JP2012214096A - Electrically-powered brake device - Google Patents

Abstract

An object of the present invention is to prevent the deformation of a piston sliding surface of a cylinder body by suppressing transmission of a load from a regulating pin to the cylinder body.
A first slave piston 88b that is accommodated in a cylinder body 82 and generates a hydraulic pressure in a first hydraulic pressure chamber 98b by moving forward, a motor that transmits a driving force to the first slave piston 88b, and a cylinder A regulation pin 102 that is inserted and fixed in a direction orthogonal to the axial direction of the main body 82 and regulates the retracted position of the first slave piston 88b when hydraulic pressure is applied to the first hydraulic pressure chamber 98b from the outside. A gap 204 is formed between the first groove 202 a and the second groove 202 b formed on the outer surface of the pin 102 and the inner peripheral wall 83 of the cylinder body 82.
[Selection] Figure 4

Description

  The present invention relates to an electric brake device incorporated in, for example, a vehicle brake system.

  2. Description of the Related Art Conventionally, a booster using a negative pressure booster or a hydraulic booster is known as an automobile brake mechanism. In recent years, an electric booster using an electric motor as a boost source has been disclosed as this type of booster (see, for example, Patent Document 1).

  The electric booster disclosed in Patent Document 1 includes a main piston (input piston) that moves forward and backward by operating a brake pedal, a cylindrical booster piston that is externally fitted so as to be relatively displaceable with the main piston, It is configured as a single unit equipped with an electric motor for moving the booster piston back and forth.

  In this case, the main piston and booster piston are used as the master cylinder pistons, and their front ends face each pressure chamber of the master cylinder, and the input thrust applied from the brake pedal to the main piston and the electric motor applied to the booster piston. The brake fluid pressure is generated in the master cylinder by the booster thrust.

JP 2010-23594 A

  By the way, in the electric booster disclosed in Patent Document 1, for example, when a hydraulic pressure is applied from the outside to a pressure chamber facing the main piston of the master cylinder, the main piston is boosted by the action of the hydraulic pressure. Retreating toward the side, but if the main piston retracts too much, it becomes difficult to secure the minimum hydraulic pressure in the master cylinder. In this case, it is conceivable to restrict the backward movement of the main piston by, for example, a restricting means or the like. However, the load applied to the restricting means may be transmitted to the cylinder body and the piston sliding surface in the cylinder body may be deformed. There is.

  The present invention has been made in view of the above points, and when the displacement of the piston is regulated by the regulating pin, the transmission of the load from the regulating pin to the cylinder body is suppressed, and the piston sliding of the cylinder body is performed. An object of the present invention is to provide an electric brake device capable of preventing surface deformation.

  In order to achieve the above object, the present invention provides an output hydraulic pressure chamber connected to a wheel cylinder, a piston for generating hydraulic pressure in the output hydraulic pressure chamber by moving forward, and the piston in a cylinder body. A cylinder for housing, a motor for driving the piston forward by transmitting a driving force to the piston, and a regulating means for regulating the backward movement of the piston when hydraulic pressure acts on the output hydraulic pressure chamber from the outside. The electric brake device has a restriction pin that is inserted into and fixed to the cylinder in a direction orthogonal to the axial direction of the cylinder body, and the inner peripheral wall of the cylinder body and the restriction pin A gap is formed between the outer surface and the outer surface.

  According to the present invention, by providing an air gap that separates the outer surface of the restriction pin from the inner peripheral wall of the cylinder body, the load transmission point for transmitting a load from the restriction pin to the cylinder body is extended radially outward from the effective inner diameter of the cylinder body. They can be separated, and deformation of the inner peripheral wall of the cylinder body can be suppressed. As a result, in the present invention, desired sliding performance on the inner peripheral wall (piston sliding surface) of the cylinder body can be ensured.

  Further, the present invention is characterized in that the regulation pin is fixed through the cylinder body.

  According to the present invention, the restriction pin is fixed through the cylinder body, whereby the load applied to the restriction pin can be dispersedly supported at two points.

  Furthermore, the present invention is characterized in that, in the insertion direction of the restriction pin, the axial length of the support portion of the restriction pin supported by the cylinder body is set larger than the axial length of the gap.

  According to the present invention, the desired support strength of the restriction pin can be ensured by setting the axial length of the support portion of the restriction pin supported by the cylinder body larger than the axial length of the gap. .

  Furthermore, the present invention is characterized in that an enlarged diameter part is formed by enlarging the inner peripheral wall of the cylinder body on which the restriction pin is supported, and a gap is formed between the enlarged diameter part and the outer surface of the restriction pin. To do.

  According to the present invention, by forming the enlarged diameter portion on the inner peripheral wall of the cylinder body, it is not necessary to process the restriction pin, and the manufacturing cost can be reduced.

  Furthermore, the present invention forms a reduced diameter part by reducing the outer diameter of the regulating pin in a portion corresponding to the inner peripheral wall of the cylinder body, and a gap is formed between the reduced diameter part and the inner peripheral wall of the cylinder body. It is characterized by that.

  According to the present invention, by forming the reduced diameter portion on the outer surface of the regulating pin, it is not necessary to process the inner peripheral wall of the cylinder body, and the manufacturing cost can be reduced. The reduced diameter portion may be formed by, for example, a groove, a taper, an overall reduced diameter, or a composite shape thereof.

  Furthermore, the present invention is characterized in that the shape on one end side and the shape on the other end side along the axial direction of the regulating pin are formed symmetrically.

  According to the present invention, by making the one end side and the other end side of the regulation pin symmetrical, the directionality during the assembly to the cylinder body can be eliminated, and erroneous assembly can be prevented.

  Furthermore, the present invention is further characterized by further comprising a restricting portion that restricts contact between the central portion of the restricting pin and the piston.

  According to the present invention, by providing the restricting portion, it is possible to suppress the bending moment from being applied to the restricting pin.

  Furthermore, the present invention is characterized by including a pressing member that presses the head of the restriction pin.

  According to the present invention, by providing the pressing member for the restriction pin, it is possible to reliably prevent the restriction pin from coming off and position thereof.

  According to the present invention, when the displacement of the piston is restricted by the restriction pin, it is possible to suppress the transmission of the load from the restriction pin to the cylinder body and to prevent the deformation of the piston sliding surface of the cylinder body. An electric brake device can be obtained.

1 is a schematic configuration diagram of a vehicle brake system in which an electric brake device according to an embodiment of the present invention is incorporated. It is a perspective view of the electric brake device shown in FIG. It is a disassembled perspective view of a cylinder mechanism. (A) is a partially omitted enlarged longitudinal sectional view showing a state in which the first slave piston housed in the cylinder body is regulated at a retracted position by a regulating pin, and (b) is a partially enlarged longitudinal section of (a). A front view and (c) are front views of the regulation pin shown in (a). (A) is a partially omitted enlarged longitudinal sectional view showing a state in which the first slave piston is regulated at a retracted position by a regulating pin according to a modification, (b) is a partially enlarged longitudinal sectional view of (a), (C) is a front view of the regulation pin concerning a modification. (A) is a partially omitted enlarged longitudinal sectional view showing a state in which the first slave piston is regulated at a retracted position by a cylindrical regulating pin, (b) is a partially enlarged longitudinal sectional view of (a), c) is a front view of a cylindrical regulation pin. (A) shows the 1st example of incorrect assembly prevention of a regulation pin, a partially abbreviated enlarged vertical sectional view in the state where a regulation pin was assembled to a cylinder body, and (b) are shown in (a). It is a front view of a control pin. (A) shows the 2nd example of prevention of incorrect assembly of a regulation pin, a partially omitted enlarged vertical sectional view of a state where the regulation pin is assembled to the cylinder body, (b) is shown in (a). It is a front view of a control pin. (A) shows the 3rd example of prevention of incorrect assembly of a regulation pin, a partially omitted enlarged vertical sectional view of a state where the regulation pin is assembled to the cylinder body, (b) is shown in (a). It is a front view of a control pin.

  Next, embodiments of the present invention will be described in detail with reference to the drawings as appropriate. FIG. 1 is a schematic configuration diagram of a vehicle brake system in which an electric brake device according to an embodiment of the present invention is incorporated.

  The vehicle brake system 10 shown in FIG. 1 transmits a hydraulic signal to a by-wire type brake system that transmits an electrical signal to operate the brake for normal use and a fail-safe type for use. It is configured with both of the traditional hydraulic brake systems that actuate the brakes.

  For this reason, as shown in FIG. 1, the vehicle brake system 10 basically includes an input device 14 that inputs an operation when the brake pedal 12 is operated by an operator, and an electric motor that controls the brake fluid pressure. The brake device 16 and a vehicle stability assist device 18 (hereinafter referred to as VSA device 18; VSA; registered trademark) that assists stabilization of vehicle behavior are provided separately.

  These input device 14, electric brake device 16, and VSA device 18 are connected by, for example, a hydraulic path formed of a tube material such as a hose or a tube, and are input as a by-wire type brake system. The device 14 and the electric brake device 16 are electrically connected by a harness (not shown).

  Among these, the hydraulic path will be described. The connection port 20a of the input device 14 and the connection point A1 are connected by the first piping tube 22a with reference to the connection point A1 in FIG. The output port 24a and the connection point A1 are connected by the second piping tube 22b, and the introduction port 26a of the VSA device 18 and the connection point A1 are connected by the third piping tube 22c.

  With reference to the other connection point A2 in FIG. 1, the other connection port 20b of the input device 14 and the connection point A2 are connected by the fourth piping tube 22d, and the other output port 24b of the electric brake device 16 is connected. The connection point A2 is connected by the fifth piping tube 22e, and the other introduction port 26b of the VSA device 18 and the connection point A2 are connected by the sixth piping tube 22f.

  The VSA device 18 is provided with a plurality of outlet ports 28a to 28d. The first outlet port 28a is connected to a wheel cylinder 32FR of the disc brake mechanism 30a provided on the right front wheel by a seventh piping tube 22g. The second outlet port 28b is connected to the wheel cylinder 32RL of the disc brake mechanism 30b provided on the left rear wheel by the eighth piping tube 22h. The third outlet port 28c is connected to the wheel cylinder 32RR of the disc brake mechanism 30c provided on the right rear wheel by the ninth piping tube 22i. The fourth outlet port 28d is connected to the wheel cylinder 32FL of the disc brake mechanism 30d provided on the left front wheel by the tenth piping tube 22j.

  In this case, the brake fluid is supplied to the wheel cylinders 32FR, 32RL, 32RR, 32FL of the disc brake mechanisms 30a-30d by the piping tubes 22g-22j connected to the outlet ports 28a-28d, and the wheel cylinders 32FR, The wheel cylinders 32FR, 32RL, 32RR, and 32FL are operated by increasing the hydraulic pressure in the 32RL, 32RR, and 32FL, and corresponding wheels (right front wheel, left rear wheel, right rear wheel, left front wheel) A braking force is applied.

  The vehicle brake system 10 is provided so as to be mountable on various vehicles including, for example, an automobile driven only by an engine (internal combustion engine), a hybrid automobile, an electric automobile, and a fuel cell automobile.

  The input device 14 includes a tandem master cylinder 34 that can generate hydraulic pressure by operating the brake pedal 12 by a driver (operator), and a first reservoir 36 attached to the master cylinder 34. In the cylinder tube 38 of the master cylinder 34, two pistons 40a and 40b spaced apart from each other by a predetermined distance along the axial direction of the cylinder tube 38 are slidably disposed. One piston 40 a is disposed in the vicinity of the brake pedal 12, is connected to the brake pedal 12 via the push rod 42, and is directly moved. Further, the other piston 40b is arranged farther from the brake pedal 12 than the one piston 40a.

  A pair of cup seals 44a and 44b are respectively attached to the outer peripheral surfaces of the one and the other pistons 40a and 40b via annular step portions. Back chambers 48a and 48b communicating with supply ports 46a and 46b, which will be described later, are formed between the pair of cup seals 44a and 44b, respectively. A spring member 50a is disposed between the one and the other pistons 40a and 40b, and another spring member 50b is disposed between the other piston 40b and the side end of the cylinder tube 38. The The pair of cup seals 44a and 44b may be mounted on the inner wall side of the cylinder tube 38 via an annular groove.

  The cylinder tube 38 of the master cylinder 34 is provided with two supply ports 46a and 46b, two relief ports 52a and 52b, and two output ports 54a and 54b. In this case, each supply port 46a (46b) and each relief port 52a (52b) are provided so as to join and communicate with a reservoir chamber (not shown) in the first reservoir 36, respectively.

  Further, in the cylinder tube 38 of the master cylinder 34, a first pressure chamber 56b and a second pressure chamber 56a for generating a brake fluid pressure corresponding to the depression force of the driver depressing the brake pedal 12 are provided. The first pressure chamber 56b is provided so as to communicate with the connection port 20b via the first hydraulic pressure path 58b, and the second pressure chamber 56a is communicated with the connection port 20a via the second hydraulic pressure path 58a. Is provided.

  A first shut-off valve 60b composed of a normally open type (normally open type) solenoid valve is provided between the master cylinder 34 and the connection port 20b and upstream of the first hydraulic pressure path 58b. A pressure sensor Pp is provided on the downstream side of the one hydraulic pressure path 58b. The pressure sensor Pp detects the downstream hydraulic pressure on the first hydraulic pressure path 58b, which is on the side of the wheel cylinders 32FR, 32RL, 32RR, 32FL with respect to the first shutoff valve 60b.

  A pressure sensor Pm is disposed between the master cylinder 34 and the connection port 20a upstream of the second hydraulic pressure path 58a, and a normally open type is provided downstream of the second hydraulic pressure path 58a. A second shut-off valve 60a composed of a (normally open) solenoid valve is provided. The pressure sensor Pm detects the upstream hydraulic pressure on the master cylinder 34 side of the second shutoff valve 60a on the second hydraulic pressure path 58a.

  The normal open in the first shut-off valve 60b and the second shut-off valve 60a is a valve configured so that the normal position (the position of the valve body when not energized) is in the open position (normally open). Say. In FIG. 1, the first shut-off valve 60 b and the second shut-off valve 60 a respectively show valve closed states in which solenoids are energized and valve bodies (not shown) are activated.

  A branch hydraulic pressure path 58c branched from the first hydraulic pressure path 58b is provided in the first hydraulic pressure path 58b between the master cylinder 34 and the first shutoff valve 60b, and the branched hydraulic pressure path 58c includes A third shut-off valve 62 composed of a normally closed type (normally closed type) solenoid valve and a stroke simulator 64 are connected in series. The normal close in the third shut-off valve 62 refers to a valve configured such that the normal position (the position of the valve body when not energized) is in the closed position (normally closed). In FIG. 1, the third shut-off valve 62 shows a valve open state in which a solenoid (not shown) is actuated by energizing a solenoid.

  The stroke simulator 64 is a device that generates a braking stroke and a reaction force at the time of by-wire control and makes the operator think as if a braking force is generated by a pedaling force, and the first hydraulic pressure path 58b. It is above and it is arrange | positioned rather than the 1st cutoff valve 60b at the master cylinder 34 side. The stroke simulator 64 is provided with a hydraulic pressure chamber 65 communicating with the branch hydraulic pressure path 58c, and brake fluid (brake fluid) led out from the first pressure chamber 56b of the master cylinder 34 via the hydraulic pressure chamber 65 is provided. ) Is provided so as to be absorbable.

  The stroke simulator 64 is a simulator that is urged by a first return spring 66a having a high spring constant, a second return spring 66b having a low spring constant, and the first and second return springs 66a and 66b arranged in series. A piston 68 is provided, and the pedal feeling of the brake pedal 12 is provided to be equivalent to that of an existing master cylinder.

  The hydraulic pressure path is roughly divided into a first hydraulic pressure system 70b that connects the first pressure chamber 56b of the master cylinder 34 and the plurality of wheel cylinders 32RR and 32FL, a second pressure chamber 56a of the master cylinder 34, and a plurality of pressure paths. The second hydraulic system 70a is connected to the wheel cylinders 32FR and 32RL.

  The first hydraulic system 70b includes a first hydraulic path 58b that connects the output port 54b of the master cylinder 34 (cylinder tube 38) and the connection port 20b in the input device 14, a connection port 20b of the input device 14, and an electric brake. Piping tubes 22d and 22e connecting the output port 24b of the device 16, piping tubes 22e and 22f connecting the output port 24b of the electric brake device 16 and the introduction port 26b of the VSA device 18, and a lead-out port of the VSA device 18 28c and 28d and pipe tubes 22i and 22j for connecting the wheel cylinders 32RR and 32FL, respectively.

  The second hydraulic system 70a includes a second hydraulic path 58a that connects the output port 54a of the master cylinder 34 (cylinder tube 38) and the connection port 20a in the input device 14, and the connection port 20a of the input device 14 and the electric brake. Piping tubes 22a, 22b connecting the output port 24a of the device 16, piping tubes 22b, 22c connecting the output port 24a of the electric brake device 16 and the introduction port 26a of the VSA device 18, and a lead-out port of the VSA device 18 The pipe tubes 22g and 22h connect the wheel cylinders 32FR and 32RL to the wheel cylinders 32FR and 32RL, respectively.

  As a result, the hydraulic pressure path is constituted by the first hydraulic system 70b and the second hydraulic system 70a, so that the wheel cylinders 32RR and 32FL and the wheel cylinders 32FR and 32RL are independently operated, Mutually independent braking forces can be generated.

FIG. 2 is a perspective view of the electric brake device shown in FIG.
As shown in FIG. 2, the electric brake device 16 includes an actuator mechanism 74 having an electric motor 72 and a driving force transmission unit 73, and a cylinder mechanism 76 biased by the actuator mechanism 74. In this case, the electric motor 72, the driving force transmission unit 73, and the cylinder mechanism 76 are provided so as to be separable.

  In addition, the driving force transmission unit 73 of the actuator mechanism 74 includes a gear mechanism (deceleration mechanism) 78 (see FIG. 1) that transmits the rotational driving force of the electric motor 72, and linear motion (axis in the linear direction). Force) and a ball screw structure (conversion mechanism) 80 (see FIG. 1) that transmits to the first and second slave pistons 88b and 88a, which will be described later.

  The electric motor 72 is driven and controlled based on a control signal (electric signal) from a control means (not shown), for example, a servo motor, and is disposed above the actuator mechanism 74. By arranging and configuring in this way, it is possible to suitably avoid oil components such as grease in the driving force transmission unit 73 from entering the electric motor 72 due to gravity. The electric motor 72 is fastened to an actuator housing 75 to be described later via a screw member.

  The driving force transmission unit 73 includes an actuator housing 75, and a driving force transmission machine such as a gear mechanism (deceleration mechanism) 78 and a ball screw structure (conversion mechanism) 80 is provided in a space in the actuator housing 75. The element is stored. As shown in FIG. 2, the actuator housing 75 includes a first body 75a disposed on the cylinder mechanism 76 side, and a second body 75b that closes the opening end of the first body 75a opposite to the cylinder mechanism 76. It is divided by.

  As shown in FIG. 2, a flange portion 79 is provided at the end of the first body 75a on the cylinder mechanism 76 side, and a pair of screw holes (not shown) for attaching the cylinder mechanism 76 to the flange portion 79 are provided. Is provided. In this case, a pair of screw members 81a penetrating a flange portion 82a provided at the other end of the cylinder body 82, which will be described later, are screwed into the screw holes, whereby the cylinder mechanism 76 and the driving force transmitting portion 73 are Are integrally coupled.

  As shown in FIG. 1, the ball screw structure 80 is formed on one end along the axial direction on a ball screw shaft 80a that abuts on the second slave piston 88a of the cylinder mechanism 76, and on the outer peripheral surface of the ball screw shaft 80a. A plurality of balls 80b that roll along the spiral thread groove formed, and a substantially cylindrical shape that is fitted in a ring gear of the gear mechanism 78, rotates integrally with the ring gear, and is screwed into the ball 80b. And a pair of ball bearings 80d rotatably supporting one end side and the other end side along the axial direction of the nut member 80c. The nut member 80c is, for example, press-fitted and fixed to the inner diameter surface of the ring gear of the gear mechanism 78.

  By configuring the driving force transmitting portion 73 in this way, after the rotational driving force of the electric motor 72 transmitted via the gear mechanism 78 is input to the nut member 80c, the driving force transmitting portion 73 is linearly moved by the ball screw structure 80. The axial force (linear motion) of the ball screw shaft 80a is moved back and forth along the axial direction.

  FIG. 3 is an exploded perspective view of the cylinder mechanism, and FIG. 4A is a partially omitted enlarged longitudinal sectional view showing a state in which the first slave piston housed in the cylinder body is regulated at the retracted position by the regulation pin. 4 (b) is a partially enlarged longitudinal sectional view of FIG. 4 (a), and FIG. 4 (c) is a front view of the regulating pin shown in FIG. 4 (a).

  The electric brake device 16 transmits the driving force of the electric motor 72 to the first slave piston 88b and the second slave piston 88a of the cylinder mechanism 76 via the driving force transmission unit 73, and the first slave piston 88b and the second slave piston 88b. The brake fluid pressure is generated by driving the slave piston 88a forward. In the following description, the displacement of the first slave piston 88b and the second slave piston 88a in the direction of the arrow X1 will be referred to as “forward”, and the displacement in the direction of the arrow X2 will be described as “backward”. An arrow X1 indicates “front”, and an arrow X2 indicates “rear”.

  As shown in FIG. 3, the cylinder mechanism 76 includes a first piston mechanism 77a configured by integrally assembling peripheral components including the first slave piston 88b, and a peripheral component including the second slave piston 88a. And a second piston mechanism 77b configured to be assembled to. The first piston mechanism 77a and the second piston mechanism 77b are configured to be integrally assembled via a connecting pin 79 described later. In the present embodiment, the cylinder mechanism 76 is described as a tandem type using two pistons including the first slave piston 88b and the second slave piston 88a. However, the present invention is not limited to this. For example, Alternatively, only a single first slave piston 88b may be used.

  The first piston mechanism 77a is disposed so as to face the first hydraulic chamber 98b (see FIG. 1) in front of the bottomed cylindrical cylinder body 82, and the inner peripheral wall (piston sliding surface) of the cylinder body 82. The first slave piston 88b slidably provided along the cylinder 83 and the first slave piston 88b fixed to the cylinder body 82 and abutting against a first flange portion 200a or a second flange portion 200b to be described later of the first slave piston 88b. A restriction pin (restricting means) 102 for restricting the movement range of the first slave piston 88b, a pair of cup seals 90a and 90b attached to the annular step portion of the first slave piston 88b, the first slave piston 88b and the cylinder body 82 1st spring which is arrange | positioned between the side edge part (bottom wall) of this, and presses the 1st slave piston 88b toward back (arrow X2). With a 6b.

  For example, when the hydraulic pressure derived from the first pressure chamber (external) 56b of the master cylinder 34 is applied to the first hydraulic chamber (output hydraulic chamber) 98b, the regulating pin 102 is a first slave piston. It functions as a regulating means for regulating the backward movement of 88b.

  As shown in FIG. 4C, an annular first groove portion that is gradually reduced in diameter from both sides in the axial direction and is recessed on the outer surface on the upper end side (one end side) along the axial direction of the regulation pin 102. 202a is formed. Further, on the lower end side (the other end side) along the axial direction of the regulation pin 102, similarly to the first groove portion 202a, an annular second groove portion 202b that is gradually reduced in diameter from both sides in the axial direction and recessed. Is formed. The first groove portion 202a and the second groove portion 202b function as reduced diameter portions obtained by reducing the outer diameter of the regulation pin 102 in a portion corresponding to the inner peripheral wall 83 of the cylinder body 82.

  The first groove 202a and the second groove 202b formed on the outer surface of the restriction pin 102 are orthogonal to the inner peripheral wall 83 of the cylinder main body 88 at a portion where the restriction pin 102 is fixed orthogonal to the axial direction of the cylinder main body 82. It is formed so as to overlap in the radial direction, and a gap 204 (clearance) is formed between the first groove 202 a and the second groove 202 b and the inner peripheral wall 83 of the cylinder body 82.

  By providing the gap 204, the inner peripheral wall 83 (piston sliding surface) of the cylinder body 82 is prevented from being deformed by the load applied to the restriction pin 102 due to the contact between the first slave piston 88b and the restriction pin 102. can do. This is because the load transmission point A transmitted to the cylinder body 82 side can be separated from the effective inner diameter B of the cylinder body 82 to a position radially outside. In FIG. 4A, a point C indicates a load transmission point at which a load is transmitted to the cylinder body 82 by the restriction pin when a conventionally used cylindrical restriction pin is used. .

  Further, as shown in FIG. 4A, in the insertion direction of the restriction pin 102 with respect to the cylinder body 82, the axial length T1 of the support portion of the restriction pin 102 supported by the cylinder body 82 is the axis of the gap 204. It is set larger than the direction length T2 (T1> T2). As described above, by setting the axial length T1 of the support portion to be larger than the axial length T2 of the gap 204 (T1> T2), a desired support strength of the regulation pin 102 can be ensured.

  FIG. 5A is a partially omitted enlarged longitudinal sectional view showing a state in which the first slave piston is regulated at the retracted position by the regulation pin according to the modification, and FIG. 5B is a diagram of FIG. A partially enlarged longitudinal sectional view, FIG. 5C, is a front view of a regulation pin according to a modification.

  As shown in FIG.5 (c), the regulation pin 102a which concerns on a modification is formed in the outer surface of the upper end part side (one end part side) along an axial direction, and the 1st taper part 210a which is gradually diameter-reduced, An axial direction formed between the second taper portion 210b formed on the lower end side (the other end portion side) along the axial direction and gradually reducing the diameter, and between the first taper portion 210a and the second taper portion 210b. A groove portion 212 is formed by a reduced diameter intermediate portion 210c having a constant outer diameter along the outer periphery.

  The groove portion 212 functions as a reduced diameter portion obtained by reducing the outer diameter of the restriction pin 102 a in a portion corresponding to the inner peripheral wall 83 of the cylinder body 82. The reduced diameter portion is not limited to the groove portion, and may be any one of a groove, a taper, an overall reduced diameter, or a composite shape thereof.

  In this case, the groove portion 212 formed on the outer surface of the restriction pin 102a according to the modification is perpendicular to the inner peripheral wall 83 of the cylinder body 88 at a portion where the restriction pin 102a is fixed perpendicular to the axial direction of the cylinder body 82. It is formed so as to overlap in the radial direction, and a gap 204 (clearance) is formed between the groove 212 and the inner peripheral wall 83 of the cylinder body 82.

  In this way, by forming the reduced diameter portion including the first groove portion 202a, the second groove portion 202b, and the groove portion 212 on the outer surface of the restriction pins 102 and 102a, the outer surface of the restriction pins 102 and 102a is connected to the cylinder body via the gap 204. The inner peripheral wall 83 of the 82 can be separated. In this case, it is not necessary to process the inner peripheral wall 83 of the cylinder body 82, and the manufacturing cost can be reduced.

  FIG. 6 shows an example in which the gap 204 is formed by processing the inner peripheral wall 83 of the cylinder body 82 using the regulation pin 102b made of a normal cylindrical body.

  6A is a partially omitted enlarged longitudinal sectional view showing a state in which the first slave piston is regulated at the retracted position by the cylindrical regulation pin, and FIG. 6B is a part of FIG. 6A. FIG. 6C is an enlarged longitudinal sectional view, and FIG. 6C is a front view of a cylindrical regulation pin.

  As shown in FIG. 6, an annular tapered surface 214 is formed at an opening portion of the locking hole 208 of the cylinder body 82 that supports the restriction pin 102 b and is inclined by a predetermined angle about the axis of the restriction pin 102 b. A gap 204 is formed between the annular tapered surface 214 formed on the inner peripheral wall 83 of the cylinder body 82 and the outer peripheral surface of the regulating pin 102b made of a cylindrical body. The annular tapered surface 214 functions as a diameter-expanded portion that is a diameter-expanded portion of the inner peripheral wall 83 of the cylinder body 82 on which the restriction pin 102b is supported.

  By providing the gap 204 as shown in FIGS. 5 and 6, the first slave piston 88b and the restriction pins 102a and 102b come into contact with each other, and the load applied to the restriction pins 102a and 102b causes the inside of the cylinder main body 82 to move. It is possible to suppress deformation of the peripheral wall 83 (piston sliding surface). In this case, the load transmission point A transmitted to the cylinder body 82 side can be separated from the effective inner diameter B of the cylinder body 82 to a position radially outside.

  Returning to FIG. 3, the restriction pin 102 is inserted and fixed in a direction orthogonal to the axial direction of the cylinder body 82. That is, when the restriction pin 102 is assembled to the cylinder body 82, the fixing pin 207 is inserted through the opening of the reservoir port 92b and formed in a direction perpendicular to the axial direction of the cylinder body 82, The upper and lower end portions of the restriction pin 102 are inserted and fixed in the lower-side locking holes 208 (see FIG. 4A). As a result, in this embodiment, the contact length between the cylinder body 82 and the regulation pin 102 can be extended via the upper fixing hole 207 and the lower locking hole 208. The restriction pin 102 may be fixed by being press-fitted into the locking hole 208 of the cylinder body 82.

  Further, the upper end portion (head portion) of the restriction pin 102 is brought into contact with a connecting leg portion 85 a provided on the lower surface of the reservoir body 85 of the second reservoir 84 to be prevented from coming off. In this case, the second reservoir 84 functions as a pressing member that presses the head of the restriction pin 102 and can reliably prevent the restriction pin 102 from coming off and position thereof. For example, a clearance is provided between the connecting leg 85a and the upper end of the restricting pin 102, and when the restricting pin 102 is displaced upward, the upper end of the restricting pin 102 abuts on the connecting leg 85a. You may make it exhibit a retaining effect.

  As shown in FIG. 3, the first slave piston 88 b has a piston body 109, and a pair of annular first flange portions 200 a having a diameter larger than that of the piston body 109 and the front and rear of the piston body 109 and The second flange portion 200b is formed with a predetermined distance.

  A through hole 91 that penetrates in a direction orthogonal to the axial direction of the first slave piston 88b is formed between the first flange portion 200a and the second flange portion 200b, and the restriction pin 102 is formed in the through hole 91. Is inserted from a direction orthogonal to the axial direction of the cylinder body 82. As shown in FIG. 4A, the through hole 91 is formed so as to extend from the first flange portion 200a to the second flange portion 200b along the axial direction of the first slave piston 88b. .

  The first flange portion 200a is formed with a restricting portion 206 that contacts the restricting pin 102 at the retracted position (retreat stroke end) of the first slave piston 88b. The restricting portion 206 is provided so as to extend in a direction orthogonal to the axial direction of the piston main body 109 continuously from the through hole 91 (see FIG. 4A).

  The displacement end position (advance stroke end) on the forward side of the first slave piston 88b is determined by the fact that the tip diameter-reduced portion along the axial direction of the first slave piston 88b contacts the bottom (inner wall) of the cylinder body 82. Be regulated.

  The restriction portion 206 that comes into contact with the restriction pin 102 fixed to the cylinder body 82 is provided on the outer peripheral side of the first slave piston 88b with respect to the piston body 109 by being formed in the first flange portion 200a.

  As shown in FIG. 4A, the restricting portion 206 is formed on each of the upper and lower sides of the first flange portion 200 a with the through hole 91 therebetween, and includes the through hole 91 and includes the restricting pin 102. A contact surface is formed.

  Thus, in the present embodiment, the restriction pin 102 is provided so as to contact not only the through hole 91 of the piston main body 109 but also the restriction portion 206 of the first flange portion 200a. The first slave piston 88b is compared with a case where only 109 is not in contact with a through hole (not shown) formed in a length that does not reach the first flange portion 200a. It is possible to extend the contact length between the control pin 102 and the restriction pin 102.

  In other words, in addition to the through hole 91 of the piston main body 109, the restricting portion 206 of the first flange portion 200a that protrudes radially outward from the piston main body 109 is added as a contact surface of the restriction pin 102 with respect to the first slave piston 88b. Therefore, the contact length between the first slave piston 88b and the regulating pin 102 can be extended by this addition.

  In addition, since the restriction pin 102 is provided so as to contact the restriction portion 206 of the first flange portion 200a, the bending moment applied to the restriction pin 102 can be suppressed.

  An insertion hole 93 into which the connecting pin 79 is inserted is formed behind the first slave piston 88b in a state where a cylindrical portion 105a of the connecting piston 105 to be described later is fitted.

  As shown in FIG. 3, the second piston mechanism 77b includes a second slave piston 88a disposed to face the second hydraulic chamber 98a behind the first slave piston 88b (in the direction of the arrow X2), and the first slave piston 88a. A cup seal 90c mounted on the shaft portion in front of the two slave pistons 88a, and disposed between the first slave piston 88b and the second slave piston 88a, and the first slave piston 88b and the second slave piston 88a And a second spring 96a biased in the direction of separation. The guide piston 103 shown in FIG. 3 is assembled after the first piston mechanism 77a and the second piston mechanism 77b are assembled, and seals the outer peripheral surface of the rod portion 89a behind the second slave piston 88a. A function of guiding the slave piston 88a linearly is exhibited.

  Further, the second piston mechanism 77b includes a bolt member 100 that regulates a separation position between the first slave piston 88b and the second slave piston 88a, a connecting piston 105 that is connected to the first slave piston 88b by a connecting pin 79, A part of a starting end and a terminal end overlapping each other in an arc shape is provided so that the diameter can be increased, and an annular clip 107 that holds the connecting pin 79 by its elastic force is provided.

  A mounting hole 89c in which one end 100b of the bolt member 100 is mounted is formed in the front shaft portion of the second slave piston 88a, and a ball screw shaft 80a is formed in the rod portion 89a behind the second slave piston 88a. An insertion hole 89b with which one end of the abutment is in contact is formed.

  As shown in FIG. 3, the connecting piston 105 is provided at a front portion along the axial direction, and a cylindrical portion 105 a that is fitted on the rear shaft portion of the first slave piston 88 b, and an axial direction of the cylindrical portion 105 a An insertion hole 105b through which the connecting pin 79 is inserted in a direction perpendicular to the mounting hole, a mounting groove 105c formed on the outer peripheral surface of the cylindrical portion 105a and mounted with the annular clip 107, and an axial direction of the cylindrical portion 105a And an engagement portion 105d formed with an engagement hole which is provided at the rear and engages with the head portion 100a of the bolt member 100.

  The second slave piston 88a is disposed in the vicinity of the ball screw structure 80, contacts the one end of the ball screw shaft 80a through the insertion hole 89b, and is integrated with the ball screw shaft 80a by the arrow X1. It is provided so as to be displaced in the direction or arrow X2. The first slave piston 88b is disposed at a position farther from the ball screw structure 80 side than the second slave piston 88a.

  On the outer peripheral surfaces of the first and second slave pistons 88b and 88b, there are formed a first back chamber 94a and a second back chamber 94b respectively communicating with reservoir ports 92a and 92b described later (see FIG. 1). .

  The cylinder body 82 of the cylinder mechanism 76 is provided with two reservoir ports 92a and 92b, two output ports 24a and 24b, and a pin insertion hole 95 into which the locking pin 97 is inserted. In this case, the reservoir port 92a (92b) is provided so as to communicate with a reservoir chamber (not shown) in the second reservoir 84.

  The cylinder mechanism (cylinder) 76 includes a second reservoir 84 attached to the cylinder body 82. The second reservoir 84 is connected to the first reservoir 36 attached to the master cylinder 34 of the input device 14 by a piping tube 86, and the brake fluid stored in the first reservoir 36 is passed through the piping tube 86 to the second reservoir 84. 84 (see FIG. 1).

  As shown in FIG. 3, the second reservoir 84 has a reservoir main body 85, and a pair of connecting legs 85 a connected to the reservoir ports 92 a and 92 b of the cylinder main body 85 on the lower surface of the reservoir main body 85. 85b (see FIG. 5) and a pair of mounting projections 89a and 89b (see FIG. 3 for mounting) that are arranged opposite to each other on both sides and are formed with insertion holes 111 through which the locking pins 97 are inserted. (Not shown for the projection 89b for use). Ring-shaped seal members 99 are mounted on the outer peripheral surfaces of the pair of connecting legs 85 a and 85 b, respectively. The seal members 99 are used for connecting the reservoir ports 92 a and 92 b of the cylinder body 82 and the second reservoir 84. The connecting portion with the leg portions 85a and 85b is sealed.

  In a state where the pair of connecting legs 85a and 85b of the second reservoir 84 to which the seal member 99 is attached is inserted into the pair of reservoir ports 92a and 92b of the cylinder body 82 and the second reservoir 84 is pressed from above, the reservoir Locking pins 97 are respectively inserted into the insertion holes 111 of one connecting projection 89a of the body 85, the pin insertion holes 95 of the cylinder body 82, and the insertion holes 111 of the other connecting protrusion 89b of the reservoir body 85. By inserting, the second reservoir 84 is integrally assembled to the cylinder body 82.

  In this case, the ring-shaped seal member 99 is formed of, for example, an elastic material such as rubber and exhibits a retaining function. By inserting the locking pin 97 into the pin insertion hole 95, the second reservoir 84 is inserted into the cylinder. The main body 82 can be easily assembled.

  Further, in the cylinder body 82, a first hydraulic pressure chamber (output hydraulic pressure chamber) 98b for controlling the brake hydraulic pressure output from the output port 24b to the wheel cylinders 32RR and 32FL side, and the wheel cylinder 32FR from the output port 24a. , A second hydraulic pressure chamber 98a for controlling the brake hydraulic pressure output to the 32RL side is provided.

  Between the first slave piston 88b and the second slave piston 88a, there is provided a bolt member 100 that regulates the maximum separation position and the minimum separation position between the first slave piston 88b and the second slave piston 88a. The first slave piston 88b engages with a through-hole 91 that penetrates in a direction substantially orthogonal to the axis of the first slave piston 88b, restricts the sliding range of the first slave piston 88b, and A restriction pin 102 is provided to prevent overreturn to the piston 88a side. These prevent the failure of other systems when one system fails, particularly during backup when braking with the brake fluid pressure generated in the master cylinder 34.

  Further, as shown in FIG. 3, a guide piston 103 is attached to the opening of the cylinder body 82 via a circlip (not shown). A seal member 103a that surrounds and seals the outer peripheral surface of the rod portion 89a of the second slave piston 88a is provided on the inner peripheral surface of the guide piston 103, and the rod of the second slave piston 88a extends along the seal member 103a. By sliding the portion 89a, the second slave piston 88a contacting the one end portion of the ball screw shaft 80a can be guided linearly. Further, the connecting piston 105 is connected to the first slave piston 88b, and the connecting piston 105 is provided with an engaging portion with which the head portion 100a of the bolt member 100 is engaged.

  Returning to FIG. 1, the VSA device 18 is a well-known one, and includes a first hydraulic system 70b connected to the disc brake mechanisms 30c, 30d (the wheel cylinder 32RR, the wheel cylinder 32FL) of the right rear wheel and the left front wheel. A first brake system 110b for controlling, and a second brake system 110a for controlling a second hydraulic system 70a connected to the disc brake mechanisms 30a and 30b (the wheel cylinder 32FR and the wheel cylinder 32RL) of the right front wheel and the left rear wheel. Have

  The second brake system 110a is composed of a hydraulic system connected to a disc brake mechanism provided on the left front wheel and the right front wheel, and the first brake system 110b is a disc provided on the left rear wheel and the left rear wheel. A hydraulic system connected to the brake mechanism may be used. Further, the second brake system 110a includes a hydraulic system connected to a disc brake mechanism provided on the right front wheel and the right rear wheel on one side of the vehicle body, and the first brake system 110b includes the left front wheel and the left rear wheel on the vehicle body side. A hydraulic system connected to a disc brake mechanism provided on the wheel may be used.

  Since the first brake system 110b and the second brake system 110a have the same structure, the corresponding parts in the first brake system 110b and the second brake system 110a are assigned the same reference numerals, and The description of the first brake system 110b will be added in parentheses with a focus on the description of the two brake system 110a.

  The second brake system 110a (first brake system 110b) has a first common hydraulic pressure path 112 and a second common hydraulic pressure path 114 that are common to the wheel cylinders 32FR, 32RL (32RR, 32FL). The VSA device 18 includes a regulator valve 116 formed of a normally open type solenoid valve disposed between the introduction port 26a and the first common hydraulic pressure path 112, and arranged in parallel with the regulator valve 116 from the introduction port 26a side. A first check valve 118 that permits the flow of brake fluid to the first common hydraulic pressure passage 112 side (blocks the flow of brake fluid from the first common hydraulic pressure passage 112 side to the introduction port 26a side); A first in-valve 120 composed of a normally open type solenoid valve disposed between the common hydraulic pressure path 112 and the first outlet port 28a, and a first inlet valve 120 disposed in parallel with the first inlet valve 120 from the first outlet port 28a side. Allow the brake fluid to flow to the first common hydraulic pressure passage 112 side (from the first common hydraulic pressure passage 112 side to the first outlet port) A second in-valve comprising a second check valve 122 (which prevents the flow of brake fluid to the 8a side) and a normally open type solenoid valve disposed between the first common hydraulic pressure passage 112 and the second outlet port 28b. 124 and the second inlet valve 124 are arranged in parallel to allow the brake fluid to flow from the second lead-out port 28b side to the first common hydraulic pressure path 112 side (second lead-out from the first common hydraulic pressure path 112 side). And a third check valve 126 for inhibiting the flow of brake fluid to the port 28b side.

  Further, the VSA device 18 includes a first out valve 128 including a normally closed solenoid valve disposed between the first outlet port 28a and the second common hydraulic pressure path 114, a second outlet port 28b, and a second outlet port 28b. A second out valve 130 composed of a normally closed solenoid valve disposed between the common hydraulic pressure path 114, a reservoir 132 connected to the second common hydraulic pressure path 114, and a first common hydraulic pressure path 112; It is arranged between the second common hydraulic pressure path 114 and allows the brake fluid to flow from the second common hydraulic pressure path 114 side to the first common hydraulic pressure path 112 side (from the first common hydraulic pressure path 112 side). The fourth check valve 134 (which prevents the flow of brake fluid to the second common hydraulic pressure path 114 side) is disposed between the fourth check valve 134 and the first common hydraulic pressure path 112, and the second common hydraulic pressure path 112 is disposed. A pump 136 that supplies brake fluid from the hydraulic pressure path 114 side to the first common hydraulic pressure path 112 side, an intake valve 138 and a discharge valve 140 provided before and after the pump 136, and a motor M that drives the pump 136, And a suction valve 142 formed of a normally closed solenoid valve disposed between the second common hydraulic pressure path 114 and the introduction port 26a.

  In the second brake system 110a, the brake output from the output port 24a of the electric brake device 16 and controlled by the second hydraulic chamber 98a of the electric brake device 16 is provided on the hydraulic pressure path close to the introduction port 26a. A pressure sensor Ph for detecting the hydraulic pressure is provided. Detection signals detected by the pressure sensors Pm, Pp, and Ph are introduced into control means (not shown). The VSA device 18 includes ABS control in addition to VSA control.

  The vehicle brake system 10 incorporating the electric brake device 16 according to the present embodiment is basically configured as described above. Next, the function and effect will be described.

  When the vehicle brake system 10 functions normally, the first shut-off valve 60b and the second shut-off valve 60a, which are normally open type solenoid valves, are energized by energization to be closed, and the normal close type solenoid valves are used. The third shut-off valve 62 is excited by energization to enter a valve open state. Accordingly, since the first hydraulic system 70b and the second hydraulic system 70a are shut off by the first shut-off valve 60b and the second shut-off valve 60a, the brake hydraulic pressure generated in the master cylinder 34 of the input device 14 is applied to the disc brake. There is no transmission to the wheel cylinders 32FR, 32RL, 32RR, 32FL of the mechanisms 30a-30d.

  At this time, the brake hydraulic pressure generated in the first pressure chamber 56b of the master cylinder 34 is transmitted to the hydraulic pressure chamber 65 of the stroke simulator 64 via the branch hydraulic pressure path 58c and the third shut-off valve 62 in the valve open state. Is done. The simulator piston 68 is displaced against the spring force of the spring members 66a and 66b by the brake hydraulic pressure supplied to the hydraulic pressure chamber 65, so that the stroke of the brake pedal 12 is allowed and a pseudo pedal reaction is achieved. A force is generated and applied to the brake pedal 12. As a result, it is possible to obtain a brake feeling that is comfortable for the driver.

  In such a system state, when the control means (not shown) detects depression of the brake pedal 12 by the driver, the control means drives the electric motor 72 of the electric brake device 16 to urge the actuator mechanism 74, and the first spring 96b and The first slave piston 88b and the second slave piston 88a are displaced (advanced) in the direction of the arrow X1 in FIG. 1 against the spring force of the second spring 96a. Due to the displacement of the first slave piston 88b and the second slave piston 88a, the brake fluid pressure in the first fluid pressure chamber 98b and the second fluid pressure chamber 98a is pressurized to generate a desired brake fluid pressure. .

  The brake hydraulic pressure in the first hydraulic pressure chamber 98b and the second hydraulic pressure chamber 98a in the electric brake device 16 is supplied to the disc brake mechanism 30a via the first and second inlet valves 120 and 124 in the valve open state of the VSA device 18. To 30d wheel cylinders 32FR, 32RL, 32RR, 32FL, and the wheel cylinders 32FR, 32RL, 32RR, 32FL are actuated to apply a desired braking force to each wheel.

  In other words, in the vehicle brake system 10 according to the present embodiment, the driver can operate the brake pedal 12 when the electric brake device 16 that functions as a power hydraulic pressure source, the ECU (not shown) that performs by-wire control, and the like are operable. The first shut-off valve 60b and the second shut-off valve communicate with the master cylinder 34 that generates brake fluid pressure by stepping on and the disc brake mechanisms 30a to 30d (wheel cylinders 32FR, 32RL, 32RR, and 32FL) that brake each wheel. A so-called brake-by-wire brake system is activated in which the disc brake mechanisms 30a to 30d are operated with the brake fluid pressure generated by the electric brake device 16 in the state of being interrupted at 60a.

  On the other hand, when the electric brake device 16 or the like becomes inoperable, the first cutoff valve 60b and the second cutoff valve 60a are opened, and the third cutoff valve 62 is closed, so that the master cylinder 34 The generated brake fluid pressure is transmitted to the disc brake mechanisms 30a to 30d (wheel cylinders 32FR, 32RL, 32RR, and 32FL), and the disc brake mechanisms 30a to 30d (wheel cylinders 32FR, 32RL, 32RR, and 32FL) are operated. The so-called traditional hydraulic brake system becomes active.

  In the present embodiment, for example, when the power supply fails and when the second hydraulic system 70a including the second slave piston 88a fails, the first hydraulic pressure chamber (output hydraulic pressure chamber) 98b of the electric brake device 16 is provided. On the other hand, in order to ensure the minimum brake hydraulic pressure in the wheel cylinders 32FR, 32RL, 32RR, 32FL when the hydraulic pressure derived from the first pressure chamber (external) 56b of the master cylinder 34 acts, the first slave piston A restriction pin 102 for restricting the backward movement of 88b is provided.

  In the present embodiment, a gap 204 (clearance) is formed between the first groove 202a and the second groove 202b formed on the outer surface of the restriction pin 102 and the inner peripheral wall 83 of the cylinder body 82, and the first slave piston 88b Deformation of the inner peripheral wall 83 (piston sliding surface) of the cylinder main body 82 can be suppressed by the load applied to the restriction pin 102 by contacting the restriction pin 102. In this case, the load transmission point A transmitted to the cylinder body 82 side can be separated from the effective inner diameter B of the cylinder body 82 to a position radially outside.

  As described above, in this embodiment, by providing the gap 204 that separates the outer surface of the regulating pin 102 and the inner circumferential wall 83 of the cylinder body 82 in the inner circumferential wall 83 of the cylinder body 82 that supports the regulating pin 102, load transmission is performed. The point A can be spaced radially outward from the effective inner diameter B of the cylinder body 82 (see FIG. 4A), and deformation of the inner peripheral wall 83 of the cylinder body 82 can be suppressed. As a result, in the present embodiment, desired sliding performance on the piston sliding surface of the cylinder body 82 can be ensured.

  Further, in the present embodiment, the restriction pin 102 is provided so as to contact not only the through hole 91 of the piston main body 109 but also the restriction portion 206 of the first flange portion 200a, whereby the restriction pin 102 of the piston main body 109 is provided. Compared with a case where only a through hole (not shown) formed through a not-shown through-hole (a through-hole formed in a length that does not reach the first flange portion 200a), the first slave piston 88b is restricted. The contact length with the pin 102 can be extended.

  Further, in the present embodiment, the restriction pin 102 is an upper fixing hole 207 and a lower locking hole 208 of the cylinder body 82 formed in a direction orthogonal to the axial direction of the cylinder body 82, and the restriction pin 102. Since the upper and lower end portions of the cylinder are inserted and fixed, the contact length between the cylinder body 82 and the regulation pin 102 can be extended through the upper fixing hole 207 and the lower locking hole 208. In this case, the load applied to the regulation pin 102 can be dispersedly supported at two points including the upper fixing hole 207 and the lower locking hole 208.

  Furthermore, in the present embodiment, the axial length T1 of the support portion of the restriction pin 102 supported by the cylinder body 82 in the insertion direction of the restriction pin 102 with respect to the cylinder body 82 is greater than the axial length T2 of the gap 204. Is also set larger (T1> T2). As described above, by setting the axial length T1 of the support portion to be larger than the axial length T2 of the gap 204 (T1> T2), a desired support strength of the regulation pin 102 can be ensured.

  Furthermore, in the present embodiment, by forming the reduced diameter portion including the first groove portion 202a, the second groove portion 202b, and the groove portion 212 on the outer surface of the restriction pins 102, 102a, the restriction pins 102, 102a are interposed via the gap 204. Can be separated from the inner peripheral wall 83 of the cylinder body 82. In this case, it is not necessary to process the inner peripheral wall 83 of the cylinder body 82, and the manufacturing cost can be reduced.

  In the present embodiment, the electric brake device 16 is capable of preventing the deformation of the inner peripheral wall 83 (piston sliding surface) of the cylinder body 82 by suppressing the transmission of the load from the regulation pin 102 to the cylinder body 82. Is obtained. Examples of the vehicle include a four-wheel drive vehicle (4WD), a front wheel drive vehicle (FF), and a rear wheel drive vehicle (FR).

Next, in the assembly of the restriction pin to the cylinder body 82, the point of eliminating the assembly direction of the restriction pin to prevent erroneous assembly will be described in detail below with reference to FIGS.
FIG. 7A shows a first example of prevention of erroneous assembly of the regulation pin, a partially omitted enlarged vertical sectional view in a state where the regulation pin is assembled to the cylinder body, and FIG. FIG. 8A is a front view of the restriction pin shown in FIG. 7A, and FIG. 8A shows a second example of prevention of incorrect attachment of the restriction pin, and is partially omitted in a state where the restriction pin is assembled to the cylinder body. FIG. 8 (b) is a longitudinal sectional view, FIG. 8 (b) is a front view of the restriction pin shown in FIG. 8 (a), and FIG. 9 (a) shows a third example of prevention of incorrect assembly of the restriction pin. FIG. 9B is a partially omitted enlarged vertical sectional view showing a state in which the restriction pin is assembled. FIG. 9B is a front view of the restriction pin shown in FIG.

  Except for the case where the cylindrical regulation pin 102b shown in FIG. 6 (c) is used, for example, when the regulation pins 102 and 102a as shown in FIG. 4 (c) and FIG. 5 (c) are used, the regulation pin Since the outer surface shape on the upper side of 102 and 102a is different from the outer surface shape on the lower side (in FIG. 4C), the separation distance from the upper end surface of the restriction pin 102 to the first groove 202a and the first surface from the lower end surface 2), the assembling direction of the restricting pins 102 and 102a is determined, and there is a possibility that an erroneous assembling that erroneously attaches the restricting pins 102 and 102a from the opposite direction may occur.

Therefore, in the present invention, such erroneous assembly can be avoided as follows.
In the first example, as shown in FIG. 7B, the entire length along the axial direction is formed relatively short, and the outer surface shape on the upper side (separation from one end surface along the axial direction to the first groove 302a). The regulation pin 300 is used in which the distance D1) and the outer shape on the lower side (the separation distance D2 from the other end surface along the axial direction to the second groove 302b) are symmetrical (D1 = D2). In this case, as shown in FIG. 7A, the restriction pin 300 is inserted into the upper fixing hole 207 and the lower locking hole 208 of the cylinder body 82 formed in a direction orthogonal to the axial direction of the cylinder body 82. After the insertion and fixing, the regulation pin 300 is prevented from coming off by the connecting leg portion 85a provided on the lower surface of the second reservoir 84 and extending beyond the normal length. FIG. 7A shows a state in which the upper end portion of the restriction pin 300 and the connecting leg portion 85a are in contact with each other (clearance is zero), but the present invention is not limited to this. A clearance may be provided between the upper end portion of 300 and the connecting leg portion 85a.

  In addition, the length of the connecting leg portion 85a of the second reservoir 84 is set so as to extend by an amount corresponding to a reduction in the overall length of the regulation pin 300 with respect to the normal length. The reservoir port 92b into which the connecting leg 85a of the second reservoir 84 is inserted is also processed to be a deep hole corresponding to the length of the connecting leg 85a.

  As described above, in the first example, the relatively short regulating pin 300 having the upper and lower outer surface shapes symmetrically formed is used, and the head of the regulating pin 300 is extended to the second reservoir. By preventing the connection by the connecting leg portion 85a of 84, the direction of assembling of the regulation pin 300 is lost, and erroneous assembly can be prevented.

  In the second example, as shown in FIG. 8B, the overall length along the axial direction is formed to be relatively long, and the upper outer surface shape (from one end surface along the axial direction to the first tapered portion 312a). , And a regulation pin 310 formed symmetrically (D1 = D2) with the outer surface shape on the lower side (the separation distance D2 from the other end surface along the axial direction to the second tapered portion 312b). . In this case, as shown in FIG. 8A, the thickness of the boss portion 314 protruding from the outer peripheral surface of the cylinder body 82 is increased, and the depth of the locking hole 208 formed in the boss portion 314 is increased. The dimension E1 is increased. The increased depth dimension E1 of the locking hole 208 is set to be substantially equal to the thickness dimension E2 of the upper side of the cylinder body 82 in which the upper side fixing hole 207 is formed (E1≈E2). ).

  As described above, in the second example, the relatively long restriction pin 310 having the upper side and the lower side formed symmetrically is used, and the lower part of the restriction pin 310 is inserted and fixed. By setting the depth dimension E1 to be larger than the normal case so as to be substantially equal to the thickness dimension E2 on the upper side of the cylinder body 82 (E1≈E2), the directionality of assembly of the regulation pin 310 It is possible to prevent erroneous assembly.

  The first example and the second example are used together to extend the connecting leg portion 85a of the second reservoir 84 by a predetermined length, and the depth of the locking hole 208 formed in the boss portion 314 of the cylinder body 82. The length dimension E1 may be increased by a predetermined length.

  In the third example, the separation distance from the upper end surface to the groove portion and the separation distance from the lower end surface to the groove portion are different. The outer surface shape of the upper side and the lower side of the regulation pin is made symmetric.

  For example, as shown in FIG. 4C, the separation distance from the upper end surface to the first groove portion 202a is different from the separation distance from the lower end surface to the second groove portion 202b, and the upper side shape and the lower side shape are asymmetric. With respect to the restriction pin 102, an annular third groove portion 202c is newly formed with respect to the separation portion from the upper end surface to the first groove portion 202a, and also to the separation portion from the lower end surface to the second groove portion 202b. A fourth groove 202d is additionally formed.

  As a result, as shown in FIG. 9 (b), the restriction pin 320 used in the newly added third example is formed of the second groove 202c and the first groove 202a in order from the upper end surface downward. Two groove portions are continuously formed, and two groove portions including the second groove portion 202b and the fourth groove portion 202d are continuously formed upward from the lower end surface.

  In this case, in the regulation pin 320 used in the third example, as shown in FIG. 9B, the separation distance from the upper end surface to the first groove 202a and the separation from the lower end surface to the fourth groove 202d (additional machining). The distance is set to be equal, and the distance from the upper end surface to the third groove 202c (additional machining) is set to be equal to the distance from the lower end surface to the second groove 202b.

  As described above, in the third example, the groove shape is newly added to the restriction pin 102 having an asymmetric shape on the upper side and the lower side, thereby making the outer surface shape on the upper side and the lower side symmetrical. be able to. In addition, for example, the first to fourth groove portions 202a to 202d are continuously formed at a time with respect to a normal restriction pin made of a cylindrical body, and the upper and lower outer surface shapes are symmetrical. The pin 320 may be formed.

16 Electric brake device 32FR, 32RL, 32RR, 32FL Wheel cylinder 34 Master cylinder (external)
72 Electric motor
76 Cylinder mechanism (cylinder)
82 Cylinder body 83 Inner wall (piston sliding surface)
84 Second reservoir (pressing member)
88b First slave piston (piston)
98b First hydraulic pressure chamber (output hydraulic pressure chamber)
102, 102a, 300, 310, 320 Restriction pin (regulation means)
202a, 202b, 212 groove (reduced diameter portion)
204 Gap 206 Restriction part 214 Annular taper surface (expanded part)

Claims (8)

An output hydraulic pressure chamber connected to the wheel cylinder; a piston that moves forward to generate hydraulic pressure in the output hydraulic pressure chamber; a cylinder that houses the piston in a cylinder body; and a driving force transmitted to the piston. An electric brake device comprising: a motor that drives the piston forward by this, and a regulating means that regulates the backward movement of the piston when hydraulic pressure acts on the output hydraulic pressure chamber from outside,
The restricting means comprises a restricting pin inserted and fixed to the cylinder in a direction orthogonal to the axial direction of the cylinder body,
An electric brake device characterized in that a gap is formed between an inner peripheral wall of the cylinder body and an outer surface of the restriction pin.   The electric brake device according to claim 1, wherein the restriction pin is fixed through the cylinder body.   The axial length of the support portion of the restriction pin supported by the cylinder body in the insertion direction of the restriction pin is set to be larger than the axial length of the gap. The electric brake device described.   An enlarged diameter portion is formed by enlarging an inner peripheral wall of the cylinder body on which the restriction pin is supported, and the gap is formed between the enlarged diameter portion and an outer surface of the restriction pin. Item 4. The electric brake device according to any one of Items 1 to 3.   A diameter-reduced portion is formed by reducing the outer diameter of the restriction pin at a portion corresponding to the inner peripheral wall of the cylinder body, and the gap is formed between the reduced-diameter portion and the inner peripheral wall of the cylinder body. The electric brake device according to any one of claims 1 to 4, wherein:   6. The electric brake device according to claim 1, wherein a shape on one end side along the axial direction of the restriction pin and a shape on the other end side are formed symmetrically. 6.   The electric brake device according to any one of claims 1 to 6, further comprising a restricting portion that restricts contact between a center portion of the restricting pin and the piston.   The electric brake device according to any one of claims 1 to 7, further comprising a pressing member that presses a head of the restriction pin.

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