the cylindrical fixing portion 23a. Each meat stealing part 23e is arrange | positioned between the cylindrical fixing | fixed part 23a and the outer peripheral wall part 23b, and is arrange | positioned along with the circumferential direction of the cylindrical fixing | fixed part 23a. Each meat stealing portion 23 e is provided to prevent deformation due to sink marks of the caliper fixing portion 23 and to reduce the weight of the case 21, and is provided so as to be recessed in the axial direction of the output shaft 39.

  Each meat stealing portion 23e is partitioned from each other by a plurality of radial ribs 23f provided radially around the output shaft 39. These radial ribs 23f are provided between the cylindrical fixing portion 23a and the outer peripheral wall portion 23b, between the cylindrical fixing portion 23a and each screw insertion portion 23c, and between the cylindrical fixing portion 23a and the motor housing portion 24, respectively. ing.

  Of these radial ribs 23f, the radial ribs 23f1 between the cylindrical fixing portions 23a and the screw insertion portions 23c increase the rigidity between them to suppress the twisting and rattling of the caliper 16 of the case 21. It has a function to do. Of the radial ribs 23f, the radial ribs 23f2 between the cylindrical fixing part 23a and the motor housing part 24 have a function of suppressing inclination and distortion of the motor housing part 24 with respect to the caliper fixing part 23. .

  Here, the pair of reinforcing ribs 24d are integrally provided so as not to overlap the meat stealing portions 23e when the motor housing portion 24 is viewed from the axial direction, and to be connected to the outer peripheral wall portion 23b. Thereby, the shape of each mold used when the case 21 is injection-molded can be simplified, and the stress applied from each reinforcing rib 24d is applied to the meat stealing portion 23e where the case 21 is thin. Is prevented.

  As described in detail above, according to the present embodiment, even if the material of the internal gear 55 (PA66 resin) and the material of the case 21 (PBT resin) are different, the internal gear 55 is fixed to the case 21 by insert molding. Therefore, rattling of the internal gear 55 with respect to the case 21 can be easily suppressed. Therefore, wear of the speed reduction mechanism 50, generation of abnormal noise, and the like can be prevented. In addition, since a material suitable for the internal gear 55 and a material suitable for the case 21 can be arbitrarily selected, it is possible to construct the brake device 10 that is unlikely to fail and has high reliability.

  It goes without saying that the present invention is not limited to the above-described embodiment, and various modifications can be made without departing from the scope of the invention. For example, in the above embodiment, the brake device 10 is an electric parking brake device. However, the present invention is not limited to this, and an actuator that is operated by a driver's brake pedal operation is provided. It can also be applied to connected brake devices (Brake by wire).

  Further, in the above embodiment, as shown in FIG. 8, the outer peripheral surface of the gear body 55a of the internal gear 55 is provided with the four detent projections 55d. However, the present invention is not limited to this. Only one anti-rotation projection 55d may be provided, or five or more anti-rotation projections 55d may be provided. Furthermore, the anti-rotation protrusions 55d are not limited to be provided at equal intervals, but may be provided at unequal intervals according to the location of the functional components (such as the rotation pin P) accommodated in the case 21.

  In the above embodiment, as shown in FIG. 8, the outer peripheral surface of the gear main body 55 a of the internal gear 55 is provided with one retaining protrusion 55 e. However, the present invention is not limited to this. Two or more retaining protrusions may be provided side by side in the axial direction on the outer peripheral surface of the gear body 55a.

  Furthermore, in the above embodiment, as shown in FIG. 5, the electric motor 30 is a brushed electric motor. However, the present invention is not limited to this, and a brushless electric motor may be adopted. it can. In this case, generation of noise from the electric motor can be suppressed, and adverse effects on other in-vehicle devices can be more effectively reduced.

  In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably. In addition, the material, shape, dimensions, number, arrangement location, and the like of each component in the above-described embodiment are arbitrary and are not limited as long as the present invention can be achieved.

DESCRIPTION OF SYMBOLS 10 Brake apparatus 11 Rotor 11a Rotor main body 11b Disk part 12 Hub bolt 13a, 13b Pad 14 Mounting bracket 14a Pin mounting part 14b Bridging part 15 Slide pin 16 Caliper 16a Caliper main body 16b Pin fixing part 16c Claw part 16d Cylinder part 16e Connection part 17 Piston 17a Feed screw mechanism 17b Male screw member 18 Bolt 20 Actuator (Brake actuator)
21 Case 21a Opening 22 Cover 23 Caliper fixing part 23a Cylindrical fixing part 23b Outer peripheral wall part 23c Screw insertion part 23d Retaining rib for fixing part 23e Meat stealing part 23f, 23f1, 23f2 Radial rib 24 Motor accommodating part 24a Cylindrical main body part 24b Bottom Wall portion 24d Reinforcing rib 25 Connector connecting portion 30 Electric motor 31 Motor case 32 Magnet 33 Coil 34 Armature 35 Armature shaft (rotating shaft)
36 pinion gear 37 commutator 38 brush 39 output shaft 40 input side two-stage gear 41 large diameter gear 42 small diameter gear 50 reduction mechanism 51 output side two stage gear 52 large diameter gear 53 small diameter gear (sun gear)
54 Planetary gear (planetary gear)
55 Internal gear (internal gear)
55a Gear body 55b Tooth portion 55c Support collar 55d Non-rotating projection 55e Retaining projection 56 Planetary carrier 57 Support pin P Rotating pin (functional component)
PF Rotating pin fixing part S Fixing screw TM Power supply terminal

Claims (10)

A brake actuator that drives a piston that is movably held by a caliper,
An electric motor having a rotating shaft;
An output shaft for transmitting the power of the electric motor to the piston;
An input-side two-stage gear and a reduction mechanism provided between the rotating shaft and the output shaft;
A case housing the electric motor , the input side two-stage gear and the speed reduction mechanism;
With
The input side two-stage gear is rotatably supported by a rotation pin,
The case is provided with a rotation pin fixing portion to which one end of the rotation pin is fixed,
The speed reduction mechanism has an internal gear fixed to the case by insert molding,
On the outer peripheral surface of the internal gear, there is provided at least one anti-rotation protrusion protruding radially outward,
The detent protrusion is disposed at a position avoiding the rotating pin fixing portion,
The material of the internal gear is different from the material of the case,
Brake actuator. The brake actuator according to claim 1, wherein
The internal gear is formed of a polyamide-based resin.
Brake actuator. The brake actuator according to claim 1 or 2,
The case is formed of polybutylene terephthalate resin.
Brake actuator. The brake actuator according to any one of claims 1 to 3 ,
The anti-rotation protrusion is arranged at a position avoiding functional parts in the case,
Brake actuator. In the brake actuator according to any one of claims 1 to 4 ,
An annular retaining protrusion extending in the circumferential direction of the internal gear is provided on the outer peripheral surface of the internal gear to prevent the internal gear from slipping from the case .
The retaining protrusion is embedded in the case by insert molding and is not exposed to the outside .
Brake actuator. A rotor,
A pad pressed against the rotor;
A piston that presses the pad;
A caliper for movably holding the piston;
An actuator provided in the caliper and driving the piston;
A brake device comprising:
The actuator is
An electric motor having a rotating shaft;
An output shaft for transmitting the power of the electric motor to the piston;
An input-side two-stage gear and a reduction mechanism provided between the rotating shaft and the output shaft;
A case that accommodates the electric motor , the input side two-stage gear, and the speed reduction mechanism, and is fixed to the caliper;
With
The input side two-stage gear is rotatably supported by a rotation pin,
The case is provided with a rotation pin fixing portion to which one end of the rotation pin is fixed,
The speed reduction mechanism has an internal gear fixed to the case by insert molding,
On the outer peripheral surface of the internal gear, there is provided at least one anti-rotation protrusion protruding radially outward,
The detent protrusion is disposed at a position avoiding the rotating pin fixing portion,
The material of the internal gear is different from the material of the case,
Brake device. The brake device according to claim 6 , wherein
The internal gear is formed of a polyamide-based resin.
Brake device. The brake device according to claim 6 or 7 ,
The case is formed of polybutylene terephthalate resin.
Brake device. In the brake device according to any one of claims 6 to 8 ,
The anti-rotation protrusion is arranged at a position avoiding functional parts in the case,
Brake device. The brake device according to any one of claims 6 to 9 ,
An annular retaining protrusion extending in the circumferential direction of the internal gear is provided on the outer peripheral surface of the internal gear to prevent the internal gear from slipping from the case .
The retaining protrusion is embedded in the case by insert molding and is not exposed to the outside .
Brake device.

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